JP2008101730A - Belt type continuously variable transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a belt type continuously variable transmission capable of inhibiting the increase of drive loss of an oil pump. <P>SOLUTION: The belt type continuously variable transmission 1-1 is provided with a primary pulley 50 and a secondary pulley, a belt 110 wound around the primary pulley 50 and the secondary pulley, a primary hydraulic pressure chamber 55 formed in the primary pulley 50 and generating belt clamping force, a working fluid supply discharge valve 70 opening when working fluid is supplied to the primary hydraulic pressure chamber 55, opening when working fluid is discharged from the primary hydraulic pressure chamber 55, and rotating as one unit with the primary pulley 50, and an actuator 80 forcibly opening each working fluid supply discharge valve 70 by sliding a piston 82 by hydraulic pressure in a drive hydraulic pressure chamber 81. Working fluid is supplied to the drive hydraulic pressure chamber 81 from a radial direction outside of a pulley bearing 112 rotatably supporting the primary pulley 50 on a transverse axle rear cover 23. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

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

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

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

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

JP 2001-323978 A

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

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

  In order to solve the above-described problems and achieve the object, in the present invention, two pulleys that rotate with respect to a stationary member, a belt that is wound around each pulley and transmits a driving force from a driving source, The hydraulic pressure chamber is formed in each pulley and generates a belt clamping pressure with respect to the belt by hydraulic pressure, and is opened when hydraulic fluid is supplied to one of the clamping pressure generation hydraulic chambers. A hydraulic oil supply valve that rotates integrally with one pulley, a hydraulic oil discharge valve that opens when the hydraulic oil is discharged from one clamping pressure generating hydraulic chamber and rotates integrally with one pulley, and a drive hydraulic pressure And a valve opening / closing means for forcibly opening the hydraulic oil discharge valve by sliding the piston in one of the sliding directions with respect to the drive hydraulic chamber by the hydraulic pressure of the chamber. In the drive hydraulic chamber, the stationary member Hydraulic oil from the radially outer side of the pulley bearing for rotatably supporting the one pulley is characterized in that it is supplied with.

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

  Further, according to the present invention, in the drive hydraulic chamber of the valve opening / closing means for forcibly opening the hydraulic oil discharge valve, one pulley is rotated with respect to a stationary member, not from one pulley which is a movable member. Hydraulic oil is supplied from the radially outer side of the pulley bearing that is freely supported, that is, from a stationary member that fixes the outer ring of the pulley bearing. That is, a passage for supplying hydraulic oil to the drive hydraulic chamber, such as the drive side main passage and the drive communication passage, does not rotate even when one pulley rotates. Therefore, the hydraulic oil supplied to the drive hydraulic chamber is not affected by the centrifugal force. Therefore, the valve opening / closing means can reduce the influence of centrifugal force when forcibly opening the hydraulic oil discharge valve. Thereby, the reliability of the operation of the valve opening / closing means and the controllability of the operation can be improved. Further, since the hydraulic oil supplied to the drive hydraulic chamber does not pass through the pulley shaft, a passage for supplying the hydraulic oil to the drive hydraulic chamber need not be formed in the pulley shaft. Thereby, the axial length of one pulley can be shortened.

  In the present invention, in the belt-type continuously variable transmission, the drive hydraulic chamber is formed in a drive-side main passage formed radially outside the pulley bearing and a bearing fixing member that fixes the pulley bearing to the stationary member. The hydraulic oil is supplied through a drive communication passage that connects the drive hydraulic chamber and the drive side main passage.

  According to the present invention, the drive communication passage for supplying hydraulic oil to the drive hydraulic chamber is formed in the bearing fixing member that fixes the pulley bearing to the stationary member, that is, the bearing fixing member that fixes the bearing outer ring of the pulley bearing to the stationary member. Yes. Therefore, the bearing fixing member can be shared as a member that forms a drive communication passage that communicates the drive-side main passage and the drive hydraulic chamber. Thereby, the number of parts can be reduced, and size reduction and cost reduction can be achieved.

  Further, in the present invention, in the belt type continuously variable transmission, the valve body of the hydraulic oil discharge valve is disposed on an extension line of the discharge passage that discharges the hydraulic oil to one clamping pressure generating hydraulic chamber via the hydraulic oil discharge valve. A valve seat surface for closing the hydraulic oil discharge valve by contact is formed.

  According to the present invention, the discharge passage is formed by penetrating the member forming the discharge passage, and is formed on the valve seat surface on the extension line of one end portion of the both ends of the discharge passage. Therefore, it is not necessary to close one end of the discharge passage. Thereby, since a part for closing one end of the discharge passage is not required, the number of parts can be reduced, and the structure can be simplified and the cost can be reduced. In addition, since one end of the discharge passage is not blocked, the reliability against leakage of hydraulic oil from the discharge passage can be improved.

  According to the present invention, in the belt type continuously variable transmission, the valve opening / closing means is supported so as to be slidable in the sliding direction with respect to one pulley, and the valve body via the piston by the hydraulic pressure of the drive hydraulic chamber. And a pressing member that presses the valve in the valve opening direction.

  In the present invention, the belt-type continuously variable transmission further includes an integral rotating means for integrally rotating the piston with respect to one pulley.

  According to the present invention, since the piston rotates integrally with the one pulley, it is possible to suppress relative rotation between the piston and the pressing member that rotates integrally with the one pulley. Therefore, drag generated between the piston and the pressing member can be suppressed, and durability can be improved.

  According to the present invention, in the belt type continuously variable transmission, the piston is positioned in the sliding direction by contacting a piston with a bearing inner ring that contacts one of the pulley bearings. .

  According to the present invention, positioning in the sliding direction of the piston, that is, restriction of movement to the other of the sliding directions of the piston, rotates integrally with one pulley by contacting with one pulley of the pulley bearings. This is done by contacting the bearing inner ring and a piston that rotates integrally with one pulley. Therefore, relative rotation between the bearing inner ring and the piston can be suppressed. Thereby, drag generated between the bearing inner ring and the piston can be suppressed, and durability can be improved. Further, when the bearing inner ring and the piston come into contact with each other, the bearing fixing member that does not rotate integrally with one pulley and the piston that rotates integrally with one pulley become non-contact. Therefore, drag generated between the bearing fixing member and the piston can be suppressed, and durability can be improved. Furthermore, in order to restrict the movement of the piston in the sliding direction to the other, no restriction component may be provided. Therefore, the number of parts can be reduced, and downsizing and cost reduction can be achieved.

  According to the present invention, in the belt type continuously variable transmission, the pressing member includes at least one clamping pressure generating hydraulic chamber and one pulley outside when at least the piston slides most in one of the sliding directions. A notch that communicates with each other is formed.

  According to the present invention, when the hydraulic oil is discharged from one of the clamping pressure generating hydraulic chambers by opening the hydraulic oil discharge valve, the hydraulic oil is discharged through the normal hydraulic oil discharge path, for example, via the discharge passage. The hydraulic oil can be discharged through the notch together with the discharged hydraulic oil. Accordingly, since the maximum discharge flow rate can be increased, it is possible to increase the maximum transmission speed at the time of downshift, that is, at the time of changing the transmission ratio to increase the transmission ratio. In addition, since the hydraulic oil can be discharged through the notch portion, when the maximum transmission speed at the time of changing the gear ratio increase is the same as when the hydraulic oil is discharged only through the hydraulic oil discharge path, The maximum discharge flow rate when the hydraulic oil is discharged through the hydraulic oil discharge path can be reduced. As a result, the hydraulic oil discharge path can be narrowed, the hydraulic oil discharge valve can be downsized, and downsizing can be achieved.

  Further, in the present invention, in the belt type continuously variable transmission, the hydraulic oil discharge valve generates a valve body closing direction pressing force that presses the valve body in a valve closing direction by generating a valve closing biasing force. The valve body closing direction pressing force generating means is further provided, and the valve body closing direction pressing force generating means varies the generated valve closing biasing force stepwise.

  Here, the opening movement amount, which is the movement amount of the pressing member necessary only for opening the hydraulic oil discharge valve, the opening pressure of the hydraulic oil discharge valve and the one clamping pressure generating hydraulic chamber and the one pulley by the notch This is different from the communication movement amount that is necessary for communication with the outside. According to the present invention, since the valve closing biasing force generated by the valve body closing direction pressing force generating means varies stepwise, the valve body closing direction pressing force acting on the valve body can be changed stepwise. Therefore, the valve opening hydraulic pressure that is the hydraulic pressure of the driving hydraulic chamber that can move the pressing member that moves by the valve opening direction pressing force that presses the valve body in the valve opening direction by the hydraulic pressure of the driving hydraulic chamber can be moved to the valve opening movement amount. The communication hydraulic pressure, which is the hydraulic pressure of the drive hydraulic chamber that can be moved to the communication movement amount, can be made different in stages. Therefore, even if the hydraulic pressure in the drive hydraulic chamber varies in the vicinity of the valve opening hydraulic pressure, it does not reach the communication hydraulic pressure. There is no communication. Thereby, controllability can be improved.

  Further, in the present invention, in the belt type continuously variable transmission, the valve body closing direction pressing force generating means is constituted by two valve body elastic members whose generated valve closing biasing forces are different in stages. Among the body elastic members, the valve body side holding member that holds the valve body elastic member on the valve body side is formed in an annular shape, and is arranged between two valve body elastic members.

  According to the present invention, since the valve body side holding member for holding the valve body side valve body elastic member is formed in an annular shape, the valve body side valve body elastic member can be reliably held. When a plurality of hydraulic oil discharge valves are provided on the circumference, the valve body elastic member on the valve body side of each hydraulic oil discharge valve can be held by one valve body side holding member. Therefore, the number of parts can be reduced, and downsizing and cost reduction can be achieved.

  According to the present invention, in the belt type continuously variable transmission, the hydraulic oil supply valve and the hydraulic oil discharge valve are the same.

  According to the present invention, the hydraulic oil is supplied to one clamping pressure generating hydraulic chamber, the hydraulic oil is discharged from one clamping pressure generating hydraulic chamber, and the hydraulic oil is held in one clamping pressure generating hydraulic chamber. Can be done with a valve.

  In the present invention, in the belt type continuously variable transmission, the valve opening / closing means is the same as the hydraulic oil discharge valve when supplying hydraulic oil to one of the clamping pressure generating hydraulic chambers. The hydraulic oil supply valve is forcibly opened.

  According to the present invention, when supplying hydraulic oil to one clamping pressure generating hydraulic chamber, the hydraulic oil supply is the same as the hydraulic oil discharge valve due to the supply pressure of the hydraulic oil supplied to one clamping pressure generating hydraulic chamber It is not necessary to open the valve. Therefore, it is possible to suppress an increase in the supply pressure of the hydraulic oil supplied to one clamping pressure generating hydraulic chamber.

  The belt-type continuously variable transmission according to the present invention can hold the hydraulic oil in one of the clamping pressure generating hydraulic chambers when the transmission gear ratio is fixed, so that an increase in driving loss of the oil pump can be suppressed. Play. Further, since the passage for supplying the hydraulic oil to the drive hydraulic chamber does not rotate even if the hydraulic oil discharge valve rotates integrally with one pulley, the influence of centrifugal force can be reduced, and the operation of the valve opening / closing means can be trusted. And controllability of operation can be improved.

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

  FIG. 1 is a skeleton diagram of a belt-type continuously variable transmission according to a first 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 oil supply control device. 5 to 8 are explanatory diagrams of the operation of the belt type continuously variable transmission when the gear ratio is changed.

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

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

  Further, as shown in FIG. 2, the transaxle rear cover 23, which is a stationary component, has a drive side main passage 23a. The drive-side main passage 23a is formed on the radially outer side of a pulley bearing 112 (described later) that rotatably supports the primary pulley 50 that is one pulley. The drive side main passage 23a communicates with R8 (described later) of the hydraulic oil supply control device 130. Accordingly, the hydraulic fluid supplied from the hydraulic fluid supply control device 130 to the drive hydraulic chamber 81 (described later) of the actuator 80 flows into the drive side main passage 23a. One end of the drive side main passage 23a communicates with a drive communication passage 23e formed in a stopper plate 23b described later. In the first embodiment, the drive side main passage 23a is formed at a plurality of locations (for example, three locations) at equal intervals on the circumference, and each drive side main passage 23a communicates with the drive communication passage 23e.

  In addition, stopper plates 23b are fixed to the transaxle rear cover 23 by plate fixing members such as bolts (not shown) (disposed at a plurality of positions on the circumference at equal intervals). The stopper plate 23 b is a bearing fixing member, and fixes a pulley bearing 112 described later to the transaxle rear cover 23. The stopper plate 23b is composed of a main body portion 23c and a protruding portion 23d. The main body 23c is formed in a ring shape, and is fixed to the transaxle rear cover 23 so that the other of the axial directions, that is, the surface on the primary pulley side of the transaxle rear cover 23 (opposite a primary partition wall 54 described later). Of the transaxle rear cover 23 and the side surface on the primary pulley side of a bearing outer ring 112a (described later) of the pulley bearing 112. Further, the main body portion 23c has a radially inner surface, that is, an inner peripheral surface opposed to an outer peripheral surface 54d of the primary partition wall 54 (one side surface in the axial direction of a piston 82 described later of the actuator 80 (the right side surface in the figure)). Opposite surface 54e and the outer peripheral surface that is continuous radially inward).

  A drive communication passage 23e is formed in the main body 23c. That is, the drive communication passage 23e is formed in the stopper plate 23b that is a bearing fixing member that fixes the pulley bearing 112 to the transaxle rear cover 23 that is a stationary member. One end portion (right end portion in the figure) of the drive communication passage 23e is open to the side surface on the primary pulley side of the main body portion 23c, and the other end portion (left end portion in the figure) is connected to the transaxle rear cover 23. It communicates with the formed drive side main passage 23a. Accordingly, the drive side main passage 23a and the drive communication passage 23e for supplying hydraulic oil to the drive hydraulic chamber 81 (to be described later) of the actuator 80 are formed in the transaxle rear cover 23 and the stopper plate 23b, which are stationary members. Even if the primary pulley 50 which is a pulley rotates, it does not rotate. That is, it is possible to suppress the occurrence of centrifugal hydraulic pressure due to the centrifugal force generated by the rotation of the primary pulley 50 in the hydraulic oil in the drive side main passage 23a and the drive communication passage 23e.

  A drive communication passage 23e for supplying hydraulic oil to the drive hydraulic chamber 81 is formed in a stopper plate 23b that is a bearing fixing member that fixes the bearing outer ring 112a of the pulley bearing 112 to the transaxle rear cover 23 that is a stationary member. Therefore, the stopper plate 23b can be shared as a member that forms the drive communication passage 23e that allows the drive side main passage 23a and the drive hydraulic chamber 81 to communicate with each other. Thereby, the number of parts of belt type continuously variable transmission 1-1 can be reduced, and size reduction and cost reduction can be achieved.

  Here, among the transaxle rear cover 23 and the stopper plate 23b, the radially outer portion and the radially inner portion of the communicating portion between the driving side main passage 23a and the driving communication passage 23e are connected to each other by a communication such as a seal ring. Part seal members S1 are provided. That is, the communication portion between the drive side main passage 23a and the drive communication passage 23e is sealed by the communication portion seal member S1.

  The protruding portion 23d is formed so as to protrude from the radially outer portion of the side surface on the primary pulley side of the main body portion 23c toward one side (the right side surface in the figure) in the axial direction. Of the side surface on the primary pulley side of the main body portion 23c, the radially inner portion faces the other side surface (the left side surface in the figure) in the axial direction of a piston 82 described later of the actuator 80. Further, the radially inner surface, that is, the inner peripheral surface of the projecting portion 23d faces the radially outer surface of the piston 82, which will be described later, of the actuator 80, that is, the outer peripheral surface.

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

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

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

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

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

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

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

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

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

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

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

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

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

  The primary pulley 50 of the belt-type continuously variable transmission 1-1 is one pulley that rotates with respect to a stationary component, for example, the transaxle 20, and is transmitted from the internal combustion engine 10 transmitted through the forward / reverse switching mechanism 40. The output torque is transmitted to the secondary pulley 60 by the belt 110. As shown in FIGS. 1 and 2, the primary pulley 50 includes a primary pulley shaft 51, a primary fixed sheave 52, a primary movable sheave 53, a primary partition wall 54, and a primary hydraulic chamber 55.

  As shown in FIG. 2, the primary pulley shaft 51 is rotatably supported by pulley bearings 111 and 112. Further, the primary pulley shaft 51 is formed with a supply / discharge side main passage 51a that opens only at one end portion (the right end portion in the figure) of both end portions in the axial direction. Here, the pulley bearing 112 is sandwiched between a step portion 23 f formed on a surface of the transaxle rear cover 23 facing the primary pulley shaft 51 and a stopper plate 23 b fixed to the transaxle rear cover 23. Fixed. The pulley bearing 112 includes a plurality of bearing support members 112c between a bearing outer ring 112a fixed to the transaxle rear cover 23, which is a stationary member, and a bearing inner ring 112b fixed to the primary pulley shaft 51 of the primary pulley 50. Is supported rotatably. Accordingly, in the pulley bearing 112, the bearing outer ring 112a and the bearing inner ring 112b are in contact with the plurality of bearing support members 112c, so that force is transmitted between each other through the plurality of bearing support members 112c while relatively rotating. It can be performed.

  The supply / discharge side main passage 51a forms part of the hydraulic oil discharge path, is formed on the primary fixed sheave side, and communicates with an oil path R7 (described later) of the hydraulic oil supply control device 130. In the supply / discharge side main passage 51a, the hydraulic oil supplied from the hydraulic oil supply control device 130 to the primary hydraulic chamber 55 flows in, and the hydraulic oil discharged from the primary hydraulic chamber 55 flows in. Accordingly, the supply / discharge-side main passage 51a allows the hydraulic oil supplied or discharged between the hydraulic oil supply control device 130 and the primary hydraulic chamber 55 to pass therethrough. The supply / discharge-side main passage 51a includes a shaft-side communication passage 51b formed in the vicinity of the tip thereof, a space T1 formed between the primary movable sheave 53 and the primary pulley shaft 51, a primary partition wall 54, and a primary movable It communicates with the partition-side communication passage 54b of the primary partition 54 via a space T2 formed between the sheave 53 and the primary pulley shaft 51. The spaces T1 and T2 communicate with each other via a spline 53c of the primary movable sheave 53 described later and a spline 51c of the primary pulley shaft 51. In the first embodiment, the shaft side communication passage 51b is formed at a plurality of locations (for example, three locations) at equal intervals on the circumference.

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

  As shown in FIG. 2, the primary movable sheave 53 includes a cylindrical portion 53a and an annular portion 53b. The cylindrical portion 53 a is formed around the same rotational axis as the primary pulley shaft 51. The annular portion 53b is formed so as to protrude radially outward from the end portion of the cylindrical portion 53a on the primary fixed sheave side. The primary movable sheave 53 is axially connected to the primary pulley shaft 51 by spline-fitting a spline 53c formed on the inner peripheral surface of the cylindrical portion 53a and a spline 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.

  As shown in FIG. 2, the primary partition wall 54 is an annular member, and is arranged around the same rotational axis as the primary pulley shaft 51. The primary partition 54 is disposed so as to face the primary fixed sheave 52 in the axial direction with the primary movable sheave 53 interposed therebetween. The primary partition wall 54 is provided so as to rotate integrally with the primary pulley shaft 51 by spline fitting with the primary pulley shaft 51.

  The primary partition wall 54 is formed with a valve arrangement passage 54 a extending in the axial direction on the radially inner side. The valve arrangement passage 54a has one end portion (the right end portion in the figure) opened to the primary hydraulic chamber 55, the other end portion (the left end portion in the figure) is closed inside the primary partition wall 54, and the partition wall It communicates with the side communication passage 54b. The valve arrangement passage 54 a is formed with an annular valve seat surface 72 that is closed by a valve body 71 (described later) of the hydraulic oil supply / discharge valve 70. Here, the valve seat surface 72 is formed at one end of the valve arrangement passage 54a.

  The partition wall side communication passage 54 b is a supply passage that constitutes a part of a supply path that supplies hydraulic oil to the primary pulley 50 that is one clamping pressure generation hydraulic chamber via the hydraulic oil supply / discharge valve 70. It is also a discharge passage that constitutes a part of the hydraulic oil discharge path for discharging the hydraulic oil from the primary pulley 50 via the supply / discharge valve 70. One end (diameter outer side end) of the partition wall side communication passage 54 b communicates with the valve arrangement passage 54 a, and the other end (diameter inner side) opens to the inner peripheral surface of the primary partition wall 54. And communicated with the space T2. In the first embodiment, the valve arrangement passage 54a and the partition wall side communication passage 54b are formed at a plurality of locations (for example, three locations) at equal intervals on the circumference. In addition, the hydraulic oil supply / discharge valve 70 is arranged in each valve arrangement passage 54a.

  Here, the valve seat surface 72 is formed on an extension of the partition wall side communication passage 54b (one-dot chain line in the figure). That is, the valve seat surface 72 has a partition wall so that a space portion (a space portion surrounded by an alternate long and short dash line in the same figure) extending from the partition wall side communication passage 54b and a space portion formed by being surrounded by the valve seat surface 72 overlap. It is formed with respect to the side communication passage 54b. The partition-side communication passage 54b that is a discharge passage is formed through the primary partition 54 that is a member that forms the partition-side communication passage 54b. Therefore, when the partition wall side communication passage 54b and the valve seat surface 72 are formed in the primary partition wall 54, the both ends of the partition wall side communication passage 54b are formed by forming the valve seat surface 72 after forming the partition wall side communication passage 54b. The valve seat surface 72 can be formed on an extension line of one end portion (outer end portion in the radial direction in the figure). Thereby, it is not necessary to block one end portion of the partition wall side communication passage 54b, and a part for closing one end portion of the partition wall side communication passage 54b is not required, so that the number of parts can be reduced. Therefore, the structure can be simplified and the cost can be reduced. In addition, since one end portion of the partition wall side communication passage 54b is not closed, the reliability against leakage of hydraulic oil from the partition wall side communication passage 54b can be improved.

  The primary partition wall 54 is formed with a sliding support hole 54c on the same axis as each valve arrangement passage 54a. Each sliding support hole 54c has one end portion (right end portion in the figure) communicating with the valve arrangement passage 54a, and the other end portion (left end portion in the figure) in the axial direction of the piston 82 of the actuator 80. An opening is formed in the facing surface 54e facing one side surface (the right side surface in the figure).

  A restriction hole 54 f is formed in the primary partition wall 54. The restriction hole 54f is formed in the facing surface 54e. In the first embodiment, the restriction holes 54f are formed at a plurality of positions (for example, three places) at equal intervals on the circumference, and the restriction pins 84 fixed to the piston 82 of the actuator 80 slide in the sliding direction of the piston 82. That is, it is set to a depth that does not come off with sliding in the axial direction.

  The primary hydraulic chamber 55 is one clamping pressure generating hydraulic chamber, and as shown in FIG. 2, by pressing the primary movable sheave 53 toward the primary fixed sheave side, the primary pulley 50, that is, the V-shaped primary groove 110a. A belt clamping pressure is generated with respect to the belt 110 wound around the belt. The primary hydraulic chamber 55 is a space formed by the primary movable sheave 53 and the primary partition wall 54. Here, between the protrusion 53d of the primary movable sheave 53 and the primary partition wall 54 and between the cylindrical portion 53a of the primary movable sheave 53 and the primary partition wall 54, for example, a seal member S2 for a primary hydraulic chamber such as a seal ring is provided. Each is provided. In other words, the space formed by the primary movable sheave 53 constituting the primary hydraulic chamber 55 and the primary partition 54 is sealed by the primary hydraulic chamber seal member S2.

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

  The secondary pulley 60 of the belt type continuously variable transmission 1-1 is the other pulley that rotates with respect to a stationary component, for example, the transaxle 20, and the output from the internal combustion engine 10 transmitted to the primary pulley 50 by the belt 110. Torque is transmitted to the final reduction gear 90 of the belt type continuously variable transmission 1. As shown in FIG. 1, the secondary pulley 60 includes a secondary pulley shaft 61, a secondary fixed sheave 62, a secondary movable sheave 63, a secondary hydraulic chamber 64, a secondary partition wall 65, and a torque cam 66. Reference numeral 69 denotes a parking brake gear.

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

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

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

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

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

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

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

  Here, the operation of the torque cam 66 will be described. When the output torque from the internal combustion engine 10 is transmitted to the primary pulley 50 and the primary pulley 50 rotates, the secondary pulley 60 rotates via the belt 100. At this time, since the secondary movable sheave 63 of the secondary pulley 60 rotates together with the secondary fixed sheave 62, the secondary pulley shaft 61, and the pulley bearing 113, relative rotation occurs between the secondary movable sheave 63 and the intermediate member 67. . Then, as shown in FIG. 3A, the first engagement portion 63b and the second engagement portion 67a are brought close to each other by the plurality of transmission members 68, as shown in FIG. The portion 63b and the second engaging portion 67a are changed to a separated state. As a result, the torque cam 66 generates a belt clamping pressure with respect to the belt 110 in the secondary pulley 60.

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

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

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

  The valve body elastic member 73 is a valve body valve closing direction pressing force generation means. The valve body elastic member 73 is disposed in a state of being biased between the valve seat surface 72 and the valve body elastic member holding member 74 via the valve body 71. Thereby, the valve body elastic member 73 generates a valve closing biasing force, and the valve closing biasing force is a direction in which the valve body 71 contacts the valve seat surface 72, that is, an elastic member pressing force in the valve closing direction. It acts on the valve body 71 as the valve body closing direction pressing force. Accordingly, the valve body 71 is pressed against the valve seat surface 72, and each hydraulic oil supply / discharge valve 70 functions as a check valve. The valve body elastic member holding member 74 has an L-shaped cross section in the axial direction. The valve body elastic member holding member 74 is inserted into a groove formed on the outer peripheral surface of the projecting portion formed on the radially inner side of one end portion of the primary partition wall 54 in the axial direction, and the other end portion. The end portion faces the surface of the primary partition wall 54 facing the primary movable sheave 53 so that a gap is formed between the primary partition wall 54 and the primary partition wall 54. The snap ring 75 is inserted and fixed in a groove into which one end of the valve body elastic member holding member 74 is inserted, so that the valve body elastic member holding member 74 moves in the axial direction with respect to the primary partition wall 54. To regulate.

  The actuator 80 is a valve opening / closing means and forcibly opens each hydraulic oil supply / discharge valve 70. The actuator 80 is provided between the stopper plate 23 b that is a stationary member and the primary partition wall 54. The actuator 80 includes a drive hydraulic chamber 81, a piston 82, and a pressing member 83. Reference numeral 84 denotes a restriction pin.

  The drive hydraulic chamber 81 is supplied with hydraulic oil, and controls the on / off valves of the hydraulic oil supply / discharge valves 70 by the pressure of the supplied hydraulic oil, that is, the hydraulic pressure P2 of the drive hydraulic chamber 81. is there. The drive hydraulic chamber 81 is configured by a ring-shaped space formed between the stopper plate 23b, the primary partition wall 54, and the piston 82. The drive hydraulic chamber 81 communicates with the drive communication passage 23e. Accordingly, hydraulic oil is supplied from the hydraulic oil supply control device 130 to the drive hydraulic chamber 81 via the drive communication passage 23e and the drive side main passage 23a. That is, hydraulic oil is supplied to the drive hydraulic chamber 81 from the radially outer side of the pulley bearing 112 that rotatably supports the primary pulley 50 that is one pulley with respect to the transaxle rear cover 23 and the stopper plate 23b that are stationary members. Supplied. Accordingly, a piston valve opening direction pressing force is applied to the piston 82 by the hydraulic pressure P <b> 2 of the drive hydraulic chamber 81.

  The piston 82 is supported so as to be slidable in the axial direction with respect to the drive hydraulic chamber 81. The piston 82 is formed in a ring shape. The piston 82 slides in the axial direction, that is, one of the sliding directions with respect to the drive hydraulic chamber 81, that is, in the valve opening direction, due to the piston valve opening direction pressing force acting by the hydraulic pressure P 2 of the drive hydraulic chamber 81. . As a result, the piston 82 forcibly opens each hydraulic oil supply / discharge valve 70 via each pressing member 83. That is, the piston 82 slides in one of the sliding directions with respect to the drive hydraulic chamber 81 by the hydraulic pressure P2 of the drive hydraulic chamber 81, and each hydraulic oil supply / discharge valve 70 can be forcibly opened. A piston seal member S3 such as a seal ring is provided between the piston 82, the stopper plate 23b, and the primary partition wall 54, respectively. That is, the space formed by the stopper plate 23b, the primary partition wall 54, and the piston 82 constituting the drive hydraulic chamber 81 is sealed by the piston seal member S3.

  The pressing member 83 is disposed between the piston 82 and the valve body 71 of each hydraulic oil supply / discharge valve 70. Each pressing member 83 is inserted into each sliding support hole 54c of the primary partition wall 54, and is supported so as to be slidable in the axial direction with respect to each sliding support hole 54c. That is, each pressing member 83 is supported so as to be slidable in the sliding direction of the piston 82 with respect to the primary pulley 50 which is one pulley. Each pressing member 83 rotates integrally with the primary pulley 50. Each pressing member 83 can be in contact with the valve body 71 of each hydraulic oil supply / discharge valve 70 at one end (the right end in the figure), and the other end (the left end in the figure) is in contact with the piston 82. it can. Accordingly, each pressing member 83 slides in the axial direction with respect to the primary pulley 50 while being in contact with each valve body 71 and the piston 82, so that between the actuator 80 and each hydraulic oil supply / discharge valve 70. An axial force and a piston valve opening direction pressing force acting on the piston 82 can be transmitted.

  The restriction pin 84 is fixed to a surface facing the facing surface 54 e of the piston 82. The restriction pin 84 is formed in the piston 82 so as to correspond to each restriction hole 54f. Each regulation pin 84 is inserted into each regulation hole 54f and slidable in the axial direction because the piston 82 is supported so as to be slidable in the sliding direction, that is, in the axial direction with respect to the drive hydraulic chamber 81. Supported. Therefore, the piston 82 rotates integrally with the primary partition wall 54 by inserting each regulating pin 84 into each regulating hole 54f. That is, each regulation pin 84 and each regulation hole 54f constitute an integral rotating means for integrally rotating the piston 82 with respect to the primary pulley 50 that is one pulley. Thereby, since the piston 82 rotates integrally with the primary pulley 50, the relative rotation between the piston 82 and the pressing member 83 rotating integrally with the primary pulley 50 can be suppressed, and is generated between the piston 82 and the pressing member 83. Drag can be suppressed. Therefore, durability can be improved. Moreover, the transmission efficiency of the primary pulley 50 and the secondary pulley 60 which are two pulleys of the belt type continuously variable transmission 1-1 according to the first embodiment can be improved. Each regulation pin 84 may not be fixed to the piston 82, and may be inserted into a regulation hole (not shown) formed in the piston 82 and each regulation hole 54f, and may be slidably supported by these. good.

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

  In the first embodiment, each hydraulic oil supply / discharge valve 70 is a valve regardless of whether 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. The valve is forcibly opened by an actuator 80 as an opening / closing means. That is, when the hydraulic oil is discharged from the primary hydraulic chamber 55, the actuator 80 forcibly opens each hydraulic oil supply / discharge valve 70, which is a hydraulic oil discharge valve, and supplies the hydraulic oil to the primary hydraulic chamber 55. In this case, each hydraulic oil supply / discharge valve 70 which is the same hydraulic oil supply valve as the hydraulic oil discharge valve is forcibly opened.

  First, the actuator 80 applies a piston valve opening direction pressing force to the piston 82 by the hydraulic pressure P2 of the drive hydraulic chamber 81, thereby causing the piston 82 to move in one of the axial directions, ie, the valve opening direction. To slide. When the piston 82 slides in the valve opening direction, the piston 82 and each pressing member 83 come into contact with each other, and each pressing member 83 slides together with the piston 82 in the valve opening direction. The piston valve-opening direction pressing force acting on the piston 82 acts on the valve body 71 of each hydraulic oil supply / discharge valve 70 in contact with each pressing member 83 as the valve body valve-opening direction pressing force. Accordingly, each hydraulic oil supply / discharge valve 70 moves in the valve opening direction with respect to the valve seat surface 72 when the valve body valve opening direction pressing force exceeds the valve body closing direction pressing force. The hydraulic oil supply / discharge valve 70 opens. The valve body closing direction pressing force is the elastic member pressing force acting on the valve body 71 by the valve closing biasing force and the hydraulic oil valve closing direction acting on the valve body 71 in the valve closing direction by the hydraulic pressure P1 of the primary hydraulic chamber 55. And pressing force.

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

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

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

  Further, since each hydraulic oil supply / discharge valve 70 has the same hydraulic oil supply valve and hydraulic oil discharge valve, each hydraulic oil supply / discharge valve 70 is opened, and forcibly opened in the first embodiment. Thus, the hydraulic oil can be supplied to the primary hydraulic chamber 55 which is one clamping pressure generating hydraulic chamber, the hydraulic oil can be discharged from the primary hydraulic chamber 55, and each hydraulic oil supply / discharge valve 70 is closed. Thus, the hydraulic oil can be held in the primary hydraulic chamber 55 with a single valve.

  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 105 is fixed to the intermediate shaft 102 and meshed with the counter drive pinion 103. The final drive pinion 105 is fixed to the intermediate shaft 102.

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

  The differential case 91 is rotatably supported by bearings 97 and 98. A ring gear 99 is provided on the outer periphery of the differential case 91, and the ring gear 99 is engaged with the final drive pinion 104. The pinion shaft 92 is attached to the hollow portion of the differential case 91. The differential pinions 93 and 94 are rotatably attached to the pinion shaft 92. The side gears 95 and 96 are meshed with both the differential pinions 93 and 94. The side gears 95 and 96 are fixed to the drive shafts 121 and 122, respectively.

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

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

  The hydraulic oil supply control device 130 supplies hydraulic oil to a hydraulic oil supply portion that requires supply of hydraulic oil in a vehicle on which the belt type continuously variable transmission 1-1 and the internal combustion engine 10 are mounted. As shown in FIG. 4, the hydraulic oil supply 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. It also controls the gear ratio of the belt type continuously variable transmission 1 by controlling the discharge flow rate. In the figure, the hydraulic oil supply portion (excluding the above-described hydraulic oil supply portion and the hydraulic oil supply portion of the internal combustion engine 10 (for example, with movable parts) excluding the primary hydraulic chamber 55, the secondary hydraulic chamber 64, and the drive hydraulic chamber 81 The illustration of a stationary part having a sliding part in between, a movable part or a movable part having a sliding part between stationary parts, a heated part or a driving device driven by oil) is omitted.

  As shown in FIG. 4, the hydraulic oil supply 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 use. A control device 136 and a secondary hydraulic chamber control device 137 are configured.

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

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

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

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

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

  When the supply-side control valve 135a is turned on, the first port 135e and the second port 135f communicate with each other. 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. 6). That is, the constant pressure PS introduced into the supply side control valve 135a is introduced into a control hydraulic chamber 135o, which will be described later, of the supply side flow control valve 135c communicating with the first port 135k. Further, the constant pressure PS introduced into the supply side control valve 135a is introduced into the fourth port 135u of the discharge side flow control valve 135d (see the figure). On the other hand, when the supply-side control valve 135a is turned off, the second port 135f and the third port 135g communicate with each other. Accordingly, the first port 135k of the supply side flow control valve 135c is released to atmospheric pressure via the supply side control valve 135a (see FIG. 8). That is, the control hydraulic pressure chamber 135o is released to atmospheric pressure through the first port 135k of the supply side flow control valve 135c. Further, the fourth port 135u of the discharge side flow control valve 135d is released to the atmospheric pressure via the supply side control valve 135a (see FIG. 8). Here, as shown in FIG. 4, supply-side control valve 135 a is electrically connected to ECU 140 and is duty-controlled by a control signal from ECU 140. Accordingly, the supply-side control valve 135a can regulate the control hydraulic chamber 135o of the supply-side flow rate control valve 135c from a constant pressure PS to atmospheric pressure by a control signal from the ECU 140.

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

  When the discharge-side control valve 135b is turned on, the first port 135h and the second port 135i communicate with each other. Accordingly, the constant pressure PS introduced into the discharge side control valve 135b is introduced into the first port 135r of the discharge side flow control valve 135d (see FIG. 8). That is, the constant pressure PS introduced into the discharge side control valve 135b is introduced into a control hydraulic chamber 135v described later of the discharge side flow control valve 135d communicating with the first port 135r. Further, the constant pressure PS introduced into the discharge side control valve 135b is introduced into the fourth port 135n of the supply side flow control valve 135c (see the same figure). On the other hand, when the discharge side control valve 135b is turned off, the second port 135i and the third port 135j communicate with each other. Accordingly, the first port 135r of the discharge side flow control valve 135d is released to atmospheric pressure via the discharge side control valve 135b (see FIG. 6). That is, the control hydraulic chamber 135v is released to the atmospheric pressure via the first port 135r of the discharge side flow control valve 135d. Further, the fourth port 135n of the supply-side flow rate control valve 135c is released to atmospheric pressure via the discharge-side control valve 135b (see the same figure). Here, as shown in FIG. 4, the discharge-side control valve 135 b is electrically connected to the ECU 140 and is duty-controlled by a control signal from the ECU 140. Accordingly, the discharge-side control valve 135b can regulate the control hydraulic chamber 135v of the discharge-side flow control valve 135d from a constant pressure PS to atmospheric pressure by a control signal from the ECU 140.

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

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

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

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

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

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

  The drive hydraulic chamber control device 136 adjusts the hydraulic pressure P2 of the drive hydraulic chamber 81. As described above, the constant pressure PS is introduced from the constant pressure control device 134 into the drive hydraulic chamber control device 136. Further, the drive hydraulic chamber control device 136 is connected to the drive hydraulic chamber 81 via an oil passage R8. In the first embodiment, the drive hydraulic chamber control device 136 is connected to the drive hydraulic chamber 81 via the oil passage R8, the drive side main passage 23a, and the drive communication passage 23e. The drive hydraulic chamber control device 136 includes a switching valve (not shown). The drive hydraulic chamber control device 136 is electrically connected to the ECU 140 and controls ON / OFF of the ON / OFF valve by a control signal from the ECU 140. When the drive hydraulic chamber control device 136 is ON-controlled, that is, when the ON / OFF valve is turned ON, the branch oil passage R32 and the oil passage R8 communicate with each other and are introduced into the drive hydraulic chamber control device 136. The constant pressure PS is introduced into the drive hydraulic chamber 81, and the hydraulic pressure P2 in the drive hydraulic chamber 81 becomes the constant pressure PS. On the other hand, when the drive hydraulic chamber control device 136 is OFF-controlled, that is, when the ON / OFF valve is turned OFF, the communication between the branch oil path R32 and the oil path R8 is cut off, and the oil path R8 is externally connected. The hydraulic pressure P2 of the drive hydraulic chamber 81 becomes atmospheric pressure. Here, the constant pressure PS is a hydraulic pressure at which each hydraulic oil supply / discharge valve 70 can be opened by the hydraulic pressure P2 of the drive hydraulic chamber 81 at least when the hydraulic pressure P2 of the drive hydraulic chamber 81 becomes the constant pressure PS. That's it.

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

  As described above, the hydraulic oil supply control device 130 is connected to an ECU (Engine Control Unit) 140 (not shown) that controls at least the operation of the internal combustion engine 10. Accordingly, the hydraulic oil supply control device 130 controls at least the belt by controlling the primary hydraulic chamber control device 135, the drive hydraulic chamber control device 136, and the secondary hydraulic chamber control device 137 based on the control signal from the ECU 140. It controls the gear ratio of the continuously variable transmission 1-1.

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

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

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

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

  The change of the gear ratio is mainly performed by supplying hydraulic oil from the hydraulic oil supply control device 130 to the primary hydraulic chamber 55 or from the primary hydraulic chamber 55 to the outside of the primary pulley 50 via the hydraulic oil supply control device 130. The primary movable sheave 53 slides in the axial direction of the primary pulley shaft 51, and the interval between the primary fixed sheave 52 and the primary movable sheave 53, that is, the width of the primary groove 110a is adjusted. As a result, the contact radius of the belt 110 in the primary pulley 50 changes, and the speed ratio, which is the ratio between the rotation speed of the primary pulley 50 and the rotation speed of the secondary pulley 60, is controlled steplessly (continuously). The speed ratio is fixed mainly by holding the working oil in the primary hydraulic chamber 55.

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

  The change of the gear ratio includes an upshift, that is, a gear ratio decrease change that decreases the gear ratio, and a downshift, that is, a gear ratio increase change that increases the gear ratio. Each will be described below.

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

  The drive hydraulic chamber control device 136 is ON-controlled by the ECU 140. Therefore, the constant pressure PS introduced into the drive hydraulic chamber controller 136 is introduced into the drive hydraulic chamber 81, and the hydraulic pressure P2 of the drive hydraulic chamber 81 becomes the constant pressure PS. The actuator 80 causes the valve opening direction pressing force acting on the piston 82 to act on the valve body 71 of each hydraulic oil supply / discharge valve 70 as the valve body opening direction pressing force by the hydraulic pressure P <b> 2 of the drive hydraulic chamber 81. Here, as described above, when the hydraulic pressure P2 of the drive hydraulic chamber 81 becomes a constant pressure PS, the actuator 80 is operated by the hydraulic pressure P2 in the drive hydraulic chamber 81 so that each hydraulic oil supply / discharge valve 70 is pressed. Therefore, the valve body closing direction pressing force is exceeded. Accordingly, as shown in FIG. 5, each hydraulic oil supply / discharge valve 70 is opened by the actuator 80 moving the valve body 71 in the valve opening direction with respect to the valve seat surface 72.

  The supply-side control valve 135a of the primary hydraulic chamber control device 135 is duty-controlled by the ECU 140 to control the supply flow rate of hydraulic oil to the primary hydraulic chamber 55 by the supply-side flow rate control valve 135c. When duty control is performed by the ECU 140, the supply-side control valve 135a repeats ON and OFF, as shown in FIG. 6, and adjusts the control hydraulic pressure in the control hydraulic chamber 135o of the supply-side flow rate control valve 135c to a predetermined pressure during supply. And a predetermined pressure at the time of supply is introduced into the fourth port 135u of the discharge side flow control valve 135d. Here, the predetermined pressure at the time of supply decreases the supply flow rate controlled by controlling the communication between the second port 135l and the third port 135m by the spool valve opening direction pressing force acting on the spool 135p. It is the pressure which can be set as the supply flow rate based on speed. Accordingly, the supply-side flow rate control valve 135c is indicated by an arrow A in FIG. 5 because the spool valve opening direction pressing force based on the control hydraulic pressure of the control hydraulic chamber 135o, that is, the supply predetermined pressure exceeds the spool closing direction pressing force. As described above, the spool 135p moves in one of the movement directions, and the second port 135l and the third port 135m communicate with each other. As a result, the supply-side flow rate control valve 135c is opened, and the supply flow rate of hydraulic fluid to the primary hydraulic chamber 55 is reduced to 0 based on the reduction gear ratio and the transmission speed.

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

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

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

  The drive hydraulic chamber control device 136 is ON-controlled by the ECU 140. Therefore, the constant pressure PS introduced into the drive hydraulic chamber controller 136 is introduced into the drive hydraulic chamber 81, and the hydraulic pressure P2 of the drive hydraulic chamber 81 becomes the constant pressure PS. The actuator 80 causes the valve opening direction pressing force acting on the piston 82 to act on the valve body 71 of each hydraulic oil supply / discharge valve 70 as the valve body opening direction pressing force by the hydraulic pressure P <b> 2 of the drive hydraulic chamber 81. Here, as described above, when the hydraulic pressure P2 of the drive hydraulic chamber 81 becomes a constant pressure PS, the actuator 80 is operated by the hydraulic pressure P2 in the drive hydraulic chamber 81 so that each hydraulic oil supply / discharge valve 70 is pressed. Therefore, the valve body closing direction pressing force is exceeded. Accordingly, as shown in FIG. 5, each hydraulic oil supply / discharge valve 70 is opened by the actuator 80 moving the valve body 71 in the valve opening direction with respect to the valve seat surface 72.

  The supply-side control valve 135a of the primary hydraulic chamber control device 135 is duty-controlled by the ECU 140 to control the supply flow rate of hydraulic oil to the primary hydraulic chamber 55 by the supply-side flow rate control valve 135c. When duty control is performed by the ECU 140, the supply side control valve 135a maintains OFF as shown in FIG. 8, and the control hydraulic chamber 135o of the supply side flow rate control valve 135c and the fourth port 135u of the discharge side flow rate control valve 135d. To atmospheric pressure. Accordingly, since only the spool closing direction pressing force acts on the spool 135p, the supply-side flow rate control valve 135c is maintained in a state where the spool 135p is positioned in the other direction in the moving direction. The third port 135m does not communicate. As a result, the supply-side flow rate control valve 135c remains closed, and the supply flow rate of hydraulic oil to the primary hydraulic chamber 55 becomes zero.

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

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

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

  When the speed ratio is fixed, as shown in FIG. 2, each hydraulic oil supply / discharge valve 70 is closed, the hydraulic oil is supplied to the primary hydraulic chamber 55 via each hydraulic oil supply / discharge valve 70, and each hydraulic oil is supplied. Discharge of hydraulic oil from the primary hydraulic chamber 55 via the supply / discharge valve 70 is prohibited. Specifically, ECU 140 outputs a control signal based on the fixed gear ratio to hydraulic oil supply control device 130.

The drive hydraulic chamber control device 136 is OFF-controlled by the ECU 140. Accordingly, the drive hydraulic chamber 81 is released to the atmospheric pressure, and the hydraulic pressure P2 of the drive hydraulic chamber 81 is almost the atmospheric pressure P _OFF . As a result, the valve body opening direction pressing force does not act on the valve body 71 of each hydraulic oil supply / discharge valve 70, and the valve body closing direction pressing force by the valve body elastic member 74 and the hydraulic pressure P <b> 1 of the primary hydraulic chamber 55. As a result, only the valve element 71 moves in the valve closing direction and comes into contact with the valve seat surface 72, and each hydraulic oil supply / discharge valve 70 is closed. Since only the valve body closing direction pressing force acts on the pressure receiving member 82a via each valve body 71 and each pressing member 82b, the piston 82 moves in the other direction of the sliding direction, that is, closes. Slides in the valve direction.

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

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

  As described above, the hydraulic oil in the primary hydraulic chamber 55 is held by prohibiting the supply of the hydraulic oil to the primary hydraulic chamber 55 and the discharge of the hydraulic oil from the primary hydraulic chamber 55. Even when the gear ratio is fixed, the belt tension of the belt 110 changes, so that the contact radius of the belt 110 in the primary pulley 50 tends to change, and the position of the primary movable sheave 53 in the axial direction with respect to the primary fixed sheave 52 may change. is there. As described above, since the hydraulic oil is held in the primary hydraulic chamber 55, if the position of the primary movable sheave 53 in the axial direction with respect to the primary fixed sheave 52 is changed, the hydraulic pressure in the primary hydraulic chamber 55 is changed. Although P1 changes, the position of the primary movable sheave 53 in the axial direction with respect to the primary fixed sheave 52 is maintained constant. Accordingly, in order to keep the position of the primary movable sheave 53 in the axial direction with respect to the primary fixed sheave 52 constant, it is not necessary to increase the hydraulic pressure P1 of the primary hydraulic chamber 55 by supplying hydraulic oil to the primary hydraulic chamber 55. good. As a result, when the transmission ratio is fixed, the oil pump 132 does not have to be driven to supply the hydraulic oil to the primary hydraulic chamber 55, so that an increase in driving loss of the oil pump 132 can be suppressed.

  Further, the drive hydraulic chamber 81 of the actuator 80 which is a valve opening / closing means for forcibly opening each hydraulic oil supply / discharge valve 70 is not a primary pulley 50 which is a movable pulley but a stationary member. The hydraulic oil is supplied from the transaxle rear cover 23 that fixes the outer bearing ring 112a of the pulley bearing 112 to the radial outer side of the pulley bearing 112 that rotatably supports the primary pulley 50 with respect to a certain transaxle rear cover 23. That is, the drive side main passage 23a and the drive communication passage 23e, which are passages for supplying hydraulic oil to the drive hydraulic chamber 81, do not rotate even when the primary pulley 50 rotates. Therefore, the hydraulic oil supplied to the drive hydraulic chamber 81 can suppress the centrifugal hydraulic pressure from being generated in the hydraulic oil in the drive-side main passage 23a and the drive communication passage 23e. Absent. Therefore, the actuator 80 can reduce the influence of centrifugal force when the hydraulic oil supply / discharge valves 70 are forcibly opened. Thereby, the reliability of the operation of the actuator 80 and the controllability of the operation can be improved.

  Further, hydraulic oil is not supplied to the drive hydraulic chamber 81 via the primary pulley shaft 51. That is, it is not necessary to form a passage for supplying hydraulic oil to the drive hydraulic chamber 81 between the pulley bearings 111 and 112 in the primary pulley shaft 51. Therefore, since the axial length between the pulley bearings 111 and 112 in the primary pulley shaft 51 can be shortened, the shaft length of the primary pulley 50 which is one of the pulleys can be shortened.

  In the first embodiment, the piston 82 is rotated integrally with the primary pulley 50, which is one pulley, by the regulation pin 84 formed in the piston 82 and the regulation hole 54f formed in the primary partition wall 54. The invention is not limited to this.

  FIG. 9 is a diagram showing another configuration example of the piston. As shown in FIG. 9, a sliding groove 54 h is formed on the outer peripheral surface 54 d of the primary partition wall 54 so as to extend in the axial direction. A sliding protrusion 82d is formed extending in the axial direction on the inner peripheral surface of the piston 82 facing one outer peripheral surface 54d. By inserting the sliding projection 82d of the piston 82 into the sliding groove 54h of the primary partition wall 54, the sliding projection 82d is supported so as to be slidable in the axial direction with respect to the sliding groove 54h. Therefore, the piston 82 is slidably supported in the axial direction, that is, the sliding direction of the piston 82 with respect to the primary pulley 50 that is one pulley, and can rotate integrally with the primary pulley 50. Note that one or more sliding groove portions 54h and sliding projection portions 82d may be formed, and a plurality of locations (for example, two locations) may be formed at equal intervals on the circumference.

  Further, in the first embodiment, the piston 82 slides most in the axial direction which is the other of the sliding directions with respect to the drive hydraulic chamber 81, that is, in the valve closing direction, and comes into contact with the stopper plate 23b. Positioning in the sliding direction of the piston 82, that is, restriction of movement to the other of the sliding directions of the piston 82 is performed, but the present invention is not limited to this.

  As shown in the figure, the piston 82 includes a main body portion 82a, a protruding portion 82b, and a contact portion 82c. The main body portion 82a has a ring shape, and protrudes from the radially inner portion of the other end portion in the axial direction (the other in the sliding direction) toward the pulley shaft side (the other in the axial direction). Is formed to protrude. The protrusion 82b has a ring shape and is supported so as to be slidable in the sliding direction together with the main body 82a between the stopper plate 23b and the primary partition wall 54 of the primary pulley 50, which is one of the pulleys. Further, the contact portion 82c further protrudes from the radially inner portion of the other end portion (the other of the sliding directions) in the axial direction of the protruding portion 82b toward the pulley shaft side (the other in the axial direction). Is formed.

  Here, the contact portion 82c is disposed in a groove portion 54g formed on the radially outer side of the surface of the primary partition wall 54 that contacts the pulley bearing 112, that is, the surface of the pulley bearing 112 that contacts the bearing inner ring 112b. The bearing inner ring 112b of the pulley bearing 112 is exposed on the pulley side of the groove 54g. The contact portion 82c is set so that the main body portion 82a does not come into contact with the stopper plate 23b when the contact portion 82c comes into contact with the bearing inner ring 112b of the pulley bearing 112. The drive hydraulic chamber 81 is configured by a space formed between the stopper plate 23b and the piston 82. Between the outer peripheral surface of the main body 82a of the piston 82 and the inner peripheral surface of the protrusion 23d of the stopper plate 23b, and between the outer peripheral surface of the main body 82a of the piston 82 and the inner peripheral surface of the protrusion 23d of the stopper plate 23b. Are provided with piston seal members S4 such as seal rings, for example. That is, the space formed by the stopper plate 23b and the piston 82 constituting the drive hydraulic chamber 81 is sealed by the piston seal member S4.

  When the piston 82 slides in the valve closing direction, the contact portion 82c also slides in the groove 54g in the valve closing direction. Then, when the contact portion 82c comes into contact with the bearing inner ring 112b of the pulley bearing 112, the piston 82 slides most in the valve closing direction, that is, in the sliding direction. In other words, the positioning of the piston 82 in the sliding direction is performed by contacting the bearing inner ring 112b that is in contact with the primary pulley shaft 51 of the primary pulley 50, which is one of the pulley bearings 112, and the contact portion 82c of the piston 82. Also good. Therefore, the movement of the piston 82 in the sliding direction is restricted to the primary pulley 50 by the bearing inner ring 112b that rotates integrally with the primary pulley 50 that is one pulley, the sliding groove 54h, and the sliding projection 82d. This is done by contacting the integrally rotating piston 82. Therefore, relative rotation between the bearing inner ring 112b and the piston 82 can be suppressed. Thereby, drag generated between the bearing inner ring 112b and the piston 82 can be suppressed, and durability can be improved.

  Further, when the contact portion 82c and the bearing inner ring 112b come into contact with each other, as described above, the stopper plate 23b that is a bearing fixing member that does not rotate integrally with the primary pulley 50 that is one pulley, and the primary pulley 50 that rotates integrally. The piston 82 is in non-contact. Therefore, drag generated between the stopper plate 23b and the piston 82 can be suppressed, and durability can be improved. Further, in order to restrict the movement of the piston 82 to the other of the sliding directions, it is not necessary to provide a restriction component. Therefore, the number of parts of the belt type continuously variable transmission 1-1 can be reduced, and the size and cost can be reduced.

  Further, in the first embodiment, each hydraulic oil supply / discharge valve 70 is provided in the primary partition wall 54, but it is only necessary to be able to rotate integrally with the primary pulley 50 that is one of the pulleys, and the present invention is limited to this. is not. For example, the hydraulic oil supply / discharge valve 70 may be provided in the primary pulley shaft 51 and the primary movable sheave 53.

  In the first embodiment, the hydraulic oil supply valve and the hydraulic oil discharge valve are the same for each hydraulic oil supply / discharge valve 70, but the hydraulic oil supply valve and the hydraulic oil discharge valve may be provided separately. . FIG. 10 is a diagram illustrating another configuration example of the primary pulley according to the first embodiment. As shown in the figure, a hydraulic oil discharge valve 150 having the same configuration as the hydraulic oil supply / discharge valve 70 is provided in the primary partition wall 54, and a hydraulic oil supply valve 160 is provided in the primary hydraulic chamber 55. That is, the hydraulic oil discharge valve 150 and the hydraulic oil supply valve 160 are provided so as to rotate integrally with the primary pulley 50 that is one pulley. The hydraulic oil supply control device 130 is configured such that the primary hydraulic chamber control device 135 controls only the supply of hydraulic oil to the primary hydraulic chamber 55.

  The hydraulic oil supply valve 160 is opened when hydraulic oil is supplied to the primary hydraulic chamber 55 which is one clamping pressure generating hydraulic chamber. The hydraulic oil supply valve 160 supplies hydraulic oil to the primary hydraulic chamber 55. The hydraulic oil supply valve 160 is a ball type check valve, and includes a valve body 161, a valve seat surface 162, a valve body elastic member 163, a cylindrical member 164, and a snap ring 165. Reference numeral 166 denotes a casing that houses the valve body 161, the valve body elastic member 163, the cylindrical member 164, and the snap ring 165. Reference numeral 167 denotes a snap ring for fixing the hydraulic oil supply valve 160, here the casing 166. Further, the hydraulic oil supply valve 160 may be formed at least one with respect to the primary pulley 50 that is one pulley that rotates integrally, and is provided at a plurality of locations (for example, two locations) at equal intervals on the circumference. May be. When providing the hydraulic oil supply valve 160 at a plurality of locations, a plurality of valve seat surfaces 162 are formed on one casing 166, and the valve body 161, the valve body elastic member 163, corresponding to each valve seat surface 162, The cylindrical member 164 and the snap ring 165 may be stored as a plurality of sets.

  The valve body 161 has a spherical shape, is disposed closer to the primary hydraulic chamber than the valve seat surface 162, and has a diameter larger than the inner diameter of the valve seat surface 162. The valve seat surface 162 is formed near one end of a cylindrical storage portion 166a formed on the casing 166, that is, near the end opposite to the primary hydraulic chamber side. The valve seat surface 162 has a tapered shape that inclines toward the radially outer side from the side opposite to the primary hydraulic chamber side toward the primary hydraulic chamber side. Here, in the casing 166, a communication portion 166 b that connects the primary hydraulic chamber 55 and the storage portion 166 a is formed in the vicinity of the valve seat surface 162.

  By contacting the valve body 161 with the valve seat surface 162, the space portion on the primary hydraulic chamber side, that is, the valve opening direction side and the space opposite to the primary hydraulic chamber side, that is, the valve closing direction side, of the storage portion 166 a. And the hydraulic oil supply valve 160 is closed. Further, when the valve body 161 is separated from the valve seat surface 162, the space portion on the valve opening direction side and the space portion on the valve closing direction side in the storage portion 166a communicate with each other, and the hydraulic oil supply valve 160 is opened. The That is, the hydraulic oil supply valve 160 opens in the valve opening direction (upward in the figure) and closes in the valve closing direction (downward in the figure).

  The valve body elastic member 163 is a valve body closing direction pressing force generating means. The valve body elastic member 163 is attached between the snap ring 165 inserted and fixed in the space portion on the valve opening direction side of the storage portion 166a and the valve seat surface 162 via the valve body 161 and the cylindrical member 164. It is arranged in a state of being urged. Thereby, the valve body elastic member 163 generates a valve closing biasing force, and the valve closing biasing force is an elastic member pressing force in a direction in which the valve body 161 contacts the valve seat surface 162. It acts on the valve body 161 as a pressing force. As a result, the valve body 161 is pressed against the valve seat surface 162, and the hydraulic oil supply valve 160 functions as a check valve.

  Here, when the hydraulic oil supply valve 160 is opened, the valve body valve opening direction pressing force, which is the pressing force acting on the valve body 161 in the direction in which the valve body 161 moves away from the valve seat surface 162, that is, the valve opening direction, is The valve body 161 exceeds the valve closing direction pressing force, which is the pressing force acting on the valve body 161 in the direction in which the valve body 161 contacts the valve seat surface 162, that is, the valve closing direction, and the valve body 161 moves away from the valve seat surface 162. Done in The valve body opening direction pressing force is applied to the storage portion 166a into which hydraulic oil flows from the hydraulic oil supply control device 130 via the supply / discharge side main passage 51a, the shaft side communication passage 51b, the space portion T1, and the sheave side communication passage 53e. Among them, the hydraulic oil valve opening direction pressing force is applied to the valve body 161 by the hydraulic pressure P (similar to the hydraulic pressure of the space portion T1) of the space portion on the opposite side to the primary hydraulic chamber side, that is, the valve closing direction side. On the other hand, the valve body closing direction pressing force is the elastic member pressing force acting on the valve body 161 by the valve closing biasing force and the hydraulic oil closing acting on the valve body 161 in the valve closing direction by the hydraulic pressure P1 of the primary hydraulic chamber 55. Valve direction pressing force. When the hydraulic oil supply valve 160 is opened, the space portion on the primary hydraulic chamber side and the space portion on the opposite side to the primary hydraulic chamber side in the storage portion 166a communicate with each other, and the storage portion is connected via the communication portion 166b. In 166 a, the hydraulic oil supplied from the hydraulic oil supply control device 130 to the space on the primary hydraulic chamber side in the storage portion 166 a is supplied to the primary hydraulic chamber 55 via the hydraulic oil supply valve 160. Since the hydraulic pressure P1 of the primary hydraulic chamber 55 acts as a valve closing direction pressing force on the valve body 161, the valve body 161 does not leave the valve seat surface 162 even when the hydraulic pressure P1 of the primary hydraulic chamber 55 rises. Accordingly, the closed state of the hydraulic oil supply valve 160 is maintained unless the valve body opening direction pressing force acting on the valve body 161 exceeds the valve body opening direction pressing force. The hydraulic oil in the primary hydraulic chamber 55 is reliably held in the primary hydraulic chamber 55.

  On the other hand, each hydraulic oil discharge valve 150 is opened only when the hydraulic oil is discharged from the primary hydraulic chamber 55. Each hydraulic oil discharge valve 150 is forcibly opened by the actuator 80 when the hydraulic oil is discharged from the primary hydraulic chamber 55. When each hydraulic oil discharge valve 150 is opened, the valve body opening direction pressing force, which is a pressing force acting on the valve body 151 in the valve opening direction, is the valve body 151 in the valve closing direction, as in the first embodiment. This is performed by exceeding the valve body closing direction pressing force, which is a pressing force acting on the valve body 151, so that the valve body 151 is separated from the valve seat surface 152. When each hydraulic oil discharge valve 150 is opened, the valve arrangement passage 54a communicates with the primary hydraulic chamber 55, and the discharge passage 54i communicates with the valve arrangement passage 54a and the outside of the primary partition wall 54, that is, the outside of the primary pulley 50. And the primary hydraulic chamber 55 communicate with each other. Accordingly, the hydraulic oil in the primary hydraulic chamber 55 is discharged to the outside of the primary pulley 50 via each hydraulic oil discharge valve 150. As in the first embodiment, the discharge passage 54i is formed with respect to the primary partition wall 54 so that the valve seat surface 152 of the hydraulic oil discharge valve 150 is formed on the extended line of the discharge passage 54i. Is preferred.

  Next, the belt type continuously variable transmission 1-2 according to the second embodiment will be described. FIG. 11 is a diagram illustrating a schematic configuration example of the primary pulley according to the second embodiment. FIG. 12 is a diagram illustrating the relationship between the hydraulic pressure in the drive hydraulic chamber and the amount of movement of the pressing member. FIGS. 13-14 is operation | movement explanatory drawing of the primary pulley concerning Example 2. FIGS. FIG. 15 is a diagram illustrating another schematic configuration example of the primary pulley according to the second embodiment. The belt-type continuously variable transmission 1-2 according to the second embodiment is different from the belt-type continuously variable transmission 1-1 according to the first embodiment in that the pressing member 83 and the piston 82 are in one of the sliding directions. A notch 83a that communicates between the primary hydraulic chamber 55 and the primary pulley 50 when it slides most is formed. The basic configuration and operation of the belt-type continuously variable transmission 1-2 according to the second embodiment are substantially the same as the basic configuration and operation of the belt-type continuously variable transmission 1-1 according to the first embodiment. The same parts will be omitted or simplified for explanation.

  As shown in FIG. 11, the pressing member 83 of the actuator 80 has a notch 83a. The notch 83a is formed from the other of the sliding methods in the axial direction, that is, from the end in the valve closing direction to the vicinity of the center. The axial length of the notch 83a is such that the gap formed by the notch 83a between the pressing member 83 and the sliding support hole 54c when the piston 82 slides most in one of the sliding directions. The length is set so as to allow communication between the primary hydraulic chamber 55 and the outside of the primary pulley 50, that is, the outside of the primary partition wall 54. The notch 83a may be formed so as to face the pressing member 83, or may be continuously formed on the circumference.

  The hydraulic oil supply / discharge valve 70, which is a hydraulic oil discharge valve, closes the valve body by causing the valve body 71 to act on the valve body 71 by pressing the valve body 71 in the valve closing direction by generating a valve closing biasing force. Two valve body elastic members 76 and 77 are provided as valve direction pressing force generating means. The two valve element elastic members, that is, the valve element elastic member 76 on the valve element side and the valve element elastic member 77 on the fixed side are valve element elastic members 76 on the valve element side with respect to the valve element 71 and the valve element elastic member 77 on the fixed side. Is disposed between the valve seat surface 72 and the snap ring 75 via the valve body side holding member 78. Thereby, the valve body elastic member 76 on the valve body side and the valve body elastic member 77 on the fixed side respectively generate valve closing biasing force, and each valve closing biasing force causes the valve body 71 to contact the valve seat surface 72. It acts on the valve body 71 as a valve body closing direction pressing force which is an elastic member pressing force in the direction, that is, the valve closing direction.

  The valve body elastic member 76 on the valve body side is an elastic member such as a helical coil spring. The valve body side elastic member 76 and the valve body side holding member 78 are provided corresponding to each hydraulic oil supply / discharge valve 70. The fixed-side valve element elastic member 77 has an L-shaped cross section in the axial direction, and is provided not for each hydraulic oil supply / discharge valve 70 but for the primary pulley 50. The fixed-side valve body elastic member 77 is axially oriented with respect to the primary partition wall 54 by a snap ring 75 that is inserted and fixed to the outer peripheral surface of the protruding portion formed radially inside of one axial end portion of the primary partition wall 54. Restricted to move to. The fixed-side valve element elastic member 77 faces the surface of the primary partition wall 54 facing the primary movable sheave 53 so that a gap is formed between the fixed side valve body elastic member 77 and the primary partition wall 54.

  Here, the valve body elastic member 76 on the valve body side and the valve body elastic member 77 on the fixed side are formed so that the valve closing urging forces generated differ stepwise. For example, the rigidity of the valve body elastic member 76 on the valve body side is made lower than that of the valve body elastic member 77 on the fixed side, that is, the valve body elastic member 76 on the valve body side has a low rigidity, and the valve body elastic member 77 on the fixed side is installed. High rigidity. Thereby, the valve body closing direction pressing force acting on the valve body 71, in the second embodiment, stepwise regardless of the change in the hydraulic oil valve closing direction pressing force acting on the valve body 71 by the hydraulic pressure P1 of the primary hydraulic chamber 55. Can be different. That is, the valve body closing direction pressing force acting on the valve body 71 by the hydraulic pressure P2 of the drive hydraulic chamber 81 causes the pressing member 83 to slide in one of the sliding directions together with the piston 82, thereby opening the valve body 71 in the valve opening direction. When the valve body is moved, the valve body elastic member 76 on the valve body side can only be contracted, and the valve body valve opening direction pressing force (hereinafter simply referred to as “first valve body valve opening direction pressing force”) The valve body elastic member 76 can be contracted, and the valve body elastic member 77 on the fixed side can be deformed (hereinafter simply referred to as “first valve body valve opening direction pressure”). Can be differentiated step by step. Therefore, the valve opening hydraulic pressure PA that is the hydraulic pressure P2 of the drive hydraulic chamber 81 that can apply the first valve element opening direction pressing force to the valve element 71 and the second valve element opening direction pressing force to the valve element 71. The communication hydraulic pressure PB that is the hydraulic pressure P2 of the drive hydraulic chamber 81 that can be actuated can be varied stepwise.

  As shown in FIG. 12, the valve body elastic member 76 on the valve body side and the valve body elastic member 77 on the fixed side have a valve opening hydraulic pressure PA (the valve body 71 is pushed in the first valve body opening direction). When the pressure is applied), the movement amount X of the pressing member 83 can only open the hydraulic oil supply / discharge valve 70, and the primary hydraulic chamber 55 and the outside of the primary pulley 50 are communicated by the notch 83a. It is set so that the valve closing urging force with the valve opening movement amount X1 not generated can be generated. Further, the valve body elastic member 76 on the valve body side and the valve body elastic member 77 on the fixed side are provided when the drive hydraulic chamber 81 becomes the communication hydraulic pressure PB (when the second valve body opening direction pressing force acts on the valve body 71). With the valve closing, the movement amount X of the pressing member 83 becomes the communication movement amount X2 that enables the opening of the hydraulic oil supply / discharge valve 70 and the communication between the primary hydraulic chamber 55 and the outside of the primary pulley 50 by the notch 83a. It is set so that it can generate power. Note that the drive hydraulic chamber control device 136 of the hydraulic oil supply control device 130 sets the pressure introduced into the drive hydraulic chamber 81 via the oil path R8, that is, the hydraulic pressure P2 of the drive hydraulic chamber 81 to at least atmospheric pressure and the valve opening hydraulic pressure. It has a function that can be adjusted to either PA or communication hydraulic pressure PB. For example, the drive hydraulic chamber control device 136 includes valves having the same functions as the supply-side control valve 135a and the discharge-side control valve 135b.

  In the gear ratio increase change in the belt-type continuously variable transmission 1-2, the hydraulic oil supply control device 130 is controlled in accordance with the increase gear ratio calculated by the ECU 140 and the gear shift speed. Here, the discharge flow rate for changing the gear ratio increase with the calculated increase gear ratio and shift speed opens only each hydraulic oil supply / discharge valve 70 so that the hydraulic oil is supplied by the hydraulic oil supply control device 130. When the valve opening maximum discharge flow rate that can be discharged is not exceeded, the ECU 140 controls the hydraulic pressure in the driving hydraulic chamber 81 to the valve opening hydraulic pressure PA by the driving hydraulic chamber control device 136. Therefore, as shown in FIG. 13, only the hydraulic oil supply / discharge valves 70 are opened, and the hydraulic oil in the primary hydraulic chamber 55 is supplied by the hydraulic oil supply control device 130 as shown by an arrow E in the figure. Discharged. On the other hand, when the discharge flow rate for changing the gear ratio increase at the calculated increase gear ratio and shift speed exceeds the maximum discharge flow rate during valve opening, the ECU 140 controls the hydraulic pressure in the drive hydraulic chamber 81 by the drive hydraulic pressure chamber control device 136. Is controlled to the communication hydraulic pressure PB. Accordingly, as shown in FIG. 14, each hydraulic oil supply / discharge valve 70 is opened, and the primary hydraulic chamber 55 and the outside of the primary pulley 50 are communicated by the notch 83a. As shown, the hydraulic oil in the primary hydraulic chamber 55 is discharged by the hydraulic oil supply control device 130 and through the notch 83a.

  As described above, the belt-type continuously variable transmission 1-2 according to the second embodiment has the same effects as the belt-type continuously variable transmission according to the first embodiment. Further, since the valve opening hydraulic pressure PA and the communication hydraulic pressure PB are stepwise different, even if the hydraulic pressure P2 in the drive hydraulic chamber 81 varies in the vicinity of the valve opening hydraulic pressure PA, the hydraulic pressure P2 in the drive hydraulic chamber 81 does not reach the communication hydraulic pressure PB. Therefore, due to the variation in the hydraulic pressure P2 of the drive hydraulic chamber 81, the communication between the primary hydraulic chamber 55 which is one clamping pressure generating hydraulic chamber and the outside of the primary pulley 50 which is one pulley by the notch 83a is suppressed. can do. Thereby, the controllability of the belt type continuously variable transmission 1-1 when the gear ratio is increased can be improved.

  Further, by opening each hydraulic oil supply / discharge valve 70 that is a hydraulic oil discharge valve, when the hydraulic oil is discharged from the primary hydraulic chamber 55 that is one clamping pressure generating hydraulic chamber, a normal hydraulic oil discharge path is provided. The hydraulic oil can be discharged through the notch portion 83a together with the hydraulic oil discharged by, for example, the hydraulic oil through the partition wall side communication passage 54b which is a discharge passage. Accordingly, the maximum discharge flow rate at which the hydraulic oil can be discharged from the primary hydraulic chamber 55 via each hydraulic oil supply / discharge valve 70 can be increased, so that the gear ratio increase change during the downshift, that is, the gear ratio is increased. The maximum shift speed at the time can be increased. Further, since the hydraulic oil can be discharged from the primary hydraulic chamber 55 via each hydraulic oil supply / discharge valve 70 via the notch 83a, compared to the case where the hydraulic oil is discharged only through the hydraulic oil discharge path, When the maximum transmission speed at the time of changing the transmission ratio is the same, the maximum discharge flow rate when the hydraulic oil is discharged through the hydraulic oil discharge path can be reduced. As a result, the hydraulic oil discharge path can be narrowed, the hydraulic oil discharge valve can be downsized, and the belt type continuously variable transmission 1-2 can be downsized.

  In the second embodiment, the valve body side holding member 78 is provided corresponding to each hydraulic oil supply / discharge valve 70, but the present invention is not limited to this. For example, as shown in FIG. 15, a valve body side holding member 79 that holds the valve body elastic member 76 on each valve body side is formed in an annular shape and fixed to the valve body side valve body elastic member 76 that is two valve body elastic members. You may arrange | position between the valve body elastic members 77 of the side. In this case, since the valve body side holding member 79 for holding the valve body elastic member 76 on each valve body side is formed in an annular shape, the valve body elastic member 76 on each valve body side can be reliably held. Further, when a plurality of hydraulic oil supply / discharge valves 70 are provided on the circumference, the valve body elastic member 76 on the valve body side of each hydraulic oil supply / discharge valve 70 can be held by one valve body side holding member 79. it can. Therefore, the number of parts can be reduced, and the belt type continuously variable transmission 1-2 can be reduced in size and cost.

1 is a skeleton diagram of a belt type continuously variable transmission according to Embodiment 1. FIG. 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-oil supply control apparatus. It is operation | movement explanatory drawing of the belt type continuously variable transmission at the time of gear ratio change. It is operation | movement explanatory drawing of the belt type continuously variable transmission at the time of gear ratio change. It is operation | movement explanatory drawing of the belt type continuously variable transmission at the time of gear ratio change. It is operation | movement explanatory drawing of the belt type continuously variable transmission at the time of gear ratio change. It is a figure which shows the other structural example of a piston. It is a figure which shows the other structural example of the primary pulley concerning Example 1. FIG. It is a figure which shows the schematic structural example of the primary pulley concerning Example 2. FIG. It is a figure which shows the relationship between the hydraulic pressure of a drive hydraulic chamber, and the movement amount of a press member. It is operation | movement explanatory drawing of the primary pulley concerning Example 2. FIG. It is operation | movement explanatory drawing of the primary pulley concerning Example 2. FIG. It is a figure which shows the other schematic structural example of the primary pulley concerning Example 2. FIG.

Explanation of symbols

1-1, 1-2 Belt type continuously variable transmission 10 Internal combustion engine (drive source)
20 Transaxle 23 Transaxle rear cover 23a Drive side main passage 23b Stopper plate (bearing fixing member)
23c Main body portion 23d Projection portion 23e Drive communication passage 30 Torque converter 40 Forward / reverse switching mechanism 50 Primary pulley 51 Primary pulley shaft 52 Primary fixed sheave 53 Primary movable sheave 54 Primary partition wall 54a Valve arrangement passage 54b Partition side communication passage 54c Sliding support hole 54d Outer peripheral surface 54e Opposing surface 54f Restriction hole (integral rotation means)
54g Groove 54h Sliding groove (integral rotation means)
54i Discharge passage 55 Primary hydraulic chamber (one clamping pressure generating hydraulic chamber)
60 Secondary pulley 64 Secondary hydraulic chamber (the other clamping pressure generating hydraulic chamber)
70 Hydraulic oil supply / discharge valve (hydraulic oil supply valve, hydraulic oil discharge valve)
71 Valve body 72 Valve seat surface 73 Valve body elastic member 74 Valve body elastic member holding member 75 Snap ring 76 Valve body side elastic body member 77 Fixed side valve body elastic member 78, 79 Valve body side holding member 80 Actuator (valve opening / closing) means)
81 Drive hydraulic chamber 82 Piston 82a Main body part 82b Protruding part 82c Contact part 83 Pressing member 83a Notch part 84 Restriction pin (integral rotation means)
90 final reduction gear 100 power transmission path 110 belt 112 pulley bearing 112a bearing outer ring 112b bearing inner ring 112c bearing support member 120 wheel 130 hydraulic oil supply control device 131 oil pan 132 oil pump 133 line pressure control device 134 constant pressure control device 135 primary hydraulic pressure Chamber control device 136 Drive hydraulic chamber control device 137 Secondary hydraulic chamber control device 140 ECU
DESCRIPTION OF SYMBOLS 150 Hydraulic oil discharge valve 151 Valve body 152 Valve seat surface 153 Valve body elastic member 154 Valve body elastic member holding member 155 Snap ring 160 Hydraulic oil supply valve 161 Valve body 162 Valve seat surface 163 Valve body elastic member 164 Cylindrical member 165 Snap ring 166 Casing 166a Storage part 166b Communication part 167 Snap ring S1 Seal member for communication part S2 Seal member for primary hydraulic chamber S3, S4 Seal member for piston

Claims (11)

Two pulleys rotating with respect to the stationary member;
A belt that is wound around each pulley and transmits a driving force from a driving source;
A clamping pressure generating hydraulic chamber formed in each pulley and generating a belt clamping pressure with respect to the belt by hydraulic pressure;
A hydraulic oil supply valve that opens when supplying hydraulic oil to one of the clamping pressure generating hydraulic chambers of the clamping pressure generating hydraulic chamber, and rotates integrally with the one pulley;
A hydraulic oil discharge valve that opens when the hydraulic oil is discharged from the one clamping pressure generating hydraulic chamber, and rotates integrally with the one pulley;
Valve opening and closing means for forcibly opening the hydraulic oil discharge valve by sliding the piston in one of the sliding directions with respect to the drive hydraulic chamber by the hydraulic pressure of the drive hydraulic chamber;
A belt type continuously variable transmission comprising:
A belt type continuously variable transmission, wherein hydraulic oil is supplied to the drive hydraulic chamber from a radially outer side of a pulley bearing that rotatably supports the one pulley with respect to the stationary member.   The drive hydraulic chamber is formed in a drive-side main passage formed on the radially outer side of the pulley bearing, and a bearing fixing member that fixes the pulley bearing to the stationary member, and includes the drive hydraulic chamber and the drive-side main passage. 2. The belt type continuously variable transmission according to claim 1, wherein hydraulic oil is supplied through a communicating communication passage.   The hydraulic oil discharge valve is closed by contact of the valve body of the hydraulic oil discharge valve on the extension line of the discharge passage for discharging the hydraulic oil from the one clamping pressure generating hydraulic chamber via the hydraulic oil discharge valve. The belt-type continuously variable transmission according to claim 1 or 2, wherein a valve seat surface is formed.   The valve opening / closing means is slidably supported in the sliding direction with respect to the one pulley, and presses the valve body in the valve opening direction via the piston by the hydraulic pressure of the drive hydraulic chamber. The belt-type continuously variable transmission according to any one of claims 1 to 3, further comprising:   The belt-type continuously variable transmission according to claim 4, further comprising an integral rotating means for integrally rotating the piston with respect to the one pulley.   The belt-type continuously variable transmission according to claim 5, wherein the piston is positioned in the sliding direction by contacting the piston with a bearing inner ring that contacts the one of the pulley bearings. Machine.   The pressing member is formed with a notch that communicates the one clamping pressure generating hydraulic chamber and the outside of the one pulley when at least the piston slides most in one of the sliding directions. The belt-type continuously variable transmission according to any one of claims 4 to 6. The hydraulic oil discharge valve includes a valve body closing direction pressing force generating means that generates a valve closing biasing force to act on the valve body in a valve body closing direction pressing force that presses the valve body in the valve closing direction. In addition,
The belt-type continuously variable transmission according to claim 7, wherein the valve body closing direction pressing force generating means varies the generated valve closing biasing force stepwise according to the amount of movement of the pressing member. Machine. The valve body closing direction pressing force generating means is constituted by two valve body elastic members that are different in stages in the generated valve closing biasing force,
The valve body-side holding member that holds the valve body-side valve body elastic member of the two valve body elastic members is formed in an annular shape and disposed between the two valve body elastic members. The belt type continuously variable transmission according to claim 8.   The belt-type continuously variable transmission according to any one of claims 1 to 9, wherein the hydraulic oil supply valve and the hydraulic oil discharge valve are the same.   The valve opening / closing means forcibly opens the hydraulic oil supply valve that is the same as the hydraulic oil discharge valve even when hydraulic oil is supplied to one of the clamping pressure generating hydraulic chambers. The belt-type continuously variable transmission according to claim 10.

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