JP5045544B2 - Belt type continuously variable transmission - Google Patents

Description

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

  In general, a vehicle 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 that is the drive source to the road surface under the 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 drive source is transmitted, a secondary pulley that changes and outputs output torque transmitted to the primary pulley, and the primary pulley. There is a belt-type continuously variable transmission that includes a belt that transmits a transmitted output torque to a secondary pulley. The 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.

  The 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, for example, as shown in Patent Documents 1 and 2, there is a technique for holding hydraulic oil in the clamping pressure generating hydraulic chamber. In the belt-type continuously variable transmission as shown in Patent Documents 1 and 2, a supply / discharge path for supplying hydraulic oil to the clamping pressure generating hydraulic chamber and discharging hydraulic oil from the clamping pressure generating hydraulic chamber, and a clamping pressure generation A hydraulic oil supply / discharge valve is provided between the hydraulic chamber and hydraulic oil is supplied to the hydraulic pressure generating hydraulic chamber when the hydraulic oil supply / discharge valve is opened, or hydraulic oil is discharged from the hydraulic pressure generating hydraulic chamber and closed. The hydraulic oil is confined in the clamping pressure generating hydraulic chamber. In the belt-type continuously variable transmission shown in Patent Document 2, the hydraulic oil supply and discharge valve is opened by moving the valve body in the direction in which hydraulic oil is supplied to the clamping pressure generating hydraulic chamber with respect to the valve seat. The hydraulic oil supply / discharge valve is closed by moving the valve body in the direction in which the hydraulic oil is discharged from the clamping pressure generating hydraulic chamber with respect to the valve seat. That is, in the conventional belt-type continuously variable transmission, the opening direction of the hydraulic oil supply / discharge valve is the direction in which the hydraulic oil is supplied to the clamping pressure generating hydraulic chamber, and the closing direction is the hydraulic oil from the clamping pressure generating hydraulic chamber. Was in the direction of being discharged. The opening of the hydraulic oil supply / discharge valve increases the drive hydraulic pressure of the drive hydraulic chamber of the actuator and moves the piston in the direction in which the hydraulic oil is supplied to one clamping pressure generating hydraulic chamber, thereby contacting the piston. This is done by moving the valve body relative to the valve seat.

JP 2006-300270 A JP 2007-263243 A

  By the way, in the conventional belt type continuously variable transmission, since the hydraulic pressure of the clamping pressure generating hydraulic chamber acts on the valve body in the valve closing direction, the hydraulic pressure in the valve closing direction is applied to the valve body by the hydraulic pressure of the clamping pressure generating hydraulic chamber. The pressing force acts as a valve body closing direction pressing force that is a pressing force for closing the valve body. In addition, the drive hydraulic pressure force in the valve opening direction acts on the valve body via the piston as the valve body valve opening direction pressing force, which is the pressing force for opening the valve body. Therefore, in order to open the hydraulic oil supply / discharge valve, a valve body opening direction pressing force exceeding the valve body closing direction pressing force is applied to the valve body. For this reason, in order to open the hydraulic oil supply / discharge valve, the hydraulic oil is supplied to the drive hydraulic chamber and the drive hydraulic pressure is increased.

  When the drive oil pressure is increased, the time is longer than when the drive oil pressure is reduced. Therefore, the conventional belt type continuously variable transmission may have a longer valve opening time. Therefore, there is a possibility that the responsiveness of the shift performed by opening the hydraulic oil supply / discharge valve, particularly when the gear ratio is reduced, that is, the downshift is not sufficient.

  Also, in the conventional belt type continuously variable transmission, when the drive hydraulic pressure cannot be increased, it is difficult to open the hydraulic oil supply / discharge valve, and there is a possibility that the hydraulic oil is held in the clamping pressure generating hydraulic chamber. there were. Therefore, there is a possibility that the gear ratio is fixed, and when the fixed gear ratio is a high gear ratio, it is difficult to reduce the gear ratio, so that the controllability of the gear ratio may be deteriorated.

  Accordingly, 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 improve at least one of speed change response and speed ratio controllability. It is what.

  In order to solve the above-described problems and achieve the object, a belt-type continuously variable transmission according to the present invention includes two pulleys, a belt that is wound around each pulley and transmits output torque from a drive source. A clamping pressure generating hydraulic chamber that is formed in each pulley and 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 and the one clamping pressure generating hydraulic chamber A supply / discharge path for discharging the hydraulic oil from the gas supply line and the supply / discharge path, and when supplying the hydraulic oil to the one clamping pressure generating hydraulic chamber or discharging the hydraulic oil from the one clamping pressure generating hydraulic chamber A hydraulic oil supply / discharge valve that opens when the hydraulic oil is held in the one clamping pressure hydraulic pressure generating chamber and rotates integrally with the one pulley, and an opening / closing valve for the hydraulic oil supply / discharge valve To control The hydraulic oil supply / discharge valve has a valve body and a valve seat, and the valve body is discharged from the one clamping pressure generating hydraulic chamber with respect to the valve seat. The actuator is slidably supported in the drive hydraulic chamber to which the hydraulic oil is supplied and the on-off valve direction of the hydraulic oil supply / discharge valve, and is driven by the drive hydraulic chamber. And a piston formed with a drive hydraulic pressure receiving portion in which the hydraulic pressure acts in the valve closing direction, and the piston is disposed at a position facing the valve seat with the valve body interposed therebetween, and the valve body is A supply pressure receiving portion is formed which is fixed and at least the pressure of the hydraulic oil supplied to the one clamping pressure generating hydraulic chamber acts in the valve opening direction when the hydraulic oil supply / discharge valve is closed. To do.

  In the belt-type continuously variable transmission, it is preferable that the drive hydraulic pressure receiving portion and the supply pressure receiving portion are flange portions that protrude radially outward from the outer peripheral surface of the piston and face the valve seat. .

  In the belt type continuously variable transmission, it is preferable that the hydraulic oil supply / discharge valve and the actuator are arranged coaxially with the pulley shaft inside the pulley shaft of the one pulley.

  Further, in the belt type continuously variable transmission, the piston constitutes the supply / discharge path, and a piston passage for supplying hydraulic oil supplied to the one clamping pressure generating hydraulic chamber to the supply pressure receiving portion is formed. It is preferable that

  In the belt-type continuously variable transmission, the actuator further includes a drive oil path member that supplies the hydraulic oil to a drive hydraulic chamber, and the drive oil path member is an inner periphery of a pulley shaft of the one pulley. It is preferable to form a drive side communication passage that communicates with the drive hydraulic chamber between the surface.

  In the belt type continuously variable transmission, it is preferable that the valve seat is formed integrally with a pulley shaft of the one pulley.

  In the belt type continuously variable transmission according to the present invention, the drive hydraulic pressure acts on the valve body in the valve closing direction via the piston, and the drive hydraulic pressure in the valve closing direction acts on the valve body via the piston by the drive hydraulic pressure. The pressing force acts as a valve body closing direction pressing force that is a pressing force for closing the valve body. Also, the hydraulic pressure of one clamping pressure generating hydraulic chamber acts on the valve body in the valve opening direction, and the hydraulic pressure in the valve opening direction opens the valve body by the hydraulic pressure of one clamping pressure generating hydraulic chamber. It acts as a valve body opening direction pressing force that is a pressing force to be generated. Also, the hydraulic oil pressure supplied to one clamping pressure generating hydraulic chamber acts on the piston in the valve opening direction, and the supply pressure pressing force in the valve opening direction is applied to the valve body via the piston. Acts as a pressing force. Therefore, by reducing the drive hydraulic pressure, the valve body closing direction pressing force acting on the valve body can be reduced, and the valve body opening direction pressing force exceeding the valve body closing direction pressing force can be applied to the valve body. The valve body hydraulic oil supply / discharge valve can be opened. As a result, the opening time of the hydraulic oil supply / discharge valve can be shortened, and the responsiveness of the shift performed by opening the hydraulic oil supply / discharge valve can be improved.

  In addition, the belt type continuously variable transmission according to the present invention operates even when there is an abnormality in which the drive hydraulic pressure cannot be increased because the hydraulic pressure force and the supply pressure pressure force act on the valve body as the valve body opening direction pressing force. The oil supply / discharge valve can be opened. Therefore, it is possible to suppress the fixed gear ratio and to improve the controllability of the gear ratio.

  In the belt type continuously variable transmission according to the present invention, since the piston passage of the piston constitutes the supply / discharge path, the supply / discharge path need not be formed in the outer peripheral portion of the piston. Therefore, the diameter of the piston can be increased, and the area of the drive hydraulic pressure receiving portion can be ensured. Thereby, even if drive hydraulic pressure is low, there exists an effect that the valve body valve closing direction pressing force which can close a hydraulic-oil supply discharge valve can be maintained with driving hydraulic pressure. Further, since the supply / discharge path does not need to be formed on the outer peripheral portion of the piston, there is an effect that the size can be reduced.

  In the belt type continuously variable transmission according to the present invention, the valve seat is formed integrally with the pulley shaft, so that the valve seat surface that contacts the valve body can be formed by processing the pulley shaft. . Therefore, there is an effect that the number of parts can be reduced and the cost can be reduced.

  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 those that are substantially the same. Here, an internal combustion engine (gasoline engine, diesel engine, LPG engine, etc.) is used as a drive source for generating output torque transmitted to the belt-type continuously variable transmission in the following embodiment, but is not limited to this. Instead, an electric motor such as a motor may be used as a drive source. In the following embodiments, 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
FIG. 1 is a skeleton diagram of a belt type continuously variable transmission according to an embodiment. 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. FIG. 5 is a diagram showing a closing operation flow of the hydraulic oil supply / discharge valve, and FIG. 6 is a diagram showing changes in the gear ratio and the like when the hydraulic oil supply / discharge valve is closed. FIG. 7 is a diagram illustrating a valve opening operation flow of the hydraulic oil supply / discharge valve. FIG. 8 is a diagram illustrating a change in a gear ratio and the like when the hydraulic oil supply / discharge valve is opened. 9 to 12 are operation explanatory views of the belt type continuously variable transmission at the time of changing the gear ratio.

  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, in the case constituted by the transaxle case 22 and the transaxle rear cover 23, a primary pulley 50 and a secondary pulley 60 which are two pulleys constituting the belt type continuously variable transmission 1 according to the embodiment, 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. 2, the transaxle rear cover 23 is formed with a protruding portion 23a, a supply / discharge side main passage 23b, and a drive side main passage 23c. The projecting portion 23 a is formed so as to project from the position facing the primary pulley shaft 51, which will be described later, to the primary pulley 50 side on the surface of the transaxle rear cover 23 on the primary pulley 50 side. One end of the supply / discharge-side main passage 23 b communicates with a space T <b> 1 described later, and the other end communicates with an oil passage R <b> 7 described later of the hydraulic control device 130. In the supply / discharge-side main passage 23b, hydraulic fluid 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. One end of the drive side main passage 23c communicates with a space T2 described later, and the other end communicates with an oil passage R8 of the hydraulic control device 130. The hydraulic fluid supplied from the hydraulic control device 130 to the drive hydraulic chamber 81 (described later) of the actuator 80 flows into the drive side main passage 23c. In the embodiment, the driving side main passage 23c 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 T1 is a part of a piston sliding passage 83a of a driving hydraulic member 83 (to be described later) of the actuator 80, and is formed between the protruding portion 23a, the piston 82, and the driving oil passage member 83. . In the embodiment, the space portion T <b> 1 is formed between the axial end surface of the protruding portion 23 a, the other end surface of the piston 82, and the inner peripheral surface of the drive oil passage member 83. The space portion T1 has a ring shape, and the other end portion (left side end portion in the figure) in the axial direction communicates with the supply / discharge side main passage 23b, and one end portion (right end portion in the figure) is the piston passage. 82a.

  The space portion T2 is formed between the protruding portion 23a and a drive oil passage member 83 described later. In the embodiment, the space portion T <b> 2 is formed between the outer peripheral surface of the protruding portion 23 a and the inner peripheral surface of the drive oil passage member 83. The space T2 has a ring shape, and the radially inner end (the lower end in the figure) communicates with the drive side main passage 23c, and the radially outer end (the upper end in the figure) has the drive oil. The passage member 83 communicates with a drive side communication passage 83b described later. That is, the drive side main passage 23c communicates with the drive side communication passage 83b via the space T2. Note that a communication portion seal member S1 such as a seal ring is provided between the outer peripheral surface of the protruding portion 23a and the inner peripheral surface of the drive oil passage member 83 with the space T2 interposed therebetween.

  As shown in FIG. 1, the torque converter 30 serving as a starting mechanism increases or transmits the output torque T from the internal combustion engine 10 serving as a driving source to the belt type continuously variable transmission 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. Further, a lockup clutch 34 that is controlled by supplying hydraulic oil from the hydraulic control device 130 is disposed between the turbine 32 and the front cover 37, and the lockup clutch 34 is a damper device 35. It is connected to the input shaft 38 via.

  Here, the operation of the torque converter 30 will be described. The 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 by the hydraulic control device 130, the output torque T from the internal combustion engine 10 transmitted to the front cover 37 is transmitted to the pump 31 and circulates between the pump 31 and the turbine 32. Is transmitted to the turbine 32 via the hydraulic oil. 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. 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 hydraulic control device 130, the output torque T from the internal combustion engine 10 transmitted to the front cover 37 does not pass through the hydraulic oil. To the input shaft 38 directly. 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 a hydraulic control device 130 to a hollow portion (not shown) of the input shaft 38 that is a hydraulic oil supply portion. When the forward clutch 42 is OFF, the output torque 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 the pinions 45 rotating relative to each other. .

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

  The primary pulley 50 of the belt-type continuously variable transmission 1 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, and a lock ring 56. Has been. The primary pulley 50 is formed with one supply / discharge path for supplying hydraulic oil to the primary hydraulic chamber 55 and 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 valve arrangement passage 51a in which one end of the both ends in the axial direction is closed and the other end (the end facing the transaxle rear cover 23) is opened. Yes. The hydraulic oil supply / discharge valve 70 is inserted into the valve arrangement passage 51a from the other end, the actuator 80 is inserted coaxially with the hydraulic oil supply / discharge valve 70, and the protrusion 23a is connected to the hydraulic oil supply / discharge valve 70 and It is inserted coaxially with the actuator 80. Here, the pulley bearing 112 is sandwiched between a stepped portion formed on the surface of the transaxle rear cover 23 facing the primary pulley shaft 51 and the stopper plate 23e, and a bolt 23d (in the embodiment, on the circumference). It is fixed to the transaxle rear cover 23 at a plurality of positions at equal intervals. Reference numeral 23f denotes a spacer that adjusts the distance between the transaxle rear cover 23 and the stopper plate 23e.

  The shaft side communication passage 51b constitutes a part of the supply / discharge path. The shaft side communication passage 51b communicates with the space portion T3 by having one end portion communicating with the valve arrangement 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 51b is formed at a plurality of locations (for example, three locations) at equal intervals on the circumference.

  The space T3 constitutes a part of the supply / discharge path. The space portion T3 is formed between the primary movable sheave 53 and the primary pulley shaft 51. In the embodiment, the space T3 is formed by the inner peripheral surface of the primary movable sheave 53, that is, the surface sliding 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. It is formed between. The space T3 has a ring shape, and its radially inner end (lower end in the figure) communicates with each axial communication passage 51b, and its radially outer end (upper end in the figure) is movable. The sheave side communication passage 53e communicates. That is, the shaft side communication passage 51b communicates with the movable sheave side communication passage 53e via the space T3.

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

  As shown in FIG. 2, the primary movable sheave 53 includes a cylindrical portion 53a and an annular portion 53b. The cylindrical portion 53 a is formed around the same rotational axis as the primary pulley shaft 51. A movable sheave side communication passage 53e is formed in the cylindrical portion 53a. The movable sheave side communication passage 53e constitutes a part of the supply / discharge path. In the movable sheave side communication passage 53e, the radially inner end (lower end in the figure) communicates with the space T3, and the radially outer end (upper end in the figure) communicates with the primary hydraulic chamber 55. is doing. Here, the movable sheave side communication passage 51e is formed at a plurality of locations (for example, three locations) at equal intervals on the circumference. The annular portion 53b is formed so as to protrude radially outward from the end portion of the cylindrical portion 53a on the primary fixed sheave side. The primary movable sheave 53 is axially connected to the primary pulley shaft 51 by spline-fitting a spline 53c formed on the inner peripheral surface of the cylindrical portion 53a and a spline 51c 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. The space T3 may be communicated with the primary hydraulic chamber 55 through a space between the spline 53c and the spline 51c.

  As shown in FIG. 2, the primary partition wall 54 is an annular member and is disposed coaxially with 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. Here, the movement of the primary partition wall 54 in the axial direction with respect to the primary pulley shaft 51 is restricted by the lock ring 56. Specifically, the primary partition wall 54 is inserted into the primary pulley shaft 51 up to the step portion formed on the outer peripheral surface of the primary pulley shaft 51 and the bearing 112 is inserted, and then the lock ring 56 is connected to the other end of the primary pulley shaft 51 ( It is inserted and fixed to the primary pulley shaft 51 from the end facing the transaxle rear cover 23. As a result, the primary partition wall 54 is sandwiched between the primary pulley shaft 51 and the lock ring 56 via the bearing 112, and movement in the axial direction with respect to the primary pulley shaft 51 is restricted.

  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 52, the primary pulley 50, that is, a V-shaped primary groove. A belt clamping pressure is generated with respect to the belt 110 wound around 110a. The primary hydraulic chamber 55 is a space formed by the primary pulley shaft 51, the primary movable sheave 53, and the primary partition wall 54. Here, between the protrusion 53d of the primary movable sheave 53 and the primary partition wall 54 and between the cylindrical portion 53a of the primary movable sheave 53 and the primary pulley shaft 51, for example, a seal member S2 for a primary hydraulic chamber such as a seal ring. Is provided. Therefore, 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 S2.

  The primary hydraulic chamber 55 is supplied with hydraulic oil from the hydraulic control device 130 that has flowed into the supply / discharge-side main passage 23b. 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 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. Further, the secondary pulley shaft 61 has a hydraulic oil passage (not shown) therein, and hydraulic oil supplied from the hydraulic control device 130 to the secondary hydraulic chamber 64 flows into the hydraulic oil passage.

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

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

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

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

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

  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. Note that the secondary hydraulic chamber 64 may be the only means for generating the belt clamping pressure for the belt 110 in the secondary pulley 60.

  The hydraulic oil supply / discharge valve 70 is opened when hydraulic oil is supplied to the primary hydraulic chamber 55 that is one clamping pressure generating hydraulic chamber, or when hydraulic fluid is discharged from the primary hydraulic chamber 55. In the embodiment, when the 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, 9, and 11, 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 in a valve arrangement passage 51a formed in the primary pulley shaft 51 of the primary pulley 50 which is one pulley. That is, the hydraulic oil supply / discharge valve 70 is arranged coaxially with the primary pulley shaft 51 inside the primary pulley shaft 51. Therefore, 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 is a check valve and includes a valve body 71, a valve seat 72, a valve body elastic member 73, and a valve seat fixing member 74. The valve body 71 has a spherical shape, is disposed closer to the transaxle rear cover 23 than the valve seat 72, and has a diameter larger than an inner diameter of a valve seat surface 72b described later of the valve seat 72. The valve seat 72 is fixed to the valve arrangement passage 51a by being arranged between a valve seat fixing member 74 fixedly inserted into the valve arrangement passage 51a, for example, a snap ring, and one end of the valve arrangement passage 51a. Has been. The valve seat 72 has a valve seat passage 72a in which one end of the both ends in the axial direction is closed and the other end (the end facing the transaxle rear cover 23) is opened to communicate with the space T4. Is formed. The valve seat passage 72a constitutes a part of the supply / discharge path. Further, the valve seat 72 has a valve seat surface 72b formed at the other end. The valve seat surface 72b is continuous with the inner wall surface forming the valve seat passage 72a, and is a tapered surface that inclines radially inward as it goes toward the primary fixed sheave 52 in the axial direction. That is, the valve seat surface 72b is formed so as to face the other end of the valve arrangement passage 51a. The valve seat 72 is formed with a valve seat side communication passage 72c having one end portion communicating with the valve seat passage 72a and the other end portion communicating with the shaft side communication passage 51b. That is, the primary hydraulic chamber 55 communicates with the valve seat passage 72a. The valve seat side communication path 72c constitutes a part of the supply / discharge path. Here, the valve seat side communication passage 72c is formed at a plurality of locations (for example, three locations) at equal intervals on the circumference.

  The space T4 constitutes a part of the supply / discharge path. The space T4 is a part of the valve arrangement passage 51a and is formed between the primary pulley shaft 51, the valve seat 72, and the piston 82. In the embodiment, the space T4 includes an inner peripheral surface of the primary pulley shaft 51, the other end surface of the valve seat 72 (including the valve seat surface 72b), and a valve seat of a flange portion 82b of the piston 82, which will be described later, of the actuator. It is formed between the side surface on the 72 side (including the outer peripheral surface on the valve seat 72 side relative to the flange portion 82b of the piston 82). The space T4 has a radially inner end (lower end in the figure) communicating with each piston-side communication passage 82c, and one end in the axial direction (right end in the figure) is connected to the valve seat passage 72a. Communicate. That is, the valve seat passage 72a communicates with the piston side communication passage 82c via the space portion T4.

  In the hydraulic oil supply / discharge valve 70, the valve body 71 is in contact with the valve seat surface 72b of the valve seat 72, so that the communication between the valve seat passage 72a and the space T4 constituting a part of the supply / discharge path 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 valve 70 is closed. Further, when the valve body 71 that has been in contact is separated from the valve seat surface 72b, the valve seat passage 72a and the space portion T4 are communicated, that is, the supply / discharge path and the primary hydraulic chamber 55 are communicated, and hydraulic oil supply / discharge is performed. The valve 70 is opened. The hydraulic oil supply / discharge valve 70 is opened when the valve body 71 moves in a direction in which hydraulic oil is discharged from the primary hydraulic chamber 55 with respect to the valve seat 72, and the valve body 71 is primary with respect to the valve seat 72. The valve is closed by moving in the direction in which hydraulic oil is supplied to the hydraulic chamber 55. That is, the opening direction of the hydraulic oil supply / discharge valve 70 is a direction in which the hydraulic oil is discharged from the primary hydraulic chamber 55, and the valve closing direction is a direction in which the hydraulic oil is supplied to the primary hydraulic chamber 55. When the hydraulic oil supply / discharge valve 70 is opened, the hydraulic oil in the primary pulley 50 and the hydraulic oil in the supply / discharge path, in the embodiment, upstream of the hydraulic oil supply / discharge valve 70 (each hydraulic oil supply / discharge The hydraulic oil in the space T4, which is the hydraulic oil on the side opposite to the primary hydraulic chamber 55 side across the valve 70, comes into contact. Here, when the hydraulic oil supply / discharge valve 70 is closed, the primary hydraulic pressure P 1 of the primary hydraulic chamber 55 acts on the valve body 71. Accordingly, when the hydraulic oil supply / discharge valve 70 is closed, the primary hydraulic pressure in the valve opening direction acts on the valve element 71 as the valve element opening direction pressing force by the primary hydraulic pressure P1. Accordingly, the valve body 71 is pressed against the valve seat surface 72b, and the hydraulic oil supply / discharge valve 70 functions as a check valve.

  The valve body elastic member 73 is a valve body valve closing direction pressing force generating means, and applies a valve body valve closing direction pressing force to the valve body 71 to press the valve body 71 in the valve closing direction. The valve body elastic member 73 is, for example, a coil spring, and is housed in a drive hydraulic chamber 81 described later of the actuator 80. The valve body elastic member 73 is disposed in a state of being biased between a piston 82 (described later) of the actuator 80 and the drive oil passage member 83. That is, the valve body elastic member 73 is arranged in a state of being biased between the valve body 71 and the primary pulley shaft 51 to which the drive oil passage member 83 is fixed. Thereby, the valve body elastic member 73 generates a valve closing biasing force, and the valve closing biasing force, that is, the elastic member pressing force in the valve closing direction acts on the piston 82 and is fixed to the piston 82 described later. The elastic member pressing force acts on the valve body 71 as a valve body closing direction pressing force.

  Here, when the hydraulic oil supply / discharge valve 70 is opened, the valve body valve opening direction pressing force, which is the pressing force acting on the valve body 71 in the direction in which the valve body 71 moves away from the valve seat 72, that is, the valve opening direction, is The valve body 71 exceeds the valve closing direction pressing force which is the pressing force acting on the valve body 71 in the direction in which the valve body 71 contacts the valve seat 72, that is, in the valve closing direction, and the valve body 71 moves away from the valve seat 72. Is called. The hydraulic oil supply / discharge valve 70 is opened when hydraulic oil is supplied to the primary hydraulic chamber 55 and when hydraulic oil is discharged from the primary hydraulic chamber 55. Further, when the hydraulic oil supply / discharge valve 70 is closed, the valve body closing direction pressing force exceeds the valve body opening direction pressing force, and the valve body 71 comes into contact with the valve seat 72. The hydraulic oil supply / discharge valve 70 is closed when the hydraulic oil is held in the primary hydraulic chamber 55.

  Here, the hydraulic oil supply / discharge valve 70 is opened and closed 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. To be spoken. That is, the actuator 80 opens the hydraulic oil supply / discharge valve 70 when discharging hydraulic oil from the primary hydraulic chamber 55, and opens the hydraulic oil supply / discharge valve 70 also when supplying hydraulic oil to the primary hydraulic chamber 55. When the hydraulic oil is held in the primary hydraulic chamber 55, the valve is closed.

  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. As shown in FIGS. 2, 9, and 11, the actuator 80 includes a drive hydraulic chamber 81, a piston 82, and a drive oil path member 83. Here, the actuator 80 is arranged in a valve arrangement passage 51 a formed in the primary pulley shaft 51. That is, the actuator 80 is disposed coaxially with the primary pulley shaft 51 inside the primary pulley shaft 51. Therefore, the actuator 80 rotates integrally with the primary pulley 50 that is one pulley.

  The drive hydraulic chamber 81 is supplied with hydraulic oil, and controls the opening and closing 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. . The drive hydraulic chamber 81 is a part of the valve arrangement passage 51 a and is formed between the piston 82, the primary pulley shaft 51, and the drive oil passage member 83. In the embodiment, the drive hydraulic chamber 81 is a ring-shaped space, and the inner peripheral surface of the primary pulley shaft 51 and the side surface (piston 82) opposite to the valve seat 72 side of a flange portion 82b described later of the piston 82. The outer peripheral surface on the opposite side to the valve seat 72 side of the flange portion 82b) and one end surface of both end surfaces in the axial direction of the drive oil passage member 83 (on the opposite side to the valve seat 72 side of the flange portion 82b). It is formed between the side surface and the opposite end surface). The drive hydraulic chamber 81 is supplied with hydraulic oil from the hydraulic control device 130 via a drive side communication passage 83b (described later) of the drive oil passage member 83, the space T2, and the drive side main passage 23c.

  The piston 82 slides with respect to the drive hydraulic chamber 81 in the other of the sliding directions, that is, in the valve opening direction (the left direction in the figure), which is the other of the axial directions, by the drive hydraulic pressure P2 of the drive hydraulic chamber 81. Thus, the hydraulic oil supply / discharge valve 70 is opened. The piston 82 is disposed at a position facing the valve seat 72 in the axial direction with the valve body 71 interposed therebetween. The piston 82 is formed with a piston passage 82a that is open at both ends in the axial direction. The piston passage 82a constitutes a part of the supply / discharge path. Moreover, the valve body 71 is being fixed to one edge part (edge part which opposes the valve seat 72) among piston both ends in the axial direction. That is, in the piston passage 82a, one end portion of both end portions in the axial direction is closed by the valve body 71, and the other end portion communicates with the space portion T1.

  The piston 82 has a flange portion 82b. The flange portion 82b is formed so as to protrude radially outward from the outer peripheral surface of the piston 82 (in the embodiment, substantially the central portion in the axial direction). The flange portion 82b is formed to face the valve seat 72 in the axial direction so as to face the inner peripheral surface of the primary pulley shaft 51 in the radial direction. That is, the piston 82 is slidably supported in the axial direction by the primary pulley shaft 51, that is, slidably supported in the opening / closing direction of the hydraulic oil supply / discharge valve 70. The piston 82 has a piston-side communication passage 82c in which one end portion communicates with the piston passage 82a and the other end portion communicates with the space portion T4. That is, the primary hydraulic chamber 55 communicates with the piston passage 82a when the hydraulic oil supply / discharge valve 70 is opened. The piston side communication passage 82c constitutes a part of the supply / discharge path. Here, the piston-side communication passage 82c is formed at a plurality of locations (for example, three locations) at equal intervals on the circumference. Here, between the flange portion 82b of the piston 82 and the primary pulley shaft 51 and between the vicinity of the other end portion of the axial end portions of the piston 82 and the drive oil passage member 83, for example, a seal ring or the like The drive hydraulic chamber seal member S3 is provided. That is, the space T4 formed by the primary pulley shaft 51, the piston 82, and the drive oil passage member 83 constituting the drive hydraulic chamber 81 is sealed by the drive hydraulic chamber seal member S3.

  Here, the flange portion 82b of the piston 82 forms a part of the drive hydraulic chamber 81, and the drive hydraulic pressure P2 of the drive hydraulic chamber 81 acts in the valve closing direction on the side surface opposite to the valve seat 72 side. As a result, the piston 82 is formed with a flange portion 82b as a drive hydraulic pressure receiving portion where the drive hydraulic pressure P2 of the drive hydraulic chamber 81 acts in the valve closing direction. Therefore, the drive hydraulic pressure P2 acts on the piston 82 in the valve closing direction. As a result, the drive hydraulic pressure force in the valve closing direction acts on the piston 82 by the drive hydraulic pressure P2, and the drive hydraulic pressure force acts on the valve body 71 fixed to the piston 82 as the valve body valve closing direction pressure force. . Further, the flange portion 82b of the piston 82 forms a part of the space portion T4. When the hydraulic oil supply / discharge valve 70 is closed, the communication between the supply / discharge path and the primary hydraulic chamber 55 is cut off, so that the hydraulic oil supplied from the hydraulic control device 130 is filled into the space T4. Accordingly, since the flange portion 82b of the piston 82 forms a part of the space portion T4, the pressure of the hydraulic oil supplied to the primary hydraulic chamber 55, that is, the oil pressure of the space portion T4 (hereinafter simply referred to as “supply pressure Pin”). Acts on the side surface on the valve seat 72 side in the valve opening direction. Thereby, the piston 82 is formed with a flange portion 82b as a supply pressure receiving portion where the pressure of the hydraulic oil supplied to the primary hydraulic chamber 55 acts in the valve opening direction when the hydraulic oil supply / discharge valve 70 is closed. . Accordingly, when the hydraulic oil supply / discharge valve 70 is closed, a supply pressure pressing force in the valve opening direction acts on the piston 82, and the supply pressure pressing force is applied to the valve body 71 fixed to the piston 82. Acts as a valve body opening direction pressing force. The piston passage 82a supplies the hydraulic oil supplied from the hydraulic control device 130 to the primary hydraulic chamber 55 to the space portion T4, and therefore, the flange portion 82b (supply pressure receiving portion) that forms a part of the space portion T4. The hydraulic oil is supplied to the side surface on the valve seat 72 side.

  In the piston 82, the piston passage 82a of the piston 82 constitutes a supply / discharge path. Therefore, the supply / discharge path need not be formed between the outer peripheral portion of the piston 82 and, in the embodiment, between the piston 82 and the primary pulley shaft 51. So the diameter can be increased. Therefore, the area of the side surface opposite to the valve seat 72 side of the flange portion 82b, which is the drive hydraulic pressure receiving portion, can be secured, and the hydraulic oil supply / discharge valve 70 can be closed even when the drive hydraulic pressure P2 is low. The possible valve body closing direction pressing force can be maintained by the driving hydraulic pressure pressing force. Further, since it is not necessary to form the supply / discharge path between the piston 82 and the primary pulley shaft 51, the primary pulley shaft 51 can be reduced in diameter even if the diameter of the piston 82 is constant. The continuously variable transmission can be reduced in size.

  The drive oil passage member 83 supplies hydraulic oil supplied from the hydraulic control device 130 to the drive hydraulic chamber 81. The drive oil passage member 83 is fixed to the valve arrangement passage 51a of the primary pulley shaft 51 in a state where the hydraulic oil supply / discharge valve 70 and the actuator 80 are inserted. The drive oil passage member 83 includes a piston sliding passage 83a and a drive side communication passage 83b. The piston sliding passage 83a is open at both ends in the axial direction, the piston 82 is slidably inserted from one end (the end facing the actuator 80), and the other end (transformer). A projecting portion 23 a is inserted from an end facing the axle rear cover 23. Here, since the drive oil passage member 83 is fixed to the primary pulley shaft 51 by press fitting or the like, when the primary pulley 50 rotates, the drive oil passage member 83 rotates relative to the stationary protruding portion 23a. Of the both ends in the axial direction, the drive side communication passage 83b has one end (the end facing the piston 82) communicating with the drive hydraulic chamber 81 and the other end (the end facing the transaxle rear cover 23). Part) communicates with the space T2. In the embodiment, the drive side communication passage 83 b is formed between a groove formed on the outer peripheral surface of the drive hydraulic member 83 and the inner peripheral surface of the primary pulley shaft 51. Here, the driving side communication passage 83b is formed at a plurality of locations (for example, three locations) at equal intervals on the circumference. The drive hydraulic member 90 is restricted from moving in the axial direction by the lock ring 56 fixed to the primary pulley shaft 51.

  As described above, the supply / discharge path of the belt-type continuously variable transmission 1 according to the embodiment includes the supply / discharge side main passage 23b, the space portion T1, the piston passage 82a, each piston side communication passage 82c, the space portion T4, the valve. It comprises a seat passage 72a, each valve seat side communication passage 72c, each shaft side communication passage 51b, a space T3, and each movable sheave side communication passage 53e. Therefore, the belt type continuously variable transmission 1 according to the embodiment supplies and discharges hydraulic oil to and from the primary hydraulic chamber 55 through one supply and discharge path.

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

  The belt 110 of the belt-type continuously variable transmission 1 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 controls the pressure of hydraulic oil supplied to the primary hydraulic chamber 55, that is, the supply pressure Pin. The hydraulic control device 130 also controls the opening and closing of the hydraulic oil supply / discharge valve 70 by the actuator 80. The hydraulic control device 130 controls the drive hydraulic pressure P2 of the drive hydraulic chamber 81. 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 hydraulic oil to the primary hydraulic chamber 55, the hydraulic control device 130 opens the hydraulic oil supply / discharge valve 70 and communicates with the primary pulley 50 and the supply / discharge path via the supply / discharge path. The hydraulic oil is supplied to the primary hydraulic chamber 55. 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 are opened to communicate with each other by opening the hydraulic oil supply / discharge valve 70. The hydraulic oil is also discharged from the primary hydraulic chamber 55 via

  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 (except the primary hydraulic chamber 55, the secondary hydraulic chamber 64, and the drive hydraulic chamber 81) (stored in the above-described hydraulic oil supply portion and the transaxle 20 such as the belt-type continuously variable transmission 1). The illustration of the lubrication 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 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 an electromagnetic valve (not shown), for example, a linear solenoid valve, that regulates the pressure of the hydraulic oil discharged from the oil pump 132. The line pressure control device 133 is electrically connected to the ECU 140, and the line pressure PL can be regulated by controlling the valve opening degree of the linear solenoid valve by a control signal from the ECU 140. In the embodiment, the line pressure control device 133 controls the pressure of the hydraulic oil supplied to the primary hydraulic chamber 55 via the primary hydraulic chamber control device 135, that is, the supply pressure Pin, by controlling the line pressure PL. It is also something to control.

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

  When the supply-side control valve 135a is turned on, the first port 135e and the second port 135f communicate with each other. Therefore, 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. 10). 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. 12). That is, the control hydraulic pressure chamber 135o is released to atmospheric pressure through the first port 135k of the supply side flow control valve 135c. Further, the fourth port 135u of the discharge side flow control valve 135d is released to the atmospheric pressure via the supply side control valve 135a (see the same figure). Here, as shown in FIG. 4, supply-side control valve 135 a is electrically connected to ECU 140 and is duty-controlled by a control signal from ECU 140. Therefore, the supply-side control valve 135a can regulate the control hydraulic chamber 135o of the supply-side flow rate control valve 135c from a constant pressure PS to atmospheric pressure by a control signal from the ECU 140.

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

  When the discharge-side control valve 135b is turned on, the first port 135h and the second port 135i communicate with each other. Accordingly, the constant pressure PS introduced into the discharge side control valve 135b is introduced into the first port 135r of the discharge side flow control valve 135d (see FIG. 12). That is, the constant pressure PS introduced into the discharge side control valve 135b is introduced into a later-described control hydraulic chamber 135v of the discharge side flow control valve 135d communicating with the first port 135r. Further, the constant pressure PS introduced into the discharge side control valve 135b is introduced into the fourth port 135n of the supply side flow control valve 135c (see the same figure). On the other hand, when the discharge side control valve 135b is turned off, the second port 135i and the third port 135j communicate with each other. Accordingly, the first port 135r of the discharge side flow control valve 135d is released to the atmospheric pressure via the discharge side control valve 135b (see FIG. 10). That is, the control hydraulic chamber 135v is released to the atmospheric pressure via the first port 135r of the discharge side flow control valve 135d. Further, the fourth port 135n of the supply-side flow rate control valve 135c is released to atmospheric pressure via the discharge-side control valve 135b (see the same figure). Here, as shown in FIG. 4, the discharge side control valve 135 b is electrically connected to the ECU 140, and is duty-controlled by a control signal from the ECU 140. Accordingly, the discharge-side control valve 135b can regulate the control hydraulic chamber 135v of the discharge-side flow control valve 135d from a constant pressure PS to atmospheric pressure by a control signal from the ECU 140.

  The supply-side flow rate control valve 135c controls the supply flow rate of the hydraulic oil supplied to the primary hydraulic chamber 55. The supply-side flow rate control valve 135c includes a first port 135k, a second port 135l, a third port 135m, a fourth port 135n, a control hydraulic chamber 135o, a spool 135p, and a spool elastic member 135q. ing. As described above, the first port 135k is connected to the second port 135f of the supply side control valve 135a. The second port 135l is connected to the line pressure control device 133 as described above. The third port 135m is connected to the primary hydraulic chamber 55 via an oil passage R7. Here, the third port 135m includes an oil passage R7 and a supply / discharge passage (supply / discharge-side main passage 23b, space portion T1, piston passage 82a, each piston-side communication passage 82c, space portion T4, valve seat passage 72a, and each valve. The seat-side communication passage 72c, the shaft-side communication passages 51b, the space T3, and the movable sheave-side communication passages 53e) are connected to the primary hydraulic chamber 55. The fourth port 135n is connected to the second port 135i of the discharge side control valve 135b as described above. In addition, as shown in the figure, between the second port 135f of the supply-side control valve 135a and the first port 135k of the supply-side flow control valve 135c, the line pressure control device 133 and the second port of the supply-side flow control valve 135c An orifice, that is, a throttle is provided between the port 135l and the hydraulic oil flowing from the supply-side control valve 135a to the supply-side flow control valve 135c and the hydraulic oil flowing from the line pressure control device 133 to the supply-side flow control valve 135c. The pressure or flow rate may be adjusted.

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

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

  The discharge side flow control valve 135d controls the discharge flow rate of the hydraulic oil discharged from the primary hydraulic chamber 55. The discharge-side flow rate control valve 135d includes a first port 135r, a second port 135s, a third port 135t, a fourth port 135u, a control hydraulic chamber 135v, a spool 135w, and a spool elastic member 135x. ing. As described above, the first port 135r is connected to the second port 135i of the discharge-side control valve 135b. The second port 135s is connected to the oil pan 131 via the merging oil path R52, the merging oil path R51, and the oil path R5. That is, the second port 135s is released to atmospheric pressure. The third port 135t is connected to the primary hydraulic chamber 55 via a branch oil passage R71 and an oil passage R7. In the embodiment, the third port 135t includes the branch oil passage R71, the oil passage R7, and the supply / discharge passage (supply / discharge side main passage 23b, space portion T1, piston passage 82a, each piston side communication passage 82c, space portion T4. The primary hydraulic chamber 55 is connected via a valve seat passage 72a, each valve seat side communication passage 72c, each shaft side communication passage 51b, a space T3, and each movable sheave side communication passage 53e). As described above, the fourth port 135u is connected to the second port 135f of the supply side control valve 135a. As shown in the figure, an orifice, that is, a throttle is provided between the second port 135i of the discharge-side control valve 135b and the first port 135r of the discharge-side flow control valve 135d, and the discharge is made from the discharge-side control valve 135b. The pressure or flow rate of the hydraulic oil flowing into the side flow rate control valve 135d may be adjusted.

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

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

  The drive hydraulic chamber control device 136 adjusts the drive hydraulic 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 is connected to the drive hydraulic chamber 81 via the oil passage R8, the drive side main passage 23c, the space T2, and each drive side communication passage 83b. 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. 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 hydraulic pressure P2 in the drive hydraulic chamber 81 is released to the outside, and the valve opening pressure PI (for example, atmospheric pressure) is lower than the constant pressure PS. Here, the constant pressure PS is operated by the drive oil pressure P2 of the drive oil pressure chamber 81 regardless of the primary oil pressure P1 of the primary oil pressure chamber 55 when at least the drive oil pressure P2 of the drive oil pressure chamber 81 becomes the constant pressure PS. The oil pressure is such that the oil supply / discharge valve 70 can be closed. The valve opening pressure PI means that the hydraulic oil supply / discharge valve 70 is moved by the primary hydraulic pressure P1 of the primary hydraulic chamber 55 even when the supply pressure Pin of the space T4 is reduced when the hydraulic oil supply / discharge valve 70 is closed. Hydraulic pressure that can be opened.

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

  ECU 140 is a control means. The ECU 140 is connected to the hydraulic control device 130 and the internal combustion engine 10 and controls the hydraulic control device 130 and the internal combustion engine 10. Accordingly, the ECU 140 controls the line pressure control device 133, the primary hydraulic chamber control device 135, the drive hydraulic chamber control device 136, and the secondary hydraulic chamber control device 137 by the control signal output to the hydraulic control device 130. The gear ratio γ of the belt type continuously variable transmission 1 is controlled. For example, the ECU 140 controls the hydraulic control device 130 so that a speed ratio γ based on a detected input speed Nin and a detected output speed Nout, which will be described later, becomes a target speed ratio γo. 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.

  The input rotation speed sensor 150 detects an input rotation speed Nin that is the rotation speed on the input side of the belt type continuously variable transmission 1. The input rotation speed sensor 150 is connected to the ECU 140, and the detected input rotation speed Nin is output to the ECU 140. The input rotation speed sensor 150 detects, for example, the rotation speed of the primary pulley shaft 51 as the input rotation speed Nin.

  The output rotation speed sensor 160 detects an output rotation speed Nout that is the rotation speed on the output side of the belt type continuously variable transmission 1. Output rotation speed sensor 160 is connected to ECU 140, and detected output rotation speed Nout is output to ECU 140. The output rotation speed sensor 160 detects, for example, the rotation speed of the secondary pulley shaft 61 as the output rotation speed Nout.

  Next, the operation of the belt type continuously variable transmission 1 according to the embodiment will be described. First, general forward and reverse travel of the vehicle will be described. When the driver selects a forward position by a shift position device (not shown) provided in the vehicle, the ECU 140 turns on the forward clutch 42 and turns off the reverse brake 43 with hydraulic oil supplied from the hydraulic control device 130, and The advance switching mechanism 40 is controlled. As a result, the input shaft 38 and the primary pulley shaft 51 are directly connected. That is, the sun gear 44 and the ring gear 46 of the planetary gear 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 oil supplied from the hydraulic control device 130. The forward / reverse switching mechanism 40 is controlled. As a result, the switching carrier 47 of the planetary gear unit 41 is fixed to the transaxle case 22 and is held by the switching carrier 47 so that each pinion 45 only rotates. Accordingly, the ring gear 46 rotates in the same direction as the input shaft 38, and each pinion 45 meshed with the ring gear 46 also rotates in the same direction as the input shaft 38. It rotates in the opposite direction to the shaft 38. That is, the primary pulley shaft 51 connected to the sun gear 44 rotates in the direction opposite to the input shaft 38. As a result, the secondary pulley shaft 61, the input shaft 101, the intermediate shaft 102, the differential case 91, the drive shafts 121, 122, and the like of the secondary pulley 60 rotate in the opposite direction to the case where the driver selects the forward position. Goes backwards.

  Here, the ECU 140 includes a map (for example, an optimum fuel consumption curve based on the engine speed and the throttle opening of the throttle valve, etc.) stored in the storage unit of the ECU 140 and various conditions such as the vehicle speed and the accelerator opening of the driver. ) Is set so that the operating state of the internal combustion engine 10 is optimal, and the speed ratio γ of the belt-type continuously variable transmission 1 is set to the target speed ratio via the hydraulic control device 130. Control such as γo, that is, feedback control is performed. Control of the transmission gear ratio γ of the belt type continuously variable transmission 1 includes fixing the transmission gear ratio γ and changing the transmission gear ratio γ, that is, shifting. The speed ratio γ is fixed and the speed ratio γ is changed by controlling the line pressure control device 133, the primary hydraulic chamber control device 135, the drive hydraulic chamber control device 136, and the secondary hydraulic chamber control device 137.

  The speed ratio γ is fixed by closing each hydraulic oil supply / discharge valve 70 and holding the working oil in the primary hydraulic chamber 55. The speed ratio γ is changed by releasing the state where the speed ratio γ is fixed. Specifically, the change of the gear ratio γ is performed by opening each hydraulic oil supply / discharge valve 70 and supplying hydraulic oil from the hydraulic control device 130 to the primary hydraulic chamber 55 or from the primary hydraulic chamber 55 to the hydraulic control device 130. The primary movable sheave 53 slides in the axial direction of the primary pulley shaft 51 by discharging the hydraulic oil to the outside of the primary pulley 50 through the primary pulley 50, and between the primary fixed sheave 52 and the primary movable sheave 53. The interval, that is, the width of the primary groove 110a 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).

  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 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 keeping the position of the primary movable sheave 53 in the axial direction with respect 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 performed when the ECU 140 determines that there is no need to change the gear ratio significantly, such as when the traveling 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 discharge of the hydraulic fluid from the primary hydraulic chamber 55 via the discharge valve 70 is prohibited, and the speed ratio γ is maintained at the target speed ratio γo set when the speed ratio γ is fixed. Specifically, ECU 140 outputs a control signal for maintaining gear ratio γ at target gear ratio γo to hydraulic control device 130.

  In the gear ratio fixed control, in order to close the hydraulic oil supply / discharge valve 70, the valve closing instruction flag Fc1 is set to 1 as shown in FIG. . The valve closing control of the hydraulic oil supply / discharge valve 70 operates at every control cycle.

  In the valve closing control of the hydraulic oil supply / discharge valve 70, first, the ECU 140 determines whether or not the valve closing instruction flag Fc is 1 as shown in FIG. 5 (step ST10). Here, the ECU 140 determines whether or not the hydraulic oil supply / discharge valve 70 needs to be closed.

  Next, when the ECU 140 determines that the valve closing instruction flag Fc is 1 (Yes in Step ST10), the ECU 140 acquires the speed ratio γ (Step ST11). Here, ECU 140 acquires gear ratio γ based on input rotational speed Nin detected by input rotational speed sensor 150 and output to ECU 140 and output rotational speed Nout detected by output rotational speed sensor 160 and output to ECU 140. . If ECU 140 determines that valve closing instruction flag Fc is not 1 (No in step ST10), ECU 140 ends the current control cycle and shifts to the next control cycle. That is, the ECU 140 does not perform the valve closing control of the hydraulic oil supply / discharge valve 70 when the gear ratio fixing control is not being performed.

  Next, ECU 140 determines whether or not gear ratio γ is stable (step ST12). Here, as shown in FIG. 6, after the valve closing instruction flag Fc becomes 1 (t1 in FIG. 6), the ECU 140 sets the gear ratio γ of the belt type continuously variable transmission 1 during the shift fixing control. It is determined whether or not the target gear ratio γo is stable. The ECU 140 determines whether or not the absolute value of the difference between the acquired speed ratio γ and the set target speed ratio γo is less than a predetermined value (for example, a value that can be determined that the speed ratio γ becomes the target speed ratio γo). Determine whether. ECU 140 may determine whether or not the absolute value of the difference has continued below a predetermined value for a predetermined time.

  Next, as shown in FIG. 5, when the ECU 140 determines that the speed ratio γ is stable (Yes in step ST12), the ECU 140 performs the valve closing operation of the hydraulic oil supply / discharge valve 70 (step ST13). Here, as shown in FIG. 6, after the transmission gear ratio γ is stabilized at the target transmission gear ratio γo (t2 in FIG. 6), the ECU 140 controls the drive hydraulic chamber control device 136 to be ON. Therefore, the constant pressure PS introduced into the drive hydraulic chamber control device 136 is introduced into the drive hydraulic chamber 81, and the drive hydraulic pressure P2 of the drive hydraulic chamber 81 becomes the constant pressure PS (t3 in the figure). In the actuator 80, the driving hydraulic pressure pressing force by the driving hydraulic pressure P2 of the driving hydraulic chamber 81 increases, and the valve body closing direction pressing force acting on the valve body 71 increases. Here, as described above, the valve body closing direction pressing force exceeds the valve body opening direction pressing force when the driving hydraulic pressure P2 of the driving hydraulic chamber 81 becomes the constant pressure PS. Accordingly, as shown in FIG. 2, the valve element 71 moves in the valve closing direction due to the difference between the valve element closing direction pressing force and the valve element opening direction pressing force, and comes into contact with the valve seat 72 to supply and discharge hydraulic oil. The valve 70 is closed. In addition, as shown in FIG. 5, when ECU 140 determines that the speed ratio γ is not stable (No in step ST12), the current control cycle is terminated and the process proceeds to the next control cycle. That is, during the gear ratio fixed control, the ECU 140 closes the hydraulic oil supply / discharge valve 70 after the gear ratio γ is stabilized. Therefore, when the transmission gear ratio γ is fixed, the hydraulic oil supply / discharge valve 70 is closed after the change amount of the transmission gear ratio γ becomes small, and a shock when the transmission gear ratio γ is fixed can be suppressed.

  Next, the ECU 140 determines whether or not the closing of the hydraulic oil supply / discharge valve 70 has been completed (step ST14). Here, for example, the ECU 140 sets the drive oil pressure P2 in the drive oil pressure chamber 81 to a constant pressure PS and then a predetermined time (a value sufficient to allow the hydraulic oil supply / discharge valve 70 to close after the drive oil pressure P2 is set to the constant pressure PS). ) Determine whether it has passed.

  Next, when the ECU 140 determines that the closing of the hydraulic oil supply / discharge valve 70 has been completed (Yes in step ST14), the ECU 140 reduces the supply pressure Pin (step ST15). Here, as shown in FIG. 6, the ECU 140, after a predetermined time has elapsed (t2 in the figure) after the drive hydraulic pressure P2 of the drive hydraulic chamber 81 is set to the constant pressure PS (P2 = PS), the line pressure control device 133. And the supply pressure Pin is reduced by lowering the line pressure PL (t5 in the figure). Therefore, the hydraulic pressure control device 130 supplies the hydraulic oil pressure to the primary hydraulic chamber 55 with the pressure of the hydraulic oil supplied to the primary hydraulic chamber 55 after the hydraulic oil supply / discharge valve 70 is closed, that is, the supply pressure Pin, when the speed ratio γ is fixed. Since the pressure is lower than the pressure at the time of supply, it is possible to reduce the energy used by the oil pump 132 for increasing the pressure of the hydraulic oil to be supplied to the primary hydraulic chamber 55. Thereby, the friction of the internal combustion engine 10 can be reduced and fuel consumption can be improved. The valve closing instruction flag Fc is maintained at 1 during the gear ratio fixing control, and is 0 when the fixing of the gear ratio γ is released, that is, when the gear ratio fixing control is switched to a gear ratio decreasing control or a gear ratio increasing control described later. It is said.

  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. When changing the gear ratio γ, the ECU 140 performs gear ratio decrease control or gear ratio increase control as the gear shift control. 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. 9, hydraulic oil is supplied from the hydraulic control device 130 to the primary hydraulic chamber 55 with the hydraulic oil supply / discharge valve 70 opened by the actuator 80. Specifically, the ECU 140 calculates a target speed ratio γo and a speed change speed that are smaller than the current speed ratio γ, and outputs a control signal based on these to the hydraulic control device 130.

  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, thereby controlling the supply flow rate of hydraulic oil to the primary hydraulic chamber 55 by the supply-side flow control valve 135c. . When duty control is performed by the ECU 140, the supply-side control valve 135a repeats ON and OFF, as shown in FIG. 10, and adjusts the control hydraulic pressure in the control hydraulic chamber 135o of the supply-side flow control valve 135c to a predetermined pressure during supply. And a predetermined pressure at the time of supply is introduced into the fourth port 135u of the discharge side flow control valve 135d. Here, the predetermined pressure at the time of supply decreases the supply flow rate controlled by controlling the communication between the second port 135l and the third port 135m by the spool valve opening direction pressing force acting on the spool 135p. It is the pressure which can be set as the supply flow rate based on speed. Accordingly, the supply-side flow rate control valve 135c is indicated by an arrow A in FIG. 5 because the spool valve opening direction pressing force based on the control hydraulic pressure of the control hydraulic chamber 135o, that is, the supply predetermined pressure exceeds the spool closing direction pressing force. As described above, the spool 135p moves in one of the movement directions, and the second port 135l and the third port 135m communicate with each other. As a result, the supply-side flow rate control valve 135c is opened, and the supply flow rate of hydraulic oil to the primary hydraulic chamber 55 becomes a supply flow rate based on the target speed ratio γo and the speed change speed.

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

  On the other hand, 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. Done in As shown in FIG. 11, the hydraulic oil is discharged from the primary hydraulic chamber 55 with the hydraulic oil supply / discharge valve 70 opened. Specifically, the ECU 140 calculates a target speed ratio γo and a speed change speed that are increased from the current speed ratio γ, and outputs a control signal based on these to the hydraulic control device 130.

  In the gear ratio increase control, as shown in FIG. 12, 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 supply flow rate of hydraulic oil to the primary hydraulic chamber 55 Becomes 0.

  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 hydraulic oil from the primary hydraulic chamber 55 becomes the discharge flow rate based on the target speed ratio γo and the shift speed.

  As described above, in the gear ratio reduction control and the gear ratio increase control, the hydraulic oil is supplied to the primary hydraulic chamber 55 and discharged from the primary hydraulic chamber 55, so that the hydraulic oil supply / discharge valve 70 is opened. Done in Therefore, in the gear ratio decrease control and the gear ratio increase control after the gear ratio fixing control, in order to open the hydraulic oil supply / discharge valve 70, as shown in FIG. The valve opening control of the hydraulic oil supply / discharge valve 70 is performed. The valve opening control of the hydraulic oil supply / discharge valve 70 operates at every control cycle.

  In the valve opening control of the hydraulic oil supply / discharge valve 70, first, the ECU 140 determines whether or not the valve opening instruction flag Fo is 1 as shown in FIG. 7 (step ST21). Here, the ECU 140 determines whether or not the hydraulic oil supply / discharge valve 70 needs to be opened.

  Next, ECU 140 calculates primary hydraulic pressure P1 (step ST22). Here, the ECU 140, for example, outputs torque T of the internal combustion engine 10 (for example, an engine speed Ne detected by a speed sensor (not shown) and a fuel injection amount supplied to the internal combustion engine 10 by a fuel injection valve (not shown)). The primary hydraulic pressure P1 based on the input rotational speed Nin detected by the input rotational speed sensor 150 and output to the ECU 140, the target speed ratio γo during the speed ratio fixing control, the secondary oil pressure P3 of the secondary hydraulic chamber 64, and the like. calculate. Instead of calculating the primary hydraulic pressure P1, the ECU 140 may use a value detected by a hydraulic sensor (not shown) that is provided in the primary pulley 50 and detects the primary hydraulic pressure P1 as the primary hydraulic pressure P1.

  Next, ECU 140 determines whether or not the shift control is a gear ratio increase control (step ST23).

  Next, when ECU 140 determines that the speed change control is speed ratio reduction control (No in step ST23), ECU 140 increases supply pressure Pin (step ST24). Here, the ECU 140 controls the line pressure control device 133 to adjust the line pressure so that the supply pressure Pin becomes the primary hydraulic pressure P1 (Pin = P1). That is, when the speed change control is the speed ratio reduction control, the ECU 140 changes the supply pressure Pin to the primary oil pressure P1 after the valve opening instruction flag Fo becomes 1 (t6 in FIG. 8), as shown in FIG. The pressure is increased (t7 in the figure).

  Next, as shown in FIG. 7, the ECU 140 opens the hydraulic oil supply / discharge valve 70 (step ST25). Here, in the case of gear ratio reduction control, ECU 140 increases supply pressure Pin to primary hydraulic pressure P1, opens hydraulic oil supply / discharge valve 70, and releases gear ratio fixing. As shown in FIG. 8, the ECU 140 controls the drive hydraulic chamber control device 136 to be OFF. Accordingly, the drive hydraulic pressure P2 of the drive hydraulic chamber 81 becomes the valve opening pressure PI (t8 in the figure). In the actuator 80, the driving hydraulic pressure pressing force by the driving hydraulic pressure P2 of the driving hydraulic chamber 81 decreases, and the valve body closing direction pressing force acting on the valve body 71 decreases. Here, as described above, when the drive hydraulic pressure P2 of the drive hydraulic chamber 81 becomes the valve opening pressure PI (P2 = PI), the valve body opening direction pressing force exceeds the valve body closing direction pressing force. Therefore, as shown in FIG. 9, the valve element 71 moves in the valve opening direction due to the difference between the valve element closing direction pressing force and the valve element opening direction pressing force, and moves away from the valve seat 72 that has been in contact. The oil supply / discharge valve 70 is opened.

  As described above, when each hydraulic oil supply / discharge valve 70 is opened by the actuator 80, the hydraulic oil introduced by the line pressure PL to the supply-side flow control valve 135c (the line pressure control device 133 and the supply-side flow control valve 135c In the case where an orifice is provided between the second port 135l and the hydraulic fluid introduced at a pressure adjusted from the line pressure PL), the supply side flow rate control valve 135c sets the target speed ratio γo, the speed change speed, and the like. Is supplied to the supply / discharge side main passage 23b of the supply / discharge path via the oil path R7. As shown by the arrow B in FIG. 9, the hydraulic oil flowing into the supply / discharge side main passage 23b is supplied / discharge side main passage 23b, space T1, piston passage 82a, piston side communication passage 82c, space T4, valve seat. The pressure is supplied to the primary hydraulic chamber 55 via the passage 72a, each valve-side communication passage 72c, each shaft-side communication passage 51b, the space T3, and each movable sheave-side communication passage 53e. 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, and the speed ratio γ is reduced to the target speed ratio γo as shown in FIG. Is done.

  Next, ECU 140 obtains gear ratio γ as shown in FIG. 7 (step ST26). Here, ECU 140 acquires gear ratio γ based on input rotational speed Nin detected by input rotational speed sensor 150 and output to ECU 140 and output rotational speed Nout detected by output rotational speed sensor 160 and output to ECU 140. .

  Next, ECU 140 determines whether or not gear ratio γ has changed based on the acquired gear ratio γ (step ST27). Here, in the case of gear ratio reduction control, ECU 140 determines whether or not gear ratio γ is decreasing with respect to gear ratio γ acquired during gear ratio fixing control.

  Next, when the ECU 140 determines that the speed ratio γ has changed based on the acquired speed ratio γ (Yes in step ST27), the ECU 140 ends the current control cycle and shifts to the next control cycle. If ECU 140 determines that gear ratio γ has not changed based on the acquired gear ratio γ (No in step ST27), ECU 140 opens the hydraulic oil supply / discharge valve 70 until the gear ratio γ changes. maintain. Further, the valve opening instruction flag Fo is set to 0 after it is determined that the speed ratio γ has changed, but the opening of the hydraulic oil supply / discharge valve 70 during the speed ratio reduction control is maintained. Therefore, when releasing the fixed gear ratio, the pressure of the hydraulic oil supplied to the primary hydraulic chamber 55 is increased to the hydraulic pressure in the primary hydraulic chamber 55 or higher, that is, the hydraulic pressure is increased after the supply pressure Pin is increased to the primary hydraulic pressure P1 or higher. Since the valve 70 is opened, it is possible to suppress the occurrence of a differential pressure between the primary hydraulic chamber P1 and the supply pressure Pin when the hydraulic oil supply / discharge valve 70 is opened. As a result, it is possible to suppress a shock when releasing the speed ratio γ.

  Further, when ECU 140 determines that the speed change control is speed ratio increase control (Yes in step ST23), ECU 140 performs an opening operation of hydraulic oil supply / discharge valve 70 (step ST25). Here, the ECU 140 opens the hydraulic oil supply / discharge valve 70 without increasing the supply pressure Pin in the case of gear ratio increase control, and releases the gear ratio lock. The ECU 140 controls the drive hydraulic chamber control device 136 to be OFF and opens the hydraulic oil supply / discharge valve 70 in the same manner as in the gear ratio reduction control. That is, when the speed change control is speed ratio increase control, the ECU 140 sets the supply pressure Pin to the primary oil pressure P1 after the valve opening instruction flag Fo becomes 1 (t6 in FIG. 8), as shown in FIG. The pressure is not increased (t7 in the figure).

  As described above, when each hydraulic oil supply / discharge valve 70 is opened by the actuator 80, the hydraulic oil in the primary hydraulic chamber 55 is communicated from the primary hydraulic chamber 55 to each movable sheave side as shown by an arrow D in FIG. Supply / discharge side through passage 53e, space T3, each shaft side communication passage 51b, each valve seat side communication passage 72c, valve seat passage 72a, space portion T4, piston side communication passage 82c, piston passage 82a, space portion T1 It flows into the main passage 23b. The hydraulic oil in the primary hydraulic chamber 55 that has flowed into the supply / discharge-side main passage 23b flows into the discharge-side flow rate control valve 135d through the oil passage R7 and the branch oil passage R71, and the target speed ratio is set by the discharge-side flow rate control valve 135d. It is controlled to a discharge flow rate based on γo and the shift speed, and is discharged to the outside of the oil pan 131, that is, the primary hydraulic chamber 55 through the merged oil passages R 52 and R 51 and the oil passage R 5. Accordingly, when the hydraulic oil is discharged from the primary hydraulic chamber 55 via the hydraulic oil supply / discharge valve 70, the primary hydraulic pressure P1 of the primary hydraulic chamber 55 is decreased, and the primary movable sheave 53 is pushed toward the primary fixed sheave side. The pressure decreases, and the primary movable sheave 53 slides in the axial direction on the side opposite to the primary fixed sheave side. As a result, the contact radius of the belt 110 in the primary pulley 50 decreases, the contact radius of the belt 110 in the secondary pulley 60 increases, the gear ratio γ is increased to the target gear ratio γo, and a downshift is performed.

  Next, ECU 140 obtains gear ratio γ as shown in FIG. 7 (step ST26). Here, ECU 140 acquires gear ratio γ based on input rotational speed Nin detected by input rotational speed sensor 150 and output to ECU 140 and output rotational speed Nout detected by output rotational speed sensor 160 and output to ECU 140. .

  Next, ECU 140 determines whether or not gear ratio γ has changed based on the acquired gear ratio γ (step ST27). Here, in the case of gear ratio increase control, ECU 140 determines whether or not gear ratio γ has increased with respect to gear ratio γ acquired during gear ratio fixing control.

  Next, when the ECU 140 determines that the speed ratio γ has changed based on the acquired speed ratio γ (Yes in step ST27), the ECU 140 ends the current control cycle and shifts to the next control cycle. If ECU 140 determines that gear ratio γ has not changed based on the acquired gear ratio γ (No in step ST27), ECU 140 opens the hydraulic oil supply / discharge valve 70 until the gear ratio γ changes. maintain. Further, the valve opening instruction flag Fo is set to 0 after it is determined that the speed ratio γ is changing, but the opening of the hydraulic oil supply / discharge valve 70 during the speed ratio increase control is maintained. Accordingly, the pressure of the hydraulic oil supplied to the primary hydraulic chamber 55 is increased to the primary hydraulic chamber 55 or higher, that is, the supply pressure Pin is increased to the primary hydraulic pressure P1 or higher after the gear ratio is released from being fixed. This is performed only when hydraulic fluid is supplied to the engine (when upshifting in the embodiment), and when hydraulic fluid is discharged from the primary hydraulic chamber 55 after releasing the fixed gear ratio (when downshifting in the embodiment). Absent. As a result, it is possible to shorten the time from the start of releasing the speed ratio γ to the time when the hydraulic oil is discharged from the primary hydraulic chamber 55, so that the responsiveness of the shift can be improved when performing a downshift. Further, since the supply pressure Pin is increased to the primary hydraulic pressure P1 or more only when the hydraulic oil is supplied to the primary hydraulic chamber 55 after the speed ratio γ is released, the speed change is performed regardless of the supply and discharge of the hydraulic oil to the primary hydraulic chamber 55. Compared with the case where the supply pressure Pin is increased to the primary hydraulic pressure P1 or higher when the ratio γ is released, the energy used by the oil pump 132 that generates the supply pressure Pin can be reduced, and fuel consumption can be improved. .

  As described above, in the belt-type continuously variable transmission 1 according to the embodiment, the drive hydraulic pressure P2 acts on the valve body 71 via the piston 82 in the valve closing direction, and the piston is driven by the drive hydraulic pressure P2. The drive hydraulic pressure force in the valve closing direction acts on the valve body 71 via 82 as a valve body valve closing direction pressure force that is a pressing force for closing the valve body 71. In addition, the primary hydraulic pressure P1 acts on the valve body 71 in the valve opening direction, and the valve opening of the valve body 71 is the hydraulic pressure in the valve opening direction of the valve body 71 by the primary hydraulic pressure P1. Acts as a directional pressing force. Further, the supply pressure Pin acts on the piston 82 in the valve opening direction, and the supply pressure pressing force in the valve opening direction acts on the valve body 71 via the piston 82 as the valve body valve opening direction pressing force. Accordingly, by reducing the drive hydraulic pressure P2, the valve body closing direction pressing force acting on the valve body 71 is reduced, and the valve body valve opening direction pressing force exceeding the valve body closing direction pressing force is applied to the valve body 71. The hydraulic oil supply / discharge valve 70 can be opened. Thereby, the valve opening time of the hydraulic oil supply / discharge valve 70 can be shortened, and the responsiveness of the shift performed by opening the hydraulic oil supply / discharge valve 70 can be improved.

  Further, in the belt type continuously variable transmission 1 according to the embodiment, the hydraulic pressure force and the supply pressure pressure force act on the valve body 71 as the valve body valve-opening direction pressure, so that the drive hydraulic pressure P2 cannot be increased. The hydraulic oil supply / discharge valve 70 can also be opened. Therefore, it is possible to suppress the speed ratio γ from being fixed, and to improve the controllability of the speed ratio.

  In the embodiment, the valve seat 72 of the hydraulic oil supply / discharge valve 70 and the primary pulley shaft 51 are separate from each other. However, the present invention is not limited to this, and the valve seat surface 72b is arranged as a valve. The valve seat 72 may be formed integrally with the primary pulley shaft 51 because it is formed to face the other end of the passage 51a that opens. Thereby, the valve seat surface 72b with which the valve body 71 contacts can be formed by processing the primary pulley shaft 51. Therefore, the number of parts of the belt type continuously variable transmission 1 can be reduced and the cost can be reduced.

  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 clamping pressure generating hydraulic chamber by closing the hydraulic oil supply / discharge valve. In particular, it is suitable for improving at least one of speed change response and speed ratio controllability.

It is a skeleton figure of the belt type continuously variable transmission concerning an embodiment. 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. It is a figure which shows the structural example of a hydraulic control apparatus. It is a figure which shows the valve closing operation | movement flow of a hydraulic-oil supply discharge valve. It is a figure which shows the change of the gear ratio etc. at the time of valve closing of a hydraulic-oil supply discharge valve. It is a figure which shows the valve opening operation | movement flow of a hydraulic-oil supply discharge valve. It is a figure which shows the change of the gear ratio etc. at the time of valve opening of a hydraulic-oil supply discharge valve. 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.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Belt type continuously variable transmission 10 Internal combustion engine 20 Transaxle 23 Transaxle rear cover 23a Projection part 23b Supply / discharge side main passage 23c Drive side main passage 23d Bolt 23e Stopper plate 23f Spacer 30 Torque converter 40 Forward / reverse switching mechanism 50 Primary pulley 51 Primary pulley shaft 51a Valve arrangement passage 51b Shaft side communication passage 52 Primary fixed sheave 53 Primary movable sheave 53e Movable sheave side communication passage 54 Primary partition wall 55 Primary hydraulic chamber 56 Lock ring 60 Secondary pulley 64 Secondary hydraulic chamber 70 Hydraulic oil supply discharge valve 71 Valve body 72 Valve seat 72a Valve seat passage 72b Valve seat surface 72c Valve seat side communication passage 73 Valve body elastic member 74 Valve seat fixing member 80 Actuator 81 Drive hydraulic chamber 82 Pis 82a Piston passage 82b Flange portion 82c Piston side communication passage 83 Drive oil passage member 83a Piston sliding passage 83b Drive side communication passage 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 133 Line pressure control device 134 Constant pressure control device 135 Primary hydraulic chamber control device 136 Drive hydraulic chamber control device 137 Secondary hydraulic chamber control device 140 ECU
150 Input rotation speed sensor 160 Output rotation speed sensor S1 Sealing member for communication portion S2 Sealing member for primary hydraulic chamber S3 Sealing member for driving hydraulic chamber T1 to T4 Space portion

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 and discharging hydraulic oil from the one clamping pressure generating hydraulic chamber;
The one clamping pressure is provided in the supply / discharge path, and is opened when hydraulic oil is supplied to the one clamping pressure generating hydraulic chamber or when the hydraulic oil is discharged from the one clamping pressure generating hydraulic chamber. A hydraulic oil supply / discharge valve that closes when hydraulic oil is retained in the hydraulic pressure generating chamber and rotates integrally with the one pulley;
An actuator for controlling the on-off valve of the hydraulic oil supply / discharge valve;
With
The hydraulic oil supply / discharge valve has a valve body and a valve seat, and opens when the valve body moves in a direction in which hydraulic oil is discharged from the one clamping pressure generating hydraulic chamber with respect to the valve seat. Speak
The actuator is slidably supported in a drive hydraulic chamber to which the hydraulic oil is supplied and an on / off valve direction of the hydraulic oil supply / discharge valve, and the drive hydraulic pressure of the drive hydraulic chamber acts in a valve closing direction. A hydraulic pressure receiving portion is formed, and
The piston is disposed at a position facing the valve seat with the valve body interposed therebetween, and the valve body is fixed, and at least when the hydraulic oil supply / discharge valve is closed, the piston is provided in the one clamping pressure generating hydraulic chamber. A belt type continuously variable transmission, characterized in that a supply pressure receiving portion is formed in which a pressure of supplied hydraulic oil acts in a valve opening direction.   2. The belt-type non-loading device according to claim 1, wherein the drive hydraulic pressure receiving portion and the supply pressure receiving portion are flange portions that protrude radially outward from an outer peripheral surface of the piston and face the valve seat. Step transmission.   The belt-type continuously variable transmission according to claim 1 or 2, wherein the hydraulic oil supply / discharge valve and the actuator are arranged coaxially with the pulley shaft inside the pulley shaft of the one pulley. Machine.   The piston constitutes the supply / discharge path, and a piston passage for supplying hydraulic oil supplied to the one clamping pressure generating hydraulic chamber is formed in the supply pressure receiving portion. The belt-type continuously variable transmission as described in any one of -3. The actuator further includes a drive oil passage member that supplies the hydraulic oil to a drive hydraulic chamber,
5. The belt-type non-contact type according to claim 4, wherein the drive oil passage member forms a drive-side communication passage that communicates with the drive hydraulic chamber between an inner peripheral surface of a pulley shaft of the one pulley. Step transmission.   The belt-type continuously variable transmission according to claim 4 or 5, wherein the valve seat is formed integrally with a pulley shaft of the one pulley.

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