JP2008101755A - Belt type continuously variable transmission - Google Patents

Abstract

A belt-type continuously variable transmission capable of suppressing an increase in driving loss of an oil pump is provided.
A belt type continuously variable transmission (1-1) is opened in a direction in which hydraulic oil is supplied to a primary pulley (50), a secondary pulley, a belt (110), a primary hydraulic chamber (55), and a primary hydraulic chamber (55); The hydraulic oil supply / discharge valve 70 that rotates integrally with the primary pulley 50, the hydraulic oil supply / discharge valve 70 is forcibly opened, and the hydraulic oil supply / discharge is forced by the actuator 80 that rotates integrally with the primary pulley 50 and the actuator 80. When the valve 70 is opened, the hydraulic oil is supplied to the primary hydraulic chamber 55 or the hydraulic oil is discharged from the primary hydraulic chamber 55 to control the transmission ratio, and the hydraulic oil temperature. An oil temperature sensor for detecting T. The actuator 80 forcibly opens each hydraulic oil supply / discharge valve 70 in accordance with the detected input rotational speed Nin.
[Selection] Figure 2

Description

  The present invention relates to a belt type continuously variable transmission.

  In general, a vehicle has a transmission on the output side of the drive source in order to transmit a driving force from an internal combustion engine or an electric motor that is a drive source, that is, an output torque, to the road surface under an optimal condition according to the traveling state of the vehicle. Is provided. The transmission includes a continuously variable transmission that controls the gear ratio steplessly (continuously) and a stepped transmission that controls the gear ratio stepwise (discontinuously). Here, the continuously variable transmission has two pulleys, namely, a primary pulley to which driving force from a driving source is transmitted, a secondary pulley that changes and outputs output torque transmitted to the primary pulley, and a transmission to the primary pulley. There is a belt-type continuously variable transmission that includes a belt that transmits the generated driving force to a secondary pulley. The primary pulley and the secondary pulley are two pulley shafts arranged in parallel, a primary pulley shaft and a secondary pulley shaft, and two movable sheaves (primary movable sheave, secondary secondary) that slide in the axial direction on each pulley shaft, respectively. Two fixed sheaves (primary fixed sheave and secondary fixed sheave) that face the two movable sheaves in the axial direction and that form a V-shaped groove between the movable sheave and the belt It is constituted by a clamping pressure generating hydraulic chamber for generating a belt clamping pressure. The belt is wound around a V-shaped groove formed in each of the primary pulley and the secondary pulley.

  In the belt type continuously variable transmission, each movable sheave slides on each pulley shaft in the axial direction by each clamping pressure generating hydraulic chamber, and the V-shaped groove formed in each of the primary pulley and the secondary pulley. Change the width. As a result, the contact radius between the belt, the primary pulley and the secondary pulley is changed steplessly, and the gear ratio is changed steplessly. That is, the output torque from the drive source is changed steplessly.

  For example, as shown in Patent Document 1, the clamping pressure generating hydraulic chamber presses the movable sheave toward the fixed sheave by the hydraulic pressure of the clamping pressure generating hydraulic chamber to generate belt clamping pressure on the belt. Here, in the belt type continuously variable transmission, there is a case where the movement of the movable sheave in the axial direction with respect to the fixed sheave is restricted, that is, the position of the movable sheave with respect to the fixed sheave in the axial direction is constant, and the gear ratio is fixed. In the conventional belt-type continuously variable transmission as shown in Patent Document 1 above, it is necessary to maintain the hydraulic pressure in the clamping pressure generating hydraulic chamber at a predetermined hydraulic pressure in order to keep the position of the movable sheave in the axial direction with respect to the fixed sheave constant. There is.

JP 2001-323978 A

  Therefore, in the conventional belt-type continuously variable transmission, it is necessary to supply hydraulic oil to the clamping pressure generating hydraulic chamber not only when the gear ratio is changed but also when the gear ratio is fixed. For this reason, it is necessary to operate the oil pump provided in the hydraulic oil supply / discharge control device. In addition, the hydraulic fluid is supplied from the hydraulic fluid supply / discharge control device to the clamping pressure generating hydraulic chamber by rotating a stationary member such as a case and a stationary member such as a pulley shaft of the belt-type continuously variable transmission. This is performed by an oil passage formed in the movable member. Therefore, in order to supply the hydraulic oil to the clamping pressure generating hydraulic chamber even when the speed ratio is fixed, there is a possibility that the hydraulic oil leaks from the sliding portion between the stationary member and the movable member.

  Therefore, the present invention has been made in view of the above, and an object of the present invention is to provide a belt type continuously variable transmission that can suppress an increase in driving loss of an oil pump.

  In order to solve the above-described problems and achieve the object, in the present invention, two pulleys, a belt wound around each pulley and transmitting a driving force from a driving source, and each pulley are formed by hydraulic pressure. A clamping pressure generating hydraulic chamber that generates a belt clamping pressure with respect to the belt, and one of the clamping pressure generating hydraulic chambers that opens in the direction of supplying hydraulic oil to one clamping pressure generating hydraulic chamber, and one pulley The hydraulic oil supply / discharge valve is forcibly opened by sliding the piston in one of the sliding directions with respect to the drive hydraulic chamber by the hydraulic oil supply / discharge valve rotating integrally and the hydraulic pressure of the drive hydraulic chamber. When the hydraulic oil supply / discharge valve is forcibly opened by the actuator that rotates integrally with the pulley, hydraulic oil is supplied to one hydraulic pressure generating hydraulic chamber or hydraulic oil is supplied from one hydraulic pressure generating hydraulic chamber Discharge Hydraulic oil supply / discharge control means for controlling the transmission ratio by this, and rotation speed detection means for detecting the input rotation speed of the pulley to which the driving force from the drive source is input among the pulleys. The hydraulic oil supply / discharge valve is forcibly opened according to the input rotational speed.

  According to the present invention, in the belt-type continuously variable transmission, the actuator maintains the opened state of the hydraulic oil supply / discharge valve when the detected input rotational speed is equal to or higher than the operation guaranteed rotational speed. .

  According to the present invention, when changing the gear ratio, the hydraulic oil is supplied to one clamping pressure generating hydraulic chamber via the hydraulic oil supply / discharge valve forcibly opened by the actuator, or one of the clamping ratios is changed. The hydraulic oil is discharged from the pressure generating hydraulic chamber. On the other hand, when the gear ratio is fixed (constant), the hydraulic oil supply / discharge valve is not forcibly opened by the actuator, that is, the hydraulic oil supply / discharge valve is kept closed, and one of the clamping pressures is generated. Do not supply hydraulic oil to the hydraulic chamber. As a result, the hydraulic oil supply / discharge valve is closed, discharge of hydraulic oil from one clamping pressure generating hydraulic chamber is prohibited, and the hydraulic fluid is held in one clamping pressure generating hydraulic chamber. Therefore, even if the position of the movable sheave in the axial direction with respect to the fixed sheave is about to change, the position of the movable sheave in the axial direction with respect to the fixed sheave can be kept constant by changing the hydraulic pressure in one of the clamping pressure generating hydraulic chambers. it can. Accordingly, in order to maintain the position of the movable sheave in the axial direction with respect to the fixed sheave, it is not necessary to supply hydraulic oil to the one clamping pressure generating hydraulic chamber from the outside of the one clamping pressure generating hydraulic chamber. The hydraulic oil can be prevented from leaking from the sliding portion between the movable member and the movable member. Therefore, an increase in the driving loss of the oil pump can be suppressed.

  Here, since the hydraulic oil supply / discharge valve and the actuator rotate integrally with one pulley, a centrifugal force acts. The centrifugal force acting on the hydraulic oil supply / discharge valve and the actuator increases as the rotational speed of one pulley increases. In addition, since hydraulic oil is supplied to the drive hydraulic chamber of the actuator, centrifugal hydraulic pressure due to centrifugal force is generated in the drive hydraulic chamber. The centrifugal hydraulic pressure generated in the drive hydraulic chamber increases because the centrifugal force increases as the rotational speed of one pulley increases. Therefore, when the rotational speed of one pulley is high, that is, when the input rotational speed is high, the centrifugal force and the centrifugal hydraulic pressure increase, so that the reliability of the operation of the actuator and the opening / closing operation of the hydraulic oil supply / discharge valve decreases. As a result, the forcible opening and closing of the hydraulic oil supply / discharge valve cannot be performed reliably, and the reliability of the shifting operation may be reduced.

  However, according to the present invention, the actuator forcibly opens the hydraulic oil supply / discharge valve and maintains the valve open state when the detected input rotational speed is equal to or higher than the operation guaranteed rotational speed. In other words, even when the gear ratio is fixed, the hydraulic oil supply / discharge valve is forcibly opened in accordance with the detected input rotational speed, and the hydraulic oil supply / discharge valve is maintained open. Supply hydraulic fluid to one clamping pressure generating hydraulic chamber or discharge hydraulic fluid from one clamping pressure generating hydraulic chamber via a hydraulic oil supply / discharge valve forcibly opened by an actuator. Thus, the gear ratio is controlled, and here, the gear ratio constant control for maintaining the gear ratio constant is performed. As a result, when the reliability of the operation of the actuator and the opening / closing operation of the hydraulic oil supply / discharge valve is reduced, the actuator opens the hydraulic oil supply / discharge valve regardless of whether the transmission ratio is changed or the transmission ratio is fixed. The hydraulic oil supply / discharge control means supplies the hydraulic oil to one clamping pressure generating hydraulic chamber or controls the gear ratio by discharging the hydraulic oil from one clamping pressure generating hydraulic chamber. The fall of property can be suppressed.

  In the present invention, the belt-type continuously variable transmission further includes oil temperature detecting means for detecting the oil temperature of the hydraulic oil, and the guaranteed operation speed is changed according to the detected oil temperature. Features.

  Here, the viscosity of the hydraulic oil decreases as the oil temperature increases. Further, when the temperature of the hydraulic oil rises, the temperature of the actuator rises. Therefore, it is provided between the piston and a support member that supports the piston slidably in the sliding direction with respect to the drive hydraulic chamber. The sliding resistance of the piston seal member decreases. Therefore, the actuator slides the piston in one of the sliding directions with respect to the drive hydraulic chamber by the hydraulic pressure of the drive hydraulic chamber, and forcibly opens the hydraulic oil supply / discharge valve. Accordingly, that is, the viscosity of the hydraulic oil and the sliding resistance of the piston seal member change, and the reliability of operation changes. The reliability of the operation of the actuator is improved as the temperature of the hydraulic oil increases.

  According to the present invention, the operation guaranteed rotation speed for maintaining the hydraulic oil supply / discharge valve in the open state is changed according to the detected oil temperature, for example, the operation guaranteed rotation speed is increased as the detected oil temperature rises. To do. In other words, when the reliability of the operation of the actuator does not decrease, the period during which the gear ratio is fixed can be lengthened by increasing the operation guaranteed rotation speed and closing the hydraulic oil supply / discharge valve. Therefore, it is possible to further suppress an increase in driving loss of the oil pump. In addition, when the reliability of the operation of the actuator is reduced, the operation guarantee rotation speed is reduced, and the period for fixing the gear ratio is lengthened by performing constant gear ratio control with the hydraulic oil supply / discharge valve opened. can do. Accordingly, it is possible to further suppress a decrease in the reliability of the speed change operation.

  According to the present invention, in the belt-type continuously variable transmission, the actuator maintains the opened state of the hydraulic oil supply / discharge valve when the detected input rotational speed is equal to or less than the shock reduction rotational speed. .

  In the present invention, the belt-type continuously variable transmission further includes torque detecting means for detecting an input torque of a pulley to which a driving force from a driving source is input, and the actuator is detected. When the input torque is equal to or less than the shock reduction torque, the hydraulic oil supply / discharge valve is maintained in an open state.

  Here, when shifting from the gear ratio change state to the gear ratio fixed state by closing the hydraulic oil supply / discharge valve, or from the gear ratio fixed state by shifting the hydraulic oil supply / discharge valve to the closed state. In the case of shifting to the ratio change state, there is a possibility that a step is generated in the change of the gear ratio. In particular, if a vehicle equipped with a belt-type continuously variable transmission has a low input rotational speed such as a creeping state or a low-speed traveling state, a belt-type continuously variable transmission will be installed if a step occurs in the change in gear ratio. There is a risk that drivability will deteriorate due to transmission of a shock at the time of shifting to the vehicle.

  However, in the present invention, the actuator maintains the open state of the hydraulic oil supply / discharge valve when the detected input rotational speed is equal to or lower than the shock reducing rotational speed or when the detected input torque is equal to or lower than the shock reduced torque. . Therefore, the hydraulic oil supply / discharge valve control means supplies the hydraulic oil to one clamping pressure generating hydraulic chamber or supplies the hydraulic oil from one clamping pressure generating hydraulic chamber regardless of the change of the transmission gear ratio or the fixed transmission gear ratio. Since the gear ratio is controlled by discharging, the gear ratio can be continuously changed. Thereby, deterioration of drivability can be suppressed. In addition, when the detected input rotational speed is equal to or less than the shock reducing rotational speed or the detected input torque is equal to or less than the shock reducing torque, the input torque is small. Since the belt clamping pressure is low, an increase in oil pump drive loss can be suppressed.

  The belt-type continuously variable transmission according to the present invention can hold the hydraulic oil in one clamping pressure generating hydraulic chamber, and thus has an effect of suppressing an increase in driving loss of the oil pump. Further, since the hydraulic oil supply / discharge valve is forcibly opened by the actuator according to the detected input rotational speed, there is an effect that the reliability of the shift operation can be improved.

  Hereinafter, the present invention will be described in detail with reference to the drawings. The present invention is not limited to the following examples. In addition, constituent elements in the following embodiments include those that can be easily assumed by those skilled in the art or that are substantially the same. Here, an internal combustion engine (gasoline engine, diesel engine, LPG engine, etc.) is used as a drive source for generating a drive force transmitted to the belt type continuously variable transmission in the following embodiment, but the invention is not limited to this. Alternatively, an electric motor such as a motor may be used as a drive source. In the following embodiment, one pulley is a primary pulley and the other pulley is a secondary pulley, but one pulley may be a secondary pulley and the other pulley may be a primary pulley.

  FIG. 1 is a skeleton diagram of a belt type continuously variable transmission according to the present invention. FIG. 2 is a cross-sectional view of the main part of the primary pulley when the transmission gear ratio is fixed (valve closed state). 3A and 3B are diagrams illustrating the torque cam. FIG. 4 is a diagram illustrating a configuration example of the hydraulic oil supply / discharge control device.

  As shown in FIG. 1, a transaxle 20 that is a stationary component is disposed on the output side of the internal combustion engine 10 that is a drive source. The transaxle 20 includes a transaxle housing 21, a transaxle case 22 attached to the transaxle housing 21, and a transaxle rear cover 23 attached to the transaxle case 22.

  A torque converter 30 is housed inside the transaxle housing 21. On the other hand, inside the case constituted by the transaxle case 22 and the transaxle rear cover 23, a primary pulley 50 and a secondary pulley 60 which are two pulleys constituting the belt type continuously variable transmission 1-1 according to the first embodiment. The primary hydraulic chamber 55, which is one clamping pressure generating hydraulic chamber, the secondary hydraulic chamber 64, the hydraulic oil supply / discharge valve 70, the actuator 80, and the belt 110 are housed. Reference numeral 40 denotes a forward / reverse switching mechanism, 90 denotes a final reduction gear that transmits the driving force of the internal combustion engine 10 to the wheels 120, 100 denotes a power transmission path, 130 denotes a hydraulic oil supply / discharge control device, and 140 denotes an ECU (Engine Control Unit). , 150 is a rotational speed sensor.

  As shown in FIG. 1, the torque converter 30 as a starting mechanism increases the driving force from the driving source, that is, the output torque from the internal combustion engine 10, or transmits it directly to the belt type continuously variable transmission 1-1. is there. The torque converter 30 includes at least a pump (pump impeller) 31, a turbine (turbine impeller) 32, a stator 33, a lockup clutch 34, and a damper device 35.

  The pump 31 is attached to a hollow shaft 36 that can rotate around the same axis as the crankshaft 11 of the internal combustion engine 10. That is, the pump 31 can rotate about the same axis as the crankshaft 11 together with the hollow shaft 36. The pump 31 is connected to the front cover 37. The front cover 37 is connected to the crankshaft 11 via the drive plate 12 of the internal combustion engine 10.

  The turbine 32 is disposed so as to face the pump 31. The turbine 32 is disposed inside the hollow shaft 36 and is attached to an input shaft 38 that can rotate around the same axis as the crankshaft 11. That is, the turbine 32 can rotate about the same axis as the crankshaft 11 together with the input shaft 38.

  A stator 33 is disposed between the pump 31 and the turbine 32 via a one-way clutch 39. The one-way clutch 39 is fixed to the transaxle housing 21. A lockup clutch 34 is disposed between the turbine 32 and the front cover 37, and the lockup clutch 34 is connected to an input shaft 38 via a damper device 35. The casing formed by the pump 31 and the front cover 37 is a hydraulic oil supply portion, and the hydraulic fluid is supplied as the hydraulic fluid from the hydraulic oil supply / discharge control device 130 that supplies the hydraulic oil to the hydraulic oil supply portion. Yes.

  Here, the operation of the torque converter 30 will be described. The output torque from the internal combustion engine 10 is transmitted from the crankshaft 11 to the front cover 37 via the drive plate 12. When the lock-up clutch 34 is released by the damper device 35, the output torque from the internal combustion engine 10 transmitted to the front cover 37 is transmitted to the pump 31 and circulates between the pump 31 and the turbine 32. It is transmitted to the turbine 32 via oil. The output torque from the internal combustion engine 10 transmitted to the turbine 32 is transmitted to the input shaft 38. That is, the torque converter 30 increases the output torque from the internal combustion engine 10 via the input shaft 38 and transmits it to the belt type continuously variable transmission 1-1. In the above, the stator 33 can change the flow of hydraulic fluid circulating between the pump 31 and the turbine 32 to obtain a predetermined torque characteristic.

  On the other hand, when the lock-up clutch 34 is locked (engaged with the front cover 37) by the damper device 35, the output torque from the internal combustion engine 10 transmitted to the front cover 37 is directly not via hydraulic oil. It is transmitted to the input shaft 38. That is, the torque converter 30 transmits the output torque from the internal combustion engine 10 to the belt type continuously variable transmission 1-1 as it is via the input shaft 38.

  As shown in FIG. 1, the forward / reverse switching mechanism 40 transmits the output torque from the internal combustion engine 10 transmitted via the torque converter 30 to the primary pulley 50 of the belt type continuously variable transmission 1-1. . The forward / reverse switching mechanism 40 includes at least a planetary gear device 41, a forward clutch 42, and a reverse brake 43.

  The planetary gear device 41 includes a sun gear 44, a pinion 45, and a ring gear 46.

  The sun gear 44 is spline-fitted to a connecting member (not shown). The connecting member is splined to the primary pulley shaft 51 of the primary pulley 50. Accordingly, the output torque from the internal combustion engine 10 transmitted to the sun gear 44 is transmitted to the primary pulley shaft 51.

  The pinion 45 meshes with the sun gear 44, and a plurality of (for example, three) pinions 45 are arranged around it. Each pinion 45 is held by a switching carrier 47 that is supported around the sun gear 44 so as to be able to revolve integrally. The switching carrier 47 is connected to the reverse brake 43 at its outer peripheral end.

  The ring gear 46 meshes with each pinion 45 held by the switching carrier 47 and is connected to the input shaft 38 of the torque converter 30 via the forward clutch 42.

  The forward clutch 42 is ON / OFF controlled by supplying hydraulic oil from the hydraulic oil supply / discharge control device 130 to a hollow portion (not shown) of the input shaft 38 that is a hydraulic oil supply portion. When the forward clutch 42 is OFF, the output torque from the internal combustion engine 10 transmitted to the input shaft 38 is transmitted to the ring gear 46. On the other hand, when the forward clutch 42 is ON, the output torque from the internal combustion engine 10 transmitted to the input shaft 38 is directly transmitted to the sun gear 44 without the ring gear 46, the sun gear 44, and the pinions 45 rotating relative to each other.

  The reverse brake 43 is ON / OFF controlled by supplying hydraulic oil from a hydraulic oil supply / discharge control device 130 to a brake piston (not shown) which is a hydraulic oil supply portion. When the reverse brake 43 is ON, the switching carrier 47 is fixed to the transaxle case 22 so that each pinion 45 cannot revolve around the sun gear 44. When the reverse brake 43 is OFF, the switching carrier 47 is released, and each pinion 45 can revolve around the sun gear 44.

  The primary pulley 50 of the belt-type continuously variable transmission 1-1 is one pulley, and the output torque from the internal combustion engine 10 transmitted via the forward / reverse switching mechanism 40 is transmitted to the secondary pulley 60 by the belt 110. Is. As shown in FIGS. 1 and 2, the primary pulley 50 includes a primary pulley shaft 51, a primary fixed sheave 52, a primary movable sheave 53, a primary partition wall 54, a primary hydraulic chamber 55, and a cover member 56. Has been.

  As shown in FIG. 2, the primary pulley shaft 51 is rotatably supported by pulley bearings 111 and 112. Further, the primary pulley shaft 51 is formed with a supply / discharge side main passage 51a and a drive side main passage 51b that are opened only at both ends in the axial direction. Here, the pulley bearing 112 is fixed by being sandwiched between a step portion of the transaxle rear cover 23 and a stopper plate (not shown) fixed to the transaxle rear cover 23.

  The supply / discharge-side main passage 51a constitutes a part of a hydraulic oil supply / discharge path for supplying hydraulic oil to the primary hydraulic chamber 55 that is one clamping pressure generating hydraulic chamber and for discharging the hydraulic oil from the primary hydraulic chamber 55. Is. The supply / discharge-side main passage 51a is formed on the primary fixed sheave side and communicates with an oil passage R7 (described later) of the hydraulic oil supply / discharge control device 130. In the supply / discharge side main passage 51a, hydraulic oil supplied from the hydraulic oil supply / discharge control device 130 to the primary hydraulic chamber 55 flows in, and hydraulic oil discharged from the primary hydraulic chamber 55 flows in. Accordingly, the supply / discharge-side main passage 51a allows the hydraulic oil supplied or discharged between the hydraulic oil supply / discharge control device 130 and the primary hydraulic chamber 55 to pass therethrough. The supply / discharge-side main passage 51a communicates with the shaft-side communication passage 51c in the vicinity of the tip.

  The shaft side communication path 51c constitutes a part of the hydraulic oil supply / discharge path. The shaft side communication passage 51c communicates with the space portion T1 by one end portion communicating with the supply / discharge side main passage 51a and the other end portion opening to the outer peripheral surface of the primary pulley shaft 51. In the first embodiment, the shaft side communication passage 51c is formed at a plurality of locations (for example, three locations) at equal intervals on the circumference.

  The space T1 constitutes a part of the hydraulic oil supply / discharge path. The space portion T <b> 1 is formed between the primary movable sheave 53 and the primary pulley shaft 51. That is, the space T1 is formed between the inner peripheral surface of the primary movable sheave 53, that is, the surface that slides in the axial direction with respect to the primary pulley shaft 51 of the primary movable sheave 53 and the outer peripheral surface of the primary pulley shaft 51. Has been. The space portion T1 has a cylindrical shape, and the radially inner end (the lower end in the figure) communicates with each of the axial communication passages 51c, and the other end in the axial direction (the left end in the figure). It communicates with the space T2.

  The space T2 constitutes a part of the hydraulic oil supply / discharge path. The space portion T <b> 2 is formed between the primary partition wall 54, the primary movable sheave 53, and the primary pulley shaft 51. That is, the space T2 includes an inner peripheral surface (a radially inner surface of a portion where the hydraulic oil supply / discharge valve 70 is formed) and an outer peripheral surface of the primary movable sheave 53 (the outer periphery of the primary movable sheave 53). It is formed between the outer peripheral surface of the primary pulley shaft 51 and the outer peripheral surface of the other side (left side in the figure) in the axial direction of the primary hydraulic chamber seal member S1 described later. The space portion T2 has a ring shape, and the radially inner end portion (the lower end portion in the figure) communicates with the space portion T1, and the radially outer end portion communicates with the partition wall side communication passage 54b of the primary partition wall 54. Communicate. That is, the supply / discharge side main passage 51a communicates with the partition wall side communication passage 54b via the shaft side communication passages 51c and the space portions T1 and T2.

  The drive-side main passage 51 b supplies hydraulic oil to a later-described drive hydraulic chamber 81 of the actuator 80 and discharges the hydraulic oil from the drive hydraulic chamber 81. The drive side main passage 51b is formed on the side opposite to the primary fixed sheave side and communicates with an oil passage R8 (described later) of the hydraulic oil supply / discharge control device 130. In the drive side main passage 51b, hydraulic oil supplied from the hydraulic oil supply / discharge control device 130 to the drive hydraulic chamber 81 flows in, and hydraulic oil discharged from the drive hydraulic chamber 81 flows in. Therefore, the hydraulic fluid supplied or discharged between the hydraulic oil supply / discharge control device 130 and the drive hydraulic chamber 81 passes through the drive-side main passage 51b. Further, the drive-side main passage 51b communicates with the shaft-side communication passage 51d in the vicinity of the tip.

  The shaft side communication passage 51d communicates with the space portion T3 by having one end portion communicating with the drive side main passage 51b and the other end portion opening to the outer peripheral surface of the primary pulley shaft 51. In the first embodiment, the shaft side communication passage 51d is formed at a plurality of locations (for example, three locations) at equal intervals on the circumference.

  The space portion T3 is formed between the primary partition wall 54 and the primary pulley shaft 51. That is, the space portion T <b> 3 is formed between the inner peripheral surface (innermost peripheral surface) of the primary partition wall 54 and the outer peripheral surface of the primary pulley shaft 51. The space T3 has a ring shape, and the radially inner side (lower end portion in the figure) communicates with each shaft side communication passage 51d, and the radially outer side (upper end portion in the figure) communicates with the partition wall side communication passage 54e. is doing. That is, the drive side main passage 51b communicates with the partition wall side communication passage 54e via each shaft side communication passage 51d and the space portion T3. Note that a communication portion seal member such as a seal ring may be provided between the inner peripheral surface of the primary partition wall 54 and the outer peripheral surface of the primary pulley shaft 51 with the space T3 interposed therebetween.

  As shown in FIG. 2, the primary fixed sheave 52 is provided to rotate integrally with the primary pulley shaft 51 at a position facing the primary movable sheave 53. Here, the primary fixed sheave 52 is formed as an annular portion that protrudes radially outward from the outer periphery of the primary pulley shaft 51. That is, in the first embodiment, the primary fixed sheave 52 is integrally formed on the outer periphery of the primary pulley shaft 51.

  As shown in FIG. 2, the primary movable sheave 53 includes a cylindrical portion 53a and an annular portion 53b. The cylindrical portion 53 a is formed around the same rotational axis as the primary pulley shaft 51. The annular portion 53b is formed so as to protrude radially outward from the end portion of the cylindrical portion 53a on the primary fixed sheave side. The primary movable sheave 53 is axially connected to the primary pulley shaft 51 by spline-fitting a spline 53c formed on the inner peripheral surface of the cylindrical portion 53a and a spline 51e formed on the outer peripheral surface of the primary pulley shaft 51. It is slidably supported on. Between the primary fixed sheave 52 and the primary movable sheave 53, that is, between the surface of the primary fixed sheave 52 that faces the primary movable sheave 53 and the surface of the primary movable sheave 53 that faces the primary fixed sheave 52. Primary grooves 110a are formed. A space between the spline 53c and the spline 51e is also included in the space T1. Further, a notch 53e is formed at the other end (right end in the figure) of the primary movable sheave 53 in the axial direction. Therefore, even if the other end portion in the axial direction of the primary movable sheave 53 slides to the other in the axial direction with respect to the primary pulley shaft 51, even if it contacts or is close to the primary partition wall 54, Communication between the space T1 and the space T2 is maintained.

  The primary partition wall 54 is a member in which the hydraulic oil supply / discharge valve 70 is disposed and the drive hydraulic chamber 81 of the primary pulley 50 that is one pulley. As shown in FIG. 2, the primary partition wall 54 is an annular member, and is arranged around the same rotational axis as the primary pulley shaft 51. The primary partition 54 is disposed so as to face the primary fixed sheave 52 in the axial direction with the primary movable sheave 53 interposed therebetween. The primary partition wall 54 is provided so as to rotate integrally with the primary pulley shaft 51 by spline fitting with the primary pulley shaft 51.

  The primary partition wall 54 is formed with a valve arrangement passage 54a extending in the axial direction. The valve arrangement passage 54a constitutes a part of the hydraulic oil supply / discharge path. One end portion (right end portion in the figure) of the valve arrangement passage 54a communicates with the primary hydraulic chamber 55, and the other end portion (left end portion in the figure) is closed inside the primary partition wall 54, so that the partition wall side communication is established. It communicates with the passage 54b. The valve arrangement passage 54 a is formed with an annular valve seat surface 72 that is closed by a valve body 71 (described later) of the hydraulic oil supply / discharge valve 70. Here, the valve seat surface 72 is formed at one end of the valve arrangement passage 54a. The valve arrangement passage 54a is formed at a plurality of locations (for example, three locations) at equal intervals on the circumference. A hydraulic oil supply / discharge valve 70 is arranged in each valve arrangement passage 54a.

  The partition wall side communication passage 54b constitutes a part of the hydraulic oil supply / discharge path. The partition wall side communication passage 54b has one end portion (end portion in the radial direction in the figure) communicating with the valve arrangement passage 54a, and the other end portion (in the radial direction in the drawing) on the inner peripheral surface of the primary partition wall 54. Open and communicate with the space T2. In the first embodiment, the valve arrangement passage 54a and the partition wall side communication passage 54b are formed at a plurality of locations (for example, three locations) at equal intervals on the circumference as shown in FIG. Accordingly, the supply / discharge side main passage 51a communicates with the primary hydraulic chamber 55 via the shaft side communication passages 51c, the space portions T1 and T2, the partition wall side communication passages 54b, and the valve arrangement passages 54a. That is, in the first embodiment, the hydraulic oil supply / discharge path is configured by the supply / discharge side main passage 51a, the shaft side communication passages 51c, the spaces T1 and T2, the partition wall side communication passages 54b, and the valve arrangement passages 54a. In the first embodiment, the partition wall side communication passage 54b is formed such that the radially inner end extends in the other direction (the left side of the figure) in the axial direction.

  The primary partition wall 54 is formed with a sliding support hole 54c on the same axis as each valve arrangement passage 54a. Each sliding support hole 54c has one end portion (right end portion in the figure) communicating with the valve arrangement passage 54a and the other end portion (left end portion in the figure) circumferentially on the outer peripheral surface of the primary partition wall 54. Are opened in a notch 54d formed continuously. In the first embodiment, the other end portion of each sliding support hole 54c is opened to a surface facing one side surface (right side surface in the figure) in the axial direction of a pressure receiving member 82a of a piston 82 described later of the actuator 80. ing.

  The partition wall side communication passage 54e has one end portion (an end portion on the radially outer side in the figure) opened to the cutout portion 54d, and the other end portion (the inner side in the radial direction in the figure) is the inner peripheral surface (the outermost surface) of the primary partition wall 54. It opens to the inner peripheral surface) and communicates with the space T3. In the first embodiment, the other end of the partition wall side communication passage 54e is opened to a surface constituting the drive hydraulic chamber 81 in the outer peripheral surface of the primary partition wall 54 constituting the notch 54d. In the first embodiment, the partition wall side communication passage 54e is formed at a plurality of locations (for example, three locations) at equal intervals on the circumference. Accordingly, the drive-side main passage 51b communicates with the notch portion 54d, that is, the drive hydraulic chamber 81 via each shaft-side communication passage 51d, the space T3, and the partition wall-side communication passage 54e.

  The primary hydraulic chamber 55 is one clamping pressure generating hydraulic chamber, and as shown in FIG. 2, by pressing the primary movable sheave 53 toward the primary fixed sheave side, the primary pulley 50, that is, the V-shaped primary groove 110a. A belt clamping pressure is generated with respect to the belt 110 wound around the belt. The primary hydraulic chamber 55 is a space formed by the primary movable sheave 53 and the primary partition wall 54. Here, between the protrusion 53d of the primary movable sheave 53 and the primary partition wall 54 and between the cylindrical portion 53a of the primary movable sheave 53 and the primary partition wall 54, for example, a primary hydraulic chamber seal member S1 such as a seal ring is provided. Each is provided. In other words, the space formed by the primary movable sheave 53 constituting the primary hydraulic chamber 55 and the primary partition 54 is sealed by the primary hydraulic chamber seal member S1.

  The primary hydraulic chamber 55 is supplied with hydraulic fluid from the hydraulic fluid supply / discharge control device 130 that has flowed into the supply / discharge side main passage 51 a of the primary pulley shaft 51. The primary hydraulic chamber 55 slides the primary movable sheave 53 in the axial direction by the pressure of the hydraulic oil supplied from the hydraulic oil supply / discharge control device 130, that is, the hydraulic pressure P1 of the primary hydraulic chamber 55, and makes the primary movable sheave 53 primary. The fixed sheave 52 is approached or separated. Thus, the primary hydraulic chamber 55 generates a belt clamping pressure with respect to the belt 110 by the hydraulic pressure P1 of the primary hydraulic chamber 55, and changes the position of the primary movable sheave 53 in the axial direction with respect to the primary fixed sheave 52. Accordingly, the primary hydraulic chamber 55 mainly changes the gear ratio of the belt type continuously variable transmission 1-1.

  The cover member 56 is a member that constitutes the drive hydraulic chamber 81. The cover member 56 has a ring shape and is disposed between the primary partition wall 54 and the pulley bearing 112, that is, in the notch 54d. The cover member 56 has a radially inner end in contact with the outer peripheral surface of the primary partition wall 54 and a radially outer end in contact with the pressure receiving member 82a of the piston 82 via the piston seal member S2. The cover member 56 is formed with a circumferentially continuous seal surface at the radially inner end and the inner peripheral surface of the primary partition wall 54. Here, in Example 1, the sealing surface is formed in the axial direction.

  The secondary pulley 60 of the belt type continuously variable transmission 1-1 is the other pulley, and the output torque from the internal combustion engine 10 transmitted to the primary pulley 50 by the belt 110 is used as the final pulley of the belt type continuously variable transmission 1-1. This is transmitted to the speed reducer 90. As shown in FIG. 1, the secondary pulley 60 includes a secondary pulley shaft 61, a secondary fixed sheave 62, a secondary movable sheave 63, a secondary hydraulic chamber 64, a secondary partition wall 65, and a torque cam 66. Reference numeral 69 denotes a parking brake gear.

  The secondary pulley shaft 61 is rotatably supported by pulley bearings 113 and 114. The secondary pulley shaft 61 has a hydraulic oil passage (not shown) inside, and hydraulic oil supplied from the hydraulic oil supply / discharge control device 130 to the secondary hydraulic chamber 64 flows into the hydraulic oil passage.

  Secondary fixed sheave 62 is provided to rotate integrally with secondary pulley shaft 61 at a position facing secondary movable sheave 63. Here, the secondary fixed sheave 62 is formed as an annular portion that protrudes radially outward from the outer periphery of the secondary pulley shaft 61. That is, in the first embodiment, the secondary fixed sheave 62 is integrally formed on the outer periphery of the secondary pulley shaft 61.

  The secondary movable sheave 63 has a spline (not shown) formed on the inner peripheral surface of the secondary movable sheave 63 and a spline (not shown) formed on the outer peripheral surface of the secondary pulley shaft 61. It is slidably supported on. Between the secondary fixed sheave 62 and the secondary movable sheave 63, that is, between the surface of the secondary fixed sheave 62 that faces the secondary movable sheave 63 and the surface of the secondary movable sheave 63 that faces the secondary fixed sheave 62. Secondary groove 110b is formed.

  The secondary hydraulic chamber 64 is the other clamping pressure generating hydraulic chamber, and as shown in FIG. 1, by pressing the secondary movable sheave 63 toward the secondary fixed sheave side, the secondary pulley 60, that is, the V-shaped secondary groove 110b. A belt clamping pressure is generated with respect to the belt 110 wound around the belt. The secondary hydraulic chamber 64 is a space formed by a secondary pulley shaft 61, a secondary movable sheave 63, and a disk-shaped secondary partition wall 65 fixed to the secondary pulley shaft 61. The secondary movable sheave 63 is formed with an annular protrusion 63 a that protrudes in one axial direction, that is, protrudes toward the final reduction gear 90. On the other hand, the secondary partition wall 65 is formed with an annular projecting portion 65a projecting in the other axial direction, that is, projecting to the secondary movable sheave 63 side. Here, a seal member (not shown) such as a seal ring is provided between the protrusion 63a and the protrusion 65a. That is, the space formed by the secondary movable sheave 63 and the secondary partition wall 65 constituting the secondary hydraulic chamber 64 is sealed by a secondary hydraulic chamber seal member (not shown).

  The hydraulic oil from the hydraulic oil supply / discharge control device 130 that has flowed into the hydraulic oil passage (not shown) of the secondary pulley shaft 61 is supplied to the secondary hydraulic chamber 64 via a hydraulic fluid supply hole (not shown). The hydraulic fluid is supplied to the secondary hydraulic chamber 64, and the secondary movable sheave 63 is slid in the axial direction by the hydraulic oil pressure supplied from the hydraulic oil supply / discharge control device 130, that is, the hydraulic pressure of the secondary hydraulic chamber 64. The sheave 63 is moved toward or away from the secondary fixed sheave 62. Thus, the secondary hydraulic chamber 64 generates a belt clamping pressure with respect to the belt 110 by the hydraulic pressure of the secondary hydraulic chamber 64, and maintains a constant contact radius of the belt 110 with respect to the primary pulley 50 and the secondary pulley 60.

  As shown in FIG. 3A, the torque cam 66 includes a mountain-shaped first engagement portion 63 b provided in an annular shape on the secondary movable sheave 63 of the secondary pulley 60, and the first engagement portion 63 b and the secondary pulley shaft 61. A plurality of disk-shaped discs disposed between the first engagement portion 63b and the second engagement portion 67a. The transmission member 68 is configured.

  The intermediate member 67 is formed integrally with the secondary partition wall 65 or is fixed to the secondary partition wall 65, and can rotate relative to the secondary pulley shaft 61 and the secondary movable sheave 63 on the secondary pulley shaft 61 by the pulley bearing 113 and the bearing 115. It is supported by. The intermediate member 67 is fixed to the input shaft 101 of the power transmission path 100 by, for example, spline fitting. That is, the output torque from the internal combustion engine 10 transmitted to the secondary pulley 60 is transmitted to the power transmission path 100 via the intermediate member 67.

  Here, the operation of the torque cam 66 will be described. When the output torque from the internal combustion engine 10 is transmitted to the primary pulley 50 and the primary pulley 50 rotates, the secondary pulley 60 rotates via the belt 110. At this time, since the secondary movable sheave 63 of the secondary pulley 60 rotates together with the secondary fixed sheave 62, the secondary pulley shaft 61, and the pulley bearing 113, relative rotation occurs between the secondary movable sheave 63 and the intermediate member 67. . Then, as shown in FIG. 3A, the first engagement portion 63b and the second engagement portion 67a are brought close to each other by the plurality of transmission members 68, as shown in FIG. The portion 63b and the second engaging portion 67a are changed to a separated state. As a result, the torque cam 66 generates a belt clamping pressure with respect to the belt 110 in the secondary pulley 60.

  That is, the secondary pulley 60 includes a torque cam 66 as a means for generating a belt clamping pressure with respect to the belt 110 in addition to the secondary hydraulic chamber 64 that is a clamping pressure generating hydraulic chamber. The torque cam 66 mainly generates belt clamping pressure, and the secondary hydraulic chamber 64 generates a shortage of belt clamping pressure generated by the torque cam 66. The secondary hydraulic chamber 64 may be the only means for generating the belt clamping pressure with respect to the belt 110 in the secondary pulley 60.

  The hydraulic oil supply / discharge valve 70 is a valve that opens in a direction to supply hydraulic oil to the primary hydraulic chamber 55 that is one clamping pressure generating hydraulic chamber. The hydraulic oil supply / discharge valve 70 is forcibly opened by the actuator 80 when hydraulic oil is supplied to the primary hydraulic chamber 55 which is one clamping pressure generating hydraulic chamber and when the hydraulic oil is discharged from the primary hydraulic chamber 55. It is something to be made. As shown in FIGS. 2, 5, and 7, the hydraulic oil supply / discharge valve 70 is connected to the primary hydraulic chamber 55 from the outside of the primary hydraulic chamber 55 that is one clamping pressure generating hydraulic chamber, that is, from the outside of the primary pulley 50. The hydraulic oil is supplied, the hydraulic oil is discharged from the primary hydraulic chamber 55 to the outside of the primary pulley 50, and the hydraulic oil in the primary hydraulic chamber 55 is retained. In the first embodiment, the hydraulic oil supply / discharge valve 70 is disposed in each valve arrangement passage 54a formed in the primary partition wall 54 of the primary pulley 50, which is one pulley (the hydraulic oil supply / discharge valve 70 is A plurality of places (for example, three places) are formed at equal intervals on the circumference). That is, each hydraulic oil supply / discharge valve 70 rotates integrally with the primary pulley 50 that is one pulley.

  Each hydraulic oil supply / discharge valve 70 is a ball type check valve, and includes a valve body 71, a valve seat surface 72, a valve body holding member 73, a valve body elastic member 74, and a snap ring 75. ing. Each valve element 71 has a spherical shape, is disposed closer to the primary hydraulic chamber than the valve seat surface 72, and has a diameter larger than the inner diameter of the valve seat surface 72. The valve seat surface 72 has a tapered shape that inclines radially outward as it goes toward the primary fixed sheave side (from the other end of the valve disposition passage 54a to one end). When the valve body 71 contacts the valve seat surface 72, the communication between the valve arrangement passage 54a and the primary hydraulic chamber 55 is shut off, and each hydraulic oil supply / discharge valve 70 is closed. Further, when the valve element 71 is separated from the valve seat surface 72, the valve arrangement passage 54a and the primary hydraulic chamber 55 are communicated with each other, and each hydraulic oil supply / discharge valve 70 is opened. That is, each hydraulic oil supply / discharge valve 70 opens in the valve opening direction and closes in the valve closing direction.

  The valve body holding member 73 is disposed at a position facing the valve seat surface 72 with the valve body 71 interposed therebetween. The valve body holding member 73 has an annular shape and is supported on the outer peripheral surface of the primary partition wall 54 on the primary hydraulic chamber side so as to be slidable in the axial direction. The valve body holding member 73 holds each valve body 71 by always contacting the valve body 71 of each hydraulic oil supply / discharge valve 70 by the valve closing biasing force generated by the valve body elastic member 74. Here, on the surface of the primary partition wall 54 facing the valve body holding member 73, each valve body 71 is in contact with each valve seat surface 72, and between the valve body holding member 73 and the primary partition wall 54. A recess 54f that is continuous in the circumferential direction is formed so that a gap is formed in the outer periphery.

  The valve body elastic member 74 is a valve body valve closing direction pressing force generating means. The valve body elastic member 74 is, for example, a disc spring, a snap ring 75 inserted and fixed to the outer peripheral surface of the primary partition wall 54 on the primary hydraulic chamber side via each valve body 71 and the valve body holding member 73, and a valve seat. It arrange | positions in the state urged | biased between the surfaces 72. FIG. Accordingly, the valve body elastic member 74 generates a valve closing biasing force, and the valve closing biasing force is an elastic member pressing force in a direction in which the valve body 71 contacts the valve seat surface 72. It acts on each valve body 71 as a pressing force. As a result, each valve element 71 is pressed against each valve seat surface 72, and each hydraulic oil supply / discharge valve 70 functions as a check valve. Accordingly, each hydraulic oil supply / discharge valve 70 can be opened in the direction of supplying hydraulic oil to the primary hydraulic chamber 55, which is one clamping pressure generating hydraulic chamber, that is, in the valve opening direction.

  The actuator 80 forcibly opens each hydraulic oil supply / discharge valve 70. The actuator 80 forcibly opens each hydraulic oil supply / discharge valve 70. The actuator 80 includes a drive hydraulic chamber 81 and a piston 82.

  The drive hydraulic chamber 81 is supplied with hydraulic oil, and controls the on / off valves of the hydraulic oil supply / discharge valves 70 by the pressure of the supplied hydraulic oil, that is, the hydraulic pressure P2 of the drive hydraulic chamber 81. is there. The drive hydraulic chamber 81 is formed between the piston 82, the primary partition wall 54, and the cover member 56 in the notch 54d. The drive hydraulic chamber 81 is a ring-shaped space, and hydraulic fluid is supplied from the hydraulic fluid supply / discharge control device 130 via the drive-side main passage 51b. Accordingly, a piston valve opening direction pressing force is applied to the piston 82 by the hydraulic pressure P <b> 2 of the drive hydraulic chamber 81.

  The piston 82 slides in one of the sliding directions with respect to the drive hydraulic chamber 81 by the hydraulic pressure P2 of the drive hydraulic chamber 81, that is, in one of the axial directions (right direction in the figure), thereby supplying each hydraulic oil. The discharge valve 70 is forcibly opened. The piston 82 includes a pressure receiving member 82a and a pressing member 82b.

  The pressure receiving member 82a is slidably supported with respect to the drive hydraulic chamber 81 by a primary partition wall 54 and a guide member 56 which are support members in a sliding direction, that is, an axial direction. The pressure receiving member 82a receives the hydraulic pressure P2 of the drive hydraulic chamber 81. Since the pressure receiving member 82a is formed in a ring shape, the pressure receiving area, which is the area where the pressure receiving member 82a receives the hydraulic pressure P2 of the drive hydraulic chamber 81, can be increased. Thereby, even if the hydraulic pressure P2 of the drive hydraulic chamber 81, that is, the pressure of the hydraulic fluid supplied to the drive hydraulic chamber 81 is low, each hydraulic oil supply / discharge valve 70 can be forcibly opened. Therefore, it is possible to suppress an increase in driving loss of an oil pump 132, which will be described later, of the hydraulic oil supply / discharge control device 130. The pressure receiving member 82a is slid in one of the axial directions, that is, one of the sliding directions with respect to the driving hydraulic chamber 81, that is, in the valve opening direction, by the piston valve opening direction pressing force acting by the hydraulic pressure P2 of the driving hydraulic chamber 81. Move.

  Here, a piston seal member S2 such as an O-ring made of rubber, for example, is provided between the primary partition wall 54 and the guide member 56, which are support members, and the pressure receiving member 82a. In other words, in the notch 54d, the space formed by the primary partition 54, the guide member 56, and the pressure receiving member 82a constituting the drive hydraulic chamber 81 is sealed by the piston seal member S2.

  The pressing member 82 b is disposed between the pressure receiving member 82 a and the valve body 71 of each hydraulic oil supply / discharge valve 70. Each pressing member 82b is inserted into each sliding support hole 54c of the primary partition wall 54, and is supported so as to be slidable in the axial direction with respect to each sliding support hole 54c. That is, each pressing member 82b is supported to be slidable in the axial direction with respect to the primary pulley 50 which is one pulley. Each pressing member 82 b has one end portion (the right end portion in the figure) opposed to the valve body 71 of each hydraulic oil supply / discharge valve 70, and can contact each valve body 71. Each pressing member 82b can be in contact with the pressure receiving member 82a with the other end (the left end in the figure) facing the pressure receiving member 82a. Accordingly, each pressing member 82b can slide in the axial direction with respect to the primary pulley 50 while being in contact with each valve body 71 and the pressure receiving member 82a. Thereby, an axial force, for example, a piston valve opening direction pressing force acting on the pressure receiving member 82a can be transmitted between the actuator 80 and each hydraulic oil supply / discharge valve 70. That is, the pressure member 82b slides in the same direction as the pressure receiving member 82a when the pressure receiving member 82a comes into contact with the pressure receiving member 82a due to the hydraulic pressure P2 of the drive hydraulic chamber 81 sliding in one of the axial directions. . Note that the actuator 80 generates a piston closing direction pressing force for causing the piston 82 sliding in one of the sliding directions to slide in the other in the sliding direction by the hydraulic pressure P2 of the drive hydraulic chamber 81. Valve direction pressing force generation means may be provided separately. In this case, it is not necessary to slide the piston 82 in the other of the sliding directions by the valve closing direction pressing force applied to the valve body 71 by the valve closing biasing force generated by the valve body elastic member 74.

  Here, when each hydraulic oil supply / discharge valve 70 is opened, the valve element 71 is pushed in the valve opening direction, which is a pressing force acting on the valve element 71 in the direction away from the valve seat surface 72, that is, in the valve opening direction. The pressure exceeds the valve body closing direction pressing force which is the pressing force acting on the valve body 71 in the direction in which the valve body 71 contacts the valve seat surface 72, that is, the valve closing direction. It is done by leaving. Accordingly, each hydraulic oil supply / discharge valve 70 is opened when hydraulic oil is supplied to the primary hydraulic chamber 55 and when hydraulic oil is discharged from the primary hydraulic chamber 55.

  In the first embodiment, each hydraulic oil supply / discharge valve 70 is an actuator regardless of whether hydraulic oil is supplied to the primary hydraulic chamber 55 that is one clamping pressure generating hydraulic chamber or when hydraulic oil is discharged from the primary hydraulic chamber 55. 80 is forcibly opened. That is, when the hydraulic oil is discharged from the primary hydraulic chamber 55, the actuator 80 forcibly opens each hydraulic oil supply / discharge valve 70, which is a hydraulic oil discharge valve, and supplies the hydraulic oil to the primary hydraulic chamber 55. At this time, each hydraulic oil supply / discharge valve 70 is forcibly opened.

  First, the actuator 80 applies a piston valve opening direction pressing force to the pressure receiving member 82a of the piston 82 by the hydraulic pressure P2 of the drive hydraulic chamber 81, thereby causing the pressure receiving member 82a to be one of the sliding directions in one of the axial directions. That is, it is slid in the valve opening direction. When the pressure receiving member 82a slides in the valve opening direction, the pressure receiving member 82a and each pressing member 82b come into contact with each other, and each pressing member 82b slides in the valve opening direction together with the pressure receiving member 82a. Then, when each pressing member 82b comes into contact with the valve body 71 of each hydraulic oil supply / discharge valve 70, the valve opening direction pressing force acting on the piston 82 becomes the above valve body opening direction pressing force, and each valve body 71 Act on each. Accordingly, each hydraulic oil supply / discharge valve 70 moves in the valve opening direction with respect to the valve seat surface 72 when the valve element valve opening direction pressing force exceeds the valve element closing direction pressing force. The hydraulic oil supply / discharge valve 70 is forcibly opened. The valve body closing direction pressing force is closed to each valve body 71 by the elastic member pressing force acting on each valve body 71 by the valve closing biasing force generated by the valve body elastic member 74 and the hydraulic pressure P1 of the primary hydraulic chamber 55. Hydraulic oil closing direction pressing force acting in the valve direction.

  Note that the hydraulic oil valve closing direction pressing force acting on the valve body 71 by the hydraulic pressure P1 of the primary hydraulic chamber 55 acts on the valve body 71 as the valve closing direction pressing force as described above. Even if P1 rises, the valve body 71 does not leave the valve seat surface 72. Accordingly, the closed state of each hydraulic oil supply / discharge valve 70 is maintained unless the valve body valve opening direction pressing force acting on the valve body 71 exceeds the valve body valve opening direction pressing force. The hydraulic oil in the primary hydraulic chamber 55 that is a chamber is reliably held in the primary hydraulic chamber 55.

  Accordingly, in order to maintain the position of the primary movable sheave 53 in the axial direction with respect to the primary fixed sheave 52 as in the conventional belt-type continuously variable transmission, one hydraulic pressure generating hydraulic pressure is supplied from the hydraulic oil supply / discharge control device 130. When hydraulic oil is continuously supplied to the primary hydraulic chamber 55, which is a chamber, hydraulic oil having a predetermined pressure exists in the hydraulic oil supply / discharge path from the hydraulic oil supply / discharge control device 130 to the primary hydraulic chamber 55. It becomes. The hydraulic oil supply / discharge path includes a plurality of sliding portions between the stationary member and the movable member, and when the transmission gear ratio is fixed, the hydraulic oil of a predetermined pressure is external to the hydraulic oil supply / discharge path from the sliding portion. There was a risk of leakage. The stationary member is a member that does not rotate, slide, or the like among the members constituting the belt type continuously variable transmission 1-1. For example, a transaxle housing 21, a transaxle case 22, and a transaxle rear cover 23 of the transaxle 20. On the other hand, the movable member is a member that rotates, slides, etc. in the members that constitute the belt type continuously variable transmission 1-1. For example, the primary pulley shaft 51 or the like. Therefore, the sliding portion includes, for example, a portion where the primary pulley shaft 51 rotates with respect to the transaxle housing 21, the transaxle case 22, the transaxle rear cover 23, and the like of the transaxle 20.

  In the belt type continuously variable transmission 1-1 according to the first embodiment, each hydraulic oil supply / discharge valve 70 is disposed between the primary hydraulic chamber 55 and the sliding portion. That is, when each hydraulic oil supply / discharge valve 70 is maintained in the closed state and the hydraulic oil is held in the primary hydraulic chamber 55, the primary hydraulic chamber 55 and each hydraulic oil supply / discharge valve 70 are interposed. There is no sliding portion between the fixed member and the movable member. Thereby, since it can suppress that hydraulic oil leaks from this sliding part, the increase in the power loss of the oil pump 132 of the hydraulic oil supply / discharge control apparatus 130 can be suppressed.

  As shown in FIG. 1, a power transmission path 100 is arranged between the secondary pulley 60 and the final reduction gear 90. The power transmission path 100 includes an input shaft 101 on the same axis as the secondary pulley shaft 61, an intermediate shaft 102 parallel to the input shaft 101, a counter drive pinion 103, a counter driven gear 104, and a final drive pinion 105. It is configured. The input shaft 101 and the counter drive pinion 103 fixed to the input shaft 101 are rotatably held by bearings 118 and 119. The intermediate shaft 102 is rotatably supported by bearings 116 and 117. The counter driven gear 104 is fixed to the intermediate shaft 102 and meshed with the counter drive pinion 103. The final drive pinion 105 is fixed to the intermediate shaft 102.

  The final reduction gear 90 of the belt type continuously variable transmission 1-1 transmits the output torque from the internal combustion engine 10 transmitted through the power transmission path 100 from the wheels 120 and 120 to the road surface. The final reduction gear 90 includes a differential case 91 having a hollow portion, a pinion shaft 92, differential pinions 93 and 94, and side gears 95 and 96.

  The differential case 91 is rotatably supported by bearings 97 and 98. A ring gear 99 is provided on the outer periphery of the differential case 91, and the ring gear 99 is engaged with the final drive pinion 105. The pinion shaft 92 is attached to the hollow portion of the differential case 91. The differential pinions 93 and 94 are rotatably attached to the pinion shaft 92. The side gears 95 and 96 are meshed with both the differential pinions 93 and 94. The side gears 95 and 96 are fixed to the drive shafts 121 and 122, respectively.

  The belt 110 of the belt type continuously variable transmission 1-1 transmits the output torque from the internal combustion engine 10 transmitted through the primary pulley 50 to the secondary pulley 60. As shown in FIG. 1, the belt 110 is wound between a primary groove 110 a for the primary pulley 50 and a secondary groove 110 b for the secondary pulley 60. That is, the belt 110 is wound around the primary pulley 50 and the secondary pulley 60. Further, the belt 110 is an endless belt composed of, for example, a large number of metal pieces and a plurality of steel rings.

  The drive shafts 121 and 122 have side gears 95 and 96 fixed to one end thereof and wheels 120 and 120 attached to the other end thereof.

  The hydraulic oil supply / discharge control device 130 supplies hydraulic oil to a hydraulic oil supply portion that requires supply of hydraulic oil in a vehicle in which the belt type continuously variable transmission 1-1 and the internal combustion engine 10 are mounted. . When each hydraulic oil supply / discharge valve 70 is forcibly opened by the actuator 80, the hydraulic oil supply / discharge control device 130 supplies hydraulic oil to the primary hydraulic chamber 55 which is one clamping pressure generating hydraulic chamber, or primary The gear ratio is controlled by discharging hydraulic oil from the hydraulic chamber 55. In addition, the hydraulic oil supply / discharge control device 130 supplies hydraulic oil to the drive hydraulic chamber 81.

  The hydraulic oil supply / discharge control device 130 is hydraulic oil supply / discharge control means, and supplies hydraulic oil to the primary hydraulic chamber 55, the secondary hydraulic chamber 64, the drive hydraulic chamber 81, etc., as shown in FIG. The transmission ratio of the belt type continuously variable transmission 1-1 is also controlled by controlling the supply flow rate of hydraulic oil and the discharge flow rate of hydraulic oil. In the figure, the hydraulic oil supply portion (excluding the above-described hydraulic oil supply portion and the hydraulic oil supply portion of the internal combustion engine 10 (for example, with movable parts) excluding the primary hydraulic chamber 55, the secondary hydraulic chamber 64, and the drive hydraulic chamber 81 The illustration of a stationary part having a sliding part in between, a movable part or a movable part having a sliding part between stationary parts, a heated part or a driving device driven by oil) is omitted. The hydraulic oil supply / discharge control device 130 includes an oil pan 131, an oil pump 132, a line pressure control device 133, a constant pressure control device 134, a primary hydraulic chamber control device 135, a drive hydraulic chamber control device 136, and a secondary. It is comprised with the control apparatus 137 for hydraulic chambers.

  The oil pump 132 sucks, pressurizes, and discharges the hydraulic oil stored in the oil pan 131. The oil pump 132 is connected to the line pressure control device 133 via the oil passage R1. The hydraulic oil pressurized and discharged by the oil pump 132 is supplied to the line pressure control device 133. That is, the discharge pressure Pout of the oil pump 132 is introduced into the line pressure control device 133. As shown in FIG. 1, the oil pump 132 is disposed between the torque converter 30 and the forward / reverse switching mechanism 40. The oil pump 132 includes a rotor 132a, a hub 132b, and a body 132c. The oil pump 132 is connected to the pump 31 by a rotor 132a via a cylindrical hub 132b. The body 132c is fixed to the transaxle case 22. The hub 132b is spline-fitted to the hollow shaft 36. Therefore, the oil pump 132 can be driven because the output torque from the internal combustion engine 10 is transmitted to the rotor 132a via the pump 31. That is, in the oil pump 132, the discharge amount of the discharged hydraulic oil increases, that is, the discharge pressure Pout increases as the rotational speed of the internal combustion engine 10 increases.

  The line pressure control device 133 adjusts the discharge pressure Pout of the oil pump 132 so that it becomes a predetermined line pressure PL. That is, the line pressure control device 133 adjusts the hydraulic pressure of the oil passage R1, which is the input hydraulic pressure, that is, the discharge pressure Pout, and sets the output hydraulic pressure from the line pressure control device 133 as the line pressure PL. The line pressure control device 133 is connected to a second port 135l of a supply-side flow rate control valve 135c, which will be described later, of the primary hydraulic chamber control device 135 via an oil passage R2, and is constant via an oil passage R2 and a branch oil passage R21. It is connected to the pressure control device 134 and is connected to the secondary hydraulic chamber control device 137 via the oil passage R2 and the branch oil passage R22. Therefore, the line pressure PL adjusted by the line pressure control device 133 is the second port 135l of the supply-side flow rate control valve 135c, the constant pressure control device 134, the drive hydraulic chamber control device 136, and the secondary hydraulic chamber control device 137. To be introduced. The line pressure control device 133 adjusts the line pressure PL in accordance with the output torque of the internal combustion engine 10. The line pressure control device 133 is provided with a solenoid valve (not shown), for example, a linear solenoid valve, which regulates the pressure of the hydraulic oil discharged from the oil pump 132. The line pressure control device 133 is electrically connected to the ECU 140, and the line pressure PL can be regulated by controlling the valve opening degree of the linear solenoid valve by a control signal from the ECU 140.

  The constant pressure control device 134 adjusts the line pressure PL output from the line pressure control device 133 so as to always become a constant pressure. That is, the constant pressure control device 134 adjusts the oil pressure of the oil passage R2 and the branch oil passage R21 that are input oil pressure, that is, the line pressure PL, and sets the output oil pressure from the constant pressure control device 134 to the constant pressure PS. is there. The constant pressure control device 134 is connected to a first port 135e of a supply-side control valve 135a, which will be described later, of the primary hydraulic chamber control device 135 via an oil passage R3, and is connected to the primary hydraulic pressure via an oil passage R3 and a branch oil passage R31. It connects with the 1st port 135h of the discharge side control valve 135b mentioned later of the chamber control apparatus 135, and is connected with the drive hydraulic chamber control apparatus 136 via the oil path R3 and the branch oil path R32. Accordingly, the constant pressure PS regulated by the constant pressure control device 134 is introduced into the first port 135e of the supply side control valve 135a, the first port 135h of the discharge side control valve 135b, and the drive hydraulic chamber control device 136. .

  The primary hydraulic chamber controller 135 controls the supply of hydraulic oil to the primary hydraulic chamber 55 or the discharge of hydraulic oil from the primary hydraulic chamber 55. In the first embodiment, the primary hydraulic chamber control device 135 controls the supply flow rate of the hydraulic oil supplied to the primary hydraulic chamber 55 and the discharge flow rate of the hydraulic oil discharged from the primary hydraulic chamber 55. The primary hydraulic chamber control device 135 includes a supply side control valve 135a, a discharge side control valve 135b, a supply side flow rate control valve 135c, and a discharge side flow rate control valve 135d.

  The supply-side control valve 135a performs supply flow control of the hydraulic oil supplied to the primary hydraulic chamber 55 by the supply-side flow control valve 135c. The supply-side control valve 135a switches communication between the three ports, that is, the first port 135e, the second port 135f, and the third port 135g by ON / OFF. The first port 135e is connected to the constant pressure control device 134 as described above. The second port 135f is connected to a first port 135k, which will be described later, of the supply-side flow rate control valve 135c via an oil passage R4. The second port 135f is connected to a later-described fourth port 135u of the discharge-side flow rate control valve 135d via the oil passage R4 and the branch oil passage R41. The third port 135g is connected to the oil pan 131 via the merging oil passage R51 and the oil passage R5. That is, the third port 135g is released to atmospheric pressure.

  When the supply-side control valve 135a is turned on, the first port 135e and the second port 135f communicate with each other. Accordingly, the constant pressure PS introduced into the supply side control valve 135a is introduced into the first port 135k of the supply side flow control valve 135c (see FIG. 7). That is, the constant pressure PS introduced into the supply side control valve 135a is introduced into a control hydraulic chamber 135o, which will be described later, of the supply side flow control valve 135c communicating with the first port 135k. Further, the constant pressure PS introduced into the supply side control valve 135a is introduced into the fourth port 135u of the discharge side flow control valve 135d (see the figure). On the other hand, when the supply-side control valve 135a is turned off, the second port 135f and the third port 135g communicate with each other. Accordingly, the first port 135k of the supply side flow control valve 135c is released to atmospheric pressure via the supply side control valve 135a (see FIG. 9). That is, the control hydraulic pressure chamber 135o is released to atmospheric pressure through the first port 135k of the supply side flow control valve 135c. Further, the fourth port 135u of the discharge side flow control valve 135d is released to the atmospheric pressure via the supply side control valve 135a (see the same figure). Here, as shown in FIG. 4, supply-side control valve 135 a is electrically connected to ECU 140 and is duty-controlled by a control signal from ECU 140. Accordingly, the supply-side control valve 135a can regulate the control hydraulic chamber 135o of the supply-side flow rate control valve 135c from a constant pressure PS to atmospheric pressure by a control signal from the ECU 140.

  The discharge side control valve 135b performs discharge flow control of the hydraulic oil discharged from the primary hydraulic chamber 55 by the discharge side flow control valve 135d. The discharge side control valve 135b switches communication between the three ports, that is, the first port 135h, the second port 135i, and the third port 135j by ON / OFF. The first port 135h is connected to the constant pressure control device 134 as described above. The second port 135i is connected to a later-described first port 135r of the discharge-side flow rate control valve 135d via the oil passage R6. The second port 135i is connected to a later-described fourth port 135n of the supply-side flow rate control valve 135c via the oil passage R6 and the branch oil passage R61. The third port 135j is connected to the oil pan 131 via the oil path R5. That is, the third port 135j is released to atmospheric pressure.

  When the discharge-side control valve 135b is turned on, the first port 135h and the second port 135i communicate with each other. Accordingly, the constant pressure PS introduced into the discharge side control valve 135b is introduced into the first port 135r of the discharge side flow control valve 135d (see FIG. 9). That is, the constant pressure PS introduced into the discharge side control valve 135b is introduced into a control hydraulic chamber 135v described later of the discharge side flow control valve 135d communicating with the first port 135r. Further, the constant pressure PS introduced into the discharge side control valve 135b is introduced into the fourth port 135n of the supply side flow control valve 135c (see the same figure). On the other hand, when the discharge side control valve 135b is turned off, the second port 135i and the third port 135j communicate with each other. Accordingly, the first port 135r of the discharge side flow control valve 135d is released to atmospheric pressure via the discharge side control valve 135b (see FIG. 7). That is, the control hydraulic chamber 135v is released to the atmospheric pressure via the first port 135r of the discharge side flow control valve 135d. Further, the fourth port 135n of the supply-side flow rate control valve 135c is released to atmospheric pressure via the discharge-side control valve 135b (see the same figure). Here, as shown in FIG. 4, the discharge-side control valve 135 b is electrically connected to the ECU 140 and is duty-controlled by a control signal from the ECU 140. Accordingly, the discharge-side control valve 135b can regulate the control hydraulic chamber 135v of the discharge-side flow control valve 135d from a constant pressure PS to atmospheric pressure by a control signal from the ECU 140.

  The supply-side flow rate control valve 135c controls the supply flow rate of the hydraulic oil supplied to the primary hydraulic chamber 55. The supply-side flow rate control valve 135c includes a first port 135k, a second port 135l, a third port 135m, a fourth port 135n, a control hydraulic chamber 135o, a spool 135p, and a spool elastic member 135q. ing. As described above, the first port 135k is connected to the second port 135f of the supply side control valve 135a. The second port 135l is connected to the line pressure control device 133 as described above. The third port 135m is connected to the primary hydraulic chamber 55 via an oil passage R7. In the first embodiment, the third port 135m includes the oil passage R7 and the hydraulic oil supply / discharge passage (supply / discharge side main passage 51a, each shaft side communication passage 51c, space portions T1, T2, each partition side communication passage 54b, and each valve. The primary hydraulic chamber 55 is connected via the arrangement passage 54a). The fourth port 135n is connected to the second port 135i of the discharge side control valve 135b as described above. In addition, as shown in the figure, between the second port 135f of the supply-side control valve 135a and the first port 135k of the supply-side flow control valve 135c, the line pressure controller 133 and the second of the supply-side flow control valve 135c An orifice, that is, a throttle is provided between the port 135l and the hydraulic oil flowing into the supply-side flow control valve 135c from the supply-side control valve 135a and the hydraulic oil flowing into the supply-side flow control valve 135c from the line pressure control device 133. The pressure or flow rate may be adjusted.

  The control hydraulic chamber 135o communicates with the first port 135k, and the spool valve opening direction pressing force that presses the spool 135p in one direction (upward in the figure) in the direction in which the spool 135p moves due to the hydraulic pressure. Acts on the spool 135p. The spool 135p is movably supported in the primary hydraulic chamber control device 135. The spool 135p communicates with the second port 135l and the third port 135m by moving in one of the moving directions, By moving in the other direction, the communication between the second port 135l and the third port 135m is cut off. The spool elastic member 135q is arranged in a state of being biased between the spool 135p and a member stationary with respect to the spool 135p. Therefore, the spool elastic member 135q generates a spool urging force, and the spool urging force pushes the spool 135p in the other direction (downward in the figure) in the direction in which the spool 135p moves. The pressure is applied to the spool 135p.

  In the supply-side flow rate control valve 135c, the spool valve opening direction pressing force acting on the spool 135p exceeds the spool valve closing direction pressing force, whereby the spool 135p moves in one of the moving directions. Here, the supply-side flow rate control valve 135c increases the degree of communication between the second port 135l and the third port 135m, that is, the second port 135l and the first port 135l as the moving amount of the spool 135p increases in one direction. The flow path cross-sectional area of the flow path communicating with the 3 port 135m increases. That is, the supply-side flow rate control valve 135c has two ports, that is, a second port 135l and a third port 135m, as the spool 135p moves by the hydraulic pressure of the control hydraulic chamber 135o regulated by the supply-side control valve 135a. And the supply flow rate is controlled.

  The discharge side flow control valve 135d controls the discharge flow rate of the hydraulic oil discharged from the primary hydraulic chamber 55. The discharge-side flow rate control valve 135d includes a first port 135r, a second port 135s, a third port 135t, a fourth port 135u, a control hydraulic chamber 135v, a spool 135w, and a spool elastic member 135x. ing. As described above, the first port 135r is connected to the second port 135i of the discharge-side control valve 135b. The second port 135s is connected to the oil pan 131 via the merging oil path R52, the merging oil path R51, and the oil path R5. That is, the second port 135s is released to atmospheric pressure. The third port 135t is connected to the primary hydraulic chamber 55 via a branch oil passage R71 and an oil passage R7. In the first embodiment, the third port 135t includes the branch oil passage R71, the oil passage R7, and the hydraulic oil supply / discharge passage (supply / discharge side main passage 51a, each shaft side communication passage 51c, space T1, T2, each partition wall side. The primary hydraulic chamber 55 is connected via the communication passage 54b and each valve arrangement passage 54a). As described above, the fourth port 135u is connected to the second port 135f of the supply side control valve 135a. As shown in the figure, an orifice, that is, a throttle is provided between the second port 135i of the discharge-side control valve 135b and the first port 135r of the discharge-side flow control valve 135d, and the discharge is made from the discharge-side control valve 135b. The pressure or flow rate of the hydraulic oil flowing into the side flow rate control valve 135d may be adjusted.

  The control hydraulic chamber 135v communicates with the first port 135r, and the spool valve opening direction pressing force that presses the spool 135w in one direction (upward in the figure) in the direction in which the spool 135w moves due to the hydraulic pressure. Is applied to the spool 135w. The spool 135w is movably supported in the primary hydraulic chamber control device 135, and moves in one direction of the movement direction to communicate the second port 135s and the third port 135t. By moving in the other direction, the communication between the second port 135s and the third port 135t is cut off. The spool elastic member 135x is disposed in a state of being biased between the spool 135w and a member stationary with respect to the spool 135w. Therefore, the spool elastic member 135x generates a spool urging force, and the spool urging force pushes the spool 135w in the other direction (downward in the figure) in the direction in which the spool 135w moves. The pressure is applied to the spool 135w.

  The discharge-side flow rate control valve 135d moves the spool 135w in one of the moving directions when the spool valve opening direction pressing force acting on the spool 135w exceeds the spool closing direction pressing force. Here, the discharge-side flow rate control valve 135d has a degree of communication between the second port 135s and the third port 135t, that is, the second port 135s and the first port 135t as the moving amount of the spool 135w increases in one direction. The flow path cross-sectional area of the flow path communicating with the 3 port 135t increases. That is, the discharge-side flow rate control valve 135d has two ports, that is, a second port 135s and a third port 135t, as the spool 135w moves by the hydraulic pressure of the control hydraulic chamber 135v regulated by the discharge-side control valve 135b. Communication and control the discharge flow rate.

  The drive hydraulic chamber control device 136 adjusts the hydraulic pressure P2 of the drive hydraulic chamber 81. As described above, the constant pressure PS is introduced from the constant pressure control device 134 into the drive hydraulic chamber control device 136. Further, the drive hydraulic chamber control device 136 is connected to the drive hydraulic chamber 81 via an oil passage R8. In the first embodiment, the drive hydraulic chamber control device 136 is connected to the drive hydraulic chamber 81 via the oil passage R8 and the drive side main passage 51b. The driving hydraulic chamber control device 136 is provided with ON / OFF (not shown). The drive hydraulic chamber control device 136 is electrically connected to the ECU 140 and controls ON / OFF of the ON / OFF valve by a control signal from the ECU 140. When the drive hydraulic chamber control device 136 is ON-controlled, that is, when the switching valve is turned on, the branch oil passage R32 and the oil passage R8 communicate with each other, and a constant pressure introduced into the drive hydraulic chamber control device 136 is reached. PS is introduced into the drive hydraulic chamber 81, and the hydraulic pressure P2 of the drive hydraulic chamber 81 becomes a constant pressure PS. On the other hand, when the drive hydraulic chamber control device 136 is OFF-controlled, that is, when the ON / OFF valve is turned OFF, the communication between the branch oil path R32 and the oil path R8 is cut off, and the oil path R8 is externally connected. The hydraulic pressure P2 of the drive hydraulic chamber 81 becomes atmospheric pressure. Here, the constant pressure PS is a hydraulic pressure at which each hydraulic oil supply / discharge valve 70 can be opened by the hydraulic pressure P2 of the drive hydraulic chamber 81 at least when the hydraulic pressure P2 of the drive hydraulic chamber 81 becomes the constant pressure PS. That's it.

  The secondary hydraulic chamber control device 137 controls the supply of hydraulic oil to the secondary hydraulic chamber 64 or the discharge of hydraulic oil from the secondary hydraulic chamber 64. As described above, the line pressure PL is introduced into the secondary hydraulic chamber control device 137 from the line pressure control device 133. The secondary hydraulic chamber control device 137 is connected to the secondary hydraulic chamber 64 via an oil passage R9. In the first embodiment, the secondary hydraulic chamber control device 137 is connected to the secondary hydraulic chamber 64 via an oil passage R9, a hydraulic oil passage (not shown) of the secondary pulley shaft 61, and a hydraulic fluid supply hole (not shown). The secondary hydraulic chamber control device 137 includes a flow rate control valve (not shown). The secondary hydraulic chamber control device 137 is electrically connected to the ECU 140, and regulates the introduced line pressure PL controlled by a control signal from the ECU 140.

  As described above, the hydraulic oil supply / discharge control device 130 is connected to an ECU (Engine Control Unit) 140 (not shown) that controls at least the operation of the internal combustion engine 10. Therefore, the hydraulic oil supply / discharge control device 130 controls the primary hydraulic chamber control device 135, the drive hydraulic chamber control device 136, and the secondary hydraulic chamber control device 137 based on the control signal from the ECU 140, thereby 80 forcibly opens each hydraulic oil supply / discharge valve 70, supplies hydraulic oil to the primary hydraulic chamber 55 that is one clamping pressure generating hydraulic chamber, or discharges hydraulic oil from the primary hydraulic chamber 55, and at least the belt It controls the gear ratio of the continuously variable transmission 1-1.

  The rotational speed sensor 150 is rotational speed detection means for detecting an input rotational speed Nin of a pulley to which a driving force from a driving source is input, that is, a primary pulley 50 to which an output torque from the internal combustion engine 10 is input. In the first embodiment, the rotation speed sensor 150 detects the rotation speed of the primary pulley shaft 51 of the primary pulley 50 and sets the rotation speed of the primary pulley shaft 51 as the input rotation speed Nin. The rotation speed sensor 150 is connected to the ECU 140 as shown in FIG. Accordingly, the input rotational speed Nin detected by the rotational speed sensor 150 is output to the ECU 140. The rotation speed detection means is not limited to the rotation speed sensor 150 that uses the rotation speed of the primary pulley shaft 51 as the input rotation speed Nin. For example, the rotation speed detection unit detects the engine rotation speed Ne of the internal combustion engine 10 and detects the engine rotation speed Ne. The input rotational speed Nin may be calculated from the above.

  Next, the operation of the belt type continuously variable transmission 1-1 according to the first embodiment will be described. First, general forward and reverse travel of the vehicle will be described. When the driver selects a forward position by a shift position device (not shown) provided in the vehicle, the ECU 140 turns on the forward clutch 42 and turns off the reverse brake 43 by the hydraulic oil supplied from the hydraulic oil supply / discharge control device 130. The forward / reverse switching mechanism 40 is controlled. As a result, the input shaft 38 and the primary pulley shaft 51 are directly connected. That is, the sun gear 44 and the ring gear 46 of the planetary gear device 41 are directly connected, the primary pulley shaft 51 is rotated in the same direction as the rotation direction of the crankshaft 11 of the internal combustion engine 10, and the output torque from the internal combustion engine 10 is converted to the primary pulley. 50. The output torque from the internal combustion engine 10 transmitted to the primary pulley 50 is transmitted to the secondary pulley 60 via the belt 110 and rotates the secondary pulley shaft 61 of the secondary pulley 60.

  The output torque of the internal combustion engine 10 transmitted to the secondary pulley 60 is transmitted from the intermediate member 67 to the intermediate shaft 102 via the input shaft 101 of the power transmission path 100, the counter drive pinion 103 and the counter driven gear 104, thereby being intermediated. The shaft 102 is rotated. The output torque transmitted to the intermediate shaft 102 is transmitted to the differential case 91 of the final reduction gear 90 via the final drive pinion 105 and the ring gear 99, and the differential case 91 is rotated. The output torque from the internal combustion engine 10 transmitted to the differential case 91 is transmitted to the drive shafts 121 and 122 via the differential pinions 93 and 94 and the side gears 95 and 96, and to the wheels 120 and 120 attached to the ends thereof. The wheels 120 and 120 are rotated with respect to a road surface (not shown), and the vehicle moves forward.

  On the other hand, when the driver selects the reverse position by a shift position device (not shown) provided in the vehicle, the ECU 140 turns off the forward clutch 42 with the hydraulic oil supplied from the hydraulic oil supply / discharge control device 130, and reverse brakes. 43 is turned ON, and the forward / reverse switching mechanism 40 is controlled. As a result, the switching carrier 47 of the planetary gear unit 41 is fixed to the transaxle case 22 and is held by the switching carrier 47 so that each pinion 45 only rotates. Accordingly, the ring gear 46 rotates in the same direction as the input shaft 38, and each pinion 45 meshed with the ring gear 46 also rotates in the same direction as the input shaft 38, and the sun gear 44 meshed with each pinion 45 becomes the input. It rotates in the opposite direction to the shaft 38. That is, the primary pulley shaft 51 connected to the sun gear 44 rotates in the direction opposite to the input shaft 38. As a result, the secondary pulley shaft 61, the input shaft 101, the intermediate shaft 102, the differential case 91, the drive shafts 121, 122, and the like of the secondary pulley 60 rotate in the opposite direction to the case where the driver selects the forward position. Goes backwards.

  Here, the ECU 140 includes a map (for example, an optimum fuel consumption curve based on the engine speed and the throttle opening of the throttle valve, etc.) stored in the storage unit of the ECU 140 and various conditions such as the vehicle speed and the accelerator opening of the driver. ), The gear ratio of the belt-type continuously variable transmission 1-1 is controlled via the hydraulic oil supply / discharge control device 130 so that the operating state of the internal combustion engine 10 is optimized. Here, the control of the gear ratio of the belt-type continuously variable transmission 1-1 includes a change of the gear ratio and a fixed speed change (gear ratio γ steady). The change of the gear ratio and the fixing of the gear ratio are performed by controlling the primary hydraulic chamber control device 135, the drive hydraulic chamber control device 136, and the secondary hydraulic chamber control device 137. FIG. 5 is a diagram illustrating an operation flow of the belt-type continuously variable transmission according to the first embodiment. 6 to 9 are operation explanatory views of the belt-type continuously variable transmission when the gear ratio is changed. FIG. 10 is an operation explanatory diagram of the belt-type continuously variable transmission when the gear ratio is fixed (valve open state). The gear ratio control using the hydraulic oil supply / discharge control device 130 is performed every control cycle.

  As shown in FIG. 5, the ECU 140 first acquires the input rotation speed Nin (step ST101). Here, ECU 140 obtains input rotation speed Nin detected by rotation speed sensor 150.

  Next, ECU 140 determines whether or not the detected input rotation speed Nin is equal to or greater than the operation guaranteed rotation speed N1 (step ST102). That is, the ECU 140 determines whether or not the detected input rotation speed Nin is equal to or higher than the operation guaranteed rotation speed N1. Here, the operation guaranteed rotation speed N1 refers to an input rotation speed that may reduce the reliability of the operation of the actuator 80 and the opening / closing operation of each hydraulic oil supply / discharge valve 70.

  Next, when ECU 140 determines that the detected input rotational speed Nin is less than the operation-guaranteed rotational speed N1 (No in step ST102), ECU 140 determines whether or not the speed ratio is fixed (step ST103). . The ECU 140 performs control to fix the gear ratio, that is, to make the gear ratio steady, when there is no need to change the gear ratio significantly, for example, when the vehicle traveling state is stable. Therefore, here, it is determined whether or not ECU 140 determines to perform control to fix the speed ratio, that is, to keep the speed ratio constant.

  Next, when ECU 140 determines that the gear ratio is fixed (Yes in step ST103), each hydraulic oil supply / discharge valve 70 is closed (step ST104). That is, when the detected input rotation speed Nin is less than the operation guaranteed rotation speed N1, each hydraulic oil supply / discharge valve 70 is closed and the gear ratio is fixed. Here, in the case where each hydraulic oil supply / discharge valve 70 is closed and the transmission gear ratio is fixed, that is, the transmission gear ratio is fixed in the closed valve state without supplying hydraulic oil to the primary hydraulic chamber 55 and this primary hydraulic pressure. The hydraulic oil is not discharged from the chamber 55, and the position of the primary movable sheave 53 in the axial direction with respect to the primary fixed sheave 52 is kept constant, and the movement of the primary movable sheave 53 with respect to the primary fixed sheave 52 is restricted.

  When the transmission gear ratio is fixed in the closed valve state, as shown in FIG. 2, each hydraulic oil supply / discharge valve 70 is closed, and the hydraulic oil is supplied to the primary hydraulic chamber 55 via each hydraulic oil supply / discharge valve 70. Further, the discharge of the hydraulic oil from the primary hydraulic chamber 55 via each hydraulic oil supply / discharge valve 70 is prohibited. Specifically, the ECU 140 controls the drive hydraulic chamber control device 136 to be OFF.

When the drive hydraulic chamber control device 136 is OFF-controlled by the ECU 140, the drive hydraulic chamber 81 is released to atmospheric pressure, and the hydraulic pressure P2 of the drive hydraulic chamber 81 is almost atmospheric pressure P _OFF . Accordingly, the valve body opening direction pressing force does not act on the valve body 71 of each hydraulic oil supply / discharge valve 70, and only the valve body closing direction pressing force by the hydraulic pressure P1 of the valve body elastic member 74 and the primary hydraulic chamber 55 is applied. The valve body 71 moves in the valve closing direction and contacts the valve seat surface 72, and the hydraulic oil supply / discharge valves 70 are closed. Since only the valve body closing direction pressing force acts on the pressure receiving member 82a via each valve body 71 and each pressing member 82b, the piston 82 moves in the other direction of the sliding direction, that is, closes. Slides in the valve direction.

  The supply-side control valve 135a of the primary hydraulic chamber control device 135 is duty-controlled by the ECU 140 to control the supply flow rate of hydraulic oil to the primary hydraulic chamber 55 by the supply-side flow rate control valve 135c. When duty control is performed by the ECU 140, the supply-side control valve 135a maintains OFF as shown in FIG. 4, and the control hydraulic chamber 135o of the supply-side flow rate control valve 135c and the fourth port 135u of the discharge-side flow rate control valve 135d. To atmospheric pressure. Accordingly, since only the spool closing direction pressing force acts on the spool 135p, the supply-side flow rate control valve 135c is maintained in a state where the spool 135p is positioned in the other direction in the moving direction. The third port 135m does not communicate. As a result, the supply-side flow rate control valve 135c remains closed, and the supply flow rate of hydraulic oil to the primary hydraulic chamber 55 becomes zero. As a result, the supply of hydraulic oil to the primary hydraulic chamber 55 via each hydraulic oil supply / discharge valve 70 is prohibited.

  On the other hand, the discharge side control valve 135b of the primary hydraulic chamber control device 135 is duty-controlled by the ECU 140 to control the discharge flow rate of the hydraulic oil from the primary hydraulic chamber 55 by the discharge side flow rate control valve 135d. When duty control is performed by the ECU 140, the discharge-side control valve 135b maintains OFF and releases the fourth port 135n of the supply-side flow control valve 135c and the control hydraulic chamber 135v of the discharge-side flow control valve 135d to atmospheric pressure. Accordingly, since only the spool closing direction pressing force acts on the spool 135w, the discharge-side flow rate control valve 135d is maintained in a state where the spool 135w is positioned in the other direction in the moving direction. The third port 135t does not communicate. As a result, the discharge-side flow rate control valve 135d is kept closed, and the discharge flow rate of hydraulic oil from the primary hydraulic chamber 55 becomes zero. As a result, the discharge of hydraulic oil from the primary hydraulic chamber 55 via each hydraulic oil supply / discharge valve 70 is prohibited.

  As described above, when the gear ratio is fixed in the valve-closed state, the operation in the primary hydraulic chamber 55 is prohibited by prohibiting the supply of the hydraulic oil to the primary hydraulic chamber 55 and the discharge of the hydraulic oil from the primary hydraulic chamber 55. Retain oil. Here, since the belt tension of the belt 110 changes even when the transmission gear ratio is fixed in the valve closed state, the contact radius of the belt 110 in the primary pulley 50 tends to change, and the shaft of the primary movable sheave 53 with respect to the primary fixed sheave 52 is changed. The position in the direction may change. As described above, since the hydraulic oil is held in the primary hydraulic chamber 55, if the position of the primary movable sheave 53 in the axial direction with respect to the primary fixed sheave 52 is changed, the hydraulic pressure of the primary hydraulic chamber 55 is changed. Although P1 changes, the position of the primary movable sheave 53 in the axial direction with respect to the primary fixed sheave 52 is maintained constant. Accordingly, in order to keep the position of the primary movable sheave 53 in the axial direction with respect to the primary fixed sheave 52 constant, it is not necessary to increase the hydraulic pressure P1 of the primary hydraulic chamber 55 by supplying hydraulic oil to the primary hydraulic chamber 55. good. Thereby, when the transmission gear ratio is fixed in the valve-closed state, it is not necessary to drive the oil pump 132 in order to supply the hydraulic oil to the primary hydraulic chamber 55, so that it is possible to suppress an increase in driving loss of the oil pump 132. it can.

  Next, when ECU 140 determines that the gear ratio is not fixed (No in step ST103), the hydraulic oil supply / discharge valve 70 is opened with the hydraulic pressure P2 in the drive hydraulic chamber 81 set to a constant pressure PS (step ST105). ). That is, the ECU 140 forcibly opens each hydraulic oil supply / discharge valve 70 by the actuator 80 when the speed ratio is not fixed, that is, when the speed ratio is changed. Specifically, the ECU 140 controls the drive hydraulic chamber control device 136 to be ON.

  When the drive hydraulic chamber control device 136 is ON-controlled by the ECU 140, the constant pressure PS introduced into the drive hydraulic chamber control device 136 is introduced into the drive hydraulic chamber 81, and the hydraulic pressure P2 of the drive hydraulic chamber 81 is constant pressure PS. It becomes. In the actuator 80, the piston valve opening direction pressing force acting on the piston 82 by the hydraulic pressure P2 of the drive hydraulic chamber 81 is transmitted from the piston 82 to the valve body 71 of each hydraulic oil supply / discharge valve 70, and the piston valve opening direction pressing force is controlled by the valve 80. It is made to act on the valve body 71 of each hydraulic oil supply / discharge valve 70 as the body opening direction pressing force. Here, as described above, when the hydraulic pressure P2 of the drive hydraulic chamber 81 becomes the constant pressure PS, the valve opening direction pressing force opens each hydraulic oil supply / discharge valve 70 by the hydraulic pressure P2 of the drive hydraulic chamber 81. Therefore, the valve body closing direction pressing force is exceeded. Accordingly, as shown in FIGS. 6 and 8, each hydraulic oil supply / discharge valve 70 is opened by moving the valve body 71 in the valve opening direction with respect to the valve seat surface 72 by the actuator 80.

  Next, as shown in FIG. 5, ECU 140 performs gear ratio change control by hydraulic oil supply / discharge control device 130 (step ST106). The gear ratio change control is mainly performed by supplying hydraulic oil from the hydraulic oil supply / discharge control device 130 to the primary hydraulic chamber 55 or from the primary hydraulic chamber 55 to the outside of the primary pulley 50 via the hydraulic oil supply / discharge control device 130. The primary movable sheave 53 slides in the axial direction of the primary pulley shaft 51, and the interval between the primary fixed sheave 52 and the primary movable sheave 53, that is, the width of the primary groove 110a is adjusted. The As a result, the contact radius of the belt 110 in the primary pulley 50 changes, and the speed ratio, which is the ratio between the rotation speed of the primary pulley 50, that is, the input rotation speed Nin, and the rotation speed of the secondary pulley 60, that is, the output rotation speed, is stepless. It is controlled (continuously).

  In the secondary pulley 60, the secondary hydraulic chamber control device 137 is controlled by the ECU 140 to regulate the hydraulic pressure in the secondary hydraulic chamber 64, and the belt 110 is sandwiched between the secondary fixed sheave 62 and the secondary movable sheave 63. The belt clamping pressure is adjusted. Thereby, the belt tension of the belt 110 wound around the primary pulley 50 and the secondary pulley 60 is controlled.

  Here, the transmission ratio change control includes an upshift, that is, a transmission ratio decrease change control that decreases the transmission ratio, and a downshift, that is, a transmission ratio increase change control that increases the transmission ratio. Each will be described below.

  The gear ratio reduction change control is performed by supplying hydraulic oil from the hydraulic oil supply / discharge control device 130 to the primary hydraulic chamber 55 and sliding (moving) the primary movable sheave 53 to the primary fixed sheave side. As shown in FIG. 7, the hydraulic oil is supplied from the hydraulic oil supply / discharge control device 130 to the primary hydraulic chamber 55 via the hydraulic oil supply / discharge valves 70 that are forcibly opened by the actuator 80. Specifically, ECU 140 calculates a reduction gear ratio and a transmission speed, and outputs a control signal for the transmission ratio based on these to hydraulic oil supply / discharge control device 130.

  The supply-side control valve 135a of the primary hydraulic chamber control device 135 is duty-controlled by the ECU 140 to control the supply flow rate of hydraulic oil to the primary hydraulic chamber 55 by the supply-side flow rate control valve 135c. When duty control is performed by the ECU 140, the supply-side control valve 135a is repeatedly turned ON and OFF as shown in FIG. And a predetermined pressure at the time of supply is introduced into the fourth port 135u of the discharge side flow control valve 135d. Here, the predetermined pressure at the time of supply decreases the supply flow rate controlled by controlling the communication between the second port 135l and the third port 135m by the spool valve opening direction pressing force acting on the spool 135p. It is the pressure which can be set as the supply flow rate based on speed. Accordingly, the supply-side flow rate control valve 135c is indicated by an arrow A in FIG. 5 because the spool valve opening direction pressing force based on the control hydraulic pressure of the control hydraulic chamber 135o, that is, the supply predetermined pressure exceeds the spool closing direction pressing force. As described above, the spool 135p moves in one of the movement directions, and the second port 135l and the third port 135m communicate with each other. As a result, the supply-side flow rate control valve 135c is opened, and the supply flow rate of the hydraulic oil to the primary hydraulic chamber 55 becomes a supply flow rate based on the reduction gear ratio and the shift speed.

  On the other hand, the discharge side control valve 135b of the primary hydraulic chamber control device 135 is duty-controlled by the ECU 140 to control the discharge flow rate of the hydraulic oil from the primary hydraulic chamber 55 by the discharge side flow rate control valve 135d. When duty control is performed by the ECU 140, the discharge-side control valve 135b maintains OFF and releases the fourth port 135n of the supply-side flow control valve 135c and the control hydraulic chamber 135v of the discharge-side flow control valve 135d to atmospheric pressure. Accordingly, since only the spool closing direction pressing force acts on the spool 135w, the discharge-side flow rate control valve 135d is maintained in a state where the spool 135w is positioned in the other direction in the moving direction, and the second port 135s and the third port The port 135t does not communicate. As a result, the discharge-side flow rate control valve 135d is kept closed, and the discharge flow rate of hydraulic oil from the primary hydraulic chamber 55 becomes zero.

As described above, each hydraulic oil supply / discharge valve 70 is forcibly opened by the actuator 80. Therefore, hydraulic oil introduced into the supply-side flow control valve 135c at the line pressure PL (when an orifice is provided between the line pressure control device 133 and the second port 135l of the supply-side flow control valve 135c, The hydraulic fluid inserted with the pressure adjusted from the line pressure PL) is controlled by the supply flow rate control valve 135c to the supply flow rate based on the reduction gear ratio and the shift speed, as shown by the arrow B in FIG. Then, it flows into the supply / discharge side main passage 51a of the hydraulic oil supply / discharge path via the oil passage R7. The hydraulic oil that has flowed into the supply / discharge side main passage 51a passes through the supply / discharge side main passage 51a through the shaft-side communication passages 51c, the spaces T1 and T2, the partition wall-side communication passages 54b, and the valve arrangement passages 54a. It is supplied to the chamber 55. That is, when the working oil is supplied to the primary hydraulic chamber 55 which is one of the clamping force generating hydraulic chamber, the supply pressure P _in the hydraulic fluid supplied to the primary hydraulic chamber 55, is identical to the hydraulic fluid discharge valves operated Each hydraulic oil supply / discharge valve 70 which is an oil supply valve may not be opened. Therefore, in order to increase the supply pressure of the hydraulic oil supplied to the primary hydraulic chamber 55, it is possible to suppress an increase in the line pressure PL introduced into the supply-side flow rate control valve 135c by the line pressure control device 133. . The hydraulic oil P <b> 1 in the primary hydraulic chamber 55 is raised by the hydraulic oil supplied via each hydraulic oil supply / discharge valve 70, and the pressing force for pressing the primary movable sheave 53 toward the primary fixed sheave side is increased. Slides toward the primary fixed sheave side in the axial direction. As a result, the contact radius of the belt 110 in the primary pulley 50 increases, the contact radius of the belt 110 in the secondary pulley 60 decreases, the gear ratio is reduced, and the reduction gear ratio is obtained.

  In changing the gear ratio, the hydraulic oil is discharged from the primary hydraulic chamber 55 via the hydraulic oil supply / discharge control device 130, and the primary movable sheave 53 is slid (moved) to the side opposite to the primary fixed sheave side. Done. As shown in FIG. 8, the hydraulic oil is discharged from the primary hydraulic chamber 55 via each hydraulic oil supply / discharge valve 70 that is forcibly opened by the actuator 80. Specifically, ECU 140 calculates an increase gear ratio and a gear shift speed, and outputs a gear ratio control signal based on these to hydraulic oil supply / discharge control device 130.

  The supply-side control valve 135a of the primary hydraulic chamber control device 135 is duty-controlled by the ECU 140 to control the supply flow rate of hydraulic oil to the primary hydraulic chamber 55 by the supply-side flow rate control valve 135c. When duty control is performed by the ECU 140, the supply side control valve 135a maintains OFF as shown in FIG. 9, and the control hydraulic chamber 135o of the supply side flow rate control valve 135c and the fourth port 135u of the discharge side flow rate control valve 135d. To atmospheric pressure. Accordingly, since only the spool closing direction pressing force acts on the spool 135p, the supply-side flow rate control valve 135c is maintained in a state where the spool 135p is positioned in the other direction in the moving direction. The third port 135m does not communicate. As a result, the supply-side flow rate control valve 135c remains closed, and the supply flow rate of hydraulic oil to the primary hydraulic chamber 55 becomes zero.

  On the other hand, the discharge side control valve 135b of the primary hydraulic chamber control device 135 is duty-controlled by the ECU 140 to control the discharge flow rate of the hydraulic oil from the primary hydraulic chamber 55 by the discharge side flow rate control valve 135d. When duty control is performed by the ECU 140, the discharge-side control valve 135b repeats ON and OFF, introduces a predetermined pressure during discharge to the fourth port 135n of the supply-side flow control valve 135c, and controls the discharge-side flow control valve 135d. The control hydraulic pressure of the hydraulic chamber 135v is adjusted to a predetermined pressure at the time of discharge. Here, the predetermined pressure at the time of discharge increases the discharge flow rate controlled by controlling the communication between the second port 135s and the third port 135t by the spool valve opening direction pressing force acting on the spool 135w. It is the pressure that can be the discharge flow rate based on the speed. Accordingly, the discharge-side flow rate control valve 135d is indicated by an arrow C in the figure because the spool opening direction pressing force based on the control hydraulic pressure of the control hydraulic chamber 135v, that is, the predetermined pressure at the time of discharging exceeds the spool closing direction pressing force. As described above, the spool 135w moves in one of the moving directions, and the second port 135s and the third port 135t communicate with each other. As a result, the discharge-side flow rate control valve 135d is opened, and the discharge flow rate of the hydraulic oil from the primary hydraulic chamber 55 becomes a discharge flow rate based on the reduction gear ratio and the shift speed.

  As described above, each hydraulic oil supply / discharge valve 70 is forcibly opened by the actuator 80. Therefore, as shown by the arrow D in FIG. 8, the hydraulic oil in the primary hydraulic chamber 55 flows from the primary hydraulic chamber 55 to the valve arrangement passage 54a of the hydraulic oil supply / discharge passage, each partition side communication passage 54b, and the space portions T1, T2. Then, it flows into the supply / discharge side main passage 51a through each shaft side communication passage 51c. The hydraulic oil in the primary hydraulic chamber 55 that has flowed into the supply / discharge-side main passage 51a flows into the discharge-side flow rate control valve 135d via the oil passage R7 and the branch oil passage R71, and is increased by the discharge-side flow rate control valve 135d. And the discharge flow rate based on the shift speed and discharged to the outside of the oil pan 131, that is, the primary hydraulic chamber 55 via the merged oil passages R52, R51 and the oil passage R5. Accordingly, the hydraulic oil is discharged from the primary hydraulic chamber 55 via each hydraulic oil supply / discharge valve 70, whereby the hydraulic pressure P1 of the primary hydraulic chamber 55 decreases, and the primary movable sheave 53 is pushed toward the primary fixed sheave side. The pressure decreases, and the primary movable sheave 53 slides in the axial direction on the side opposite to the primary fixed sheave side. Thereby, the contact radius of the belt 110 in the primary pulley 50 decreases, the contact radius of the belt 110 in the secondary pulley 60 increases, the transmission ratio is increased, and the increased transmission ratio is obtained.

  Next, when the ECU 140 determines that the detected input rotational speed Nin is equal to or higher than the operation guaranteed rotational speed N1 (No in step ST102), the ECU 140 determines whether each hydraulic oil supply / discharge valve 70 is open. (Step ST107). That is, the ECU 140 determines whether or not each hydraulic oil supply / discharge valve 70 has already been opened when the detected input rotational speed Nin is equal to or higher than the operation guaranteed rotational speed N1.

  Next, when ECU 140 determines that each hydraulic oil supply / discharge valve 70 is not in an open state (No in step ST107), ECU 140 opens each hydraulic oil supply / discharge valve 70 with the hydraulic pressure P2 in drive hydraulic chamber 81 set to a constant pressure PS. (Step ST108). That is, when the detected input rotation speed Nin is equal to or higher than the operation-guaranteed rotation speed N1, the ECU 140 forces each hydraulic oil supply / discharge valve 70 to be forced by the actuator 80 regardless of whether the transmission gear ratio is changed or the transmission gear ratio is fixed. Open the valve. Specifically, the ECU 140 controls the drive hydraulic chamber control device 136 to be ON.

  When the drive hydraulic chamber control device 136 is ON-controlled by the ECU 140, the constant pressure PS introduced into the drive hydraulic chamber control device 136 is introduced into the drive hydraulic chamber 81. In the actuator 80, the piston valve opening direction pressing force acting on the piston 82 by the hydraulic pressure P2 of the drive hydraulic chamber 81 is transmitted from the piston 82 to the valve body 71 of each hydraulic oil supply / discharge valve 70, and the piston valve opening direction pressing force is controlled by the valve 80. It is made to act on the valve body 71 of each hydraulic oil supply / discharge valve 70 as the body opening direction pressing force. Here, as described above, when the hydraulic pressure P2 of the drive hydraulic chamber 81 becomes a constant pressure PS, the hydraulic oil supply / discharge valve 70 is reliably opened by the hydraulic pressure P2 of the drive hydraulic chamber 81. Therefore, the valve body closing direction pressing force is exceeded. Accordingly, as shown in FIGS. 6, 8, and 10, each hydraulic oil supply / discharge valve 70 is opened by moving the valve body 71 in the valve opening direction with respect to the valve seat surface 72 by the actuator 80.

  Next, the ECU 140 determines that each hydraulic oil supply / discharge valve 70 is in the open state (Yes in step ST107), or sets the hydraulic pressure P2 in the drive hydraulic chamber 81 to a constant pressure PS, and each hydraulic oil supply / discharge valve 70. When is opened, it is determined whether or not the gear ratio is fixed (step ST109). Here, it is determined whether or not ECU 140 determines to perform control to fix the gear ratio, that is, to make the gear ratio steady.

  Next, when ECU 140 determines that the gear ratio is fixed (Yes in step ST109), ECU 140 performs constant gear ratio control (step ST110). The speed ratio constant control is, for example, a ratio between an input rotation speed Nin detected by the rotation speed sensor 150 and an output rotation speed Nout detected by a rotation speed detection means (not shown) that detects the rotation speed of the secondary pulley shaft 61. That is, feedback control is performed so that the detected gear ratio becomes a fixed gear ratio when ECU 140 determines to perform control to fix the gear ratio. The constant gear ratio control is mainly performed by supplying hydraulic oil from the hydraulic oil supply / discharge control device 130 to the primary hydraulic chamber 55 or from the primary hydraulic chamber 55 to the outside of the primary pulley 50 via the hydraulic oil supply / discharge control device 130. The operation is performed by discharging the hydraulic oil, and the position of the primary movable sheave 53 in the axial direction with respect to the primary fixed sheave 52 is fixed, and the movement of the primary movable sheave 53 with respect to the primary fixed sheave 52 is restricted.

  As described above, each hydraulic oil supply / discharge valve 70 is forcibly opened by the actuator 80. Accordingly, as shown by an arrow E in FIG. 10, when the detected gear ratio increases from the fixed gear ratio, the ECU 140 causes the hydraulic oil supply / discharge control device 130 to connect the oil path R7 and the oil passage R7. The hydraulic oil is supplied to the primary hydraulic chamber 55 via the hydraulic oil supply / discharge path. When the detected gear ratio decreases below the fixed gear ratio, the ECU 140 causes the hydraulic oil supply / discharge control device 130 to move from the primary hydraulic chamber 55 to the oil path R7, the branch oil path R71, the hydraulic oil supply / discharge path, and the hydraulic oil. The hydraulic oil is discharged via the supply / discharge control device 130. Thereby, the contact radius of the belt 110 in the primary pulley 50 is maintained constant, the contact radius of the belt 110 in the secondary pulley 60 is also maintained constant, and the transmission ratio is fixed.

  When ECU 140 determines that the gear ratio is not fixed (No in step ST109), ECU 140 performs gear ratio change control (step ST106).

  As described above, the actuator 80 forcibly opens each hydraulic oil supply / discharge valve 70 and maintains the open state when the detected input rotation speed Nin is equal to or higher than the operation guaranteed rotation speed N1. That is, even when the gear ratio is fixed, each hydraulic oil supply / discharge valve 70 is forcibly opened according to the detected input rotational speed Nin, and the open state of each hydraulic oil supply / discharge valve 70 is maintained. Then, the hydraulic oil supply / discharge control device 130, which is the hydraulic oil supply / discharge control means, passes through each hydraulic oil supply / discharge valve 70 which is forcibly opened by the actuator 80, so that the primary hydraulic pressure which is one clamping pressure generating hydraulic chamber is provided. Speed ratio constant control is performed to maintain the speed ratio constant by supplying hydraulic oil to the chamber 55 or discharging hydraulic oil from the primary hydraulic chamber 55. As a result, when the reliability of the operation of the actuator 80 and the opening / closing operation of each hydraulic oil supply / discharge valve 70 decreases as the centrifugal force increases or the centrifugal hydraulic pressure generated by the drive hydraulic chamber 81 increases, Regardless of when the gear ratio is fixed, the actuator 80 keeps each hydraulic oil supply / discharge valve 70 open. Accordingly, the hydraulic oil supply / discharge control device 130 supplies hydraulic oil to the primary hydraulic chamber 55 without opening / closing each hydraulic oil supply / discharge valve 70 by the actuator 80 according to the change of the gear ratio and the fixing of the gear ratio. Since the gear ratio is controlled by discharging the hydraulic oil from the hydraulic chamber 55, it is possible to suppress a decrease in the reliability of the speed change operation of the belt type continuously variable transmission 1-1.

  Further, in order to suppress a decrease in the reliability of the operation of the actuator 80, the hydraulic pressure P2 of the drive hydraulic chamber 81 does not always have to be a high hydraulic pressure, and therefore the oil pump 132 of the oil pump 132 accompanying the increase of the hydraulic pressure P2 of the drive hydraulic chamber 81 is not required. Driving loss can be suppressed. Further, since the hydraulic pressure P2 of the drive hydraulic chamber 81 does not always have to be a high hydraulic pressure, an increase in the valve body urging force generated by the valve body elastic member 74 that applies the valve body closing direction pressing force to each valve body 71 is prevented. Can be suppressed. Therefore, the enlargement of the valve body elastic member 74 can be suppressed, and the belt-type continuously variable transmission 1-1 can be reduced in size and cost. Further, since it is not necessary to simplify or provide a mechanism for canceling the centrifugal hydraulic pressure generated by the drive hydraulic chamber 81, it is possible to suppress the drive loss of the oil pump 132 and to reduce the size and cost of the belt type continuously variable transmission 1-1. Can be achieved. Further, when the detected input rotational speed Nin is equal to or higher than the operation guaranteed rotational speed N1, the gear ratio change control by the hydraulic oil supply / discharge control device 130 is often performed. Therefore, even if the detected input rotation speed Nin is equal to or higher than the operation-guaranteed rotation speed N1, each hydraulic oil supply / discharge valve 70 is maintained in the open state, and the constant shift ratio control is performed by the hydraulic oil supply / discharge control device 130, A reduction in fuel consumption due to leakage of hydraulic oil can be suppressed.

  Next, the belt type continuously variable transmission 1-2 according to the second embodiment will be described. FIG. 11 is a diagram illustrating an operation flow of the belt-type continuously variable transmission according to the second embodiment. FIG. 12 is a diagram illustrating the relationship between the oil temperature of the hydraulic oil and the operation guaranteed rotation speed. The belt-type continuously variable transmission 1-2 according to the second embodiment is different from the belt-type continuously variable transmission 1-1 according to the first embodiment in that an oil temperature sensor (not shown) that detects the oil temperature T of the hydraulic oil is used. The operation guaranteed rotation speed N1 is changed in accordance with the detected oil temperature T. The basic configuration of the belt-type continuously variable transmission 1-2 according to the second embodiment is substantially the same as the basic configuration of the belt-type continuously variable transmission 1-1 according to the first embodiment shown in FIGS. Therefore, the same parts will be described by omitting or simplifying them.

  The oil temperature sensor (not shown) is temperature detection means for detecting the oil temperature T of the hydraulic oil, here the hydraulic oil supplied to the drive hydraulic chamber 81. The oil temperature sensor is provided, for example, in the hydraulic oil supply / discharge path, and is connected to the ECU 140. Therefore, the oil temperature T detected by the oil temperature sensor is output to the ECU 140.

  Next, the operation of the belt type continuously variable transmission 1-2 according to the second embodiment will be described. The operation of the belt-type continuously variable transmission 1-2 according to the second embodiment is substantially the same as the operation of the belt-type continuously variable transmission 1-1 according to the first embodiment, and therefore the same parts are omitted or simplified. Will be explained.

  When controlling the gear ratio of the belt type continuously variable transmission 1-2, as shown in FIG. 11, the ECU 140 first acquires the oil temperature T of the hydraulic oil (step ST201). Here, ECU 140 acquires oil temperature T of the hydraulic oil detected by an oil temperature sensor (not shown).

  Next, ECU 140 determines an operation guaranteed rotation speed N1 according to the detected oil temperature T (step ST202). Here, the ECU 140 is, for example, based on the detected oil temperature T and the rotation speed map of the hydraulic oil temperature T and the operation guaranteed rotation speed N1 stored in advance in a storage unit (not shown). To decide. As shown in FIG. 12, the rotation speed map is set so that the operation guaranteed rotation speed N1 determined as the oil temperature T of the hydraulic oil increases is increased. Therefore, the higher the detected oil temperature T, the higher the guaranteed operation speed N1. This is because the viscosity of the hydraulic oil decreases as the hydraulic oil temperature rises, the temperature of the actuator 80 decreases, the sliding resistance of the piston seal member S2 decreases, and the operation reliability of the actuator 80 increases. It is for improving.

  Next, ECU 140 obtains input rotation speed Nin (step ST203). Next, ECU 140 determines whether or not detected input rotational speed Nin is equal to or higher than operation guaranteed rotational speed N1 corresponding to the determined detected oil temperature T (step ST204).

  Next, when ECU 140 determines that the detected input rotation speed Nin is less than the operation-guaranteed rotation speed N1 (No in step ST204), ECU 140 determines whether or not the speed ratio is fixed (step ST205). . Next, when ECU 140 determines that the gear ratio is fixed (Yes in step ST205), each hydraulic oil supply / discharge valve 70 is closed (step ST206). That is, when the detected input rotation speed Nin is less than the operation guaranteed rotation speed, each hydraulic oil supply / discharge valve 70 is closed and the gear ratio is fixed. When the transmission gear ratio is fixed in the valve-closed state, as shown in FIG. 2, each hydraulic oil supply / discharge valve 70 is closed, and the hydraulic oil to the primary hydraulic chamber 55 via each hydraulic oil supply / discharge valve 70 is closed. And the discharge of the hydraulic oil from the primary hydraulic chamber 55 via the hydraulic oil supply / discharge valves 70 are prohibited. Thus, as in the first embodiment, the oil pump 132 does not have to be driven to supply the hydraulic oil to the primary hydraulic chamber 55 when the transmission gear ratio is fixed in the valve-closed state. An increase in loss can be suppressed.

  Next, when ECU 140 determines that the gear ratio is not fixed (No in step ST205), the hydraulic oil supply / discharge valve 70 is opened with the hydraulic pressure P2 in the drive hydraulic chamber 81 set to a constant pressure PS (step ST207). ). That is, the ECU 140 forcibly opens each hydraulic oil supply / discharge valve 70 by the actuator 80 when the speed ratio is not fixed, that is, when the speed ratio is changed. Next, ECU 140 performs gear ratio change control by hydraulic oil supply / discharge control device 130 (step ST208).

  Next, when ECU 140 determines that the detected input rotational speed Nin is equal to or greater than the guaranteed operation rotational speed N1 (No in step ST204), ECU 140 determines whether each hydraulic oil supply / discharge valve 70 is in an open state. (Step ST209). That is, the ECU 140 determines whether or not each hydraulic oil supply / discharge valve 70 has already been opened when the detected input rotational speed Nin is equal to or higher than the operation guaranteed rotational speed N1.

Next, when ECU 140 determines that each hydraulic oil supply / discharge valve 70 is not open (NO in step ST209), ECU 140 opens each hydraulic oil supply / discharge valve 70 with the hydraulic pressure P2 of drive hydraulic chamber 81 set to a constant pressure PS. (Step ST210). That is, when the detected input rotation speed Nin is equal to or higher than the operation-guaranteed rotation speed N1, the ECU 140 forces each hydraulic oil supply / discharge valve 70 to be forced by the actuator 80 regardless of whether the transmission gear ratio is changed or the transmission gear ratio is fixed. Open the valve. Specifically, the ECU 140 controls the drive hydraulic chamber control device 136 to be ON. When the drive hydraulic chamber control device 136 is ON-controlled by the ECU 140, the constant pressure PS introduced into the drive hydraulic chamber control device 136 is introduced into the drive hydraulic chamber 81, and the drive hydraulic chamber in which the atmospheric pressure P _OFF is approximately _OFF. The hydraulic pressure P2 of 81 becomes a constant pressure PS.

  Next, ECU 140 determines that each hydraulic oil supply / discharge valve 70 is in an open state (Yes in step ST209), or sets hydraulic pressure P2 of drive hydraulic chamber 81 to a constant pressure PS, and sets each hydraulic oil supply / discharge valve 70. Is opened, it is determined whether or not the gear ratio is fixed (step ST211). Next, when ECU 140 determines that the speed ratio is fixed (Yes in step ST211), ECU 140 performs constant speed ratio control (step ST212). If ECU 140 determines that the gear ratio is not fixed (No at step ST211), ECU 140 performs gear ratio change control (step ST208).

  In the first and second embodiments, the actuator 80 may maintain the open state of each hydraulic oil supply / discharge valve 70 even if the detected input rotation speed Nin is equal to or less than the shock reduction rotation speed N2. . In this case, in FIG. 5 and FIG. 11, when the input rotational speed Nin detected by the ECU 140 determines that the operation guaranteed rotational speed N1 is less than the operation guaranteed rotational speed N1 (No in step ST102, negative in step ST204), the detected input rotational speed is detected. It is determined whether Nin is equal to or less than the shock reduction rotational speed N2. If the detected input rotation speed Nin is equal to or less than the shock reduction rotation speed N2, the hydraulic fluid supply / discharge valve 70 is forcibly opened by the actuator 80 regardless of whether the transmission gear ratio is changed or the transmission gear ratio is fixed ( Steps ST107 and 108, Steps ST209 and 210). Then, the hydraulic oil supply / discharge control device 130 performs constant gear ratio control when the gear ratio is fixed (steps ST110 and ST212), and performs gear ratio change control when the gear ratio is changed (steps ST106 and ST208). Here, the shock reduction rotational speed N2 means that if a step occurs in the change in the gear ratio, a shock at the time of shifting is transmitted to a vehicle on which the belt type continuously variable transmission 1-2 is mounted, and drivability may be deteriorated. It refers to a certain input rotational speed Nin.

  Accordingly, the actuator 80 maintains the open state of each hydraulic fluid supply / discharge valve 70 when the detected input rotational speed Nin becomes equal to or less than the shock reduction rotational speed N2, so the hydraulic oil supply / discharge control device 130 causes the gear ratio to change. Can be changed continuously. As a result, when the vehicle equipped with the belt-type continuously variable transmission 1-2 has a low input rotational speed Nin such as a creeping traveling state or a low-speed traveling state, it is possible to prevent a step from occurring in a change in the gear ratio. Therefore, a shock at the time of shifting can be suppressed and deterioration of drivability can be suppressed. When the detected input rotational speed Nin is equal to or less than the shock reduction rotational speed N2, the driving force input from the internal combustion engine 10 to the primary pulley shaft 51 of the primary pulley 50, that is, the input torque is small. The belt clamping pressure generated with respect to the belt 110 by P2 is low. Therefore, even if the open state of each hydraulic oil supply / discharge valve 70 is maintained and the gear ratio is continuously changed by the hydraulic oil supply / discharge control device 130, an increase in driving loss of the oil pump 132 can be suppressed. .

  Further, the actuator 80 is provided with torque detecting means for detecting the input torque Fin of the primary pulley 50 that is a pulley to which the driving force from the internal combustion engine 10 that is the driving source is input. When the torque becomes equal to or less than F1, the open state of each hydraulic oil supply / discharge valve 70 may be maintained. Here, the shock reduction torque F1 means that the operating loss of the oil pump 132 is maintained even when the hydraulic oil supply / discharge valve 70 is kept open and the gear ratio is continuously changed by the hydraulic oil supply / discharge control device 130. This is the input torque Fin that can suppress the increase.

  Accordingly, when the detected input torque Fin becomes equal to or less than the shock reduction torque F1, the actuator 80 maintains the open state of each hydraulic oil supply / discharge valve 70, so that the hydraulic oil supply / discharge control device 130 continuously increases the gear ratio. Can be changed. As a result, when the input torque Fin is small, that is, when the belt clamping pressure generated with respect to the belt 110 by the hydraulic pressure P2 of the primary hydraulic chamber 55 is low, the open state of each hydraulic oil supply / discharge valve 70 is maintained to operate. Since the gear ratio is continuously changed by the oil supply / discharge valve control device 130, an increase in driving loss of the oil pump 132 can be suppressed. Further, when the detected input torque Fin is equal to or less than the shock reduction torque F1, the vehicle equipped with the belt-type continuously variable transmission 1-2 may have a low input rotational speed Nin such as a creeping state or a low-speed traveling state. Therefore, by suppressing the occurrence of a step in the change in the gear ratio, a shock at the time of shifting can be suppressed and deterioration of drivability can be suppressed.

It is a skeleton figure of the belt type continuously variable transmission concerning the present invention. It is principal part sectional drawing of the primary pulley at the time of gear ratio fixed (valve closing state). It is a figure which shows a torque cam. It is a figure which shows a torque cam. It is a figure which shows the structural example of a hydraulic-oil supply / discharge control apparatus. It is a figure which shows the operation | movement flow of the belt type continuously variable transmission concerning Example 1. FIG. It is operation | movement explanatory drawing of the belt type continuously variable transmission at the time of gear ratio change. It is operation | movement explanatory drawing of the belt type continuously variable transmission at the time of gear ratio change. It is operation | movement explanatory drawing of the belt type continuously variable transmission at the time of gear ratio change. It is operation | movement explanatory drawing of the belt type continuously variable transmission at the time of gear ratio change. It is principal part sectional drawing of the primary pulley at the time of gear ratio fixed (valve open state). It is a figure which shows the operation | movement flow of the belt type continuously variable transmission concerning Example 2. FIG. It is a figure which shows the relationship between the oil temperature of hydraulic oil, and operation | movement guarantee rotation speed.

Explanation of symbols

1-1, 1-2 Belt type continuously variable transmission 10 Internal combustion engine (drive source)
20 transaxle 30 torque converter 40 forward / reverse switching mechanism 50 primary pulley 51 primary pulley shaft 51a supply / discharge side main passage 51b drive side main passage 51c, d shaft side communication passage 52 primary fixed sheave 53 primary movable sheave 54 primary partition 54a valve arrangement Passage 54b, e Bulkhead side communication passage 54c Sliding support hole 54d Notch 54f Recess 55 Primary hydraulic chamber (one clamping pressure generating hydraulic chamber)
56 Cover member 60 Secondary pulley 64 Secondary hydraulic chamber 70 Hydraulic oil supply / discharge valve 71 Valve body 72 Valve seat surface 73 Valve body holding member 74 Valve body elastic member 75 Snap ring 80 Actuator 81 Drive hydraulic chamber 82 Piston 82a Pressure receiving member 82b Pressing member 90 Final reduction gear 100 Power transmission path 110 Belt 112 Pulley bearing 120 Wheel 130 Hydraulic oil supply / discharge control device (hydraulic oil supply / discharge control means)
131 Oil pan 132 Oil pump 133 Line pressure control device 134 Constant pressure control device 135 Primary hydraulic chamber control device 136 Drive hydraulic chamber control device 137 Secondary hydraulic chamber control device 140 ECU
150 Rotational speed sensor (Rotational speed detection means)
S1 Primary hydraulic chamber seal member S2 Piston seal member

Claims (5)

Two pulleys,
A belt that is wound around each pulley and transmits a driving force from a driving source;
A clamping pressure generating hydraulic chamber formed in each pulley and generating a belt clamping pressure with respect to the belt by hydraulic pressure;
A hydraulic oil supply / discharge valve that opens in the direction in which hydraulic oil is supplied to one of the clamping pressure generating hydraulic chambers and rotates integrally with the one pulley, of each of the clamping pressure generating hydraulic chambers;
The hydraulic oil in the drive hydraulic chamber causes the piston to slide in one of the sliding directions relative to the drive hydraulic chamber, thereby forcibly opening the hydraulic oil supply / discharge valve and rotating integrally with the one pulley. An actuator,
When the hydraulic oil supply / discharge valve is forcibly opened by the actuator, the hydraulic oil is supplied to the one clamping pressure generating hydraulic chamber or the hydraulic oil is discharged from the one clamping pressure generating hydraulic chamber. Hydraulic oil supply / discharge control means for controlling the ratio;
Among the pulleys, a rotational speed detection means for detecting an input rotational speed of a pulley to which a driving force from the driving source is input;
With
The belt type continuously variable transmission, wherein the actuator forcibly opens the hydraulic oil supply / discharge valve in accordance with the detected input rotational speed.   2. The belt-type continuously variable transmission according to claim 1, wherein the actuator maintains an open state of the hydraulic oil supply / discharge valve when the detected input rotational speed is equal to or higher than an operation guaranteed rotational speed. . Oil temperature detecting means for detecting the oil temperature of the hydraulic oil is further provided,
The belt-type continuously variable transmission according to claim 2, wherein the operation-guaranteed rotational speed is changed according to the detected oil temperature.   4. The actuator according to claim 1, wherein the hydraulic oil supply / discharge valve is maintained in an open state when the detected input rotation speed is equal to or less than a shock reduction rotation speed. 5. Belt type continuously variable transmission. Torque detection means for detecting an input torque of a pulley to which a driving force from the driving source is input among the pulleys,
The belt according to any one of claims 1 to 3, wherein the actuator maintains an open state of the hydraulic oil supply / discharge valve when the detected input torque is equal to or less than a shock reduction torque. Type continuously variable transmission.

Images