JP5115381B2 - Belt type continuously variable transmission - Google Patents

Description

  The present invention relates to a belt-type continuously variable transmission, and more particularly to a belt-type continuously variable transmission that holds hydraulic oil in a clamping pressure generating hydraulic chamber by closing a hydraulic oil supply / discharge valve.

  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. There are two types of transmissions: 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 includes two pulleys, namely, a primary pulley to which output torque from a drive source is transmitted, a secondary pulley that changes and outputs output torque transmitted to the primary pulley, and the primary pulley. There is a belt-type continuously variable transmission that includes a belt that transmits a transmitted output torque 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 form a V-shaped groove between the movable sheave and the belt It is constituted by a clamping pressure generating hydraulic chamber that generates 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 in the axial direction on each pulley shaft by the hydraulic pressure of each clamping pressure generating hydraulic chamber, and is formed in a V-shape formed in each of the primary pulley and the secondary pulley. Change the width of the groove. 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.

  Such a belt type continuously variable transmission regulates the movement of the movable sheave in the axial direction so that the contact radius of the belt does not change when the transmission gear ratio is fixed. In this case, the hydraulic pressure in the clamping pressure generating hydraulic chamber is kept constant so that the movable sheave does not slide in the axial direction. Conventionally, as a technique for keeping the hydraulic pressure in the clamping pressure generating hydraulic chamber constant, for example, as shown in Patent Document 1, there is a technique for holding hydraulic oil in the clamping pressure generating hydraulic chamber. That is, in the belt-type continuously variable transmission described in Patent Document 1, a supply / discharge path for supplying hydraulic oil to the clamping pressure generating hydraulic chamber and discharging hydraulic oil from the clamping pressure generating hydraulic chamber, and a clamping pressure A hydraulic oil supply / discharge valve is provided between the generated hydraulic chamber and the hydraulic oil is supplied to the clamping pressure generating hydraulic chamber when the hydraulic oil supply / discharge valve is opened, or the hydraulic oil is discharged from the clamping pressure generating hydraulic chamber and closed. Occasionally, hydraulic oil is confined in the clamping pressure generating hydraulic chamber.

JP 2006-300270 A

  Incidentally, in the belt-type continuously variable transmission described in Patent Document 1 as described above, for example, further improvement in drivability has been desired.

  Therefore, an object of the present invention is to provide a belt type continuously variable transmission that can improve drivability.

In order to achieve the above object, a belt type continuously variable transmission according to the invention of claim 1 includes two pulleys, a belt wound around each of the pulleys and transmitting an output torque from a driving source, A hydraulic pressure chamber that is formed on a pulley and generates a belt clamping pressure with respect to the belt by hydraulic pressure, and hydraulic oil is supplied to or operated from one clamping pressure generation hydraulic chamber. When supplying hydraulic oil to the one clamping pressure generating hydraulic chamber, or when discharging the hydraulic oil from the one clamping pressure generating hydraulic chamber, provided in the supply / discharge path for discharging oil and the supply / discharge path A hydraulic oil supply / discharge valve that is closed when the transmission gear ratio is fixed and that rotates integrally with the one pulley, and a valve opening / closing control means that controls opening / closing of the hydraulic oil supply / discharge valve; Valve opening / closing control The valve closing response period, which is a period for shifting the hydraulic oil supply / discharge valve from the valve opening state to the valve closing state, is set to a period longer than the valve opening response period, which is a period for shifting from the valve closing state to the valve opening state. Supply means for supplying and discharging hydraulic oil to the drive hydraulic chamber of the valve opening / closing control means, setting means , first hydraulic control means for controlling supply and discharge of hydraulic oil to the one clamping pressure generating hydraulic chamber via the supply and discharge path A second hydraulic control means for controlling the first hydraulic control means, a first control means for controlling the first hydraulic pressure control means and the second hydraulic pressure control means, and a gear ratio capable of detecting a gear ratio which is a rotational speed ratio of the two pulleys. The hydraulic oil supply / discharge valve is opened in a direction in which hydraulic oil is supplied to the one clamping pressure generating hydraulic chamber, and the valve opening / closing control unit is configured to move the piston by the hydraulic pressure of the driving hydraulic chamber. The drive hydraulic chamber The hydraulic oil supply / discharge valve is opened by sliding in one of the sliding directions, and the first control unit is configured to supply the hydraulic oil to the one clamping pressure generating hydraulic chamber, The first hydraulic pressure control means is controlled to increase the hydraulic pressure of the supply / discharge path, and after the change of the transmission gear ratio is detected by the transmission gear ratio detection means, the hydraulic pressure of the drive hydraulic chamber is increased by the second hydraulic pressure control means. It is characterized by raising .

The belt-type continuously variable transmission according to the invention of claim 2 includes second control means for executing control for keeping the hydraulic pressure of the supply / discharge path constant during the valve-opening response period or the valve-closing response period. It is characterized by.

In order to achieve the above object, a belt-type continuously variable transmission according to a third aspect of the present invention includes two pulleys, a belt wound around each of the pulleys and transmitting an output torque from a drive source, A hydraulic pressure chamber that is formed on a pulley and generates a belt clamping pressure with respect to the belt by hydraulic pressure, and hydraulic oil is supplied to or operated from one clamping pressure generation hydraulic chamber. When supplying hydraulic oil to the one clamping pressure generating hydraulic chamber, or when discharging the hydraulic oil from the one clamping pressure generating hydraulic chamber, provided in the supply / discharge path for discharging oil and the supply / discharge path A hydraulic oil supply / discharge valve that opens in a direction to supply hydraulic oil to the one clamping pressure generating hydraulic chamber, closes when the transmission gear ratio is fixed, and rotates integrally with the one pulley; For hydraulic pressure of hydraulic chamber A valve opening / closing control means for controlling the opening / closing of the hydraulic oil supply / discharge valve by sliding the piston in one of the sliding directions with respect to the drive hydraulic chamber, and the one pinch via the supply / discharge path. The first hydraulic pressure control means for controlling supply / discharge of hydraulic oil to / from the pressure generating hydraulic chamber, the second hydraulic pressure control means for controlling supply / discharge of hydraulic oil to / from the drive hydraulic pressure chamber, and the rotational speed ratio of the two pulleys. A gear ratio detecting means capable of detecting a gear ratio; and when supplying hydraulic oil to the one clamping pressure generating hydraulic chamber, the first hydraulic pressure control means is controlled to increase the hydraulic pressure of the supply / discharge path, And a control means for increasing the hydraulic pressure of the drive hydraulic chamber by the second hydraulic pressure control means after the change of the speed ratio is detected by the speed ratio detection means.

  According to the belt type continuously variable transmission according to the present invention, the valve closing response period, which is a period during which the hydraulic oil supply / discharge valve is shifted from the open state to the closed state by the valve opening / closing control means, is changed from the closed state to the open state. Since the setting means for setting a period longer than the valve opening response period, which is a period for shifting, is provided, it is possible to suppress the occurrence of shock when the hydraulic oil supply / discharge valve is closed, and to improve drivability.

  According to the belt type continuously variable transmission according to the present invention, when supplying hydraulic oil to one clamping pressure generating hydraulic chamber, the first hydraulic control means is controlled to increase the hydraulic pressure in the supply / discharge path, thereby detecting the transmission ratio. Since the control means for increasing the hydraulic pressure of the drive hydraulic chamber by the second hydraulic control means after the change of the transmission gear ratio is detected by the means, the shift response is improved while reliably preventing the backflow of the hydraulic oil. And drivability can be improved.

  Hereinafter, the present invention will be described in detail with reference to the drawings. In addition, this invention is not limited by the following embodiment. 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 (a gasoline engine, a diesel engine, an LPG engine, or the like) 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. However, one pulley may be a secondary pulley and the other pulley may be a primary pulley.

(Embodiment 1)
FIG. 1 is a skeleton diagram of a belt-type continuously variable transmission according to Embodiment 1 of the present invention, and FIG. 2 is a diagram when the gear ratio of the belt-type continuously variable transmission according to Embodiment 1 of the present invention is fixed (valve closed state). FIG. 3-1 and FIG. 3-2 are views showing a torque cam of a belt-type continuously variable transmission according to Embodiment 1 of the present invention, and FIG. 4 is Embodiment 1 of the present invention. FIG. 5 to FIG. 8 are diagrams for explaining the operation of the belt-type continuously variable transmission according to the first embodiment of the present invention when the gear ratio is changed. is there.

  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 present embodiment. A primary hydraulic chamber 55 that is one clamping pressure generating hydraulic chamber, a secondary hydraulic chamber 64 that is the other clamping pressure generating hydraulic chamber, a hydraulic oil supply / discharge valve 70, an actuator 80 as a valve opening / closing control means, A belt 110 is accommodated. 40 is a forward / reverse switching mechanism, 90 is a final reduction gear that transmits the output torque of the internal combustion engine 10 to the wheels 120, 100 is a power transmission path, 130 shown in FIG. 4 is a hydraulic control device as hydraulic control means, 140 is An ECU (Electronic Control Unit) as control means, 150 is an input rotation speed sensor as gear ratio detection means, and 160 is an output rotation speed sensor as gear ratio detection means.

  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 about 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 lock-up clutch 34 that is controlled by supplying hydraulic oil from the hydraulic control device 130 is disposed between the turbine 32 and the front cover 37. 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 hydraulic oil is supplied as a hydraulic fluid from a hydraulic control device 130 that supplies the hydraulic oil to the hydraulic oil supply portion.

  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 lockup clutch 34 is released, the output torque from the internal combustion engine 10 transmitted to the front cover 37 is transmitted to the pump 31, and the hydraulic oil circulates between the pump 31 and the turbine 32. Is transmitted to the turbine 32. Then, the output torque (engine 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 as it is to the belt-type continuously variable transmission 1-1 through 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 through 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 a hydraulic 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 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 through 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 54, a primary hydraulic chamber 55, a valve arrangement member 56, The cover member 57 is constituted. Further, the primary pulley 50 is provided with a supply / discharge path for supplying hydraulic oil to the primary hydraulic chamber 55 or discharging hydraulic oil from the primary hydraulic chamber 55.

  As shown in FIGS. 1 and 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 open 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 supply / discharge path for supplying hydraulic oil to the primary hydraulic chamber 55 which is one clamping pressure generating hydraulic chamber and discharging the hydraulic oil from the primary hydraulic chamber 55. is there. The supply / discharge side main passage 51 a is formed on the primary fixed sheave side inside the primary pulley shaft 51 and communicates with an oil passage R <b> 7 (described later) of the hydraulic control device 130. In the supply / discharge-side main passage 51a, hydraulic oil supplied from the hydraulic control device 130 to the primary hydraulic chamber 55 flows in, and hydraulic fluid discharged from the primary hydraulic chamber 55 flows in. Therefore, the supply / discharge-side main passage 51a is a passage through which hydraulic oil supplied or discharged between the hydraulic control device 130 and the primary hydraulic chamber 55 passes. 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 passage 51c constitutes a part of the supply / discharge path. The shaft side communication passage 51c communicates with the space portion T1 by having 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. Here, 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 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 ring shape, and its radially inner end portion communicates with each shaft-side communication passage 51c, and the other end portion in the axial direction (the left end portion in the figure) communicates with the space portion T2. .

  The space T2 constitutes a part of the supply / discharge path. The space T2 is formed by the primary partition wall 54, the primary movable sheave 53, and the primary pulley shaft 51. The space portion T2 has a ring shape, and the radially inner end portion communicates with the space portion T1, and the radially outer end portion communicates with the partition wall side communication passage 54e. That is, the supply / discharge side main passage 51a communicates with the partition wall side communication passage 54e 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 inside the primary pulley shaft 51, and the insertion portion 23a of the transaxle rear cover 23 is inserted therein. Here, the insertion portion 23a is formed with a first communication passage 23b having one end communicating with the drive-side main passage 51b and the other end communicating with an oil passage R8 (described later) of the hydraulic control device 130. . Accordingly, the drive side main passage 51b communicates with the oil passage R8 of the hydraulic control device 130 via the first communication passage 23b. The hydraulic fluid supplied from the hydraulic control device 130 to the drive hydraulic chamber 81 flows into the drive side main passage 51b, and the hydraulic fluid discharged from the drive hydraulic chamber 81 flows into the drive side main passage 51b. Accordingly, the hydraulic fluid supplied or discharged between the hydraulic 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 T3 by having one end communicating with the drive-side main passage 51b and the other end opening on the outer peripheral surface of the primary pulley shaft 51. Here, 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 T3 is formed between the inner peripheral surface of the primary partition wall 54 (the inner peripheral surface of the radially inner protruding portion 54b) and the outer peripheral surface of the primary pulley shaft 51. The space T3 has a ring shape, and the radially inner side communicates with each shaft-side communication passage 51d and the radially outer side communicates with the partition-side communication passage 54f of the primary partition wall 54. That is, the drive side main passage 51b communicates with the partition wall side communication passage 54f via each shaft side communication passage 51d and the space 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.

  Here, a cancel-side main passage 23c is formed in the insertion portion 23a inserted into the drive-side main passage 51b of the transaxle rear cover 23. One end of the cancel side main passage 23c is closed inside the insertion portion 23a, communicates with the second communication passage 23d, and the other end communicates with a later-described branch oil passage R11 of the hydraulic control device 130.

  The second communication passage 23d communicates with the space portion T4 by having one end portion communicating with the cancel side main passage 23c and the other end portion opening to the outer peripheral surface of the insertion portion 23a. Here, the second communication passage 23d is formed at a plurality of locations (for example, three locations) at equal intervals on the circumference.

  The space portion T4 is formed between the primary pulley shaft 51 and the insertion portion 23a. That is, the space T4 is formed between the inner peripheral surface of the primary pulley shaft 51 (the inner peripheral surface constituting the drive side main passage 51b) and the outer peripheral surface of the insertion portion 23a. The space T4 has a ring shape, and the radially inner side communicates with each second communication passage 23d, and the radially outer side communicates with the shaft side communication passage 51e of the primary pulley shaft 51. That is, the cancel-side main passage 23c communicates with the shaft-side communication passage 51e via each second communication passage 23d and the space portion T4. A communication portion seal member S2 such as a seal ring is provided between the inner peripheral surface of the primary pulley shaft 51 and the outer peripheral surface of the insertion portion 23a with the space T4 interposed therebetween.

  The shaft-side communication passage 51e has one end opened to the inner peripheral surface of the primary pulley shaft 51 so as to communicate with the space T4, and the other end opened to the outer peripheral surface of the primary pulley shaft 51. , Communicated with the space T5. Here, the shaft side communication passage 51e is formed at a plurality of locations (for example, three locations) at equal intervals on the circumference.

  The space portion T <b> 5 is formed between the primary pulley shaft 51, the pulley bearing 112, and the cover member 57. That is, the space T5 is formed between the outer peripheral surface of the primary pulley shaft 51, the inner peripheral surface of the pulley bearing 112, and the inner peripheral surface of the cover member 57. The space portion T5 has a ring shape, the radially inner side communicates with each shaft-side communication passage 51e, and the radially outer side passes through the space portion formed between the pulley bearing 112 and the primary partition wall 54, and covers the cover side. It communicates with the communication passage 57a. That is, the cancel-side main passage 23c communicates with the cover-side communication passage 57a via each second communication passage 23d, the space T4, each shaft-side communication passage 51e, and the space T5. In addition, between the outer peripheral surface of the primary pulley shaft 51, the inner peripheral surface of the pulley bearing 112, and the inner peripheral surface of the cover member 57, for example, a communication portion seal member such as a seal ring is interposed with a space T5 interposed therebetween. It may be provided.

  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, here, 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 51f 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 51f is also included in the space T1. A cutout 53e is formed at the other end (the left 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 54 is a partition member and constitutes a primary hydraulic chamber 55 which is one clamping pressure generating hydraulic chamber. 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 sandwiched between the stepped portion formed on the primary pulley shaft 51 and the partition fixing member 58 fixed to the primary pulley shaft 51 together with the cover member 57 and the pulley bearing 112, so that the primary pulley shaft 51. Is fixed with respect to the axial direction.

  The primary partition 54 includes a cylindrical portion 54a, a radially inner protruding portion 54b, a recessed portion 54c, and a radially outer protruding portion 54d. The cylindrical portion 54a has a cylindrical shape and is formed extending in the axial direction. A partition wall side communication passage 54e is formed in the cylindrical portion 54a in the vicinity of the center portion in the axial direction. The partition wall side communication passage 54e constitutes a part of the supply / discharge path. The partition wall side communication passage 54e has an inner end in the radial direction that opens to the inner peripheral surface of the primary partition wall 54 (the inner peripheral surface of the cylindrical portion 54a) and communicates with the space T2 that forms part of the supply / discharge path. The radially outer end opens to the outer peripheral surface of the primary partition wall 54 (the outer peripheral surface of the cylindrical portion 54a) and communicates with the space T7. Here, the partition-side communication passage 54e is formed at a plurality of locations (for example, three locations) at equal intervals on the circumference.

  The radially inner projecting portion 54b has an annular shape, and is formed so as to project radially inward from the other end portion (the left end portion in the figure) in the axial direction of the cylindrical portion 54a. On the radially inner projecting portion 54b, a partition wall side communication passage 54f is formed in the vicinity of the central portion in the axial direction. The partition wall side communication passage 54f has an inner end in the radial direction that opens to the inner peripheral surface of the primary partition wall 54 (the inner peripheral surface of the cylindrical portion 54a), communicates with the space T3, and the outer end in the radial direction has the primary partition wall. 54 opens to the outer peripheral surface (the outer peripheral surface of the cylindrical portion 54a), and communicates with a drive hydraulic chamber 81 (described later) of the actuator 80. Therefore, the drive side main passage 51b communicates with the drive hydraulic chamber 81 via the shaft side communication passages 51d, the space T3, and the partition wall side communication passages 54f. Here, the partition-side communication passages 54f are formed at a plurality of locations (for example, three locations) at equal intervals on the circumference.

  Further, a partition wall side communication passage 54g is formed from the cylindrical portion 54a to the radially inner protruding portion 54b. One end portion (right end portion in the figure) of the partition wall side communication passage 54g opens to the outer peripheral surface of the primary partition wall 54 (the outer peripheral surface of the cylindrical portion 54a), communicates with a cancel chamber 84 described later, and the other end portion. Opens on the other side surface of the primary partition wall 54 in the axial direction (the other side surface (the left side surface in the figure) of the both side surfaces in the axial direction of the radially inner projecting portion 54b), and the cover side of the cover member 57 It communicates with the communication passage 57a. Here, the partition-side communication passages 54g are formed at a plurality of locations (for example, three locations between adjacent partition-side communication passages 54f) at equal intervals on the circumference.

  The recess 54c is formed so as to protrude in the axial direction toward the primary hydraulic chamber 55 that is one clamping pressure generating hydraulic chamber, that is, in the valve opening direction. The recess 54c is formed continuously in the circumferential direction. The recess 54c is formed with a partition-side storage portion 54h and an opening hole 54i. One end (right side end in the figure) of the partition wall side storage portion 54h is closed inside the recess 54c, and the other end (left side end in the figure) opens to a surface facing the valve arrangement member 56. This communicates with a space T6 described later. Here, a plurality of locations (for example, 3 locations) are formed at equal intervals on the circumference. The opening hole 54i opens in a surface where one end (right side end in the figure) is exposed to the primary hydraulic chamber 55, communicates with the primary hydraulic chamber 55, and the other end (left side end in the figure) has a valve. It opens to the surface facing the arrangement member 56 and communicates with a space T6 described later. Here, the opening holes 54i are formed at a plurality of locations on the circumference at equal intervals (for example, three locations between adjacent partition wall side storage portions 54h).

  The space portion T6 constitutes a part of the supply / discharge path. The space portion T6 is formed by the primary partition wall 54 and the valve arrangement member 56. The space portion T6 has a ring shape, and one end portion (the right end portion in the figure) communicates with each opening hole 54i, and the other end portion (the left end portion in the figure) is the valve arrangement passage of the valve arrangement member 56. It communicates with 56a. A communication portion seal member S3 such as a seal ring is provided between the inner peripheral surface of the recess 54c of the primary partition wall 54 and the valve disposing member 56 with the space portion T6 interposed therebetween. Accordingly, the space T6 formed by the primary partition wall 54 and the valve arrangement member 56 is sealed by the communication portion seal member S3.

  The radially outer projecting portion 54d has an annular shape, and is formed to project from the radially outer end of the recessed portion 54c to the radially outer mold. The radially outer projecting portion 54d substantially comes into contact with a projecting portion 53d formed to project from the radially outer end of the annular portion 53b of the primary movable sheave 53 to the other of the axial directions (left direction in the figure). Projected to the position.

  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 (mainly, the concave portion 54c and the radially outer protruding portion 54d). Here, a seal ring, for example, is provided between the protrusion 53d of the primary movable sheave 53 and the radially outer protrusion 54d of the primary partition 54, and between the cylindrical portion 53a of the primary movable sheave 53 and the recess 54c of the primary partition 54. A primary hydraulic chamber seal member S1 is provided. Accordingly, the space formed by the primary movable sheave 53 as the primary hydraulic chamber 55 and the primary partition wall 54 is sealed by the primary hydraulic chamber seal member S1.

  The hydraulic oil from the hydraulic control device 130 that has flowed into the supply / discharge main passage 51 a of the primary pulley shaft 51 is supplied to the primary hydraulic chamber 55. 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 control device 130, that is, the primary hydraulic pressure P1 of the primary hydraulic chamber 55, and the primary movable sheave 53 is moved to the primary fixed sheave. 52 to approach or separate. Thus, the primary hydraulic chamber 55 generates a belt clamping pressure with respect to the belt 110 by the primary 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 valve arrangement member 56 is for arranging the hydraulic oil supply / discharge valve 70 and is formed separately from the primary partition wall 54 which is a partition member. The valve arrangement member 56 has a cylindrical shape, is arranged on the primary partition wall 54, and is fixed to the primary partition wall 54. Here, the valve arrangement member 56 is inserted into a recessed portion 54c formed to protrude toward the primary hydraulic chamber side of the primary partition wall 54 that is a partition member, and is a snap that is a fixed member for a valve arrangement member that is inserted into and fixed to the recessed portion 54c. The ring 59 is fixed in the axial direction.

  The valve arrangement member 56 is formed with a valve arrangement passage 56a extending in the axial direction at a central portion in the radial direction. The valve arrangement passage 56a constitutes a part of the supply / discharge path. The valve arrangement passage 56a has one end portion (right side end portion in the figure) communicating with the space portion T6, and the other end portion (left end portion in the figure) is closed inside the valve arrangement member 56, so that the arrangement side communication is established. It communicates with the passage 56b. The valve arrangement passage 56 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 in the vicinity of one end of the valve arrangement passage 56a. The valve arrangement passage 56a is formed corresponding to each partition-side storage portion 54h of the primary partition 54. Therefore, the valve arrangement passage 56a 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 56a.

  The arrangement-side communication passage 56b constitutes a part of the supply / discharge path. As for the arrangement side communication passage 56b, one end portion (an end portion on the radially outer side in the figure) communicates with the valve arrangement passage 56a, and the other end portion (the inner side in the radial direction in the figure) is on the inner peripheral surface of the primary partition wall 54. Open and communicate with the space T7. Here, the arrangement-side communication passage 56b is formed at a plurality of locations (for example, three locations) at equal intervals on the circumference.

  The space portion T7 constitutes a part of the supply / discharge path. The space portion T7 is formed by the valve arrangement member 56 and the primary partition wall 54. The space T7 has a ring shape, and its radially inner end communicates with each partition wall side communication passage 54e, and its radially outer end communicates with each valve arrangement passage 56a. That is, the supply / discharge path includes the supply / discharge side main passage 51a, the shaft side communication passages 51c, the space portions T1 and T2, the partition wall side communication passages 54e, the space portion T7, the arrangement side communication passages 56b, and the valve arrangement passages 56a. , The space T6 and each opening hole 54i. Therefore, the belt-type continuously variable transmission 1-1 according to the present embodiment supplies and discharges hydraulic oil to and from the primary hydraulic chamber 55 through one supply / discharge path.

  The valve arrangement member 56 is formed with sliding support holes 56c on the same axis as the valve arrangement passages 56a. The sliding support hole 56c has one end portion (right end portion in the figure) communicating with the valve arrangement passage 56a, and the other end portion (left end portion in the figure) on both side surfaces in the axial direction of the valve arrangement member 56. Of these, it opens on the other side surface (the left side surface in the figure) and communicates with the cancel chamber 84.

  Further, the valve arrangement member 56 is formed with an arrangement side storage portion 56d. One end (the right end in the figure) of the arrangement side storage portion 56d is closed inside the valve arrangement member 56, and the other end (the left end in the figure) is both sides in the axial direction of the valve arrangement member 56. It opens to the other side surface (the left side surface in the figure) of the surfaces and communicates with the cancel chamber 84. Here, the arrangement side storage portions 56d are formed at a plurality of locations (for example, three locations between adjacent sliding support holes 56c) at equal intervals on the circumference.

  The cover member 57 is a drive hydraulic chamber constituent member that constitutes the drive hydraulic chamber 81 of the actuator 80, and covers the piston 82. The cover member 57 has a ring shape and is disposed between the primary partition wall 54 and the pulley bearing 112. The cover member 57 has a cover-side communication passage 57a formed at the radially inner end. The cover side communication passage 57a has one end portion (end portion on the radially outer side in the figure) communicating with the partition wall side communication passage 54g, and the other end portion (end portion on the inner side in the drawing direction in the drawing) with the pulley bearing 112. It communicates with the space portion T5 through a space portion formed between the primary partition wall 54 and the primary partition wall 54. Here, the cover side communication passage 57a is formed at a plurality of locations (for example, three locations) at equal intervals on the circumference. Accordingly, the cancel side main passage 23c communicates with the cancel chamber 84 via the second communication passage 23d, the space T4, each shaft side communication passage 51e, the space T5, the cover side communication passage 57a, and the partition wall side communication passage 54g. is doing. In addition, an axially protruding portion 57b that protrudes in one of the axial directions (rightward in the figure) is formed at the radially outer end of the cover member 57. The axial projecting portion 57b is formed to project to a position where it enters the concave portion 54c of the primary partition wall 54. Further, in the vicinity of the radial center of the cover member 57, a restricting projection 57c that restricts movement of the actuator 80 in the axial direction of a pressure receiving member 82a of a piston 82 (to be described later) to the other (left direction in the figure) is formed. Has been.

  Returning to FIG. 1, 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 converted into a belt-type continuously variable transmission. This is transmitted to the final reduction gear 90 of the machine 1-1. 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. Further, the secondary pulley shaft 61 has a hydraulic oil passage (not shown) therein, and hydraulic oil supplied from the hydraulic 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, here, 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 facing the secondary movable sheave 63 and the surface of the secondary movable sheave 63 facing 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, 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 secondary hydraulic chamber 64 is supplied with hydraulic oil from the hydraulic control device 130 that has flowed into a hydraulic oil passage (not shown) of the secondary pulley shaft 61 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 pressure of the hydraulic fluid supplied from the hydraulic control device 130, that is, the hydraulic pressure of the secondary hydraulic chamber 64. The secondary fixed sheave 62 is approached or separated. 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 engaging portion 63b and the second engaging portion 67a. The transmission member 68 is configured.

  As shown in FIG. 1, the intermediate member 67 is formed integrally with the secondary partition wall 65 or fixed to the secondary partition wall 65. The shaft 61 is supported so as to be relatively rotatable. 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. 3B. 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. Note that the secondary hydraulic chamber 64 may be the only means for generating the belt clamping pressure for the belt 110 in the secondary pulley 60.

  The hydraulic oil supply / discharge valve 70 is also opened when hydraulic oil is supplied to the primary hydraulic chamber 55 that is one clamping pressure generating hydraulic chamber, or when hydraulic fluid is discharged from the primary hydraulic chamber 55. In the present embodiment, when one hydraulic oil supply / discharge valve 70 is opened, the hydraulic oil is supplied to the primary hydraulic chamber 55 and discharged from the primary hydraulic chamber 55. As shown in FIGS. 2, 5, and 7, the hydraulic oil supply / discharge valve 70 is closed to hold the hydraulic oil in the primary hydraulic chamber 55 to fix the gear ratio and open the valve. The hydraulic oil is supplied from the outside of the primary hydraulic chamber 55, that is, from the primary pulley 50 to the primary hydraulic chamber 55 to reduce (upshift) the gear ratio, open the valve, and open from the primary hydraulic chamber 55 to the outside of the primary pulley 50. The hydraulic oil is discharged and the gear ratio is increased (downshifted). Here, the hydraulic oil supply / discharge valve 70 is arranged on the valve arrangement member 56. That is, the hydraulic oil supply / discharge valve 70 rotates integrally with the primary pulley 50 that is one pulley.

  As shown in FIG. 2, the hydraulic oil supply / discharge valve 70 includes a valve body 71, a valve seat surface 72, and a valve body elastic member 73. The valve body 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 arrangement passage 56a to one end). When the valve element 71 contacts the valve seat surface 72, the communication between the valve arrangement passage 56a and the space portion T6 is blocked, that is, the communication between the supply / discharge path and the primary hydraulic chamber 55 is blocked, and the 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 56a and the space T6 are communicated, that is, the supply / discharge path and the primary hydraulic chamber 55 are communicated, and the hydraulic oil supply / discharge valve 70 is opened. To be spoken. The hydraulic oil supply / discharge valve 70 is opened when the valve element 71 moves in the valve opening direction (the direction toward the primary hydraulic chamber 55, in other words, the direction away from the valve seat surface 72), and the valve element 71 is closed. The valve is closed by moving in the valve direction (the direction toward the opposite side of the primary hydraulic chamber 55, in other words, the direction approaching the valve seat surface 72).

  The valve body elastic member 73 is a valve body valve closing direction pressing force generating means, and applies a valve body valve closing direction pressing force to the valve body 71 to press the valve body 71 in the valve closing direction. The valve body elastic member 73 is, for example, a coil spring, and a part thereof is housed in the partition side housing portion 54 h of the primary partition wall 54. The valve body elastic member 73 is disposed in a state of being urged between the partition wall side accommodating portion 54 h and the valve seat surface 72 via the valve body 71. That is, the valve body elastic member 73 is arranged in a state of being biased between the valve arrangement member 56 and the primary partition wall 54 that is a partition wall member via the valve body 71. Thereby, the valve body elastic member 73 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, that is, a valve closing direction. It acts on the valve body 71 as the valve body closing direction pressing force. That is, the valve body 71 is pressed against the valve seat surface 72, and the hydraulic oil supply / discharge valve 70 functions as a check valve.

  The actuator 80 is a valve opening / closing control means. The actuator 80 controls the opening and closing of the hydraulic oil supply / discharge valve 70 and is operated by hydraulic pressure. The actuator 80 opens the hydraulic oil supply / discharge valve 70. The actuator 80 includes a drive hydraulic chamber 81 and a piston 82. Reference numeral 83 denotes a piston elastic member, 84 denotes a cancel chamber, and 85 denotes an elastic member holding member that holds the piston elastic member.

  The drive hydraulic chamber 81 is supplied with hydraulic oil, and the on / off valve of the hydraulic oil supply / discharge valve 70, that is, the pressure of the supplied hydraulic oil, that is, the drive hydraulic chamber hydraulic pressure P2 of the drive hydraulic chamber 81, that is, The valve body 71 is controlled. The drive hydraulic chamber 81 is formed between a pressure receiving member 82a (described later) of the piston 82, the primary partition wall 54, and the cover member 57. The drive hydraulic chamber 81 is a ring-shaped space, and hydraulic oil is supplied from the hydraulic 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 drive hydraulic chamber hydraulic pressure P <b> 2 of the drive hydraulic chamber 81. Here, between the pressure receiving member 82a and the primary partition wall 54 and the cover member 57, for example, a drive hydraulic chamber seal member S4 such as a seal ring is provided. That is, the space formed by the cover member 57 constituting the drive hydraulic chamber 81, the primary partition wall 54, and the pressure receiving member 82a of the piston 82 is sealed by the drive hydraulic chamber seal member S4.

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

  The pressure receiving member 82 a is supported by the primary partition wall 54 and the cover member 57 so as to be slidable in the sliding direction, that is, in the axial direction with respect to the drive hydraulic chamber 81. The pressure receiving member 82 a receives the drive hydraulic chamber hydraulic pressure P <b> 2 of the drive hydraulic chamber 81. The pressure receiving member 82a is driven in the axial direction which is one of the sliding directions with respect to the drive hydraulic chamber 81, that is, the valve is opened by the piston valve opening direction pressing force acting by the drive hydraulic chamber hydraulic pressure P2 of the drive hydraulic chamber 81. Slide in the direction. The pressure receiving member 82a has a pressure receiving side storage portion 82c. One end portion (right end portion in the figure) of the pressure receiving side storage portion 82c opens to one side surface (right side surface in the figure) of both side surfaces in the axial direction of the pressure receiving member 82a, and communicates with the cancel chamber 84. The other end portion (the left end portion in the figure) is closed inside the pressure receiving member 82a. Here, the pressure-receiving side storage portion 82 c is formed so as to oppose each of the arrangement side storage portions 56 d of the valve arrangement member 56.

  The pressing members 82 b are respectively disposed between the pressure receiving member 82 a and the valve body 71 of the hydraulic oil supply / discharge valve 70. The pressing member 82b is inserted into the sliding support hole 56c of the valve arrangement member 56, and is supported so as to be slidable in the axial direction with respect to the sliding support hole 56c. That is, the pressing member 82b is supported so as to be slidable in the axial direction with respect to the primary pulley 50 which is one pulley. One end portion (right end portion in the figure) of the pressing member 82 b faces the valve body 71 of the hydraulic oil supply / discharge valve 70 and can contact the valve body 71. Further, the other end portion (the left end portion in the figure) of the pressing member 82b faces the pressure receiving member 82a, and can contact the pressure receiving member 82a. Accordingly, the pressing member 82b can slide in the axial direction with respect to the primary pulley 50 while being in contact with the 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 the hydraulic oil supply / discharge valve 70. That is, when the pressure receiving member 82a comes into contact with the pressure receiving member 82a by sliding the pressure receiving member 82a in one of the axial directions by the driving hydraulic chamber hydraulic pressure P2 of the driving hydraulic chamber 81, the pressing member 82b is in the same direction as the pressure receiving member 82a. Slide.

  The piston elastic member 83 is a piston valve closing direction pressing force generating means. The piston elastic member 83 is arranged in a state of being biased between the arrangement-side storage portion 56d and the pressure-receiving side storage portion 82c. Here, the piston elastic member 83 is also a piston when the piston 82 is located in the most other direction in the sliding direction with respect to the drive hydraulic chamber 81 (in other words, the most other direction in the axial direction), that is, in the most valve closing direction. It arrange | positions so that a biasing force may generate | occur | produce. Therefore, the piston elastic member 83 generates a piston urging force, and the piston urging force causes the pressure receiving member 82a of the piston 82 to move in the other direction (in other words, the most other in the axial direction) with respect to the drive hydraulic chamber 81. Direction), that is, an elastic member pressing force in the valve closing direction acts on the pressure receiving member 82a as a piston valve closing direction pressing force. Thus, the piston 82 does not have to slide in the other sliding direction 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 73.

  Here, when the hydraulic oil supply / discharge valve 70 is opened, the valve body valve opening direction pressing force, which is a pressing force acting on the valve body 71 in the direction in which the valve body 71 moves away from the valve seat surface 72, that is, in the valve opening direction. However, the valve body 71 exceeds the valve 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, and the valve body 71 moves away from the valve seat surface 72 Is done. Accordingly, the 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.

  Here, the hydraulic oil supply / discharge valve 70 is opened by the actuator 80 regardless of whether the hydraulic oil is supplied to the primary hydraulic chamber 55 that is one clamping pressure generating hydraulic chamber or when the hydraulic oil is discharged from the primary hydraulic chamber 55. To be spoken. That is, the actuator 80 opens the hydraulic oil supply / discharge valve 70 that is a hydraulic oil discharge valve when discharging the hydraulic oil from the primary hydraulic chamber 55, and also supplies hydraulic oil to the primary hydraulic chamber 55. The hydraulic oil supply / discharge valve 70 is opened.

  The actuator 80 first slides the pressure receiving member 82a in the valve opening direction by applying a piston valve opening direction pressing force to the pressure receiving member 82a of the piston 82 by the driving hydraulic chamber hydraulic pressure P2 of the driving hydraulic chamber 81. When the pressure receiving member 82a slides in the valve opening direction, the pressure receiving member 82a and the pressing member 82b come into contact with each other, and the pressing member 82b slides in the valve opening direction together with the pressure receiving member 82a. When the pressing member 82b comes into contact with the valve body 71 of the hydraulic oil supply / discharge valve 70, the differential pressing force obtained by subtracting the piston valve closing direction pressing force from the piston valve opening direction pressing force acting on the piston 82 is the valve body. It acts on the valve body 71 as a valve opening direction pressing force. Accordingly, the hydraulic oil supply / discharge valve 70 has the valve body 71 in the valve opening direction with respect to the valve seat surface 72 when the differential pressing force, which is the valve body opening direction pressing force, exceeds the valve body closing direction pressing force. The hydraulic oil supply / discharge valve 70 is opened. The valve body closing direction pressing force includes the elastic member pressing force that acts on the valve body 71 by the valve closing urging force generated by the valve body elastic member 73, and the primary partition wall side of the valve arrangement passage 56a with respect to the valve body 71. , That is, the hydraulic oil valve closing direction pressing force acting on the valve body 71 in the valve closing direction by the primary hydraulic pressure P1 of the primary hydraulic chamber 55.

  The hydraulic oil valve closing direction pressing force acting on the valve body 71 by the primary 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 the primary hydraulic pressure P1 rises, the valve body 71 does not leave the valve seat surface 72. Accordingly, the closed state of the hydraulic oil supply / discharge valve 70 is maintained as long as the valve body opening direction pressing force acting on the valve body 71 does not exceed the valve body closing direction pressing force. The hydraulic oil in the primary hydraulic chamber 55 is reliably held in the primary hydraulic chamber 55. In the present embodiment, the actuator 80 is actuated by hydraulic pressure, but the present invention is not limited to this, and rotational force such as a motor or electromagnetic force may be used.

  The cancel chamber 84 is supplied with hydraulic oil, and is disposed to face the drive hydraulic chamber 81 with the pressure receiving member 82a of the piston 82 interposed therebetween. The cancellation chamber 84 is configured to cancel the centrifugal hydraulic pressure generated in the hydraulic oil in the drive hydraulic chamber 81 by the centrifugal hydraulic pressure generated in the hydraulic oil in the cancellation chamber 84 by the rotation of the primary pulley 50 that is one pulley. It is. The cancel chamber 84 includes a primary partition 54, a valve arrangement member 56, a cover member 57, and a pressure receiving member 82 a for the piston 82. The cancel chamber 84 communicates with the partition wall side communication passage 54g at the radially inner end. The centrifugal hydraulic pressure generated in the hydraulic oil supplied to the cancel chamber 84 is the same as that in the valve closing direction when the centrifugal hydraulic pressure generated in the hydraulic oil supplied to the drive hydraulic chamber 81 acts on the piston as a pressing force in the valve opening direction. Acting on the piston 82 as a pressing force, the centrifugal hydraulic pressure generated in the hydraulic oil in the drive hydraulic chamber 81 is offset. Here, a cancel chamber seal member S5 such as a seal ring is provided between the primary partition wall 54 and the valve arrangement member 56 and between the valve arrangement member 56 and the cover member 57, for example. In other words, the space formed by the primary partition wall 54, the valve disposing member 56, the cover member 57, and the pressure receiving member 82a of the piston 82 constituting the cancel chamber 84 is composed of the drive hydraulic chamber seal member S4 and the cancel chamber. Sealed with the seal member S5.

  Returning to FIG. 1 again, a power transmission path 100 is disposed 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 speed reducer 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 via 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.

  Next, the hydraulic control device 130 shown in FIG. 4 is hydraulic control means. That is, the hydraulic control device 130 includes a supply / discharge path (supply / discharge side main passage 51a, each shaft side communication passage 51c, space portions T1, T2, each partition wall side communication passage 54e, space portion T7, each arrangement side communication passage 56b, This is the first hydraulic control means of the present invention that controls the supply and discharge of hydraulic fluid to and from the primary hydraulic chamber 55 that is one clamping pressure generating hydraulic chamber via each valve arrangement passage 56a, the space T6, and each opening hole 54i). At the same time, it is also a second hydraulic pressure control means for controlling the supply and discharge of hydraulic oil to and from the drive hydraulic pressure chamber 81 of the actuator 80 which is a valve opening / closing control means. That is, when the hydraulic control device 130 supplies hydraulic oil to the primary hydraulic chamber 55, the primary pulley 50 and the supply / discharge path communicate with each other, whereby the hydraulic oil is supplied to the primary hydraulic chamber 55 via the supply / discharge path. Supply. Further, when the hydraulic control device 130 discharges the hydraulic oil from the primary hydraulic chamber 55, the primary hydraulic chamber 55 and the supply / discharge path communicate with each other, whereby the hydraulic oil is supplied from the primary hydraulic chamber 55 via the supply / discharge path. It is also what discharges. The hydraulic control device 130 also supplies and discharges hydraulic oil to and from the drive hydraulic chamber 81. Further, here, the hydraulic control device 130 supplies hydraulic oil to a hydraulic oil supply portion that requires supply of hydraulic oil in a vehicle on which the belt type continuously variable transmission 1-1 and the internal combustion engine 10 are mounted. But there is. In the following description, the first hydraulic control means and the second hydraulic control means of the present invention are described as being shared by the hydraulic control device 130, but each may be provided separately.

  As shown in FIG. 4, the hydraulic control device 130 supplies hydraulic oil to the primary hydraulic chamber 55, the secondary hydraulic chamber 64, the drive hydraulic chamber 81, and the like, and supplies the hydraulic pressure, the hydraulic oil supply flow rate, and the hydraulic oil discharge flow rate. Is also used to control the gear ratio of the belt type continuously variable transmission 1-1. In the figure, a hydraulic oil supply portion excluding the primary hydraulic chamber 55, the secondary hydraulic chamber 64, and the drive hydraulic chamber 81 (the above-described hydraulic oil supply portion and the transaxle 20 such as the belt type continuously variable transmission 1-1). The illustration of a lubrication part (for example, a stationary part having a sliding part between the movable parts and a movable part or a movable part having a sliding part between the stationary parts) is omitted. As shown in FIG. 4, the hydraulic 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, and a drive hydraulic chamber control device. 136 and a secondary hydraulic chamber control device 137.

  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 housing 21. 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 oil pump 132 is connected to the cancel chamber 84 via, for example, an oil passage R1 and a branch oil passage R11. Here, the oil pump 132 passes through the oil passage R1, the branch oil passage R11, the second communication passage 23d, the space portion T4, the shaft side communication passage 51e, the space portion T5, the cover side communication passage 57a, and the partition wall side communication passage 54g. Connected to the cancellation chamber 84. Therefore, hydraulic oil is always supplied from the hydraulic control device 130 to the cancel chamber 84. Although the cancel chamber 84 is connected to the oil pump 132 here, it may be connected to a return passage for returning oil supplied to a lubrication portion (not shown) to the oil pan 131.

  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 Pout of the oil passage R1, which is the input hydraulic pressure, 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 introduced into the second port 135l of the supply side flow control valve 135c, the constant pressure control device 134, and the secondary hydraulic chamber control device 137. 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 an electromagnetic valve (not shown), for example, a linear solenoid valve, that 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 PL of the oil passage R2 and the branch oil passage R21, which are input oil pressures, and sets the output oil pressure from the constant pressure control device 134 to the constant pressure PS. 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 this embodiment, the primary hydraulic chamber control device 135 controls the supply flow rate of hydraulic oil supplied to the primary hydraulic chamber 55 and the discharge flow rate of 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 controls the supply flow rate of the hydraulic oil supplied to the primary hydraulic chamber 55 by the supply side flow rate 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 through 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. 6). 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 same 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. 8). 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. Therefore, 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. 8). That is, the constant pressure PS introduced into the discharge side control valve 135b is introduced into a later-described control hydraulic chamber 135v 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. 6). 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. Here, the third port 135m includes the oil passage R7 and the supply / discharge passage (supply / discharge side main passage 51a, each shaft side communication passage 51c, space portions T1, T2, each partition wall side communication passage 54e, space portion T7, each arrangement. The primary hydraulic chamber 55 is connected via the side communication passage 56b, each valve arrangement passage 56a, the space portion T6, and each opening hole 54i). 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 control device 133 and the second port 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 from the supply-side control valve 135a to the supply-side flow control valve 135c and the hydraulic oil flowing from the line pressure control device 133 to the supply-side flow control valve 135c. 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. Is made to act 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 blocked. The spool elastic member 135q is disposed 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 has a degree of communication between the second port 135l and the third port 135m, that is, with respect to the second port 135l as the movement amount in one direction of the movement direction of the spool 135p increases. The channel cross-sectional area of the channel that communicates with the third 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 present embodiment, the third port 135t includes the branch oil passage R71, the oil passage R7, and the supply / discharge passage (the supply / discharge-side main passage 51a, the shaft-side communication passage 51c, the space portions T1 and T2, and the partition-wall-side communication passages). 54e, space portion T7, each arrangement side communication passage 56b, each valve arrangement passage 56a, space portion T6 and each opening hole 54i), and is connected to the primary hydraulic chamber 55. 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 blocked. The spool elastic member 135x is arranged 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, with respect to the second port 135s as the movement amount in one direction of the movement direction of the spool 135w increases. The channel cross-sectional area of the channel that communicates with the third 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 drive hydraulic chamber hydraulic pressure P <b> 2 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. Here, the drive hydraulic chamber control device 136 includes the drive hydraulic chamber 81 via the oil passage R8, the first communication passage 23b, the drive side main passage 51b, the shaft side communication passage 51d, the space T3, and the partition wall side communication passage 54f. Connected with. The drive hydraulic chamber control device 136 is provided with at least a control valve (not shown). The drive hydraulic chamber control device 136 is electrically connected to the ECU 140 and controls a control valve by a control signal from the ECU 140. When the control valve is controlled and the branch oil passage R32 and the oil passage R8 communicate with each other, the drive hydraulic chamber control device 136 introduces the constant pressure PS introduced into the drive hydraulic chamber control device 136 into the drive hydraulic chamber 81. The drive hydraulic chamber hydraulic pressure P2 of the drive hydraulic chamber 81 becomes the constant pressure PS. On the other hand, when the control valve is controlled and the communication between the branch oil path R32 and the oil path R8 is blocked, for example, when the oil path R8 is released to the outside, the drive hydraulic chamber control device 136 controls the drive hydraulic chamber 81. The drive hydraulic chamber hydraulic pressure P2 becomes atmospheric pressure. Here, the constant pressure PS means that the hydraulic oil supply / discharge valve 70 is opened by the drive hydraulic chamber hydraulic pressure P2 of the drive hydraulic chamber 81 at least when the drive hydraulic chamber hydraulic pressure P2 of the drive hydraulic chamber 81 becomes the constant pressure PS. It can be more than hydraulic.

  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 present 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.

  ECU 140 is a control means. The ECU 140 is connected to the hydraulic control device 130 and the internal combustion engine 10 and controls the hydraulic control device 130 and the internal combustion engine 10. Therefore, the ECU 140 controls the primary hydraulic chamber control device 135, the drive hydraulic chamber control device 136, and the secondary hydraulic chamber control device 137 according to the control signal output to the hydraulic control device 130, so that the belt type continuously variable transmission is performed. The gear ratio of the machine 1-1 is controlled. That is, the hydraulic control device 130 is forced by the actuator 80 by controlling the primary hydraulic chamber control device 135, the drive hydraulic chamber control device 136, and the secondary hydraulic chamber control device 137 based on a control signal from the ECU 140. The hydraulic oil supply / discharge valve 70 is opened, and the hydraulic oil is supplied to or discharged from the primary hydraulic chamber 55, which is one of the clamping pressure generating hydraulic chambers. The gear ratio of the machine 1-1 is controlled. Further, the ECU 140 controls the output torque of the internal combustion engine 10 by controlling a fuel injection valve, a spark plug, and a throttle valve (not shown) of the internal combustion engine 10 according to a control signal output to the internal combustion engine 10. In the following description, the setting means, the first control means, and the second control means of the present invention are described as being shared by the ECU 140 as the control means, but each may be provided separately. . The basic configuration of the ECU 140 is the same as that of an ECU mounted on a conventional vehicle, and a description thereof will be omitted.

  Further, the ECU 140 is electrically connected to an input rotation speed sensor 150 and an output rotation speed sensor 160.

  The input rotation speed sensor 150 also constitutes a part of the gear ratio detection means. The input rotation speed sensor 150 detects an input rotation speed Nin of a pulley to which driving force from a driving source is input, that is, a primary pulley 50 to which output torque from the internal combustion engine 10 is input. The input 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 input rotation speed sensor 150 is connected to the ECU 140 as shown in FIG. Accordingly, the input rotational speed Nin detected by the input rotational speed sensor 150 is output to the ECU 140. The input rotational speed sensor 150 is not limited to the input rotational speed Nin that is the rotational speed of the primary pulley shaft 51. For example, the input rotational speed sensor 150 detects the engine rotational speed Ne of the internal combustion engine 10 and inputs it from the engine rotational speed Ne. The rotational speed Nin may be calculated.

  The output rotation speed sensor 160 also constitutes a part of the gear ratio detection means. The output rotation speed sensor 160 detects the output rotation speed Nout of the secondary pulley 60 to which the driving force from the drive source input to the primary pulley 50, that is, the output torque of the internal combustion engine 10 is transmitted via the belt 110. is there. In this embodiment, the output rotation speed sensor 160 detects the rotation speed of the secondary pulley shaft 61 of the secondary pulley 60, and sets the rotation speed of the secondary pulley shaft 61 as the output rotation speed Nout. The output rotation speed sensor 160 is connected to the ECU 140 as shown in FIG. Therefore, the output rotation speed Nout detected by the output rotation speed sensor 160 is output to the ECU 140.

  Here, the ratio between the input rotational speed Nin (in other words, input rotational speed) detected by the input rotational speed sensor 150 and the output rotational speed Nout (in other words, output rotational speed) detected by the output rotational speed sensor 160. Is the gear ratio of the belt type continuously variable transmission 1-1. That is, the input rotation speed sensor 150 and the output rotation speed sensor 160 detect the gear ratio. Therefore, the ECU 140 receives the input speed ratio Nin detected by the input speed sensor 150 and the output speed Nout detected by the output speed sensor 160, so that the detected gear ratio is input. Become.

  Next, the operation of the belt type continuously variable transmission 1-1 according to the present 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 with hydraulic oil supplied from the hydraulic control device 130, and The advance 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 drive position by a shift position device (not shown) provided in the vehicle, the ECU 140 turns off the forward clutch 42 and turns on the reverse brake 43 by the hydraulic oil supplied from the hydraulic control device 130. 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. 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 speed of the vehicle and the accelerator opening of the driver. ), The gear ratio of the belt-type continuously variable transmission 1-1 is controlled via the hydraulic control device 130 so that the operation state of the internal combustion engine 10 is optimized. Control of the gear ratio of the belt type continuously variable transmission 1-1 includes changing the gear ratio and fixing the gear ratio. 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. Note that the control of the gear ratio using the hydraulic control device 130 is performed every control cycle.

  To change the gear ratio, the hydraulic oil supply / discharge valve 70 is opened, the hydraulic oil is supplied from the hydraulic control device 130 to the primary hydraulic chamber 55, or the primary pulley 50 is supplied from the primary hydraulic chamber 55 via the hydraulic control device 130. By discharging the hydraulic oil to the outside, 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 primary groove 110a. The width is adjusted. 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 and the rotation speed of the secondary pulley 60, is controlled steplessly (continuously). The gear ratio is fixed by closing the hydraulic oil supply / discharge valve 70 and holding the working oil in the primary hydraulic chamber 55.

  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.

  The change in the gear ratio includes an upshift, that is, a gear ratio decrease change that decreases the gear ratio, and a downshift, that is, a gear ratio increase change that increases the gear ratio. The ECU 140 performs gear ratio decrease control or gear ratio increase control when changing the gear ratio. Each will be described below.

  Here, FIG. 5 is a cross-sectional view of the main part of the primary pulley when the gear ratio of the belt-type continuously variable transmission according to the first embodiment of the present invention is reduced (during upshift), and FIG. 6 is the first embodiment of the present invention. FIG. 7 is a diagram showing the operation of the hydraulic control device when the gear ratio of the belt-type continuously variable transmission according to the present invention is decreasing (during upshift), and FIG. FIG. 8 is a cross-sectional view of the main part of the primary pulley at the time of downshift (during downshift), and FIG. FIG.

  The gear ratio reduction control (upshift control) by the ECU 140 is performed by supplying hydraulic oil from the hydraulic control device 130 to the primary hydraulic chamber 55 and sliding (moving) the primary movable sheave 53 toward the primary fixed sheave side. As shown in FIG. 5, the hydraulic oil supply / discharge valve 70 is opened by an actuator 80, and hydraulic oil is supplied from the hydraulic control device 130 to the primary hydraulic chamber 55. Specifically, ECU 140 calculates a reduction gear ratio and a transmission speed, and outputs a control signal based on these to hydraulic control device 130.

  In the gear ratio reduction control, the drive hydraulic chamber control device 136 is controlled by the ECU 140. Therefore, when the drive hydraulic chamber control device 136 is 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 hydraulic pressure P2 of the drive hydraulic chamber 81 is increased. Becomes a constant pressure PS. The actuator 80 generates a differential pressing force obtained by subtracting a piston valve closing direction pressing force acting on the piston 82 by the piston elastic member 83 from a piston valve opening direction pressing force acting on the piston 82 by the driving hydraulic chamber hydraulic pressure P2 of the driving hydraulic chamber 81. The valve body 71 is acted on the valve body 71 of the hydraulic oil supply / discharge valve 70 as a valve body opening direction pressing force. Here, as described above, when the drive hydraulic chamber hydraulic pressure P2 of the drive hydraulic chamber 81 reaches the constant pressure PS, the actuator 80 opens the hydraulic oil supply / discharge valve 70 by the drive hydraulic chamber hydraulic pressure P2 of the drive hydraulic chamber 81. Therefore, the valve body opening direction pressing force exceeds the valve body closing direction pressing force. Therefore, as shown in FIG. 5, the hydraulic oil supply / discharge valve 70 is opened by moving the valve body 71 in the valve opening direction with respect to the primary partition wall 54 by the actuator 80.

  In the gear ratio reduction control, the supply-side control valve 135a of the primary hydraulic chamber control device 135 is duty-controlled by the ECU 140, whereby the supply flow control of the hydraulic oil to the primary hydraulic chamber 55 is performed by the supply-side flow control valve 135c. I do. When duty control is performed by the ECU 140, the supply-side control valve 135a repeats ON and OFF, as shown in FIG. 6, and adjusts the control hydraulic pressure in the control hydraulic chamber 135o of the supply-side flow rate control valve 135c to a predetermined pressure during supply. 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.

  In the gear ratio reduction control, the discharge side control valve 135b of the primary hydraulic chamber control device 135 is duty-controlled by the ECU 140, so that the discharge flow control of the hydraulic oil from the primary hydraulic chamber 55 by the discharge side flow control valve 135d is performed. I do. 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, the hydraulic oil supply / discharge valve 70 is 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 introduced at a pressure adjusted from the line pressure PL) is controlled by the supply-side flow rate control valve 135c to a supply flow rate based on the reduction gear ratio and the shift speed, as shown by an arrow B in FIG. Then, it flows into the supply / discharge side main passage 51a of the supply / discharge route through the oil passage R7. The hydraulic fluid that has flowed into the supply / discharge side main passage 51a flows from the supply / discharge side main passage 51a to the shaft side communication passages 51c, the space portions T1, T2, the partition wall side communication passages 54e, the space portion T7, and the arrangement side communication passages 56b. The primary hydraulic chamber 55 is supplied through the valve arrangement passages 56a, the space T6, and the opening holes 54i. Then, the hydraulic oil P1 in the primary hydraulic chamber 55 is increased by the hydraulic oil supplied via the 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 speed ratio is reduced to the reduced speed ratio, and an upshift is performed.

  In the gear ratio increase control (downshift control) by the ECU 140, hydraulic oil is discharged from the primary hydraulic chamber 55 via the hydraulic control device 130, and the primary movable sheave 53 is slid (moved) to the side opposite to the primary fixed sheave side. ). As shown in FIG. 7, the hydraulic oil supply / discharge valve 70 is opened, and the hydraulic oil is discharged from the primary hydraulic chamber 55. Specifically, ECU 140 calculates an increase gear ratio and a shift speed, and outputs a control signal based on these to hydraulic control device 130.

  In the gear ratio increase control, the drive hydraulic chamber control device 136 is controlled by the ECU 140 as in the gear ratio decrease control. Therefore, as shown in FIG. 7, the hydraulic oil supply / discharge valve 70 is opened by the actuator 80 moving the valve body 71 in the valve opening direction with respect to the primary partition wall 54.

  Further, in the gear ratio increase control, as shown in FIG. 8, the supply-side control valve 135a is kept OFF by the ECU 140, the supply-side flow rate control valve 135c is kept closed, and the hydraulic oil is supplied to the primary hydraulic chamber 55. The supply flow rate becomes zero.

  In the gear ratio increase control, the discharge-side control valve 135b is repeatedly turned ON and OFF by the ECU 140, and the control hydraulic pressure in the control hydraulic chamber 135v is adjusted to a predetermined pressure during 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 the discharge flow rate based on the reduction gear ratio and the shift speed.

  As described above, the hydraulic oil supply / discharge valve 70 is opened by the actuator 80. Accordingly, the hydraulic oil in the primary hydraulic chamber 55 is communicated from the primary hydraulic chamber 55 to each opening hole 54i, the space T6, each valve arrangement passage 56a, each arrangement side communication from the primary hydraulic chamber 55, as indicated by an arrow D in FIG. It flows into the supply / discharge side main passage 51a through the passage 56b, the space portion T7, the partition wall side communication passages 54e, the space portions T2 and T1, and the shaft side communication passages 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, when the hydraulic oil is discharged from the primary hydraulic chamber 55 via the hydraulic oil supply / discharge valve 70, the primary hydraulic pressure P1 of the primary hydraulic chamber 55 is decreased, 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. As a result, 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 gear ratio is increased to the increased gear ratio, and a downshift is performed.

  The speed ratio is fixed without supplying hydraulic oil to the primary hydraulic chamber 55 and without discharging hydraulic oil from the primary hydraulic chamber 55, and making the position of the primary movable sheave 53 in the axial direction relative to the primary fixed sheave 52 constant, This is performed by restricting the movement of the primary movable sheave 53 with respect to the primary fixed sheave 52. The ECU 140 performs gear ratio fixing control when fixing the gear ratio. Note that the gear ratio fixing control is when the ECU 140 determines that there is no need to change the gear ratio significantly, such as when the running state of the vehicle is stable.

  In the gear ratio fixed control by the ECU 140, as shown in FIG. 2, the hydraulic oil supply / discharge valve 70 is closed, and the hydraulic oil is supplied to the primary hydraulic chamber 55 via the hydraulic oil supply / discharge valve 70, and the hydraulic oil is supplied / discharged. The hydraulic oil is prevented from being discharged from the primary hydraulic chamber 55 via the valve 70, and the gear ratio is maintained at the fixed gear ratio. Specifically, ECU 140 outputs a control signal for maintaining the gear ratio at a fixed gear ratio to hydraulic control device 130.

  In the gear ratio fixed control, the drive hydraulic chamber control device 136 is controlled by the ECU 140. Accordingly, the drive hydraulic chamber 81 is released to the atmospheric pressure, and the drive hydraulic chamber hydraulic pressure P2 of the drive hydraulic chamber 81 becomes almost atmospheric pressure. Thereby, only the piston valve closing direction pressing force by the piston elastic member 83 acts on the pressure receiving member 82a of the piston 82, so that the pressure receiving member 82a slides in the other direction, that is, the valve closing direction. As a result, the valve body valve opening direction pressing force does not act on the valve body 71 of the hydraulic oil supply / discharge valve 70, and only the valve body valve closing direction pressing force acts, and the valve body 71 moves in the valve closing direction. It moves and contacts the valve seat surface 72, and the hydraulic oil supply / discharge valve 70 is closed.

  Further, in the gear ratio fixed control, the line pressure control device 133 is controlled by the ECU 140, and the line pressure PL is lowered. In the present embodiment, in the gear ratio fixed control, the line pressure control device 133 regulates the line pressure PL by the ECU 140 to be lower than the line pressure PL in the gear ratio reduction control.

  In the gear ratio fixed control, as shown in FIG. 4, the supply-side control valve 135 a is maintained almost OFF by the ECU 140, and the supply-side flow rate control valve 135 c is kept almost closed to the primary hydraulic chamber 55. The hydraulic oil supply flow rate is almost zero. Accordingly, the hydraulic pressure of the upstream hydraulic oil, which is the hydraulic oil upstream of the valve body 71 of the hydraulic oil supply / discharge valve 70 in the supply / discharge path (opposite the primary hydraulic chamber 55 side across the hydraulic oil supply / discharge valve 70). (Hereinafter, simply referred to as “supply pressure Pin”) becomes lower than the primary hydraulic pressure P1 of the primary hydraulic chamber 55.

  Further, in the gear ratio fixed control, the discharge side control valve 135b is kept OFF by the ECU 140, the discharge side flow control valve 135d is kept closed, and the discharge flow rate of the 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 the hydraulic oil supply / discharge valve 70 is prohibited.

  As described above, when the transmission ratio is fixed when the hydraulic oil supply / discharge valve 70 is closed, the supply of hydraulic oil to the primary hydraulic chamber 55 and the discharge of hydraulic oil from the primary hydraulic chamber 55 are prohibited. The hydraulic oil in the primary hydraulic chamber 55 is held. Here, since the belt tension of the belt 110 changes even when the 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 The position in the direction may change. However, as described above, since the hydraulic oil is held in the primary hydraulic chamber 55, when the position of the primary movable sheave 53 with respect to the primary fixed sheave 52 in the axial direction is changed, the primary hydraulic chamber 55 is changed. However, the position of the primary movable sheave 53 in the axial direction with respect to the primary fixed sheave 52 is kept 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 an increase in driving loss of the oil pump 132 can be suppressed. it can.

  Here, in the belt-type continuously variable transmission 1-1 of this embodiment, the ECU 140 closes the hydraulic oil supply / discharge valve 70 in the gear ratio fixed release control when the gear ratio is changed from the gear ratio fixed state. By setting the period to be longer than the valve opening response period, the occurrence of shock when the hydraulic oil supply / discharge valve 70 is closed is suppressed, and drivability is improved.

  FIG. 9 is a time chart for explaining an example of the control of the belt type continuously variable transmission according to the first embodiment of the present invention. The vertical axis is supplied to the drive hydraulic chamber hydraulic pressure P2 of the drive hydraulic chamber 81 and the primary hydraulic chamber 55. The hydraulic oil supply pressure Pin, the transmission gear ratio γ, and the horizontal axis are time axes. In addition, although this figure has illustrated as an example the case where it transfers to gear ratio reduction control (upshift control) from a gear ratio fixed state, it transfers not only to this but to gear ratio increase control (downshift control). It may be the case.

  Here, as shown in FIG. 9, the valve opening response period X <b> 1 of the hydraulic oil supply / discharge valve 70 is a period during which the hydraulic oil supply / discharge valve 70 is shifted from the closed state to the open state by the actuator 80. That is, during the valve opening response period X1 of the hydraulic oil supply / discharge valve 70, the hydraulic oil supply / discharge valve in which the drive hydraulic chamber hydraulic pressure P2 of the drive hydraulic chamber 81 is set to the atmospheric pressure and the valve element 71 is in contact with the valve seat surface 72. In the closed valve state of 70, the drive hydraulic chamber control device 136 is controlled by a control signal from the ECU 140, and the constant pressure PS introduced into the drive hydraulic chamber control device 136 is started to be introduced into the drive hydraulic chamber 81. From the valve operation start time t11, the drive hydraulic chamber hydraulic pressure P2 of the drive hydraulic chamber 81 becomes the constant pressure PS, and the valve opening operation is completed in which the hydraulic oil supply / discharge valve 70 in which the valve element 71 is separated from the valve seat surface 72 is opened. This is the period until time t12.

  On the other hand, as shown in FIG. 9, the valve closing response period X2 of the hydraulic oil supply / discharge valve 70 is a period during which the hydraulic oil supply / discharge valve 70 is shifted from the open state to the closed state by the actuator 80. That is, during the valve closing response period X2 of the hydraulic oil supply / discharge valve 70, the hydraulic oil supply / discharge in which the drive hydraulic chamber hydraulic pressure P2 of the drive hydraulic chamber 81 is set to a constant pressure PS and the valve element 71 is separated from the valve seat surface 72. In the open state of the valve 70, the drive hydraulic chamber control device 136 is controlled by a control signal from the ECU 140, and the introduction of the constant pressure PS introduced into the drive hydraulic chamber control device 136 into the drive hydraulic chamber 81 is stopped. When the valve closing operation start time t14 is started, the drive hydraulic chamber hydraulic pressure P2 of the drive hydraulic chamber 81 becomes atmospheric pressure, and the hydraulic oil supply / discharge valve 70 in which the valve element 71 contacts the valve seat surface 72 is closed. This is the period until the operation end time t15.

  Then, the ECU 140 controls the hydraulic control device 130 to control the drive hydraulic chamber hydraulic pressure P2 of the drive hydraulic chamber 81 of the actuator 80, thereby setting the valve closing response period X2 of the hydraulic oil supply / discharge valve 70 to the valve opening response period. Control for a period longer than X1.

  Thus, when the hydraulic oil supply / discharge valve 70 is closed, the valve closing response period X2 is set to a relatively long period, and the drive hydraulic chamber hydraulic pressure P2 is gradually reduced. The moving speed of the valve body 71 when contacting the seat surface 72 can be reduced. For this reason, when the hydraulic oil supply / discharge valve 70 is closed, the speed of the valve body 71 when the valve body 71 contacts the valve seat surface 72 is reduced, so that the supply / discharge path communicating with the primary hydraulic chamber 55 is reduced. Since it is possible to prevent sudden closure and to gradually close this supply / discharge path, it is possible to suppress the occurrence of surge pressure in the hydraulic oil. As a result, the occurrence of shock when the hydraulic oil supply / discharge valve 70 is closed can be suppressed, drivability can be improved, and durability of the belt 110 can be improved. Further, when the valve body 71 contacts the valve seat surface 72 by reducing the speed of the valve body 71 when the valve body 71 contacts the valve seat surface 72 when the hydraulic oil supply / discharge valve 70 is closed. Can also reduce the impact generated. As a result, the occurrence of shock when the hydraulic oil supply / discharge valve 70 is closed can be suppressed, drivability can be improved, and the wear amount of the contact portion between the valve body 71 and the valve seat surface 72 can be reduced. The durability of the hydraulic oil supply / discharge valve 70 can be improved.

  Further, in the belt-type continuously variable transmission 1-1 of the present embodiment, the ECU 140 controls the hydraulic control device 130 to keep the hydraulic pressure in the supply / discharge path constant during the valve opening response period X1 and the valve closing response period X2. Execute control. Here, as described above, the supply / discharge path includes the supply / discharge side main passage 51a, the shaft side communication passages 51c, the space portions T1 and T2, the partition wall side communication passages 54e, the space portion T7, and the arrangement side communication passages 56b. The hydraulic pressure of the supply / discharge path is, in other words, the supply pressure Pin of hydraulic oil supplied to the primary hydraulic chamber 55.

  When the ECU 140 determines that it is necessary to perform the valve opening operation of the hydraulic oil supply / discharge valve 70 in order to change the gear ratio from the gear ratio fixed state, the ECU 140 corresponds to the fixed gear ratio γ (T) in the gear ratio fixed state. The primary hydraulic pressure P1 of the primary hydraulic chamber 55 is calculated. The ECU 140 determines the hydraulic oil supply / discharge valve 70 based on, for example, the engine torque (output torque) generated by the internal combustion engine 10, the input rotational speed detected by the input rotational speed sensor 150, the hydraulic pressure of the secondary hydraulic chamber 64, and the gear ratio. When the valve is closed, the hydraulic pressure P1 confined in the primary hydraulic chamber 55 may be estimated and calculated, or the primary hydraulic pressure P1 may be detected by a hydraulic sensor.

  Then, the ECU 140 controls the hydraulic control device 130 at a time t10 before the valve opening operation start time t11, and supplies the supply / discharge path (supply / discharge side main) before starting the valve opening operation of the hydraulic oil supply / discharge valve 70. The passage 51a, the shaft-side communication passages 51c, the space portions T1, T2, the partition wall-side communication passages 54e, the space portion T7, the arrangement-side communication passages 56b, the valve arrangement passages 56a, the space portions T6, and the opening holes 54i). The hydraulic pressure is increased, that is, the hydraulic oil supply pressure Pin supplied to the primary hydraulic chamber 55 is increased. At this time, the hydraulic control device 130, for example, supplies the primary oil pressure P1 (that is, the fixed gear ratio γ (T) confined in the primary oil pressure chamber 55 when the hydraulic oil supply / discharge valve 70 is closed. ) To the supply pressure Pin (T) in the vicinity of the primary oil pressure P1). As a result, the differential pressure between the primary hydraulic pressure P1 confined in the primary hydraulic chamber 55 and the supply pressure Pin decreases, and the primary hydraulic pressure P1 in the primary hydraulic chamber 55 suddenly increases when the hydraulic oil supply / discharge valve 70 opens. Fluctuation can be prevented. As a result, the shock when the hydraulic oil supply / discharge valve 70 is opened can be reduced, and the gear ratio can be controlled appropriately.

  Then, at time t10, the ECU 140 controls the hydraulic control device 130 to increase the supply pressure Pin to the supply pressure Pin (T) and keep the supply pressure Pin constant at the supply pressure Pin (T). When the supply pressure Pin is kept constant at the supply pressure Pin (T), the ECU 140 then controls the hydraulic control device 130 to open the constant pressure PS to the drive hydraulic chamber 81 at the valve opening operation start time t11. The opening of the hydraulic oil supply / discharge valve 70 is started by starting the introduction.

  Then, at the valve opening operation end time t12, the ECU 140 determines that the drive hydraulic chamber hydraulic pressure P2 of the drive hydraulic chamber 81 becomes a constant pressure PS, the valve body 71 is completely separated from the valve seat surface 72, and the hydraulic oil supply / discharge valve 70 is When the valve is fully opened, the hydraulic pressure control device 130 is controlled to increase the hydraulic pressure in the supply / discharge path again after the opening operation of the hydraulic oil supply / discharge valve 70 is completed, that is, the hydraulic oil supplied to the primary hydraulic chamber 55 The supply pressure Pin is increased again. At this time, for example, the hydraulic control device 130 supplies the supply pressure Pin (T + 1) by further adding α to the supply pressure Pin (T + 1) corresponding to the primary oil pressure P1 at the target speed ratio γ (T + 1) after the shift. Increase to + α. Here, the hydraulic pressure control device 130 raises the supply pressure Pin to the supply pressure Pin (T + 1) + α obtained by further adding α to the supply pressure Pin (T + 1) corresponding to the target speed ratio γ (T + 1). The responsiveness of the primary hydraulic pressure P1 to the increase in Pin, that is, the responsiveness of the speed ratio γ can be improved.

  When the actual gear ratio γ is close to the target gear ratio γ (T + 1), the ECU 140 controls the hydraulic control device 130 to decrease the supply pressure Pin by α to correspond to the target gear ratio γ (T + 1). Reduce to supply pressure Pin (T + 1). Note that when the supply pressure Pin is decreased by α, the ECU 140 may gradually decrease the supply pressure Pin according to the response of the speed ratio γ.

  Further, at time t13 prior to the valve closing operation start time t14, the ECU 140 keeps the actual transmission ratio γ near the target transmission ratio γ (T + 1) and the supply pressure Pin (T + 1) constant. Then, at the valve closing operation start time t14, the hydraulic control device 130 is controlled to start stopping the introduction of the constant pressure PS into the drive hydraulic chamber 81, thereby closing the hydraulic oil supply / discharge valve 70. To start. Then, at the valve closing operation end time t15, the ECU 140 causes the drive hydraulic chamber hydraulic pressure P2 of the drive hydraulic chamber 81 to become atmospheric pressure, so that the valve element 71 completely contacts the valve seat surface 72 and the hydraulic oil supply / discharge valve 70 is completely set. When the valve is closed, the hydraulic control device 130 is controlled to reduce the hydraulic pressure in the supply / discharge path again after the closing operation of the hydraulic oil supply / discharge valve 70 is completed, that is, supply of the hydraulic oil supplied to the primary hydraulic chamber 55 The pressure Pin is decreased again.

  As a result, the ECU 140 controls the hydraulic control device 130 to execute the control to keep the hydraulic pressure of the supply / discharge path, that is, the supply pressure Pin, constant during the valve opening response period X1 and the valve closing response period X2. The primary hydraulic pressure P1 of the primary hydraulic chamber 55 fluctuates rapidly during the valve opening response period X1 when the oil supply / discharge valve 70 is opened and during the valve closing response period X2 when the hydraulic oil supply / discharge valve 70 is closed. Can be prevented. As a result, the shock during the valve opening response period X1 and the valve closing response period X2 can be reduced, and drivability can be improved.

  According to the belt-type continuously variable transmission 1-1 according to the embodiment of the present invention described above, the primary pulley 50 and the secondary pulley 60 as two pulleys, and the primary pulley 50 and the secondary pulley 60 are wound around. A primary hydraulic chamber 55 and a secondary hydraulic chamber 64 that are formed in each of the belt 110 that transmits output torque from the internal combustion engine 10, the primary pulley 50, and the secondary pulley 60, and generates belt clamping pressure against the belt 110 by hydraulic pressure; A supply / discharge path (supply / discharge-side main passage 51a, each shaft-side communication passage 51c, space for supplying hydraulic oil to the primary hydraulic chamber 55 as one clamping pressure generating hydraulic chamber or discharging the hydraulic oil from the primary hydraulic chamber 55 Portions T1, T2, partition wall side communication passages 54e, space portion T7, arrangement side communication passages 56 When the hydraulic fluid is supplied to the primary hydraulic chamber 55 or discharged from the primary hydraulic chamber 55, provided in each valve arrangement passage 56a, the space T6 and each opening hole 54i) and the supply / discharge path. The hydraulic oil supply / discharge valve 70 that rotates integrally with the primary pulley 50 as one pulley, and the actuator that controls the opening / closing of the hydraulic oil supply / discharge valve 70 is opened. 80, and a valve opening response period X1 which is a period for shifting the valve closing response period X2, which is a period for shifting the hydraulic oil supply / discharge valve 70 from the valve opening state to the valve closing state by the actuator 80, from the valve closing state to the valve opening state. ECU 140 set to a longer period.

  Therefore, when the hydraulic oil supply / discharge valve 70 is closed, the valve closing response period X2 is set to a relatively long period, so that the valve body 71 when the valve body 71 contacts the valve seat surface 72 is set. Since the moving speed can be reduced, it is possible to suppress the occurrence of a shock when the hydraulic oil supply / discharge valve 70 is closed, thereby improving drivability. Moreover, since the moving speed of the valve body 71 when the valve body 71 contacts the valve seat surface 72 can be reduced, the durability of the belt 110 and the durability of the hydraulic oil supply / discharge valve 70 can be improved. .

  Furthermore, according to the belt-type continuously variable transmission 1-1 according to the embodiment of the present invention described above, the hydraulic pressure of the supply / discharge path, that is, the supply pressure Pin, during the valve opening response period X1 or the valve closing response period X2. ECU 140 is executed to execute control to keep the value constant. Therefore, the ECU 140 controls the hydraulic control device 130 to execute control to keep the supply pressure Pin constant during the valve opening response period X1 and the valve closing response period X2, so that the hydraulic oil supply / discharge valve 70 opens. The primary hydraulic pressure P1 of the primary hydraulic chamber 55 can be prevented from abruptly fluctuating during the valve opening response period X1 and during the valve closing response period X2 when the hydraulic oil supply / discharge valve 70 is closed. Shock can be reduced and drivability can be improved.

(Embodiment 2)
FIG. 10 is a time chart for explaining an example of the control of the belt type continuously variable transmission according to the second embodiment of the present invention. The belt-type continuously variable transmission according to the second embodiment has substantially the same configuration as that of the belt-type continuously variable transmission according to the first embodiment, but the control when supplying hydraulic oil to one clamping pressure generating hydraulic chamber is performed. This is different from the belt-type continuously variable transmission according to the first embodiment. In addition, about the structure, effect | action, and effect which are common in embodiment mentioned above, while overlapping description is abbreviate | omitted as much as possible, the same code | symbol is attached | subjected. For the configuration of the main part, refer to FIGS.

  Here, in the conventional belt-type continuously variable transmission, further improvement in shift response is desired. Accordingly, when the belt type continuously variable transmission 1-2 according to the present embodiment supplies hydraulic oil to the primary hydraulic chamber 55 serving as one clamping pressure generating hydraulic chamber, here, the gear ratio reduction control (upshift control) is performed. ), The ECU 140 controls the hydraulic control device 130 to supply and discharge paths (supply / discharge side main passage 51a, shaft-side communication passages 51c, space portions T1 and T2, partition wall side communication passages 54e, space portion T7, and arrangements. The hydraulic pressure of the side communication passage 56b, each valve arrangement passage 56a, the space T6 and each opening hole 54i), that is, the supply pressure Pin, is increased, and the input rotational speed sensor 150 and the output rotational speed sensor 160 are used as a gear ratio detection means. After the change in the gear ratio is detected, the hydraulic pressure in the drive hydraulic chamber 81 is increased by the hydraulic control device 130, thereby appropriately improving the shift response and improving the drivability. To have.

  That is, when ECU 140 determines that it is necessary to perform the valve opening operation of hydraulic oil supply / discharge valve 70 in order to change the gear ratio from the fixed gear ratio state to the decreasing side, ECU 140 is prior to valve opening operation start time t21. At time t20, the hydraulic control device 130 is controlled so that the supply / discharge path (supply / discharge side main passage 51a, each shaft side communication passage 51c, space portions T1, T2 before the opening operation of the hydraulic oil supply / discharge valve 70 is started). The hydraulic pressure of each partition wall side communication passage 54e, space T7, each arrangement side communication passage 56b, each valve arrangement passage 56a, space T6 and each opening hole 54i) is increased, that is, supplied to the primary hydraulic chamber 55. The hydraulic oil supply pressure Pin is increased. At this time, the hydraulic control device 130 of the present embodiment, for example, supplies the supply pressure Pin to the supply pressure Pin (T + 1) corresponding to the primary oil pressure P1 at the target gear ratio γ (T + 1) after the shift, and further adds α. Increase to Pin (T + 1) + α.

  Then, the hydraulic pressure in the supply / discharge path, that is, the supply pressure Pin (T + 1) + α acts on the valve body 71 as the valve body opening direction pressing force, and the valve body opening direction pressing force by the supply pressure Pin (T + 1) + α is Body closing direction pressing force (elastic member pressing force acting on the valve body 71 by the valve closing biasing force generated by the valve body elastic member 73 and the primary hydraulic pressure P1 of the primary hydraulic chamber 55 acting on the valve body 71 in the valve closing direction. When the hydraulic oil closing direction pressing force is exceeded, the valve element 71 is separated from the valve seat surface 72, and the hydraulic oil supply / discharge valve 70 is gradually opened. That is, at time t20 prior to the valve opening operation start time t21, the ECU 140 controls the hydraulic control device 130 to execute control for increasing the supply pressure Pin to the supply pressure Pin (T + 1) + α, thereby opening the valve. At the operation start time t21, the ECU 140 controls the hydraulic control device 130 to start introduction of the constant pressure PS into the drive hydraulic chamber 81, and the differential pressing force corresponding to the drive hydraulic chamber hydraulic pressure P2 is applied to the valve body via the piston 82. Before acting on the valve body 71 as the valve opening direction pressing force, the supply pressure Pin (T + 1) + α acts on the valve body 71 as the valve body opening direction pressing force, and the valve body 71 moves away from the valve seat surface 72, The hydraulic oil supply / discharge valve 70 is gradually opened. As a result, hydraulic oil is supplied to the primary hydraulic chamber 55, the primary hydraulic pressure P1 gradually increases, and the speed ratio γ gradually decreases.

  Then, the ECU 140 controls the hydraulic control device 130 to increase the supply pressure Pin to the supply pressure Pin (T + 1) + α, and keep the supply pressure Pin constant at the supply pressure Pin (T + 1) + α, at time tA. After the change of the transmission gear ratio is detected by the input rotation speed sensor 150 and the output rotation speed sensor 160, the hydraulic pressure control device 130 is controlled at the valve opening operation start time t21 to transfer the constant pressure PS to the drive hydraulic chamber 81. Start installation. When the introduction of the constant pressure PS into the drive hydraulic chamber 81 is started and the differential pressing force corresponding to the drive hydraulic chamber hydraulic pressure P2 acts on the valve body 71 as the valve body opening direction pressing force via the piston 82, the valve body 71 The separation speed from the valve seat surface 72 is accelerated, the primary hydraulic pressure P1 rises at a stretch, the transmission speed increases, and the hydraulic oil supply / discharge valve 70 is completely opened at the valve opening operation end time t22.

  When the actual gear ratio γ is close to the target gear ratio γ (T + 1), the ECU 140 controls the hydraulic control device 130 to decrease the supply pressure Pin by α to correspond to the target gear ratio γ (T + 1). Reduce to supply pressure Pin (T + 1).

  At time t23 prior to the valve closing operation start time t24, the ECU 140 has the actual speed ratio γ near the target speed ratio γ (T + 1) and the supply pressure Pin is kept constant at the supply pressure Pin (T + 1). Thereafter, at the valve closing operation start time t24, the hydraulic control device 130 is controlled to stop the introduction of the constant pressure PS into the drive hydraulic chamber 81, thereby starting the closing of the hydraulic oil supply / discharge valve 70. To do. Then, at the valve closing operation end time t25, the ECU 140 causes the drive hydraulic chamber hydraulic pressure P2 of the drive hydraulic chamber 81 to become atmospheric pressure, the valve body 71 completely contacts the valve seat surface 72, and the hydraulic oil supply / discharge valve 70 is completely set. When the valve is closed, the hydraulic control device 130 is controlled to decrease the hydraulic pressure in the supply / discharge path after the closing operation of the hydraulic oil supply / discharge valve 70 is completed, that is, the supply pressure of the hydraulic oil supplied to the primary hydraulic chamber 55 Decrease Pin.

  As a result, when hydraulic oil is supplied to the primary hydraulic chamber 55, the ECU 140 controls the hydraulic control device 130 to increase the supply pressure Pin, and the change of the gear ratio is caused by the input rotation speed sensor 150 and the output rotation speed sensor 160. After the detection, the hydraulic pressure of the drive hydraulic chamber 81 is increased by the hydraulic control device 130. Therefore, before the hydraulic pressure of the drive hydraulic chamber 81 is increased, the supply pressure Pin acts on the valve body 71 to supply and discharge hydraulic oil. Since the valve 70 is gradually opened and the primary hydraulic pressure P1 is gradually increased and the shift is started gradually, the shift response can be improved. Then, after the supply pressure Pin acts on the valve body 71 and the shift is started, the hydraulic control device 130 increases the hydraulic pressure of the drive hydraulic chamber 81, and the differential pressing force corresponding to the drive hydraulic chamber hydraulic pressure P <b> 2 passes through the piston 82. By acting on the valve body 71 as the valve body opening direction pressing force, the valve opening operation of the hydraulic oil supply / discharge valve 70 is accelerated, and the primary hydraulic pressure P1 rises at a stretch and the speed change speed increases. The period can be shortened. As a result, drivability can be improved. At this time, the ECU 140 increases the hydraulic pressure of the drive hydraulic chamber 81 by the hydraulic control device 130 after the change of the gear ratio is detected by the input rotation speed sensor 150 and the output rotation speed sensor 160. It is possible to reliably prevent the backflow of the hydraulic oil that may be generated when the chamber oil pressure P2 rises before the supply pressure Pin. Therefore, it is possible to improve the shift response and shorten the shift period while reliably preventing backflow of the hydraulic oil, and as a result, it is possible to improve drivability.

  According to the belt type continuously variable transmission 1-2 according to the embodiment of the present invention described above, the valve closing response period X2 is set to a relatively long period when the hydraulic oil supply / discharge valve 70 is closed. Therefore, since the moving speed of the valve body 71 when the valve body 71 contacts the valve seat surface 72 can be reduced, the occurrence of a shock when the hydraulic oil supply / discharge valve 70 is closed is suppressed. Therefore, drivability can be improved. Moreover, since the moving speed of the valve body 71 when the valve body 71 contacts the valve seat surface 72 can be reduced, the durability of the belt 110 and the durability of the hydraulic oil supply / discharge valve 70 can be improved. .

  Furthermore, according to the belt-type continuously variable transmission 1-2 according to the embodiment of the present invention described above, the ECU 140 controls the hydraulic control device 130 to supply during the valve opening response period X1 and the valve closing response period X2. Since the control to keep the pressure Pin constant is executed, the valve closing response period X2 during the valve opening response period X1 when the hydraulic oil supply / discharge valve 70 opens and the valve closing response period X2 when the hydraulic oil supply / discharge valve 70 closes. It is possible to prevent the primary hydraulic pressure P1 of the primary hydraulic chamber 55 from fluctuating abruptly, thereby reducing shocks and improving drivability.

  Furthermore, according to the belt-type continuously variable transmission 1-2 according to the embodiment of the present invention described above, the supply / discharge path (the supply / discharge side main passage 51a, the shaft side communication passages 51c, the space portions T1, T2, With respect to the primary hydraulic chamber 55 as one clamping pressure generating hydraulic chamber via each partition wall side communication passage 54e, space portion T7, each arrangement side communication passage 56b, each valve arrangement passage 56a, space portion T6, and each opening hole 54i). A hydraulic control device 130 that controls the supply and discharge of hydraulic fluid and controls the supply and discharge of hydraulic fluid to the drive hydraulic chamber 81 of the actuator 80, an ECU 140 that controls the hydraulic control device 130, and a primary pulley 50 as two pulleys. And an input rotation speed sensor 150 and an output rotation speed sensor 160 that can detect a transmission gear ratio that is a rotation speed ratio of the secondary pulley 60, and supply hydraulic fluid. The discharge valve 70 opens in a direction to supply hydraulic oil to the primary hydraulic chamber 55, and the actuator 80 causes the piston 82 to move in the sliding direction relative to the drive hydraulic chamber 81 by the drive hydraulic chamber hydraulic pressure P 2 of the drive hydraulic chamber 81. When the hydraulic oil is supplied to the primary hydraulic chamber 55, the ECU 140 controls the hydraulic control device 130 to supply the hydraulic pressure in the supply / discharge path, that is, The supply pressure Pin is increased, and after the change of the gear ratio is detected by the input rotation speed sensor 150 and the output rotation speed sensor 160, the hydraulic control device 130 increases the drive hydraulic chamber hydraulic pressure P2 of the drive hydraulic chamber 81.

  That is, according to the belt-type continuously variable transmission 1-2 according to the embodiment of the present invention described above, the primary pulley 50 and the secondary pulley 60 as two pulleys, and the primary pulley 50 and the secondary pulley 60 are wound around. The primary hydraulic chamber 55 and the secondary hydraulic chamber 64 that are formed in each of the belt 110 that transmits the output torque from the internal combustion engine 10, the primary pulley 50, and the secondary pulley 60 and generates belt clamping pressure against the belt 110 by hydraulic pressure. And a supply / discharge path (supply / discharge side main passage 51a, each shaft side communication path 51c) for supplying hydraulic oil to the primary hydraulic chamber 55 as one clamping pressure generating hydraulic chamber or discharging the hydraulic oil from the primary hydraulic chamber 55 , Spaces T1, T2, each partition wall side communication passage 54e, space T7, each arrangement side communication The passage 56b, each valve arrangement passage 56a, the space T6 and each opening hole 54i) are provided in the supply / discharge path, and when supplying the hydraulic oil to the primary hydraulic chamber 55, or the hydraulic oil is discharged from the primary hydraulic chamber 55 The hydraulic oil supply and discharge valve 70 is opened in the direction in which the hydraulic oil is supplied to the primary hydraulic chamber 55 and closed when the transmission gear ratio is fixed, and rotates integrally with the primary pulley 50 as one pulley. And an actuator 80 for controlling the opening and closing of the hydraulic oil supply / discharge valve 70 by sliding the piston 82 in one of the sliding directions with respect to the drive hydraulic chamber 81 by the drive hydraulic chamber hydraulic pressure P2 of the drive hydraulic chamber 81; Oil for controlling supply / discharge of hydraulic oil to / from the primary hydraulic chamber 55 via the supply / discharge path and controlling supply / discharge of hydraulic oil to / from the drive hydraulic chamber 81 When supplying hydraulic oil to the control device 130, the input rotation speed sensor 150 that can detect the transmission gear ratio that is the rotation speed ratio of the primary pulley 50 and the secondary pulley 60, the output rotation speed sensor 160, and the primary hydraulic chamber 55, The hydraulic control device 130 is controlled to increase the hydraulic pressure of the supply / discharge path, that is, the supply pressure Pin, and after the change of the gear ratio is detected by the input rotational speed sensor 150 and the output rotational speed sensor 160, ECU 140 which raises drive oil pressure P2 of drive oil pressure room 81 is provided.

  Therefore, when supplying hydraulic oil to the primary hydraulic chamber 55, the ECU 140 controls the hydraulic control device 130 to increase the supply pressure Pin, and a change in the gear ratio is detected by the input rotation speed sensor 150 and the output rotation speed sensor 160. Then, the hydraulic pressure in the drive hydraulic chamber 81 is increased by the hydraulic control device 130, so that the backflow of the hydraulic oil is surely prevented and the shift response until the shift is started is improved and the shift period is shortened. As a result, drivability can be improved.

  The belt-type continuously variable transmission according to the above-described embodiment of the present invention is not limited to the above-described embodiment, and various modifications can be made within the scope described in the claims.

  As described above, the setting unit, the first control unit, and the second control unit of the present invention have been described as being shared by the ECU 140 as the control unit, but each may be provided separately. Similarly, the first hydraulic control means and the second hydraulic control means of the present invention are described as being shared by the hydraulic control device 130, but each may be provided separately. Furthermore, although the gear ratio detection means has been described as being the input rotation speed sensor 150 and the output rotation speed sensor 160, the present invention is not limited to this, and various known speed ratio detection means may be used.

  In the above description of the second embodiment, the valve closing response period, which is the period during which the hydraulic oil supply / discharge valve is shifted from the open state to the closed state by the valve opening / closing control means, is shifted from the closed state to the open state. Although it has been described that the period is longer than the valve opening response period, which is the period, the present invention is not limited thereto.

  As described above, the belt-type continuously variable transmission according to the present invention can improve drivability, and is suitable for application to various belt-type continuously variable transmissions.

It is a skeleton figure of the belt type continuously variable transmission concerning Embodiment 1 of the present invention. It is principal part sectional drawing of the primary pulley at the time of gear ratio fixed of the belt-type continuously variable transmission which concerns on Embodiment 1 of this invention (valve closed state). It is a figure which shows the torque cam of the belt-type continuously variable transmission which concerns on Embodiment 1 of this invention. It is a figure which shows the torque cam of the belt-type continuously variable transmission which concerns on Embodiment 1 of this invention. It is a figure which shows the structural example of the hydraulic control apparatus of the belt-type continuously variable transmission which concerns on Embodiment 1 of this invention. It is principal part sectional drawing of the primary pulley at the time of gear ratio reduction of the belt-type continuously variable transmission which concerns on Embodiment 1 of this invention (at the time of upshift). It is a figure which shows operation | movement of the hydraulic control apparatus at the time of gear ratio reduction of the belt-type continuously variable transmission which concerns on Embodiment 1 of this invention (at the time of upshift). It is principal part sectional drawing of the primary pulley at the time of the gear ratio increase (at the time of downshift) of the belt-type continuously variable transmission which concerns on Embodiment 1 of this invention. It is a figure which shows operation | movement of the hydraulic control apparatus at the time of the gear ratio increase (at the time of downshift) of the belt-type continuously variable transmission which concerns on Embodiment 1 of this invention. It is a time chart explaining an example of control of the belt type continuously variable transmission concerning Embodiment 1 of the present invention. It is a time chart explaining an example of control of the belt type continuously variable transmission concerning Embodiment 2 of the present invention.

Explanation of symbols

1-1, 1-2 Belt type continuously variable transmission 10 Internal combustion engine (drive source)
50 Primary pulley (one pulley)
51 Primary pulley shaft 51a Supply / discharge side main passage (supply / discharge route)
51c Shaft side communication path (supply / discharge path)
52 Primary fixed sheave 53 Primary movable sheave 54 Primary partition 54e Bulkhead communication path (supply / discharge path)
54i Opening hole (supply / discharge route)
55 Primary hydraulic chamber (one clamping pressure generating hydraulic chamber)
56 Valve arrangement member 56a Valve arrangement passage (supply / discharge path)
56b Arrangement side communication passage (supply / discharge route)
57 Cover member 58 Bulkhead fixing member 60 Secondary pulley (the other pulley)
61 Secondary pulley shaft 62 Secondary fixed sheave 63 Secondary movable sheave 64 Secondary hydraulic chamber (the other clamping pressure generating hydraulic chamber)
65 Secondary partition wall 66 Torque cam 67 Intermediate member 68 Transmission member 70 Hydraulic oil supply / discharge valve 71 Valve body 72 Valve seat surface 73 Valve body elastic member 80 Actuator (valve opening / closing control means)
81 Drive hydraulic chamber 82 Piston 83 Piston elastic member 84 Cancel chamber 110 Belt 110a Primary groove 110b Secondary groove 130 Hydraulic control device (hydraulic control means, first hydraulic control means, second hydraulic 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 (control means, setting means, first control means) , Second control means)
150 Input rotational speed sensor (speed ratio detecting means)
160 Output speed sensor (speed ratio detecting means)
P1 Primary hydraulic pressure P2 Drive hydraulic chamber hydraulic pressure Pin Supply pressure PS Constant pressure T1, T2, T6, T7 Space (supply / discharge path)
X1 Valve opening response period X2 Valve closing response period

Claims (3)

Two pulleys,
A belt wound around each pulley and transmitting an output torque from a drive 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 supply / discharge path for supplying hydraulic oil to one of the clamping pressure generating hydraulic chambers or discharging the hydraulic oil from the one clamping pressure generating hydraulic chamber;
The gear ratio is fixed by opening the valve when supplying hydraulic oil to the one clamping pressure generating hydraulic chamber or discharging hydraulic oil from the one clamping pressure generating hydraulic chamber. A hydraulic oil supply / discharge valve that closes when the transmission gear ratio is fixed and rotates integrally with the one pulley;
Valve opening / closing control means for controlling opening / closing of the hydraulic oil supply / discharge valve;
A valve closing response period, which is a period for shifting the hydraulic oil supply / discharge valve from the valve opening state to the valve closing state by the valve opening / closing control means, is longer than a valve opening response period for shifting the valve closing state to the valve opening state. Setting means to set the period ;
First hydraulic control means for controlling supply / discharge of hydraulic oil to / from the one clamping pressure generating hydraulic chamber via the supply / discharge path;
Second hydraulic control means for controlling supply / discharge of hydraulic oil to / from the drive hydraulic chamber of the valve opening / closing control means;
First control means for controlling the first hydraulic pressure control means and the second hydraulic pressure control means;
A gear ratio detecting means capable of detecting a gear ratio that is a rotational speed ratio of the two pulleys;
The hydraulic oil supply / discharge valve opens in a direction to supply hydraulic oil to the one clamping pressure generating hydraulic chamber,
The valve opening / closing control means opens the hydraulic oil supply / discharge valve by sliding the piston in one of the sliding directions with respect to the drive hydraulic chamber by the hydraulic pressure of the drive hydraulic chamber,
The first control means controls the first hydraulic pressure control means to raise the hydraulic pressure of the supply / discharge path when supplying hydraulic oil to the one clamping pressure generating hydraulic pressure chamber, and the transmission ratio detection means After the change of the gear ratio is detected, the hydraulic pressure of the drive hydraulic chamber is raised by the second hydraulic pressure control means ,
Belt type continuously variable transmission. In the valve opening response period or the valve closing response period, there is provided second control means for executing control for keeping the hydraulic pressure of the supply / discharge path constant.
The belt-type continuously variable transmission according to claim 1 . Two pulleys,
A belt wound around each pulley and transmitting an output torque from a drive 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 supply / discharge path for supplying hydraulic oil to one of the clamping pressure generating hydraulic chambers or discharging the hydraulic oil from the one clamping pressure generating hydraulic chamber;
The one clamping pressure generation hydraulic chamber provided in the supply / discharge path and when supplying the hydraulic oil to the one clamping pressure generation hydraulic chamber, or when discharging the hydraulic oil from the one clamping pressure generation hydraulic chamber A hydraulic oil supply / discharge valve that opens in a direction to supply hydraulic oil to the valve, closes when the transmission gear ratio is fixed, and rotates integrally with the one pulley;
Valve opening / closing control means for controlling opening / closing of the hydraulic oil supply / discharge valve by sliding the piston in one of the sliding directions with respect to the driving hydraulic chamber by the hydraulic pressure of the driving hydraulic chamber;
First hydraulic control means for controlling supply / discharge of hydraulic oil to / from the one clamping pressure generating hydraulic chamber via the supply / discharge path;
Second hydraulic control means for controlling supply and discharge of hydraulic oil to and from the drive hydraulic chamber;
Gear ratio detecting means capable of detecting a gear ratio which is a rotation speed ratio of the two pulleys;
When supplying hydraulic oil to the one clamping pressure generating hydraulic chamber, the first hydraulic control means is controlled to increase the hydraulic pressure in the supply / discharge path, and the change in the transmission ratio is detected by the transmission ratio detection means. And a control means for increasing the hydraulic pressure of the drive hydraulic chamber by the second hydraulic pressure control means.
Belt type continuously variable transmission.

Images