JP2009257534A - Belt-type continuously variable transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a belt-type continuously variable transmission for preventing rise of temperature of hydraulic fluid. <P>SOLUTION: This belt-type continuously variable transmission 1-1 includes a primary pulley 50 and a secondary pulley, a belt 110 for transmitting output torque T from an internal combustion engine 10, a primary oil pressure chamber 55 and a secondary oil pressure chamber 64 for generating pressure for nipping belt for the belt 110 by oil pressure, supply and discharge paths for supplying hydraulic fluid into the primary oil pressure chamber 55 and discharging the hydraulic fluid from the primary oil pressure chamber 55, a hydraulic fluid supply and discharge valve 70 provided in the supply and discharge path, being opened when supplying the hydraulic fluid into the primary oil pressure chamber 55 and discharging the hydraulic fluid from the primary oil pressure chamber 55, being closed when fixing a gear ratio γ, and rotating integrally with the primary pulley 50, and an actuator 80 for controlling opening and closing of the hydraulic fluid supply and discharge valve 70 and controlling temporary opening and closing to open and close the hydraulic fluid supply and discharge valve 70 at least once when the gear ratio is fixed. <P>COPYRIGHT: (C)2010,JPO&INPIT

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 drought pressure generating hydraulic chamber by closing a hydraulic oil supply / discharge valve.

  In general, a vehicle is provided with a transmission on the output side of the drive source in order to transmit the output torque from the internal combustion engine or electric motor, which is a drive source, to the road surface under optimum conditions according to the running state of the vehicle. . 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 driving 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 secondary pulley and the primary pulley are each provided with a clamping pressure generating hydraulic chamber that generates a belt clamping pressure with respect to the belt.

  A belt-type continuously variable transmission is a belt in which a movable sheave slides on each pulley shaft in the axial direction by the hydraulic pressure of each clamping pressure generating hydraulic chamber and is wound between the movable sheave of each pulley and a fixed sheave. Change the contact radius. As a result, the contact radius between the belt and each pulley is changed steplessly, and the gear ratio is changed steplessly. That is, the output torque from the drive source is changed steplessly.

  When the transmission gear ratio is fixed, the movement of the movable sheave in the axial direction is restricted so that the contact radius of the belt does not change. 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, there is a technique for holding hydraulic oil in the clamping pressure generating hydraulic chamber as disclosed in Patent Document 1, for example. In the prior art, a hydraulic oil supply / discharge valve is provided between 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 the clamping pressure generating hydraulic chamber. The hydraulic fluid is supplied to the clamping pressure generating hydraulic chamber when the hydraulic fluid supply / discharge valve is opened, or is discharged from the clamping pressure generating hydraulic chamber, and the hydraulic fluid is confined in the clamping pressure generating hydraulic chamber when the valve is closed. .

JP 2006-300270 A

  Here, the hydraulic oil in the clamping pressure generating hydraulic chamber when the transmission gear ratio is fixed is not circulated like the hydraulic oil supplied to other parts. May rise.

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

  In order to solve the above-mentioned problems and achieve the object, the present invention is formed in two pulleys, a belt wound around each pulley and transmitting output torque from a driving source, and each pulley. Supplying hydraulic fluid to a clamping pressure generating hydraulic chamber that generates a belt clamping pressure with respect to the belt by hydraulic pressure, and supplying hydraulic oil to the one clamping pressure generating hydraulic chamber, or discharging hydraulic fluid from the one clamping pressure generating 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, the valve is opened. A hydraulic fluid 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 fluid supply / discharge valve, The open / close control means And performing a temporary closing control at least one opening and closing said hydraulic fluid supply and discharge valve at a ratio fixed.

  In the belt-type continuously variable transmission, the valve opening / closing control means is preferably an actuator that is operated by the hydraulic pressure.

  The belt-type continuously variable transmission further includes hydraulic control means for controlling supply and discharge of hydraulic oil to at least one of the clamping pressure generating hydraulic chambers, and the hydraulic control means is configured to control the one of the ones during the temporary opening / closing control. It is preferable to perform hydraulic pressure holding control in which the pressure of the hydraulic oil supplied to the clamping pressure generating hydraulic chamber is set to the hydraulic pressure of the one clamping pressure generating hydraulic chamber when the speed ratio is fixed.

  In the belt type continuously variable transmission, it is preferable that the hydraulic pressure control unit performs the hydraulic pressure holding control before the hydraulic oil supply / discharge valve is opened.

  In the belt type continuously variable transmission, it is preferable that the hydraulic pressure control means performs the hydraulic pressure holding control until after the hydraulic oil supply / discharge valve is closed.

  In the belt-type continuously variable transmission, the drive source is an internal combustion engine, and hydraulic control means for controlling supply / discharge of hydraulic oil to / from at least one of the clamping pressure generating hydraulic chambers, the hydraulic control means, Control means for controlling the internal combustion engine, wherein the control means supplies hydraulic oil to the one clamping pressure generating hydraulic chamber by the hydraulic control means or the one clamping pressure during the temporary opening / closing control. After either one of the hydraulic oil discharge from the generated hydraulic chamber is performed, the other is performed until the transmission gear ratio becomes the fixed transmission gear ratio, and the power of the internal combustion engine is fixed when the transmission gear ratio is fixed. It is preferable to perform constant power control for maintaining the power at a fixed time.

  The belt type continuously variable transmission according to the present invention performs temporary opening / closing control for opening / closing the hydraulic oil supply / discharge valve at least once when the transmission gear ratio is fixed, so that one clamping pressure generating hydraulic pressure is generated when the hydraulic oil supply / discharge valve is opened. The hydraulic oil in the chamber and the hydraulic oil upstream of the hydraulic oil supply / discharge valve in the supply / discharge path (opposite the hydraulic pressure chamber side opposite to the hydraulic oil supply / discharge valve), that is, the upstream hydraulic oil Contact and transfer of heat becomes possible. Therefore, if the oil temperature of the hydraulic oil in one clamping pressure generating hydraulic chamber is higher than the oil temperature upstream of the hydraulic oil supply / discharge valve in the supply / discharge path, the hydraulic oil supply / discharge valve is opened when the gear ratio is fixed. By doing so, the oil temperature of the hydraulic oil in one clamping pressure generating hydraulic chamber can be lowered, so that an increase in the oil temperature of the hydraulic oil in one clamping pressure generating hydraulic chamber when the transmission gear ratio is fixed can be suppressed. . Thereby, there exists an effect that the raise of the oil temperature of hydraulic fluid can be suppressed.

  Further, in the present invention, while the hydraulic oil supply / discharge valve is opened, the pressure of the upstream hydraulic oil becomes the hydraulic pressure of one clamping pressure generating hydraulic chamber when the transmission gear ratio is fixed by the hydraulic pressure holding control. Supply of hydraulic oil to the pressure generation hydraulic chamber or discharge of hydraulic fluid from one clamping pressure generation hydraulic chamber can be suppressed, and changes in the gear ratio during valve opening can be suppressed. Therefore, it is possible to suppress the occurrence of a shock during the temporary opening / closing control and improve drivability.

  Further, in the present invention, since the hydraulic pressure holding control is performed before the hydraulic oil supply / discharge valve is opened, when the hydraulic oil supply / discharge valve is opened, the hydraulic hydraulic pressure is controlled by the hydraulic pressure holding control when the transmission ratio is fixed. Since the hydraulic pressure of one of the clamping pressure generating hydraulic chambers is set, a change in the gear ratio when the valve is opened can be suppressed. Therefore, it is possible to suppress the occurrence of a shock at the time of starting the temporary opening / closing control and improve drivability.

  In the present invention, the hydraulic pressure holding control is performed until after the hydraulic oil supply / discharge valve is closed. Since the hydraulic pressure in one of the clamping pressure generating hydraulic chambers is maintained, a change in the gear ratio when the valve is closed can be suppressed. Therefore, the occurrence of a shock at the end of the temporary opening / closing control can be suppressed, and the drivability can be improved.

  Further, in the present invention, during the temporary opening / closing control, the hydraulic oil is discharged from one clamping pressure generating hydraulic chamber until the transmission gear ratio becomes a fixed transmission ratio after supplying the hydraulic oil to one clamping pressure generating hydraulic chamber, or Since hydraulic oil is supplied to one clamping pressure generating hydraulic chamber after the hydraulic oil is discharged from the clamping pressure generating hydraulic chamber until the transmission gear ratio becomes the fixed transmission ratio, one of the clamping pressure generating hydraulic chambers is opened when the hydraulic oil supply / discharge valve is opened. The hydraulic fluid in the pressure generating hydraulic chamber and the upstream hydraulic fluid come into contact with each other, so that heat can be exchanged, and the hydraulic fluid in one clamping pressure generating hydraulic chamber and the upstream hydraulic fluid can be exchanged. Therefore, when the oil temperature of the hydraulic oil in one clamping pressure generating hydraulic chamber is higher than the oil temperature of the upstream hydraulic oil, the hydraulic oil supply / discharge valve is opened when the gear ratio is fixed. Since the hydraulic fluid in one clamping pressure generating hydraulic chamber is replaced with the upstream hydraulic fluid having a low oil temperature, the oil temperature of the hydraulic fluid in one clamping pressure generating hydraulic chamber can be effectively suppressed when the gear ratio is fixed. Can do. Thereby, there exists an effect that the raise of the oil temperature of hydraulic fluid can be suppressed effectively. In addition, since the constant power control is performed during the temporary opening / closing control, the power generated by the internal combustion engine is maintained constant even if there is a change in the gear ratio when the gear ratio is fixed, thereby suppressing a sense of discomfort given to the driver. There is an effect that can be done.

  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 an output torque transmitted to the belt type continuously variable transmission in the following embodiment. 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 the present invention. FIG. 2 is a cross-sectional view of the main part of the primary pulley when the transmission gear ratio is fixed. 3A and 3B are diagrams illustrating the torque cam. FIG. 4 is a diagram illustrating a configuration example of the hydraulic control device. 5 to 8 are explanatory diagrams of the operation of the belt type continuously variable transmission when the gear ratio is changed.

  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, which are two pulleys constituting the belt type continuously variable transmission 1-1 according to the first embodiment. 60, a primary hydraulic chamber 55 which is one clamping pressure generating hydraulic chamber, a hydraulic oil supply / discharge valve 70, an actuator 80, and a belt 110 are accommodated. Reference numeral 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 is a hydraulic control device, and 140 is an ECU.

  As shown in FIG. 1, the torque converter 30 as a starting mechanism increases or transmits the output torque T from the internal combustion engine 10 as a drive source to the belt type continuously variable transmission 1-1 as it is. 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 lockup clutch 34 that is controlled by hydraulic fluid supplied from the hydraulic control device 130 is disposed between the turbine 32 and the front cover 37. It is connected to the input shaft 38 via.

  Here, the operation of the torque converter 30 will be described. Output torque T 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 T 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. And transmitted to the turbine 32. The output torque T 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 T 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 lockup clutch 34 is locked (engaged with the front cover 37) by the damper device 35, the output torque T from the internal combustion engine 10 transmitted to the front cover 37 does not pass through the hydraulic oil. Directly transmitted to the input shaft 38. That is, the torque converter 30 transmits the output torque T from the internal combustion engine 10 as it is to the belt type continuously variable transmission 1 via the input shaft 38.

  As shown in FIG. 1, the forward / reverse switching mechanism 40 transmits the output torque T from the internal combustion engine 10 transmitted via the torque converter 30 to the primary pulley 50 of the belt type continuously variable transmission 1. 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 T from the internal combustion engine 10 transmitted to the sun gear 44 is transmitted to the primary pulley shaft 51.

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

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

  The forward clutch 42 is ON / OFF controlled by supplying hydraulic oil from the hydraulic 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 T 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 T 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 each pinion 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 is one pulley, and transmits the output torque T from the internal combustion engine 10 transmitted through the forward / reverse switching mechanism 40 to the secondary pulley 60 by the belt 110. It 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, And a cover member 57. 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 FIG. 2, the primary pulley shaft 51 is rotatably supported by pulley bearings 111 and 112. Further, the primary pulley shaft 51 is formed with a supply / discharge side main passage 51a and a drive side main passage 51b that 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 51a is formed on the primary fixed sheave side and communicates with an oil passage R7 (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, the radially inner end portion (lower end portion in the figure) communicates with each shaft side communication passage 51c, and the other end portion in the axial direction (left end portion in the figure). It communicates with the space T2.

  The space T2 constitutes a part of the supply / discharge path. The space portion T <b> 2 is formed by the primary partition wall 54, the primary movable sheave 53, and the primary pulley shaft 51. The space T2 has a ring shape, and the radially inner end (the lower end in the figure) communicates with the space T1, and the radially outer end 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, 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 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 (lower end portion in the figure) communicates with each shaft side communication passage 51d, and the radially outer side (upper end portion in the figure) communicates with the partition wall side of the primary partition wall 54. It communicates with the passage 54f. That is, the drive side main passage 51b communicates with the partition wall side communication passage 54f through the shaft side communication passages 51d and the space portion T3. Note that a communication portion seal member such as a seal ring may be provided between the inner peripheral surface of the primary partition wall 54 and the outer peripheral surface of the primary pulley shaft 51 with the space T3 interposed therebetween.

  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 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 portion T4 has a ring shape, the radially inner side (lower end portion in the figure) communicates with each second communication passage 23d, and the radially outer side (upper end portion in the figure) is the axial side of the primary pulley shaft 51. It communicates with the communication passage 51e. 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 that opens to the inner peripheral surface of the primary pulley shaft 51 and communicates with the space T4, and the other end that opens the primary pulley shaft 51 to the outer peripheral surface. , 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 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, and the radially inner side (lower end portion in the figure) communicates with each shaft-side communication passage 51e, and the radially outer side (upper end portion in the figure) has the pulley bearing 112 and the primary partition wall 54. The cover side communication passage 57a communicates with a space formed therebetween. 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 inner peripheral surface of the primary pulley shaft 51 and the outer peripheral surface of the pulley bearing 112 and the outer peripheral surface of the cover member 57, a seal member for a communication portion such as a seal ring is provided with the space T5 interposed therebetween. May be.

  As shown in FIG. 2, the primary fixed sheave 52 is provided so as 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 an 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. Further, a notch 53e is formed at the other end (right end in the figure) of the primary movable sheave 53 in the axial direction. Therefore, even if the other end portion in the axial direction of the primary movable sheave 53 slides to the other in the axial direction with respect to the primary pulley shaft 51, even if it contacts or is close to the primary partition wall 54, Communication between the space T1 and the space T2 is maintained.

  The primary partition 54 is a partition member and constitutes a primary hydraulic chamber 55 that is one clamping pressure generating hydraulic chamber. As shown in FIG. 2, the primary partition wall 54 is an annular member, and is disposed 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 in the primary pulley shaft 51 and the partition wall fixing member 58 fixed to the primary pulley shaft 51 together with the cover member 57 and the pulley bearing 112, whereby the primary pulley shaft 51. Is fixed with respect to the axial direction.

  The primary partition wall 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 a radially inner end 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 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-side communication passage 54f has an inner end in the radial direction that opens to the inner peripheral surface of the primary partition 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. 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. Accordingly, 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 projecting 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. The partition-side storage portion 54h has one end portion (the right end portion in the figure) closed inside the recess 54c, and the other end portion (the left end portion in the figure) opens to a surface facing the valve arrangement member. It 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 (for example, three locations between adjacent storage portions 54h) at equal intervals on the circumference.

  The space 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 T6 has a ring shape, one end (the right end in the figure) communicates with each opening hole 54i, and the other end (the left end in the figure) has a 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, for example, a seal ring is provided between the protrusion 53 d of the primary movable sheave 53 and the radially outer protrusion 54 d of the primary partition 54, and between the cylindrical portion 53 a of the primary movable sheave 53 and the recess 54 c of the primary partition 54. A primary hydraulic chamber seal member S1 is provided. Accordingly, the space formed by the primary movable sheave 53, which is the primary hydraulic chamber 55, and the primary partition 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 speed ratio γ of the belt type continuously variable transmission 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 recess 54c formed to protrude toward the primary hydraulic chamber side of the primary partition wall 54, which is a partition member, and is a snap that is a valve arrangement member fixing member that is inserted into and fixed to the recess 54c. It is fixed with respect to the axial direction by a ring 59.

  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. Accordingly, 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. The arrangement side communication passage 56b has one end portion (an end portion on the radially outer side in the figure) communicating with the valve arrangement passage 56a, and the other end portion (the inner side in the radial direction in the drawing) 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 the radially inner end (the lower end in the figure) communicates with each partition wall side communication passage 54e, and the radially outer end communicates with each valve arrangement passage 56a. is doing. 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 first 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. Each 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. Among 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 accommodation 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 constituting 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 inside in the radial 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 57 b is formed so as to project to a position where it enters the concave portion 54 c of the primary partition wall 54. Further, in the vicinity of the central portion of the cover member 57 in the radial direction, a restricting protrusion 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.

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

  The secondary pulley shaft 61 is rotatably supported by pulley bearings 113 and 114. The secondary pulley shaft 61 has a hydraulic oil passage (not shown) inside, and hydraulic oil supplied from the hydraulic 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 is axially connected to the secondary pulley shaft 61 by spline fitting a spline (not shown) formed on the inner peripheral surface of the secondary movable sheave 63 with 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 side, the secondary pulley 60, that is, the V-shaped secondary groove 110b. A belt clamping pressure is generated with respect to the belt 110 wound around the belt. The secondary hydraulic chamber 64 is a space formed by a secondary pulley shaft 61, a secondary movable sheave 63, and a disk-shaped secondary partition wall 65 fixed to the secondary pulley shaft 61. The secondary movable sheave 63 is formed with an annular protrusion 63 a that protrudes in one axial direction, that is, protrudes toward the final reduction gear 90. On the other hand, the secondary partition wall 65 is formed with an annular projecting portion 65a projecting in the other axial direction, that is, projecting toward 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. And a plurality of disk-shaped discs arranged between the first engaging portion 63b and the second engaging portion 67a. The transmission member 68 is configured.

  The intermediate member 67 is formed integrally with the secondary partition wall 65 or is fixed to the secondary partition wall 65, and can rotate relative to the secondary pulley shaft 61 and the secondary movable sheave 63 on the secondary pulley shaft 61 by the pulley bearing 113 and the bearing 115. It is supported by. The intermediate member 67 is fixed to the input shaft 101 of the power transmission path 100 by, for example, spline fitting. That is, the output torque T 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 T 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. The secondary hydraulic chamber 64 may be the only means for generating the belt clamping pressure with respect to the belt 110 in the secondary pulley 60.

  The hydraulic oil supply / discharge valve 70 is also opened when hydraulic oil is supplied to the primary hydraulic chamber 55 which is one clamping pressure generating hydraulic chamber, or when hydraulic fluid is discharged from the primary hydraulic chamber 55. In the first 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 γ and open the valve. At the same time, hydraulic fluid is supplied to the primary hydraulic chamber 55 from the outside of the primary hydraulic chamber 55, that is, from the primary pulley 50 to reduce (upshift) the gear ratio γ, open the valve, and from the primary hydraulic chamber 55 to the primary pulley 50. The hydraulic oil is discharged to the outside, and the gear ratio γ 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.

  The hydraulic oil supply / discharge valve 70 includes a valve body 71, a valve seat surface 72, and a valve body elastic member 73. Each valve element 71 has a spherical shape, is disposed closer to the primary hydraulic chamber than the valve seat surface 72, and has a diameter larger than the inner diameter of the valve seat surface 72. The valve seat surface 72 has a tapered shape that inclines radially outward as it goes toward the primary fixed sheave side (from the other end of the valve arrangement passage 56a to one end). When the valve body 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 each hydraulic oil supply / discharge is performed. The 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 portion T6 are communicated, that is, the supply / discharge path and the primary hydraulic chamber 55 are communicated, and each hydraulic oil supply / discharge valve 70 is connected. The valve is opened. Accordingly, when each hydraulic oil supply / discharge valve 70 is closed, the hydraulic oil in the primary pulley 50 and the upstream side of each hydraulic oil supply / discharge valve 70 in the supply / discharge path (with each hydraulic oil supply / discharge valve 70 interposed therebetween) The hydraulic fluid in the primary hydraulic chamber 55 side (the side opposite to the primary hydraulic chamber 55 side) (hereinafter, simply referred to as “upstream hydraulic fluid”) comes into contact. Each hydraulic oil supply / discharge valve 70 opens in the valve opening direction and closes in the valve closing direction.

  The valve body elastic member 73 is a valve body valve closing direction pressing force generating means for applying 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 storage 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 storage portion 54 h and the valve body 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 a direction in which the valve body 71 contacts the valve seat surface 72, that is, an elastic member pressing force in the 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 each 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 controls the open / close valve of the hydraulic oil supply / discharge valve 70 by the pressure of the supplied hydraulic oil, that is, the drive hydraulic pressure P2 of the drive hydraulic chamber 81. is there. 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. Therefore, the piston valve opening direction pressing force is applied to the piston 82 by the driving hydraulic pressure P <b> 2 of the driving 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. In other words, 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 in one of the sliding directions with respect to the drive hydraulic chamber 81 by the drive hydraulic pressure P2 of the drive hydraulic chamber 81, that is, in one of the axial directions (right direction in the figure), thereby supplying each hydraulic oil. The discharge valve 70 is opened. The piston 82 includes a pressure receiving member 82a and a pressing member 82b.

  The pressure receiving member 82a 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 82a receives the drive hydraulic pressure P2 of the drive hydraulic chamber 81. The pressure receiving member 82a is moved in one of the axial directions of the sliding direction with respect to the drive chamber hydraulic pressure 81, that is, in the valve opening direction by the piston valve opening direction pressing force acting by the drive hydraulic pressure P2 of the drive hydraulic chamber 81. Slide. 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 to face each arrangement side storage portion 56 d of the valve arrangement member 56.

  The pressing member 82 b is disposed between the pressure receiving member 82 a and the valve body 71 of each hydraulic oil supply / discharge valve 70. Each pressing member 82b is inserted into each sliding support hole 56c of the valve arrangement member 56, and is supported so as to be slidable in the axial direction with respect to each sliding support hole 56c. That is, each pressing member 82b is supported to be slidable in the axial direction with respect to the primary pulley 50 which is one pulley. Each pressing member 82 b has one end portion (the right end portion in the figure) opposed to the valve body 71 of each hydraulic oil supply / discharge valve 70, and can abut against each valve body 71. Further, each pressing member 82b can be in contact with the pressure receiving member 82a with the other end (the left end in the figure) facing the pressure receiving member 82a. Accordingly, each pressing member 82b can slide in the axial direction with respect to the primary pulley 50 while being in contact with each valve body 71 and the pressure receiving member 82a. Thereby, an axial force, for example, a piston valve opening direction pressing force acting on the pressure receiving member 82a can be transmitted between the actuator 80 and each hydraulic oil supply / discharge valve 70. That is, the pressing member 82b slides in the same direction as the pressure receiving member 82a when the pressure receiving member 82a slides in one of the axial directions by the drive hydraulic pressure P2 of the drive hydraulic chamber 81, and the pressure receiving member 82a contacts. To do.

  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 has a piston urging force even when the piston 82 is positioned in the most other direction of the axial direction which is the other direction among the sliding directions with respect to the drive chamber hydraulic pressure 81, that is, in the most valve closing direction. Arranged to occur. 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 of the axial direction which is the other direction of the sliding direction with respect to the drive hydraulic chamber 81, that is, The elastic member pressing force in the valve closing direction acts on the pressure receiving member 82a as the 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 each hydraulic oil supply / discharge valve 70 is opened, the valve element 71 is pushed in the valve opening direction, which is a pressing force acting on the valve element 71 in the direction away from the valve seat surface 72, that is, in the valve opening direction. The pressure exceeds the valve body closing direction pressing force which is the pressing force acting on the valve body 71 in the direction in which the valve body 71 contacts the valve seat surface 72, that is, the valve closing direction. It is done by leaving. Accordingly, each hydraulic oil supply / discharge valve 70 is opened when hydraulic oil is supplied to the primary hydraulic chamber 55 and when hydraulic oil is discharged from the primary hydraulic chamber 55.

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

  First, the actuator 80 applies a piston valve opening direction pressing force to the pressure receiving member 82a of the piston 82 by the driving hydraulic pressure P2 of the driving hydraulic chamber 81, thereby causing the pressure receiving member 82a to move in one of the sliding directions. On the other hand, that is, in the valve opening direction. When the pressure receiving member 82a slides in the valve opening direction, the pressure receiving member 82a and each pressing member 82b come into contact with each other, and each pressing member 82b slides in the valve opening direction together with the pressure receiving member 82a. Then, when each pressing member 82b comes into contact with the valve body 71 of each hydraulic oil supply / discharge valve 70, the 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 above. Each valve element 71 acts as a valve element opening direction pressing force. Accordingly, each hydraulic oil supply / discharge valve 70 has the valve element 71 opened in the valve opening direction with respect to the valve seat surface 72 when the differential pressing force, which is the valve element opening direction pressing force, exceeds the valve element 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 acting on each valve body 71 by the valve closing biasing force generated by the valve body elastic member 73 and the primary partition wall of each valve arrangement passage 56a than the valve body 71. Pressure of the hydraulic oil existing on the side, that is, hydraulic oil valve closing direction pressing force acting on each valve body 71 in the valve closing direction by the primary hydraulic pressure P1 of the primary hydraulic chamber 55 is included.

  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 each hydraulic oil supply / discharge valve 70 is maintained unless the valve body valve opening direction pressing force acting on the valve body 71 exceeds the valve body valve opening direction pressing force. The hydraulic oil in the primary hydraulic chamber 55 that is a chamber is securely held in the primary hydraulic chamber 55. In the first 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. That is, the space formed by the primary partition 54 constituting the cancel chamber 84, the valve arrangement member 56, the cover member 57, and the pressure receiving member 82a of the piston 82 is the drive hydraulic chamber seal member S4 and the cancel chamber. Sealed with the seal member S5.

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

  The final reduction gear 90 of the belt type continuously variable transmission 1-1 transmits the output torque T 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. Further, a ring gear 99 is provided on the outer periphery of the differential case 91, and the ring gear 99 is meshed 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 T from the internal combustion engine 10 transmitted through the primary pulley 50 to the secondary pulley 60. As shown in FIG. 1, the belt 110 is wound between a primary groove 110 a for the primary pulley 50 and a secondary groove 110 b for the secondary pulley 60. That is, the belt 110 is wound around the primary pulley 50 and the secondary pulley 60. Further, the belt 110 is an endless belt composed of, for example, a large number of metal pieces and a plurality of steel rings.

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

  The hydraulic control device 130 is hydraulic control means. The hydraulic control device 130 controls supply and discharge of hydraulic fluid to and from the primary hydraulic chamber 55 that is one clamping pressure generating hydraulic chamber. The hydraulic control device 130 also 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 and the internal combustion engine 10 are mounted. When supplying the hydraulic oil to the primary hydraulic chamber 55, the hydraulic control device 130 supplies the hydraulic oil to the primary hydraulic chamber 55 through the supply / discharge path by communicating the primary pulley 50 and the supply / discharge path. Is. 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, so that the hydraulic oil is discharged from the primary hydraulic chamber 55 via the supply / discharge path. It is also what is discharged. The hydraulic control device 130 also supplies hydraulic oil to the drive hydraulic chamber 81.

  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. By controlling this, the gear ratio γ of the belt type continuously variable transmission 1 is also controlled. In the figure, the 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 income within the transaxle 20 such as the belt-type continuously variable transmission 1). The illustration of the lubricated part (for example, a stationary part having a sliding part between the movable parts, 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 case 22. The hub 132b is spline-fitted to the hollow shaft 36. Therefore, the oil pump 132 can be driven because the output torque T 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. Are connected to the primary hydraulic chamber 55. 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 according to the output torque T of the internal combustion engine 10. The line pressure control device 133 is provided with a solenoid valve (not shown), for example, a linear solenoid valve, which regulates the pressure of the hydraulic oil discharged from the oil pump 132. The line pressure control device 133 is electrically connected to the ECU 140, and the line pressure PL can be regulated by controlling the valve opening degree of the linear solenoid valve by a control signal from the ECU 140.

  The constant pressure control device 134 adjusts the line pressure PL output from the line pressure control device 133 so as to always become a constant pressure. That is, the constant pressure control device 134 adjusts the oil pressure 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 the first embodiment, the primary hydraulic chamber control device 135 controls the supply flow rate of the hydraulic oil supplied to the primary hydraulic chamber 55 and the discharge flow rate of the hydraulic oil discharged from the primary hydraulic chamber 55. The primary hydraulic chamber control device 135 includes a supply side control valve 135a, a discharge side control valve 135b, a supply side flow rate control valve 135c, and a discharge side flow rate control valve 135d.

  The supply side control valve 135a 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 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. Accordingly, the supply-side control valve 135a can regulate the control hydraulic chamber 135o of the supply-side flow rate control valve 135c from a constant pressure PS to atmospheric pressure by a control signal from the ECU 140.

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

  When the discharge-side control valve 135b is turned on, the first port 135h and the second port 135i communicate with each other. Accordingly, the constant pressure PS introduced into the discharge side control valve 135b is introduced into the first port 135r of the discharge side flow control valve 135d (see FIG. 8). That is, the constant pressure PS introduced into the discharge side control valve 135b is introduced into a control hydraulic chamber 135v described later of the discharge side flow control valve 135d communicating with the first port 135r. Further, the constant pressure PS introduced into the discharge side control valve 135b is introduced into the fourth port 135n of the supply side flow control valve 135c (see the same figure). On the other hand, when the discharge side control valve 135b is turned off, the second port 135i and the third port 135j communicate with each other. Accordingly, the first port 135r of the discharge side flow control valve 135d is released to atmospheric pressure via the discharge side control valve 135b (see FIG. 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 control valve 135c is released to the atmospheric pressure via the discharge side control valve 135b (see the 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. Therefore, the discharge-side control valve 135b can regulate the control hydraulic chamber 135v of the discharge-side flow control valve 135d between a constant pressure PS and 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 an oil passage R7 and a supply / discharge passage (supply / discharge-side main passage 51a, shaft-side communication passages 51c, space portions T1, T2, partition wall-side communication passages 54e, space portions T7, and arrangements. It is connected to the primary hydraulic chamber 55 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 controller 133 and the second of the supply-side flow control valve 135c An orifice, that is, a throttle is provided between the port 135l and the hydraulic oil flowing into the supply-side flow control valve 135c from the supply-side control valve 135a and the hydraulic oil flowing into the supply-side flow control valve 135c from the line pressure control device 133. The pressure or flow rate may be adjusted.

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

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

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

  The control hydraulic chamber 135v communicates with the first port 135r, and the spool valve opening direction pressing force that presses the spool 135w in one direction (upward in the figure) in the direction in which the spool 135w moves due to the hydraulic pressure. Is applied to the spool 135w. The spool 135w is movably supported in the primary hydraulic chamber control device 135, and moves in one direction of the movement direction to communicate the second port 135s and the third port 135t. By moving in the other direction, the communication between the second port 135s and the third port 135t is cut off. The spool elastic member 135x is 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, the second port 135s and the first port 135t as the moving amount of the spool 135w increases in one direction. The flow path cross-sectional area of the flow path communicating with the 3 port 135t increases. That is, the discharge-side flow rate control valve 135d has two ports, that is, a second port 135s and a third port 135t, as the spool 135w moves by the hydraulic pressure of the control hydraulic chamber 135v regulated by the discharge-side control valve 135b. Communication and control the discharge flow rate.

  The drive hydraulic chamber control device 136 adjusts the drive hydraulic pressure P2 of the drive hydraulic chamber 81. As described above, the constant pressure PS is introduced from the constant pressure control device 134 into the drive hydraulic chamber control device 136. Further, the drive hydraulic chamber control device 136 is connected to the drive hydraulic chamber 81 via an oil passage R8. 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. And connected. The drive hydraulic chamber control device 136 includes an ON / OFF valve (not shown). The drive hydraulic chamber control device 136 is electrically connected to the ECU 140 and controls ON / OFF of the ON / OFF valve by a control signal from the ECU 140. When the drive hydraulic chamber control device 136 is ON-controlled, that is, when the ON / OFF valve is turned ON, the branch oil passage R32 and the oil passage R8 communicate with each other and are introduced into the drive hydraulic chamber control device 136. The constant pressure PS is introduced into the drive hydraulic chamber 81, and the drive hydraulic pressure P2 of the drive hydraulic chamber 81 becomes the constant pressure PS. On the other hand, when the drive hydraulic chamber control device 136 is controlled to be OFF, that is, when the ON / OFF valve is turned OFF, the communication between the branch oil path R32 and the oil path R8 is blocked, and for example, the oil path R8 is The drive oil pressure P2 in the drive oil pressure chamber 81 becomes atmospheric pressure. Here, the constant pressure PS means that the hydraulic oil supply / discharge valve 70 can be opened by the drive hydraulic pressure P2 of the drive hydraulic chamber 81 at least when the drive hydraulic pressure P2 of the drive hydraulic chamber 81 becomes the constant pressure PS. 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 first embodiment, the secondary hydraulic chamber control device 137 is connected to the secondary hydraulic chamber 64 via an oil passage R9, a hydraulic oil passage (not shown) of the secondary pulley shaft 61, and a hydraulic fluid supply hole (not shown). The secondary hydraulic chamber control device 137 includes a flow rate control valve (not shown). The secondary hydraulic chamber control device 137 is electrically connected to the ECU 140, and regulates the introduced line pressure PL controlled by a control signal from the ECU 140.

  The 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 in accordance with the control signal output to the hydraulic control device 130, so that the belt type continuously variable transmission is performed. The transmission ratio γ of the machine 1-1 is controlled. Further, the ECU 140 controls the output torque T 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. Note that 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.

  Next, the operation of the belt type continuously variable transmission 1-1 according to the first embodiment will be described. First, general forward and reverse travel of the vehicle will be described. When the driver selects a forward position by a shift position device (not shown) provided in the vehicle, the ECU 140 turns on the forward clutch 42 and turns off the reverse brake 43 by the hydraulic oil supplied from the hydraulic 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 unit 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 T from the internal combustion engine 10 is primary. It is transmitted to the pulley 50. The output torque T 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 T 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, and the intermediate The shaft 102 is rotated. The output torque T 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 T 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 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 fluid 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, and the sun gear 44 meshed with each pinion 45 It rotates in the opposite direction to the shaft 38. That is, the primary pulley shaft 51 connected to the sun gear 44 rotates in the direction opposite to the input shaft 38. As a result, the secondary pulley shaft 61, the input shaft 101, the intermediate shaft 102, the differential case 91, the drive shafts 121, 122, and the like of the secondary pulley 60 rotate in the opposite direction to the case where the driver selects the forward position. Goes backwards.

  Here, the ECU 140 includes a map (for example, an optimum fuel consumption curve based on the engine speed and the throttle opening of the throttle valve, etc.) stored in the storage unit of the ECU 140 and various conditions such as the vehicle speed and the accelerator opening of the driver. ), The speed ratio γ of the belt-type continuously variable transmission 1 is controlled via the hydraulic control device 130 so that the operating state of the internal combustion engine 10 is optimized. The control of the transmission gear ratio γ of the belt type continuously variable transmission 1 includes changing the transmission gear ratio γ and fixing the transmission gear ratio γ. The speed ratio γ is changed and the speed ratio γ is fixed by controlling the primary hydraulic chamber control device 135, the drive hydraulic chamber control device 136, and the secondary hydraulic chamber control device 137.

  To change the gear ratio γ, each hydraulic oil supply / discharge valve 70 is opened and hydraulic oil is supplied from the hydraulic control device 130 to the primary hydraulic chamber 55 or from the primary hydraulic chamber 55 via the hydraulic control device 130 to the primary pulley. 50, 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 of is adjusted. As a result, the contact radius of the belt 110 in the primary pulley 50 changes, and the speed ratio γ, 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 γ is fixed by closing each 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 of the gear ratio γ includes an upshift, that is, a gear ratio decrease change that decreases the gear ratio γ, and a downshift, that is, a gear ratio increase change that increases the gear ratio γ. The ECU 140 performs gear ratio decrease control or gear shift increase control when changing the gear ratio γ. Each will be described below.

  The gear ratio reduction 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, each 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 γu 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 ON-controlled by the ECU 140. Therefore, the constant pressure PS introduced into the drive hydraulic chamber controller 136 is introduced into the drive hydraulic chamber 81, and the drive hydraulic pressure P2 of the drive hydraulic chamber 81 becomes the constant pressure PS. The actuator 80 has a valve body that is obtained by subtracting a differential valve pressing force that acts on the piston 82 by the piston elastic member 83 from a piston valve opening direction pressure that acts on the piston 82 by the driving hydraulic pressure P2 of the driving hydraulic chamber 81. It is made to act on the valve element 71 of each hydraulic oil supply / discharge valve 70 as a valve opening direction pressing force. Here, as described above, the valve body opening direction pressing force is determined by the actuator 80 when the drive hydraulic pressure P2 of the drive hydraulic chamber 81 becomes the constant pressure PS. Since 70 can be opened, the valve body closing direction pressing force will be exceeded. Therefore, as shown in FIG. 5, 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.

  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 moving 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 hydraulic oil to the primary hydraulic chamber 55 becomes a supply flow rate based on the reduction gear ratio and the transmission 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 remains closed, and the hydraulic oil discharge flow rate from the primary hydraulic chamber 55 becomes zero.

  As described above, each 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 and 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. As a result, the contact radius of the belt 110 in the primary pulley 50 increases, the contact radius of the belt 110 in the secondary pulley 60 decreases, the gear ratio γ is reduced in principle, and the upshift is performed.

  In the gear ratio increase 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. Is called. 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 γd and a speed change speed, and outputs a control signal based on these to hydraulic control device 130.

  In the gear ratio increase control, the drive hydraulic chamber controller 136 is ON-controlled by the ECU 140, as in the gear ratio decrease control. Accordingly, as shown in FIG. 7, the hydraulic oil supply / discharge valve 70 is opened by the actuator 80 moving the valve element 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 a discharge flow rate based on the reduction gear ratio and the shift speed.

  As described above, each hydraulic oil supply / discharge valve 70 is 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 each hydraulic oil supply / discharge valve 70, the primary hydraulic pressure P1 of the primary hydraulic chamber 55 decreases, and the primary movable sheave 53 is pressed toward the primary fixed sheave side. The pressing force 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 γ is increased to the increased gear ratio γd, and a downshift is performed.

  The gear ratio γ 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. The movement of the primary movable sheave 53 with respect to the primary fixed sheave 52 is restricted. The ECU 140 performs gear ratio fixing control when fixing the gear ratio γ. 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, the hydraulic oil is supplied to the primary hydraulic chamber 55 via the hydraulic oil supply / discharge valve 70, and each hydraulic oil is supplied. The hydraulic oil is prevented from being discharged from the primary hydraulic chamber 55 via the discharge valve 70, and the gear ratio γ is maintained at the fixed gear ratio γh. Specifically, ECU 140 outputs a control signal for maintaining gear ratio γ at fixed gear ratio γh to hydraulic control device 130.

  In the gear ratio fixed control, the drive hydraulic chamber control device 136 is OFF-controlled by the ECU 140. Accordingly, the drive hydraulic chamber 81 is released to the atmospheric pressure, and the drive 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 opening direction pressing force does not act on the valve body 71 of each hydraulic oil supply / discharge valve 70, and only the valve body closing direction pressing force acts, and the valve body 71 is closed. 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 first embodiment, in the gear ratio fixed control, the line pressure control device 130 adjusts the line pressure PL lower than the line pressure PL in the gear ratio reduction control by the ECU 140.

  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. Therefore, the hydraulic pressure of the above-described upstream hydraulic oil (hereinafter simply referred to as “supply pressure Pin”) is 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 each hydraulic oil supply / discharge valve 70 is prohibited.

  In the belt type continuously variable transmission 1-1 according to the first embodiment, the hydraulic control device 130 performs temporary opening / closing control for opening / closing each hydraulic oil supply / discharge valve 70 once when the transmission gear ratio is fixed. In the first embodiment, the ECU 140 causes the actuator 80 to perform temporary opening / closing control for opening and closing each hydraulic oil supply / discharge valve 70 in the closed state once during the gear ratio fixed control. FIG. 9 is a diagram illustrating a temporary opening / closing control flow according to the first embodiment. FIG. 10 is a diagram illustrating a change in the oil temperature during the temporary opening / closing control according to the first embodiment. FIG. 10 is a diagram showing the relationship among the supply pressure Pin, the drive hydraulic pressure P2, and the oil temperature OT. Hereinafter, the temporary opening / closing control during the shift fixing control will be described. The ECU 140 operates every control cycle.

  First, ECU 140 determines whether or not the shift fixing control is being performed as shown in FIG. 9 (step ST101). Here, ECU 140 determines whether or not the gear ratio fixing control is being performed in which the gear ratio γ is fixed and maintained at the fixed gear ratio γh.

  Next, when ECU 140 determines that shift fixing control is being performed (Yes in step ST101), ECU 140 performs counting using a counter (step ST102). Here, ECU 140 measures the passage of time from the start of the gear ratio fixed control by counting with a counter (not shown) (K = K + 1). If ECU 140 determines that the shift fixing control is not in progress (No in step ST101), ECU 140 ends the current control cycle and shifts to the next control cycle.

  Next, ECU 140 determines whether or not the count value K of the counter is greater than or equal to a first predetermined value K1 (step ST103). Here, ECU 140 determines whether or not a first predetermined time has elapsed since the start of shift fixing control. Here, the first predetermined value K1 (first predetermined time) is an arbitrary value. For example, the time until the oil temperature OT of the hydraulic oil in the primary hydraulic chamber 55 rises after the shift fixing control is started, It is set in advance based on the time until the oil temperature OT of the hydraulic oil in the primary hydraulic chamber 55 rises to the predetermined oil temperature OT1 after the start of the shift fixing control.

  Next, when ECU 140 determines that the count value K of the counter is equal to or greater than the first predetermined value K1 (Yes in step ST103), the ECU 140 increases the supply pressure Pin (step ST104). Here, the ECU 140 sets the hydraulic pressure of the upstream hydraulic oil that is the pressure of the hydraulic oil supplied to the primary hydraulic chamber 55 during the temporary opening / closing control, that is, the supply pressure Pin as the hydraulic pressure P1 of the primary hydraulic chamber 55 when the gear ratio is fixed. The hydraulic pressure holding control is started (Pin = P1). In the hydraulic pressure holding control, as shown in FIG. 10, the line pressure control device 133 is controlled by the ECU 140 to increase the line pressure PL. In the first embodiment, in the hydraulic pressure holding control, the line pressure control device 130 adjusts the line pressure PL by the ECU 140 so that the supply pressure Pin becomes the primary hydraulic pressure P1 (t1 in the figure). Note that the primary hydraulic pressure P1 is a value detected by a hydraulic sensor that detects the primary hydraulic pressure P1, an output torque T of the internal combustion engine 10 (for example, an engine rotational speed Ne detected by a rotational speed sensor (not shown), and a fuel injection (not shown)). Calculated based on the fuel injection amount supplied to the internal combustion engine 10 by the valve), the input rotational speed Nin of the belt-type continuously variable transmission 1-1 (for example, detected by an input rotational speed sensor not shown), and the fixed speed ratio γh. (For example, based on the input rotational speed Nin and an output rotational speed Nout detected by an output rotational speed sensor (not shown)), an estimated value calculated based on the secondary hydraulic pressure P3 of the secondary hydraulic chamber 64 or the like is used. Further, as shown in FIG. 9, when the ECU 140 determines that the count value K of the counter is less than the first predetermined value K1 (No in step ST103), the ECU 140 ends the current control cycle and shifts to the next control cycle. To do. Therefore, when the gear ratio fixing control is continued, the counter is counted until the count value K of the counter becomes equal to or greater than the first predetermined value K1.

  Next, ECU 140 opens each hydraulic oil supply / discharge valve 70 (step ST105). Here, the ECU 140 sets the drive oil pressure P2 of the drive oil pressure chamber 81 to a constant pressure PS by the drive oil pressure chamber control device 136, and opens each hydraulic oil supply / discharge valve 70 by the actuator 80 as shown in FIG. T2). As a result, the hydraulic control device 130 starts the temporary opening / closing control. In the first embodiment, the hydraulic pressure holding control is performed by the ECU 140 before (i.e., t1) before opening (t2) of each hydraulic oil supply / discharge valve 70. Accordingly, when each hydraulic oil supply / discharge valve 70 is opened, the supply pressure Pin becomes the primary hydraulic pressure P1 by the hydraulic pressure holding control, so that hydraulic oil is supplied to the primary hydraulic chamber 55 or hydraulic oil is supplied from the primary hydraulic chamber 55 when the valve is opened. Can be suppressed, and a change in gear ratio due to opening of the valve can be suppressed. As a result, it is possible to suppress the occurrence of a shock at the start of the temporary opening / closing control, and to improve drivability.

  Next, as shown in FIG. 9, ECU 140 determines whether or not the count value K of the counter is greater than or equal to a second predetermined value K2 (step ST106). Here, ECU 140 determines whether or not the second predetermined time has elapsed since the start of the shift fixing control. Here, the second predetermined value K2 (second predetermined time) is an arbitrary value larger than the first predetermined value K1 (first predetermined time). Is set in advance based on the time until the oil temperature OT of the hydraulic oil decreases, the time until the oil temperature OT of the hydraulic oil in the primary hydraulic chamber 55 decreases to the predetermined oil temperature OT2 after the temporary opening / closing control starts. Has been.

  Next, when ECU 140 determines that the count value K of the counter is the second predetermined value K2 (Yes in step ST106), it closes each hydraulic oil supply / discharge valve 70 (step ST107). Here, the ECU 140 sets the drive hydraulic pressure P2 of the drive hydraulic chamber 81 to atmospheric pressure by the drive hydraulic chamber control device 136, and closes each hydraulic oil supply / discharge valve 70 by the actuator 80 as shown in FIG. (Figure t3). Thereby, the hydraulic control device 130 ends the temporary opening / closing control. During the temporary opening / closing control (t2 to t3 in the figure), that is, while each hydraulic oil supply / discharge valve 70 is open, the supply pressure Pin becomes the primary hydraulic pressure P1 by the hydraulic pressure holding control, so that the hydraulic oil is supplied to the primary hydraulic chamber 55. Or it can suppress that hydraulic fluid is discharged | emitted from the primary hydraulic chamber 55, and can suppress the change of the gear ratio during valve opening. Thereby, generation | occurrence | production of the shock during temporary opening / closing control can be suppressed, and drivability can be improved. In addition, as shown in FIG. 9, when the ECU 140 determines that the count value K of the counter is not the second predetermined value K2 (No in step ST106), the ECU 140 ends the current control cycle and shifts to the next control cycle. Therefore, when the transmission ratio fixing control is continued, the counter is counted until the count value K of the counter reaches the second predetermined value K2, and the hydraulic oil supply / discharge valves 70 are kept open. .

  Next, ECU 140 reduces the supply pressure Pin (step ST108). Here, the ECU 140 reduces the hydraulic pressure of the upstream hydraulic oil that is the pressure of the hydraulic oil supplied to the primary hydraulic chamber 55, that is, the supply pressure Pin, after the temporary opening / closing control ends. As shown in FIG. 10, the line pressure control device 133 is controlled by the ECU 140 so that the line pressure PL is lower than the line pressure PL during the hydraulic pressure holding control. In the first embodiment, the line pressure control device 130 adjusts the line pressure PL by the ECU 140 so that the supply pressure Pin is lower than the supply pressure Pin at the time of hydraulic pressure holding control and becomes the supply pressure Pin at the time of the above-described shift fixing control. (T4 in the figure). That is, in the first embodiment, the hydraulic pressure holding control is performed by the ECU 140 until the hydraulic oil supply / discharge valve 70 is closed (t3 in the same figure) (t4 in the same figure). Therefore, when each hydraulic oil supply / discharge valve 70 is closed, the supply pressure Pin is maintained at the primary hydraulic pressure P1 by the hydraulic pressure holding control, so that the hydraulic oil is supplied to the primary hydraulic chamber 55 or the primary hydraulic chamber 55 when the valve is closed. Therefore, it is possible to suppress the hydraulic oil from being discharged, and it is possible to suppress the change in the gear ratio due to the valve closing. Thereby, the occurrence of shock at the end of the temporary opening / closing control can be suppressed, and drivability can be improved.

  Next, as shown in FIG. 9, ECU 140 clears the count K of the counter (K = 0) (step ST109).

  As described above, in the belt type continuously variable transmission 1-1 according to the first embodiment, when the transmission gear ratio is fixed, the hydraulic oil supply / discharge valve 70 is temporarily opened / closed and the hydraulic oil supply / discharge valve 70 is temporarily opened / closed. During the opening of the valve 70, the hydraulic fluid in the primary hydraulic chamber 55 and the upstream hydraulic fluid come into contact, and heat can be transferred between the hydraulic fluid in the primary hydraulic chamber 55 and the upstream hydraulic fluid. As shown in FIG. 10, the hydraulic oil temperature OT in the primary hydraulic chamber 55 rises (prior to t2 in the figure) while each hydraulic oil supply / discharge valve 70 is closed during the gear ratio fixed control. However, during the opening of each hydraulic oil supply / discharge valve 70 (t2 to t3 in the figure), when the oil temperature OT of the hydraulic oil in the primary hydraulic chamber 55 is higher than the oil temperature of the upstream hydraulic oil, the primary hydraulic chamber Heat is transferred from the hydraulic oil in 55 to the upstream hydraulic oil, and the oil temperature OT of the hydraulic oil in the primary hydraulic chamber 55 can be lowered. Therefore, an increase in the oil temperature of the hydraulic oil in the primary hydraulic chamber 55 when the speed ratio is fixed can be suppressed, and an increase in the oil temperature of the hydraulic oil can be suppressed. Since an increase in the oil temperature of the hydraulic oil can be suppressed, deterioration of the hydraulic oil can be suppressed. Further, since the increase in the temperature of the hydraulic oil can be suppressed, it is possible to suppress the deterioration of the primary hydraulic chamber seal member S1 and the communication portion seal member S3 that the hydraulic oil in the primary hydraulic chamber 55 contacts. it can. Further, since the increase in the oil temperature of the hydraulic oil can be suppressed, tempering of members (movable sheave 53, primary partition wall 54, etc.) constituting the primary hydraulic chamber 55 can be suppressed.

[Embodiment 2]
Next, the belt type continuously variable transmission according to the second embodiment will be described. FIG. 11 is a diagram illustrating a configuration example of a hydraulic control device and an ECU according to the second embodiment. FIG. 12 is a diagram showing an equipower line map. The belt type continuously variable transmission 1-2 according to the second embodiment is different from the belt type continuously variable transmission 1-1 according to the first embodiment in that the speed ratio γ is changed from the fixed speed ratio γh during the temporary opening / closing control. It is a point which changes and returns to fixed gear ratio (gamma) h. The basic configuration of the belt-type continuously variable transmission 1-2 according to the second embodiment is substantially the same as the basic configuration of the belt-type continuously variable transmission 1-1 according to the first embodiment. Description of is omitted.

  As shown in FIG. 11, the ECU 140 has an equal power line map storage unit 141 for the internal combustion engine 10 in advance. As shown in FIG. 12, the equal power line map includes the output torque T [Nm] of the internal combustion engine 10, the engine speed Ne [rpm] of the internal combustion engine 10, and the power [kW] generated by the internal combustion engine 10. A map with a relationship set. In the equal power line map, the relationship between the output torque T and the engine speed Ne required to generate an arbitrary power in the internal combustion engine 10 is set. An equal power line is set in the equal power line map. The power generated by the internal combustion engine 10 is kept constant as the internal combustion engine 10 maintains the relationship between the output torque T on the equal power line and the engine speed Ne. In the second embodiment, the ECU 140 performs constant power control for maintaining a fixed power at a fixed gear ratio based on the equal power line map and the engine speed Ne.

  The rotational speed sensor 150 detects the engine rotational speed Ne of the internal combustion engine 10. The rotational speed sensor 150 is connected to the ECU 140, and the detected engine rotational speed Ne is output to the ECU 140.

  In the belt-type continuously variable transmission 1-2 according to the second embodiment, as in the belt-type continuously variable transmission 1-1 according to the first embodiment, each operation in the valve-closed state is performed by the ECU 140 during the gear ratio fixed control. The actuator 80 is caused to perform temporary opening / closing control for opening and closing the oil supply / discharge valve 70 once through the hydraulic control device 130. FIG. 13 is a diagram illustrating a temporary opening / closing control flow of the belt-type continuously variable transmission according to the second embodiment. FIG. 14 is a diagram illustrating a change in the oil temperature during the temporary opening / closing control of the belt-type continuously variable transmission according to the second embodiment. FIG. 14 is a diagram showing the relationship among the drive oil pressure P2, the speed ratio γ, and the oil temperature OT. Hereinafter, the temporary opening / closing control during the shift fixing control will be described. The basic procedure of the temporary opening / closing control of the belt-type continuously variable transmission 1-2 according to the second embodiment is the same as the basic procedure of the temporary opening / closing control of the belt-type continuously variable transmission 1-1 according to the first embodiment. The description of the overlapping part is simplified or omitted.

  First, ECU 140 determines whether or not the shift fixing control is being performed as shown in FIG. 13 (step ST201). Here, ECU 140 determines whether or not the gear ratio fixing control is being performed in which the gear ratio γ is fixed and maintained at the fixed gear ratio γh.

  Next, when ECU 140 determines that the shift fixing control is being performed (Yes in step ST101), ECU 140 performs counting using a counter (step ST202).

  Next, ECU 140 determines whether or not the count value K of the counter is greater than or equal to a first predetermined value K1 (step ST203).

  Next, when ECU 140 determines that count value K of the counter is greater than or equal to first predetermined value K1 (Yes at step ST203), ECU 140 obtains engine speed Ne, output torque T, and equal power line map (step ST204). . Here, the ECU 140 acquires the engine speed Ne and the output torque T (and the equal power line map stored in the equal power line map storage unit 141) detected by the rotation sensor 150 and output to the ECU 140 (step ST204). .

  Next, ECU 140 calculates fixed power Ph (step ST205). Here, the ECU 140 calculates a fixed power Ph that is the power generated by the internal combustion engine 10 when the shift is fixed based on the acquired engine speed Ne and output torque T.

  Next, ECU 140 performs gear ratio increase control (step ST206). Here, as shown in FIG. 14, the ECU 140 opens each hydraulic oil supply / discharge valve 70 by the actuator 80, and discharges hydraulic oil from the primary hydraulic chamber 55 via the hydraulic control device 130 (t5 in FIG. 14). . As a result, the hydraulic control device 130 starts the temporary opening / closing control, the gear ratio γ is increased from the fixed gear ratio γh, and a downshift is performed. Here, when the transmission ratio increase control is performed by the ECU 140, the transmission ratio γ increases from the fixed transmission ratio γh. Therefore, as shown in FIG. 12, for example, when the fixed power Ph is calculated (point A in the figure). When the engine speed Ne is Ne1, the engine speed Ne increases to Ne2.

  Next, ECU 140 acquires engine speed Ne again as shown in FIG. 13 (step ST207).

  Next, ECU 140 performs constant power control (step ST208). Here, the ECU 140 may cause the internal combustion engine 10 to generate fixed power based on the calculated fixed power Ph, the engine speed Ne acquired again, and the acquired equal power line map. The output torque T that can be generated is calculated, and the internal combustion engine 10 is controlled so that the calculated output torque T is generated by the internal combustion engine 10. As shown in FIG. 12, even if the speed ratio γ increases from the fixed speed ratio γh, if the output torque T of the internal combustion engine 10 remains the output torque T1 when the fixed power Ph is calculated, the engine speed Since Ne1 has increased to the engine speed Ne2, the power generated by the internal combustion engine 10 is reduced from the fixed power Ph (point B in the figure). That is, if the output torque T generated by the internal combustion engine 10 is kept constant during the shift increase control by the ECU 140, the power generated by the internal combustion engine deviates from the equal power line corresponding to the fixed power Ph. During the primary opening / closing control of the belt-type continuously variable transmission 1-2 according to the second embodiment, when the engine speed Ne1 increases to the engine speed Ne2 due to the shift increase control, the ECU 140 increases the engine speed Ne2. The output torque T2 on the equal power line corresponding to the fixed power Ph is calculated, the output torque T2 is generated in the internal combustion engine 10, and the power generated by the internal combustion engine 10 during the shift increase control is maintained at the fixed power Ph. .

  Next, as shown in FIG. 13, ECU 140 determines whether or not counter value K is equal to or greater than a third predetermined value K3 (step ST209). Here, ECU 140 determines whether or not a third predetermined time has elapsed since the start of shift fixing control. Here, the third predetermined value K3 (third predetermined time) is an arbitrary value larger than the first predetermined value K1 (first predetermined time). For example, the third predetermined value K3 (third predetermined time) is an amount of change of the speed ratio γ with respect to the fixed speed ratio γh. It is preset based on this.

  Next, when ECU 140 determines that count value K of the counter is third predetermined value K3 (Yes in step ST209), ECU 140 performs gear ratio reduction control (step ST210). Here, as shown in FIG. 14, the ECU 140 maintains the opening of each hydraulic oil supply / discharge valve 70 by the actuator 80 and supplies the hydraulic oil to the primary hydraulic chamber 55 via the hydraulic control device 130 (see FIG. 14). t6). As a result, during the temporary opening / closing control, the hydraulic control device 130 reduces the speed ratio γ and performs an upshift. That is, the gear ratio decrease control is performed after the gear ratio increase control is performed during the temporary opening / closing control. Here, when the transmission ratio increase control is performed by the ECU 140, the transmission ratio γ decreases from the transmission ratio γ at the end of the transmission ratio increase control toward the fixed transmission ratio γh, and thus the engine speed at the end of the transmission ratio increase control. The engine speed Ne decreases with respect to Ne. If ECU 140 determines that count value K of the counter is not the third predetermined value K3 (No in step ST209), as shown in FIG. 13, the current control cycle is terminated, and the process proceeds to the next control cycle. Therefore, when the gear ratio fixed control is continued, the counter is counted until the counter count value K reaches the third predetermined value K3, the gear ratio increase control is maintained, and the gear ratio γ increases. .

  Next, ECU 140 obtains engine speed Ne again (step ST211).

  Next, ECU 140 performs constant power control (step ST212). Here, the ECU 140 is based on the calculated fixed power Ph, the engine speed Ne acquired again, and the acquired equal power line map, similarly to the constant power control during the shift increase control. Then, the output torque T that can be generated by the internal combustion engine 10 with the fixed power is calculated, and the internal combustion engine 10 is controlled so that the calculated output torque T is generated by the internal combustion engine 10. During the primary opening / closing control of the belt-type continuously variable transmission 1-2 according to the second embodiment, when the engine speed Ne is reduced by the shift reduction control, the fixed power Ph is set at the engine speed Ne reduced by the ECU 140. The output torque on the corresponding equal power line is calculated, the output torque is generated in the internal combustion engine 10, and the power generated by the internal combustion engine 10 during the shift reduction control is maintained at the fixed power Ph.

  Next, the ECU 140 determines whether or not the speed ratio γ has become the fixed speed ratio γh (step 213). Here, the ECU 140 determines whether or not the speed ratio γ increased with respect to the fixed speed ratio γh by the speed increase control has returned to the fixed speed ratio γh by the speed ratio reduction control.

  Next, when ECU 140 determines that gear ratio γ has become fixed gear ratio γh (Yes in step 213), ECU 140 ends the gear ratio reduction control and power constant control (step ST214). Here, when the transmission gear ratio γ becomes the fixed transmission gear ratio γh, the ECU 140 closes each hydraulic oil supply / discharge valve 70 by the actuator 80 and returns to the transmission gear ratio fixing control as shown in FIG. ). In addition, when the transmission gear ratio γ becomes the fixed transmission gear ratio γh, the ECU 140 permits a change in the power generated by the internal combustion engine 10 that has been maintained at the fixed power. If ECU 140 determines that gear ratio γ is not fixed gear ratio γh (No at step 213), ECU 140 ends the current control cycle and proceeds to the next control cycle. Therefore, when the gear ratio fixed control is continued, the gear ratio increase control is maintained until the gear ratio γ becomes the fixed gear ratio γh, and the gear ratio γ decreases toward the fixed gear ratio γh.

  Next, ECU 140 clears the count K of the counter (K = 0) (step ST215).

  As described above, in the belt type continuously variable transmission 1-2 according to the second embodiment, the hydraulic oil supply / discharge valve 70 is temporarily opened and closed when the transmission gear ratio is fixed, and the hydraulic oil supply / discharge valve is controlled. During the opening of the valve 70, the hydraulic fluid in the primary hydraulic chamber 55 and the upstream hydraulic fluid come into contact, and heat can be transferred between the hydraulic fluid in the primary hydraulic chamber 55 and the upstream hydraulic fluid. Also, during the temporary opening / closing control, after hydraulic oil is discharged from the primary hydraulic chamber 55 by performing a downshift, the hydraulic fluid is supplied to the primary hydraulic chamber 55 by performing an upshift until the gear ratio γ becomes the fixed gear ratio γh. Since the hydraulic oil is supplied, the hydraulic oil in the primary hydraulic chamber 55 and the upstream hydraulic oil can be exchanged while each hydraulic oil supply / discharge valve 70 is opened. As shown in FIG. 14, the oil temperature OT of the hydraulic oil in the primary hydraulic chamber 55 rises (prior to t5 in the figure) while each hydraulic oil supply / discharge valve 70 is closed during the gear ratio fixed control. However, during the opening of each hydraulic oil supply / discharge valve 70 (t5 to t7 in the figure), when the oil temperature OT of the hydraulic oil in the primary hydraulic chamber 55 is higher than the oil temperature of the upstream hydraulic oil, the primary hydraulic chamber As the heat is transferred from the hydraulic oil in 55 to the upstream hydraulic oil, the hydraulic oil in the primary hydraulic chamber 55 is replaced with the upstream hydraulic oil having a low oil temperature when the transmission gear ratio is fixed, and the operation in the primary hydraulic chamber 55 is performed. The oil temperature OT of the oil can be reliably reduced. Therefore, it is possible to effectively suppress an increase in the oil temperature of the hydraulic oil in the primary hydraulic chamber 55 when the speed ratio is fixed, and it is possible to effectively suppress an increase in the oil temperature of the hydraulic oil. In addition, since the power constant control is performed during the temporary opening / closing control, the power generated by the internal combustion engine 10 is maintained constant (fixed power) even if there is a change in the gear ratio γ when the gear ratio is fixed. The feeling of discomfort given can be suppressed. Further, the hydraulic oil leaks from the primary hydraulic chamber 55 and the hydraulic oil in the primary hydraulic chamber 55 expands due to the rise in the oil temperature OT, so that the fixed gear ratio γh at the time of the gear ratio fixing is just after the gear ratio fixing control. Even if the gear ratio γ is changed, the fixed gear ratio γh changed by performing the temporary opening / closing control can be returned to the gear ratio γ immediately after the gear ratio fixing control. Therefore, fuel consumption can be improved and drivability can be improved.

  In the first embodiment, the internal combustion engine 10 is used as a drive source. However, the present invention is not limited to this, and an electric motor such as a motor may be used as the drive source.

  In the second embodiment, switching from the speed ratio increase control to the speed ratio decrease control is performed based on whether or not the counter count value K is the third predetermined value K3, but is not limited to this. Alternatively, it may be performed based on the amount of change of the transmission gear ratio γ with respect to the fixed transmission gear ratio γh.

  In the second embodiment, the gear ratio decrease control is performed after the gear ratio increase control is performed during the temporary opening / closing control, that is, the hydraulic oil is discharged from the primary hydraulic chamber 55 and then the primary hydraulic chamber 55 is operated. However, the present invention is not limited to this, and the gear ratio increase control is performed after the gear ratio decrease control is performed, that is, the hydraulic oil is supplied from the primary hydraulic chamber 55 to the primary hydraulic chamber 55. The hydraulic oil may be discharged.

  In the first and second embodiments, during the gear ratio increase control, the temporary opening / closing control is performed only once. However, the present invention is not limited to this and may be performed a plurality of times.

  In the first and second embodiments, the start of the temporary opening / closing control is determined by the elapsed time from the start of the gear ratio fixed control. However, the present invention is not limited to this, and the hydraulic oil in the primary hydraulic chamber 55 is not limited to this. Temporary opening / closing control may be started based on the temperature OT.

  As described above, the belt-type continuously variable transmission according to the present invention is useful for a belt-type continuously variable transmission that holds hydraulic oil in a drought pressure generating hydraulic chamber by closing a hydraulic oil supply / discharge valve. In particular, it is suitable for suppressing an increase in the temperature of hydraulic oil.

It is a skeleton figure of the belt type continuously variable transmission concerning the present invention. It is principal part sectional drawing of the primary pulley at the time of gear ratio fixation. It is a figure which shows a torque cam. It is operation | movement explanatory drawing of a torque cam. 1 is a diagram illustrating a configuration example of a hydraulic control device and an ECU according to a first embodiment; It is operation | movement explanatory drawing of the belt type continuously variable transmission at the time of gear ratio change. It is operation | movement explanatory drawing of the belt type continuously variable transmission at the time of gear ratio change. It is operation | movement explanatory drawing of the belt type continuously variable transmission at the time of gear ratio change. It is operation | movement explanatory drawing of the belt type continuously variable transmission at the time of gear ratio change. It is a figure which shows the temporary opening / closing control flow of the belt-type continuously variable transmission concerning Embodiment 1. FIG. It is a figure which shows the change of the oil temperature at the time of temporary opening / closing control of the belt-type continuously variable transmission concerning Embodiment 1. FIG. It is a figure which shows the structural example of the hydraulic control apparatus and ECU concerning Embodiment 2. FIG. It is a figure which shows an equal power line map. It is a figure which shows the temporary opening and closing control flow of the belt-type continuously variable transmission concerning Embodiment 2. FIG. It is a figure which shows the change of the oil temperature at the time of temporary opening / closing control of the belt-type continuously variable transmission concerning Embodiment 2. FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Belt type continuously variable transmission 10 Internal combustion engine 20 Transaxle 30 Torque converter 40 Forward / reverse switching mechanism 50 Primary pulley 51 Primary pulley shaft 51a Supply / discharge side main passage 52 Primary fixed sheave 53 Primary movable sheave 54 Primary partition wall 55 Primary hydraulic chamber 56 Valve arrangement member 57 Cover member 58 Bulkhead fixing member 59 Snap ring 60 Secondary pulley 64 Secondary hydraulic chamber 70 Hydraulic oil supply / discharge valve 71 Valve body 72 Valve seat surface 73 Valve body elastic member 80 Actuator 81 Drive hydraulic chamber 82 Piston 83 Piston elastic member 84 Cancellation chamber 85 Elastic member holding member 90 Final reduction gear 100 Power transmission path 110 Belt 112 Pulley bearing 120 Wheel 130 Hydraulic control device 131 Oil pan 132 Oil pump 33 line pressure control device 134 constant pressure control device 135 the primary hydraulic chamber control device 136 drives the hydraulic chamber control unit 137 secondary hydraulic chamber control device 140 ECU
141 equal power line map storage portion S1 seal member for primary hydraulic chamber S2, S3 seal member for communication portion S4 seal member for drive hydraulic chamber S5 seal member for cancel chamber

Claims (6)

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 the one clamping pressure generating hydraulic chamber or discharging 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;
With
The belt-type continuously variable transmission, wherein the valve opening / closing control means performs temporary opening / closing control for opening / closing the hydraulic oil supply / discharge valve at least once when the gear ratio is fixed.   The belt-type continuously variable transmission according to claim 1, wherein the valve opening / closing control means is an actuator operated by the hydraulic pressure. A hydraulic control means for controlling supply / discharge of hydraulic oil to / from at least one clamping pressure generating hydraulic chamber;
The hydraulic control means performs hydraulic pressure holding control that uses the pressure of the hydraulic oil supplied to the one clamping pressure generating hydraulic chamber as the hydraulic pressure of the one clamping pressure generating hydraulic chamber when the speed ratio is fixed during the temporary opening / closing control. The belt-type continuously variable transmission according to claim 1 or 2.   The belt-type continuously variable transmission according to claim 3, wherein the hydraulic pressure control means performs the hydraulic pressure holding control before the hydraulic oil supply / discharge valve is opened.   The belt-type continuously variable transmission according to claim 3 or 4, wherein the hydraulic pressure control means performs the hydraulic pressure holding control until after the hydraulic oil supply / discharge valve is closed. The drive source is an internal combustion engine;
Hydraulic control means for controlling supply and discharge of hydraulic fluid to at least one of the clamping pressure generating hydraulic chambers;
Control means for controlling the hydraulic control means and the internal combustion engine;
Further comprising
In the temporary opening / closing control, the control means may either supply hydraulic oil to the one clamping pressure generating hydraulic chamber or discharge hydraulic oil from the one clamping pressure generating hydraulic chamber by the hydraulic control means. After performing one of these, performing the other until the transmission gear ratio becomes the fixed transmission gear ratio, and performing power constant control for maintaining the power of the internal combustion engine at the fixed power when the transmission gear ratio is fixed. The belt-type continuously variable transmission according to claim 1 or 2, characterized by the above.

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