JP2008101752A - 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 working fluid supply valve 70 permitting only supply of working fluid to a primary hydraulic pressure chamber 55 and rotating as one unit with the primary pulley 50, a valve open close device 80 controlling permission and prohibition of discharge of the working fluid from the primary hydraulic pressure chamber 55 by the working fluid supply discharge valve 70 and discharge of the working fluid from the primary hydraulic pressure chamber 55, and rotating as one unit with the primary pulley 50, and a discharge flow rate control valve 90 controlling discharge flow rate of the working fluid discharged from the primary hydraulic pressure chamber 55 by the working fluid supply valve 70 and rotating as one unit with the primary pulley 50. The valve open close device 80 applies valve open direction pressing force (piston valve open direction pressing force F4) in an open direction of the working fluid supply valve 70 on a valve element 71 of the working fluid supply valve 70 when the working fluid is supplied to the primary hydraulic pressure chamber 55. <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. This 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 includes 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 the primary pulley. There is a belt-type continuously variable transmission configured by a belt that transmits a transmitted driving force to a secondary pulley. The primary pulley and the secondary pulley include a primary pulley shaft and a secondary pulley shaft, which are two pulley shafts arranged in parallel, and two movable sheaves (primary movable sheave, Secondary movable sheave), two fixed sheaves (primary fixed sheave, secondary fixed sheave) that are opposed to the two movable sheaves in the axial direction and that form a V-shaped groove between the movable sheave and hydraulically, The movable sheave is constituted by a positioning hydraulic chamber that generates a belt clamping pressure against the belt by pressing the movable sheave toward the fixed sheave. The belt is wound around a V-shaped groove formed in each of the primary pulley and the secondary pulley.

  In this belt type continuously variable transmission, each movable sheave slides in the axial direction on each pulley shaft by each positioning hydraulic chamber, and the width of the V-shaped groove formed in each of the primary pulley and the secondary pulley. To change. 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 positioning hydraulic chamber presses the movable sheave toward the fixed sheave by the hydraulic pressure of the positioning 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, the hydraulic pressure in the positioning hydraulic chamber needs to be held 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. .

JP 2001-323978 A

  Therefore, in the conventional belt-type continuously variable transmission, it is necessary to supply hydraulic oil to the positioning hydraulic chamber not only when the speed ratio is changed but also when the speed ratio is fixed. For this reason, it is necessary to operate the oil pump provided in the hydraulic oil supply control device. Further, the hydraulic oil is supplied from the hydraulic oil supply control device to the positioning hydraulic chamber by a passage formed in a fixed member such as a case and a movable member such as a pulley shaft of the belt type continuously variable transmission. Therefore, in order to supply the working oil to the positioning hydraulic chamber even when the transmission ratio is fixed, the working oil may leak from the sliding portion between the fixed member and the movable member.

  Accordingly, the present invention has been made in view of the above, and an object of the present invention is to provide a belt type continuously variable transmission that can 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 and a driving force from a driving source wound around each pulley and transmitted to one pulley are transmitted to the other pulley. And a hydraulic oil supply that is formed in each of the pulleys and that supplies hydraulic oil to one of the positioning hydraulic chambers among the positioning hydraulic chamber and the positioning hydraulic chamber that presses the movable sheave toward the fixed sheave by hydraulic pressure. A hydraulic oil discharge channel that communicates with the flow channel, the hydraulic oil supply channel, and discharges the hydraulic oil from the one positioning hydraulic chamber; and the one positioning hydraulic chamber disposed in the hydraulic oil supply channel. The hydraulic oil supply valve that only allows the hydraulic oil to be supplied to the hydraulic pulley and rotates integrally with the one pulley, and the hydraulic oil supply valve is forcibly opened to thereby open the hydraulic oil supply valve from the one positioning hydraulic chamber. Hydraulic oil A valve opening / closing means for controlling allowance or prohibition of discharge, and a hydraulic oil disposed in the hydraulic oil discharge passage and discharged from the one positioning hydraulic chamber by the hydraulic oil supply valve opened by the valve opening / closing means A discharge flow rate control valve that controls a discharge flow rate of the first pulley and rotates integrally with the one pulley, and the valve opening and closing means is configured to supply the hydraulic oil supply valve when the hydraulic oil is supplied to the one positioning hydraulic chamber. The valve body opening direction pressing force in the valve opening direction is applied to the valve body of the hydraulic oil supply valve.

  Also, in the present invention, in the belt-type continuously variable transmission, the valve opening / closing means is slidably supported in a driving hydraulic chamber to which the hydraulic oil is supplied, and in an opening / closing valve direction of the hydraulic oil supply valve, And a piston that causes the valve body to act on the valve body in the valve opening direction by the hydraulic pressure of the drive hydraulic chamber.

  According to the present invention, in the belt-type continuously variable transmission, the discharge flow rate control valve includes a spool that is slidably supported in an on-off valve direction, and the spool is driven by the hydraulic pressure of the drive hydraulic chamber. The discharge flow rate is controlled by the spool valve opening direction pressing force in the valve opening direction of the flow rate control valve.

  According to this invention, when changing the gear ratio, the hydraulic oil supply valve is opened to supply hydraulic oil to one positioning hydraulic chamber, or the hydraulic oil supply valve is forcibly opened. Then, the hydraulic fluid is discharged from the one positioning hydraulic chamber by opening the discharge flow rate control valve. On the other hand, when the transmission ratio is fixed (constant), the hydraulic oil supply valve is closed to prohibit the hydraulic oil from being discharged from one positioning hydraulic chamber. In other words, since the hydraulic oil supply valve only allows the hydraulic oil to be supplied to one positioning hydraulic chamber, the hydraulic oil in one positioning hydraulic chamber is held in the one positioning hydraulic chamber. . Therefore, even if the position of the movable sheave in the axial direction with respect to the fixed sheave is changed, the position of the movable sheave in the axial direction with respect to the fixed sheave can be kept constant by changing the oil pressure in the one positioning hydraulic chamber. . As a result, 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 one positioning hydraulic chamber from the outside of the one positioning hydraulic chamber, and the movable sheave can move with the fixed member. It can suppress that hydraulic fluid leaks from the sliding part with a member. Thereby, an increase in driving loss of the oil pump can be suppressed.

  Further, when supplying the hydraulic oil to one positioning hydraulic chamber, the valve opening / closing means operates the valve opening direction pressing force in the valve opening direction of the hydraulic oil supply valve on the valve body of the hydraulic oil supply valve. The valve body opening direction pressing force that opens the oil supply valve, that is, can move the valve body in the valve opening direction, is the valve body opening direction pressing force by the valve opening and closing means and one positioning hydraulic chamber. The valve body opening direction pressing force acting on the valve body is combined with the pressure of the supplied hydraulic oil. Therefore, when supplying the hydraulic oil to one positioning hydraulic chamber, the valve body opening direction pressing force by the valve opening / closing means is not applied to the valve body of the hydraulic oil supply valve. The valve body opening direction pressing force acting on the valve body by the pressure of the supplied hydraulic oil can be reduced. Thereby, the supply pressure of the hydraulic fluid supplied to one positioning hydraulic chamber can be made small.

  According to the present invention, in the belt-type continuously variable transmission, the hydraulic pressure of the drive hydraulic chamber that causes the valve body to act in the valve body opening direction pressing force when the hydraulic oil is supplied to the one positioning hydraulic chamber. Is less than the hydraulic pressure of the drive hydraulic chamber capable of opening the discharge flow rate control valve.

  According to this invention, when supplying the hydraulic oil to one positioning hydraulic chamber, the valve opening / closing means acts on the valve body opening direction pressing force in the valve opening direction of the hydraulic oil supply valve on the valve body of the hydraulic oil supply valve. Even if it is made to do, a discharge flow control valve maintains a closed state. Therefore, it is possible to suppress the hydraulic oil supplied to one positioning hydraulic chamber from leaking from the hydraulic oil discharge passage.

  In the belt-type continuously variable transmission according to the present invention, the hydraulic oil supply valve and the discharge flow rate control valve are arranged on the same axis.

  According to this invention, the hydraulic oil supply valve and the discharge flow rate control valve are integrated and arranged on one pulley that rotates integrally. Therefore, the size can be reduced.

  In the invention, in the belt type continuously variable transmission, the spool is the piston.

  According to this invention, since the spool is a piston, the forced opening of the hydraulic oil supply valve and the discharge flow rate can be controlled by moving the piston in the direction of the on-off valve. Therefore, since the piston and the spool can be shared, the number of parts can be reduced and the manufacturing cost can be reduced.

  According to the present invention, in the belt-type continuously variable transmission, the discharge flow rate control valve acts on the spool in the valve closing direction pressing force in the valve closing direction of the spool due to the hydraulic pressure in the one positioning hydraulic chamber. It is characterized by that.

  According to the present invention, when the hydraulic pressure of one positioning hydraulic chamber is low, the spool valve closing direction pressing force acting on the spool is lower than when the hydraulic pressure of one positioning hydraulic chamber is high. Therefore, when the hydraulic pressure in one positioning hydraulic chamber is low, the spool valve opening direction pressing force for fully opening the discharge flow rate control valve can be reduced as compared with the case where the hydraulic pressure in one positioning hydraulic chamber is high. . Thereby, the spool valve opening direction pressing force, for example, the spool valve opening direction pressing force by the hydraulic pressure of the driving hydraulic chamber can be changed according to the hydraulic pressure of one positioning hydraulic chamber.

  In the belt-type continuously variable transmission according to the present invention, the tip of the spool in the valve opening direction is exposed to one positioning hydraulic chamber.

  According to the present invention, it is possible to change the spool valve opening direction pressing force, for example, the spool valve opening direction pressing force due to the hydraulic pressure of the drive hydraulic chamber, with a simple configuration.

  The belt type continuously variable transmission according to the present invention has an effect of suppressing an increase in driving loss of the oil pump. In addition, there is an effect that the supply pressure of the hydraulic oil supplied to one positioning hydraulic chamber can be reduced.

  The present invention will be described in detail with reference to the drawings. In addition, this invention is not limited by the following Example. 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, the primary pulley is one pulley and the primary hydraulic chamber is one positioning hydraulic chamber, but the secondary pulley may be one pulley and the secondary hydraulic chamber may be one positioning hydraulic chamber.

  FIG. 1 is a skeleton diagram of a belt type continuously variable transmission according to the present invention. FIG. 2 is an axial sectional view of the primary pulley according to the first embodiment. FIG. 3A is a diagram illustrating a torque cam. FIG. 3-2 is an explanatory diagram of the operation of the torque cam. FIG. 4 is a diagram illustrating the hydraulic pressure in the drive hydraulic chamber and the valve open state. FIG. 5 is an explanatory diagram of the operation of the belt type continuously variable transmission when the gear ratio is changed. FIG. 6 is an explanatory diagram of the operation of the flow rate adjusting valve when the gear ratio is changed.

  As shown in FIG. 1, a transaxle 20 is disposed on the output side of the internal combustion engine 10. 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 accommodated in the transaxle housing 21. On the other hand, inside the case constituted by the transaxle case 22 and the transaxle rear cover 23, a primary pulley 50 and a secondary pulley which are two pulleys constituting the belt type continuously variable transmission 1-1 according to the first embodiment. 60, a primary hydraulic chamber 55 which is one positioning hydraulic chamber, a secondary hydraulic chamber 64 which is the other positioning hydraulic chamber, a hydraulic oil supply valve 70, a valve opening / closing device 80, a discharge flow rate control valve 90, a belt 120 is housed. Reference numeral 40 denotes a forward / reverse switching mechanism, 100 denotes a final reduction gear that transmits the driving force of the internal combustion engine 10 to the wheels 130, 110 denotes a power transmission path, and 140 denotes a hydraulic oil supply control device (see FIGS. 2, 4, and 5). , 150 is an ECU (Engine Control Unit).

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

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

  The turbine 32 is disposed so as to face the pump 31. The turbine 32 is disposed inside the hollow shaft 36 and is attached to an input shaft 38 that can rotate 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 supplied with hydraulic oil as a hydraulic fluid from a hydraulic oil supply controller 140 (not shown).

  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 any one of the belt-type continuously variable transmissions 1-1 described later. In the above, the stator 33 can change the flow of hydraulic fluid circulating between the pump 31 and the turbine 32 to obtain a predetermined torque characteristic.

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

  An oil pump 142 is provided between the torque converter 30 and a forward / reverse switching mechanism 40 described later. The oil pump 142 includes a rotor 142a, a hub 142b, and a body 142c. The oil pump 142 is connected to the pump 31 by a rotor 142a via a cylindrical hub 142b. The body 142c is fixed to the transaxle case 22. The hub 142b is splined to the hollow shaft 36. Therefore, the oil pump 142 can be driven because the output torque from the internal combustion engine 10 is transmitted to the rotor 142a via the pump 31.

  The forward / reverse switching mechanism 40 transmits the output torque from the internal combustion engine 10 transmitted through the torque converter 30 to the primary pulley 50 of any one of the belt-type continuously variable transmissions 1-1 described later. 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). This connecting member is spline-fitted to a primary pulley shaft 51 of a primary pulley 50 described later. 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 hydraulic oil supplied from a hydraulic oil supply control device 140 (not shown) to a hollow portion (not shown) of the input shaft 38. 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 a brake piston (not shown) to which hydraulic oil is supplied from a hydraulic oil supply control device 140 (not shown). 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 transmits the output torque from the internal combustion engine 10 transmitted through the forward / reverse switching mechanism 40 to the secondary pulley 60 by a belt 120 described later. 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 that is a positioning hydraulic chamber. It is configured.

  The primary pulley shaft 51 is rotatably supported by bearings 121 and 122. Further, the primary pulley shaft 51 is provided with a supply side passage 51a and a drive side passage 51b that do not communicate with each other. The hydraulic fluid supplied from the hydraulic fluid supply control device 140 to the primary hydraulic chamber 55 flows into the supply side passage 51a. The hydraulic fluid supplied from the hydraulic fluid supply control device 140 to the drive hydraulic chamber 82 described later flows into the drive-side passage 51b.

  Further, the primary pulley shaft 51 is formed with a communication passage 51c through which the hydraulic oil that has flowed into the supply-side passage 51a flows into a space T1 formed between the primary partition wall 54 and the primary pulley shaft 51. Further, the primary pulley shaft 51 is formed with a communication passage 51 d through which the hydraulic oil that has flowed into the drive side passage 51 b flows into a space T <b> 2 formed between the primary partition wall 54 and the primary pulley shaft 51. Here, a seal member S such as a seal ring is provided between the primary partition wall 54 and the primary pulley shaft 51 so as to sandwich the space portion T1 and the space portion T2, respectively. That is, the space portion T1 and the space portion T2 are respectively sealed by the seal member S.

  Primary fixed sheave 52 is provided to rotate with primary pulley shaft 51 at a position facing primary movable sheave 53. Specifically, 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.

  The primary movable sheave 53 includes a cylindrical portion 53a and an annular portion 53b. Further, the primary movable sheave 53 is formed with an annular projecting portion 53d that projects in the other direction of the axial direction, that is, an annular projecting portion 53d that projects toward the primary partition wall, in the vicinity of the outer peripheral end of the annular portion 53b. The cylindrical portion 53 a is formed around the same axis as the axis of 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 has a spline 53c formed on the inner peripheral surface of the cylindrical portion 53a and a spline 51e formed on the outer peripheral surface of the primary pulley shaft 51. It is slidably supported in the axial direction. Between the primary fixed sheave 52 and the primary movable sheave 53, that is, the surface of the primary fixed sheave 52 that faces the primary movable sheave 53 of the annular portion (not shown), and the primary fixed sheave 52 of the annular portion 53b of the primary movable sheave 53 that faces the primary fixed sheave 52 A V-shaped primary groove 120a is formed between the first and second surfaces.

  The primary partition wall 54 is disposed at a position facing the primary fixed sheave 52 in the axial direction with the primary movable sheave 53 interposed therebetween. Further, the primary partition 54 is an annular member. Further, the primary partition 54 is formed with a first flow path 54a, a second flow path 54b, and a third flow path 54c from the radially inner side to the outer side. The primary partition wall 54 is formed with a first communication channel 54d and a second communication channel 54e toward the other axial direction, that is, toward the valve closing direction of the hydraulic oil supply valve 70 and the discharge flow rate control valve 90. Has been. Here, the primary partition wall 54 rotates together with the primary pulley shaft 51 by the spline fitting between the spline 54f formed on the inner peripheral surface of the primary partition wall 54 and the spline 51f formed on the outer peripheral surface of the primary pulley shaft 51. It is provided as follows.

  The first flow path 54 a is formed in the axial direction, that is, in the opening / closing valve direction of the hydraulic oil supply valve 70 and the discharge flow rate control valve 90. The first flow path 54 a is formed at a plurality of positions on the circumference with respect to the primary partition wall 54, for example, at three positions at equal intervals. Each first flow path 54a has a columnar shape, an end in the valve closing direction communicates with each third flow path 54c, and an end in the valve opening direction is a side surface in the valve opening direction of the primary partition wall 54, That is, the primary hydraulic chamber 55 is opened. Each of the first flow paths 54a is formed with a ring-shaped valve seat protrusion 72 at the center in the opening / closing valve direction.

  The second flow path 54b is formed in the on-off valve direction. The second flow path 54b is formed at a plurality of positions on the circumference with respect to the primary partition wall 54, for example, three positions at equal intervals. Each of the second flow paths 54b has a cylindrical shape, the end in the valve closing direction is closed by the closing member 54g, and the end in the valve opening direction is closed inside the primary partition wall 54, respectively.

  The third flow path 54c is formed in the on-off valve direction. The third flow path 54c is formed at a plurality of positions on the circumference with respect to the primary partition wall 54, for example, three positions at equal intervals. Each third channel 54c is formed on the same axis as each first channel 54a. Each of the third flow paths 54c has a cylindrical shape, the end in the valve closing direction is closed by the closing member 54h, and the end in the valve opening direction is in communication with each first flow path 54a. . In addition, the diameter of the part which each 1st flow path 54a and each 3rd flow path 54c communicate is formed smaller than the diameter of each 3rd flow path 54c.

  The first communication channel 54 d is formed in the radial direction, that is, the orthogonal direction orthogonal to the on-off valve direction of the hydraulic oil supply valve 70 and the discharge flow rate control valve 90. The first communication channel 54d is formed at a plurality of positions on the circumference with respect to the primary partition wall 54, for example, at three equal intervals. Each of the first communication channels 54d has a cylindrical shape, the radially inner end thereof communicates with the end of each first channel 54a in the valve closing direction, and the radially outer end thereof is a blocking member. 54i is blocked. Each first communication channel 54d communicates with the second channel 54b in the middle thereof. Each first communication channel 54d communicates with the other end of the communication passage 54k, one end of which communicates with the space T1 at the radially inner end. That is, each first flow path 54a and each first communication flow path 54d communicate with the supply-side path 51a of the primary pulley shaft 51 via each communication path 54k, the space portion T1, and the communication path 51c. Accordingly, the hydraulic oil supplied from the hydraulic oil supply control device 140 to the supply-side passage 51a flows into the first flow paths 54a and the first communication flow paths 54d.

  The second communication channel 54 e is formed in the radial direction, that is, in the orthogonal direction orthogonal to the on-off valve direction of the hydraulic oil supply valve 70 and the discharge flow rate control valve 90. The second communication channel 54e is formed at a plurality of positions on the circumference with respect to the primary partition wall 54, for example, at three equal intervals. Each of the second communication channels 54e has a cylindrical shape, and its radially inner end communicates with the vicinity of the end of each third channel 54c in the valve closing direction, and its radially outer end is closed. Each member 54j is closed. In addition, each second communication channel 54e communicates with the vicinity of the end of the second channel 54b in the valve closing direction. Each of the second communication channels 54e communicates with the other end of the communication passage 54l with one end communicating with the space T2 at the radially inner end. That is, each of the third flow paths 54c and each of the second communication flow paths 54e communicates with the drive-side path 51b of the primary pulley shaft 51 via each communication path 54l, the space portion T2, and the communication path 51d. Accordingly, the hydraulic oil supplied from the hydraulic oil supply control device 140 to the drive side passage 51b flows into the third flow paths 54c and the second communication flow paths 54e.

  A plurality of discharge channels 54m are formed on the outer side in the radial direction than the second channel 54b and between the first communication channel 54d and the second communication channel 54e. Each discharge channel 54m communicates with one end at the center of each second channel 54b in the on-off valve direction, and the other end communicates with the outer peripheral surface of the primary partition wall 54, that is, the outside. ing. Further, a plurality of release passages 54n are formed on the outer side in the radial direction than the second flow path 54b and in the valve opening direction with respect to the first communication flow path 54d. Each release passage 54n has one end communicating with the vicinity of the end of each second flow path 54b in the valve opening direction, and the other end communicating with the outer peripheral surface of the primary partition wall 54, that is, the outside. is doing. Further, a plurality of release passages 54o are formed between the second flow path 54b and the third flow path 54c and between the first communication flow path 54d and the second communication flow path 54e. Each release passage 54o communicates with one end of each third channel 54c in the valve opening direction, and the other end communicates with each second channel 54b.

  Here, the working oil supply flow path for supplying the working oil to the primary hydraulic chamber 55, which is one positioning hydraulic chamber, is connected to the supply side passage 51a, the communication passage 51c, the space portion T1, and the communication in this embodiment 1. The passage 54k and the first flow path 54a are configured. In the first embodiment, the hydraulic oil discharge flow path for discharging the hydraulic oil from the primary hydraulic chamber 55 that is one positioning hydraulic chamber is the first communication flow path 54d, the second flow path 54b, and the discharge flow path. 54m.

  The primary hydraulic chamber 55 is one positioning hydraulic chamber that presses the primary movable sheave 53 toward the primary fixed sheave side, and is a space formed by the primary movable sheave 53 and the primary partition wall 54. Here, a seal member S such as a seal ring is provided between the protruding portion 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, respectively. Yes. That is, the space formed by the primary movable sheave 53 and the primary partition wall 54 constituting the primary hydraulic chamber 55 is sealed by the seal member S.

  The primary hydraulic chamber 55 is supplied with hydraulic oil that has flowed into the supply-side passage 51 a of the primary pulley shaft 51 by opening the hydraulic oil supply valve 70. That is, hydraulic oil is supplied to the primary hydraulic chamber 55, and the primary movable sheave 53 is slid in the axial direction by the pressure of the supplied hydraulic oil, that is, the hydraulic pressure P1 of the primary hydraulic chamber 55. The fixed sheave 52 is approached or separated. The primary hydraulic chamber 55 generates a primary side belt clamping pressure with respect to the belt 120 wound around the primary groove 120a by pressing the primary movable sheave 53 to the primary fixed sheave side by the hydraulic pressure P1 of the primary hydraulic chamber 55, The position of the primary movable sheave 53 in the axial direction with respect to the primary fixed sheave 52 is changed. Thereby, it also has a function as a gear ratio changing means for changing the gear ratio.

  The secondary pulley 60 of the belt type continuously variable transmission 1-1 transmits the output torque from the internal combustion engine 10 transmitted to the primary pulley 50 by the belt 120 to the final speed reducer 100 of the belt type continuously variable transmission 1-1. Is. 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 bearings 123 and 124. Further, the secondary pulley shaft 61 has a hydraulic oil passage (not shown) inside, and hydraulic oil that is a hydraulic fluid supplied from the hydraulic oil supply control device 140 to the secondary hydraulic chamber 64 is supplied to the hydraulic oil passage. Inflow.

  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 facing the secondary movable sheave 63 and the surface of the secondary movable sheave 63 facing the secondary fixed sheave 62. A secondary groove 120b having a shape is formed.

  The secondary hydraulic chamber 64 is the other positioning hydraulic chamber that presses the secondary movable sheave 63 toward the secondary fixed sheave side, and is formed by the secondary movable sheave 63 and a disk-shaped secondary partition wall 65 fixed to the secondary pulley shaft 61. It is a space part. The secondary movable sheave 63 is formed with an annular protrusion 63a that protrudes in one axial direction, that is, protrudes toward the final reduction gear. On the other hand, the secondary partition wall 65 is formed with an annular protrusion 65a that protrudes in the other axial direction, that is, protrudes toward the secondary movable sheave. 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 seal member (not shown).

  The secondary hydraulic chamber 64 is supplied with hydraulic oil from the hydraulic oil supply control device 140 that has flowed into a hydraulic oil passage (not shown) of the secondary pulley shaft 61 via a hydraulic fluid supply hole (not shown). That is, the hydraulic oil 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 supplied hydraulic oil, that is, the hydraulic pressure of the secondary hydraulic chamber 64, and the secondary movable sheave 63 is fixed to the secondary hydraulic chamber 63. It approaches or leaves the sheave 62. The secondary hydraulic chamber 64 generates secondary belt clamping pressure on the belt 120 wound around the secondary groove 120b by pressing the secondary movable sheave 63 toward the secondary fixed sheave side by the hydraulic pressure of the secondary hydraulic chamber 64. The contact radius with respect to the primary pulley 50 and the secondary pulley 60 of 120 is maintained constant.

  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 supported by the bearings 123 and 125 so as to be relatively rotatable on the secondary pulley shaft 61 with respect to the secondary pulley shaft 61 and the secondary movable sheave 63. Has been. This intermediate member 67 is spline-fitted with the input shaft 111 of the power transmission path 110. That is, the output torque from the internal combustion engine 10 transmitted to the secondary pulley 60 is transmitted to the power transmission path 110 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 120. 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 bearing 123, 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. Thereby, the torque cam 66 generates a secondary side belt clamping pressure with respect to the belt 120 in the secondary pulley 60.

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

  The hydraulic oil supply valve 70 allows only supply of hydraulic oil to the primary hydraulic chamber 55 which is one positioning hydraulic chamber. As shown in FIGS. 2, 5, and 6, the hydraulic oil supply valve 70 is a hydraulic fluid that flows from the primary hydraulic chamber 55 that is one positioning hydraulic chamber, that is, from the outside of the primary pulley 50 to the primary hydraulic chamber 55. The hydraulic oil is supplied, the hydraulic oil is discharged from the primary hydraulic chamber 55 to the outside of the primary pulley 50 by the valve opening / closing device 80 described later, and the hydraulic oil in the primary hydraulic chamber 55 is retained. In the first embodiment, the hydraulic oil supply valve 70 is provided corresponding to the first flow path 54a formed in the primary partition wall 54 of the primary pulley 50 that is one of the pulleys. Accordingly, the hydraulic oil supply valve 70 is provided at a plurality of positions on the circumference with respect to the primary partition wall 54, for example, three positions at equal intervals. That is, the hydraulic oil supply valve 70 rotates integrally with the primary pulley 50 that is one pulley. The hydraulic oil supply valve 70 includes a valve body 71, the above-described valve seat protrusion 72, a valve body elastic member 73, and a locking member 74.

  The valve body 71 has a disk shape and a diameter larger than the diameter of the inner diameter of the valve seat protrusion 72. The valve element 71 is arranged in the valve opening direction with respect to the valve seat protrusion 72 of the first flow path 54a so that the axial direction thereof is parallel to the on-off valve direction. When the valve body 71 contacts the valve seat protrusion 72, the communication between the valve opening direction side and the valve closing direction side of the first flow path 54a is blocked, that is, the hydraulic oil supply valve 70 is disconnected. The valve is closed. Further, when the valve body 71 is separated from the valve seat protrusion 72, communication between the valve opening direction side and the valve closing direction side of the first flow path 54a, that is, the hydraulic oil supply valve 70 is opened. To be spoken. That is, the hydraulic oil supply valve 70 opens in the first flow path 54a in the valve opening direction and closes in the valve closing direction.

  The valve body elastic member 73 is a piston valve closing direction pressing means. The valve body elastic member 73 is arranged in a state of being biased between the locking member 74 fixed to the first flow path 54 a and the valve body protruding portion 72 via the valve body 71. As a result, the valve body elastic member 73 generates a valve closing biasing force, and this valve closing biasing force causes the pressing force in the direction in which the valve body 71 contacts the valve seat protrusion 72, that is, the elastic member pressing force F2. Acts on the valve body 71 as a valve body closing direction pressing force. As a result, the valve body 71 is pressed against the valve seat protrusion 72, and the hydraulic oil supply valve 70 functions as a check valve. Further, the locking member 74 has a disk shape, and an opening for allowing the hydraulic oil to pass therethrough is formed at the center thereof.

  Here, when the hydraulic oil supply valve 70 is opened, the valve body valve opening direction pressing force, which is a pressing force acting on the valve body 71 in the direction in which the valve body 71 moves away from the valve seat protrusion 72, that is, the valve opening direction. However, the valve body 71 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 protrusion 72, that is, the valve closing direction. This is done by moving away from 72. The valve body opening direction pressing force is usually the pressure of the hydraulic oil supplied from the communication passage 54k to the first flow path 54a, that is, the hydraulic oil pressure acting on the valve body 71 by the hydraulic pressure P2 of the first flow path 54a. There is a pressure F1. On the other hand, as the valve body closing direction pressing force, the elastic member pressing force F2 acting on the valve body 71 by the valve closing biasing force, and the hydraulic oil pressing force F3 acting on the valve body 71 by the hydraulic pressure P1 of the primary hydraulic chamber 55 And are included. Since the hydraulic pressure P1 of the primary hydraulic chamber 55 acts as a pressing force in the valve closing direction on the valve body 71, the valve body 71 is separated from the valve seat protrusion 72 even when the hydraulic pressure P1 of the primary hydraulic chamber 55 rises. There is no. Therefore, the closed state of the hydraulic oil supply 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 is securely held in the primary hydraulic chamber 55.

  Further, 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, the hydraulic oil supply control device 140 is one positioning hydraulic chamber. When the hydraulic oil is continuously supplied to the primary hydraulic chamber 55, the hydraulic oil having a predetermined pressure exists in the hydraulic oil supply flow path from the hydraulic oil supply control device 140 to the primary hydraulic chamber 55. The hydraulic oil supply channel includes a plurality of sliding portions between the fixed member and the movable member, and hydraulic fluid of a predetermined pressure is supplied from the sliding portion to the hydraulic oil supply channel when the speed ratio is fixed. There was a risk of leaking outside. The fixing 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, this 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, the hydraulic oil supply valve 70 is disposed between the primary hydraulic chamber 55 and the sliding portion. That is, when the hydraulic oil supply valve 70 is maintained in the closed state and the hydraulic oil is held in the primary hydraulic chamber 55, the fixing between the primary hydraulic chamber 55 and the hydraulic oil supply valve 70 is performed as described above. There is no sliding part between the member and the movable member. Thereby, since it is possible to suppress the hydraulic oil from leaking from the sliding portion, it is possible to suppress an increase in power loss of the oil pump 142.

  The valve opening / closing device 80 is a valve opening / closing means, and controls the allowance or prohibition of the discharge of hydraulic oil from the primary hydraulic chamber 55. The valve opening / closing device 80 forcibly opens the hydraulic oil supply valve 70. In the first embodiment, the valve opening / closing device 80 is provided corresponding to the third flow path 54c formed in the primary partition wall 54 of the primary pulley 50, which is one pulley. Accordingly, the valve opening / closing device 80 is provided at a plurality of positions on the circumference with respect to the primary partition wall 54, for example, three positions at equal intervals. That is, the valve opening / closing device 80 rotates integrally with the primary pulley 50 that is one pulley. The valve opening / closing device 80 includes a piston 81 and a drive hydraulic chamber 82.

  The piston 81 moves the valve body 71 in the valve opening direction. The piston 81 is supported in the third flow path 54c so as to be slidable in the on-off valve direction. The piston 81 has a columnar shape, and a valve body pressing projection 81a that protrudes in the valve opening direction is formed at an end in the valve opening direction. The valve body pressing projection 81a protrudes from the end of the third flow path 54c in the valve opening direction to the first flow path 54a and is formed so as to come into contact with the valve body 71. The valve body pressing projection 81a contacts the valve body 71 by sliding the piston 81 in the valve opening direction by the piston valve opening direction pressing force F4 acting on the piston 81 by the hydraulic pressure P3 of the drive hydraulic chamber 82. To do. The piston valve opening direction pressing force F4 acting on the piston 81 acts on the valve body 71 as the valve body opening direction pressing force. Accordingly, even when the piston valve opening direction pressing force F4 exceeds the valve body closing direction pressing force, the valve body 71 moves in the valve opening direction with respect to the valve seat protrusion 72, and the hydraulic oil supply valve 70 is moved. Open the valve. That is, the hydraulic oil supply valve 70 is forcibly opened in the direction in which the hydraulic oil is discharged from the primary hydraulic chamber 55 to the outside.

  The drive hydraulic chamber 82 is supplied with hydraulic oil, and controls the hydraulic oil supply valve 70 and the discharge flow rate control valve 90 by the pressure of the supplied hydraulic oil, that is, the hydraulic pressure P3 of the drive hydraulic chamber 82. It is. That is, the hydraulic oil supply valve 70 is controlled by the hydraulic pressure P3 of the drive hydraulic chamber 82 to permit only the supply of hydraulic oil to the primary hydraulic chamber 55 and to permit or prohibit the discharge of hydraulic oil from the primary hydraulic chamber 55. Further, the discharge flow rate control valve 90 has its discharge flow rate controlled by the hydraulic pressure P 3 of the drive hydraulic chamber 82. The drive hydraulic chamber 82 is formed between the second flow path 54b, the third flow path 54c, the second communication flow path 54e, the piston 81, the spool 91, and the closing members 54g, h, j. Is. Accordingly, the piston valve opening direction pressing force F4 acts on the piston 81 and the spool valve opening direction pressing force F6 acts on the spool 91 by the hydraulic pressure P3 of the drive hydraulic chamber 82.

  The discharge flow rate control valve 90 controls the discharge flow rate of the hydraulic oil discharged from the primary hydraulic chamber 55 which is one positioning hydraulic chamber by the hydraulic oil supply valve 70. In the first embodiment, the discharge flow rate control valve 90 is provided corresponding to the second flow path 54b formed in the primary partition wall 54 of the primary pulley 50 that is one pulley. That is, the primary partition wall 54 is provided at a plurality of locations on the circumference, for example, three locations at equal intervals. That is, the discharge flow rate control valve 90 rotates integrally with the primary pulley 50 that is one pulley. The discharge flow rate control valve 90 includes a spool 91 and a spool elastic member 92.

  The spool 91 has a cylindrical shape, and is supported by the second flow path 54b so as to be slidable in the on-off valve direction so that its axial direction is parallel to the on-off valve direction. In the spool 91, a throttle portion 91a that is continuous in the circumferential direction is formed at a central portion in the opening / closing valve direction. A tapered surface 91b whose diameter increases in the valve opening direction is formed on the valve opening direction side of the throttle portion 91a. Here, the diameter of the first main body portion 91c in the valve opening direction relative to the throttle portion 91a of the spool 91 is such that the first main body portion 91c can slide in the on-off valve direction with respect to the second flow path 54b. The second flow path 54b is connected so that the communication between the first communication flow path 54d via the two flow paths 54b, the discharge flow path 54m, and the release passages 54n, o is blocked (including the case where the flow is almost blocked). It is set for the inner diameter. Further, the diameter of the second main body portion 91d in the valve closing direction relative to the throttle portion 91a of the spool 91 is such that the second main body portion 91d can slide in the on-off valve direction with respect to the second flow path 54b. With respect to the inner diameter of the second flow path 54b, the communication between the second communication flow path 54e via the flow path 54b, the discharge flow path 54m, and the release path 54o is blocked (including the case where it is substantially blocked). Is set.

  Here, when the spool 91 is positioned closest to the second flow path 54b in the valve closing direction, the first main body portion 91c is positioned to face the first communication flow path 54d. Accordingly, the communication between the first communication channel 54d and the discharge channel 54m via the second channel 54b is blocked, and the discharge flow rate control valve 90 is closed. Further, when the spool 91 slides with respect to the second flow path 54b in the valve opening direction from the state where the spool 91 is positioned in the most valve closing direction, the tapered surface 91b of the throttle portion 91a is the first. The position is opposite to the communication channel 54d. Accordingly, the communication between the first communication channel 54d and the discharge channel 54m via the second channel 54b is released, and the discharge flow rate control valve 90 is opened. Further, the discharge flow rate control valve 90 discharges from the first communication channel 54d via the second channel 54b in accordance with the discharge channel area formed by the tapered surface 91b and the first communication channel 54d. The discharge flow rate of the hydraulic oil flowing into the passage 54m is controlled.

  The spool elastic member 92 is a spool valve closing direction pressing means. The spool elastic member 92 is disposed in a state of being biased between the end of the second flow path 54 b in the valve opening direction and the spool 91. The spool elastic member 92 generates a valve closing biasing force, and an elastic member pressing force that slides the first main body 91c of the spool 91 to a position facing the first communication channel 54d by the valve closing biasing force. Spool valve closing direction pressing force F5 acts on spool 91.

  Here, when the discharge flow rate control valve 90 is opened, the spool valve opening direction pressing force F6, which is the pressing force acting on the spool 91 in the valve opening direction, is the pressing force acting on the spool 91 in the valve closing direction. This is performed by sliding the spool 91 up to a position where the spool valve closing direction pressing force F5 is exceeded and the tapered surface 91b faces the first communication channel 54d. This spool closing direction pressing force F5 is an elastic member pressing force acting on the spool 91 by the valve closing biasing force. On the other hand, the spool valve opening direction pressing force F6 is a pressing force in the valve opening direction that acts on the spool 91 by the hydraulic pressure P3 of the drive hydraulic chamber 82.

  The discharge flow rate control valve 90 is provided in the drive hydraulic chamber 82 that can forcibly open the hydraulic oil supply valve 70 when the hydraulic oil supply valve 70 is opened by the hydraulic pressure P3 of the drive hydraulic chamber 82. The valve is set to open at a hydraulic pressure equal to or higher than the hydraulic pressure P3. Here, the hydraulic pressure P3 of the drive hydraulic pressure chamber 82 that can open the hydraulic oil supply valve 70 corresponds to the change in the hydraulic pressure P1 of the primary hydraulic pressure chamber 55 in the valve closing direction pressing force acting on the valve body 71. Change. Therefore, the hydraulic pressure P3 of the drive hydraulic chamber 82 that can open the discharge flow rate control valve 90 is, as shown in FIG. 4, when the hydraulic oil supply valve 70 is opened when the hydraulic pressure P1 of the primary hydraulic chamber 55 is maximum. More than hydraulic PA that can be valved. That is, the discharge flow rate control valve 90 is set so that the discharge flow rate is controlled with a hydraulic pressure equal to or higher than the hydraulic pressure PA at which the hydraulic oil supply valve 70 can be opened when the hydraulic pressure P1 of the primary hydraulic chamber 55 is maximum. ing. Specifically, when the hydraulic pressure P1 of the primary hydraulic chamber 55 is maximum, the piston is set such that the discharge flow rate control valve 90 can be opened with a hydraulic pressure higher than the hydraulic pressure PA that can open the hydraulic oil supply valve 70. The pressure receiving area of the spool 91 with respect to the pressure receiving area of 81 and the valve closing urging force generated by the spool elastic member 92 are set. In the first embodiment, the hydraulic pressure P3 of the drive hydraulic chamber 82 when the discharge flow rate control valve 90 is fully opened is PB, and the hydraulic pressure P3 of the drive hydraulic chamber 82 is discharged by the discharge flow rate control valve 90 between the hydraulic pressure PA and PB. The flow rate is controlled. Thus, by controlling the hydraulic pressure P3 of one drive hydraulic chamber 82, the hydraulic oil supply valve 70 can be opened and the discharge flow rate can be controlled by the discharge flow rate control valve 90. Therefore, it is possible to allow or prohibit the discharge of the hydraulic oil in the primary hydraulic chamber 55, which is one positioning hydraulic chamber, and control the discharge flow rate with a simple configuration.

  A power transmission path 110 is disposed between the secondary pulley 60 and the final reduction gear 100. The power transmission path 110 includes an input shaft 111 on the same axis as the secondary pulley shaft 61, an intermediate shaft 112 parallel to the secondary pulley shaft 61, a counter drive pinion 113, a counter driven gear 114, and a final drive pinion 115. It is comprised by. The input shaft 111 and the counter drive pinion 113 fixed to the input shaft 111 are held rotatably by bearings 128 and 129. The intermediate shaft 112 is rotatably supported by bearings 126 and 127. The counter driven gear 114 is fixed to the intermediate shaft 112 and meshed with the counter drive pinion 113. The final drive pinion 115 is fixed to the intermediate shaft 112.

  The final speed reducer 100 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 110 from the wheels 130 and 130 to the road surface. The final reduction gear 100 includes a differential case 101 having a hollow portion, a pinion shaft 102, differential pinions 103 and 104, and side gears 105 and 106.

  The differential case 101 is rotatably supported by bearings 107 and 108. A ring gear 109 is provided on the outer periphery of the differential case 101, and the ring gear 109 is engaged with the final drive pinion 115. The pinion shaft 102 is attached to the hollow portion of the differential case 101. The differential pinions 103 and 104 are rotatably attached to the pinion shaft 102. The side gears 105 and 106 are meshed with both of the differential pinions 103 and 104. The side gears 105 and 106 are fixed to drive shafts 131 and 132, respectively.

  The belt 120 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 120 is wound between the primary groove 120 a of the primary pulley 50 and the secondary groove 120 b of the secondary pulley 60. The belt 120 is an endless belt composed of a number of metal pieces and a plurality of steel rings.

  Side shafts 105 and 106 are fixed to one end of the drive shafts 131 and 132, respectively, and wheels 130 and 130 are attached to the other end.

  The hydraulic oil supply control device 140 is provided at least in the lubricating portion of each component of the belt-type continuously variable transmission 1-1 and in each hydraulic chamber (including the primary hydraulic chamber 55, the secondary hydraulic chamber 64, and the drive hydraulic chamber 82). Supply hydraulic fluid. The hydraulic oil supply controller 140 includes an oil tank 141, an oil pump 142, a pressure regulator 143, a pinching pressure regulating valve 144, and a pressing pressure regulating valve 145.

  As described above, the oil pump 142 operates in conjunction with the output of the internal combustion engine 10, for example, rotation of a crankshaft (not shown), and sucks, pressurizes, and discharges the hydraulic oil stored in the oil tank 141. To do. The pressurized hydraulic oil discharged is supplied to the clamping pressure regulating valve 144 and the pressing pressure regulating valve 145 via the pressure regulator 143. Here, the pressure regulator 143 returns a part of the hydraulic oil on the downstream side to the oil tank 141 when the hydraulic pressure on the downstream side of the pressure regulator 143 becomes equal to or higher than a predetermined hydraulic pressure.

  The clamping pressure regulating valve 144 regulates the pressure of the hydraulic oil supplied to the primary hydraulic chamber 55 which is one positioning hydraulic chamber by controlling the valve opening degree. Thereby, the clamping pressure regulating valve 144 regulates the hydraulic pressure P1 of the primary hydraulic chamber 55. That is, the clamping pressure regulating valve 144 controls the belt clamping pressure generated in the primary hydraulic chamber 55. The clamping pressure regulating valve 144 is connected to the supply side passage 51a of the primary pulley shaft 51, and the hydraulic oil regulated by the clamping pressure regulating valve 144 is communicated with the supply side passage 51a, the space portion T1, and the communication. The oil is supplied to the primary hydraulic chamber 55 through the passage 54k and the hydraulic oil supply valve 70. The hydraulic oil supply control device 140 includes another clamping pressure regulating valve (not shown) in addition to the clamping pressure regulating valve 144, and the clamping pressure regulating valve (not shown) is the hydraulic oil (not shown) of the secondary pulley shaft 61. The hydraulic fluid that is connected to the passage and is regulated by the clamping pressure regulating valve is supplied to the secondary hydraulic chamber 64 via the hydraulic fluid passage (not shown).

  The pressing pressure regulating valve 145 regulates the pressure of the hydraulic oil supplied to the drive hydraulic chamber 82 by controlling the valve opening degree. Thereby, the pressure adjusting valve 145 adjusts, that is, changes the hydraulic pressure P3 of the drive hydraulic chamber 82. That is, the pressure adjusting valve 145 controls the piston valve opening direction pressing force acting on the valve element 71 via the piston 81 by the hydraulic pressure P3 of the drive hydraulic chamber 82, and forcibly opens the hydraulic oil supply valve 70. It is something that makes you speak. The pressure adjusting valve 145 controls the valve opening direction pressing force acting on the spool 91 by the hydraulic pressure P3 of the drive hydraulic chamber 82, and controls the discharge flow rate by the discharge flow rate control valve 90. The pressing pressure regulating valve 145 is connected to the driving side passage 51b of the primary pulley shaft 51, and the hydraulic oil regulated by the pressing pressure regulating valve 145 is communicated with the driving side passage 51b, the space T2, and the communication. The oil is supplied to the drive hydraulic chamber 82 through the passage 54l.

  The hydraulic oil supply control device 140 is connected to at least an ECU 150 that controls the operation of the internal combustion engine 10. Therefore, the hydraulic oil supply control device 140 controls the pressure adjusting valve 144 for adjusting the hydraulic pressure P1 of the primary hydraulic chamber 55 and the pressure P3 for adjusting the hydraulic pressure P3 of the drive hydraulic chamber 82 based on the gear ratio control signal from the ECU 150. At least the speed ratio of the belt-type continuously variable transmission 1-1 is controlled by controlling the pressure regulating valve 145 and the clamping pressure regulating valve (not shown) that regulates the hydraulic pressure in the secondary hydraulic chamber 64.

  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 150 turns on the forward clutch 42 and turns off the reverse brake 43 with the hydraulic oil supplied from the hydraulic oil supply control device 140. 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 120 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 112 via the input shaft 111 of the power transmission path 110, the counter drive pinion 113, and the counter driven gear 114, and is intermediated. The shaft 112 is rotated. The output torque transmitted to the intermediate shaft 112 is transmitted to the differential case 101 of the final reduction gear 100 via the final drive pinion 115 and the ring gear 109, and this differential case 101 is rotated. The output torque from the internal combustion engine 10 transmitted to the differential case 101 is transmitted to the drive shafts 131 and 132 via the differential pinions 103 and 104 and the side gears 105 and 106, and to the wheels 130 and 130 attached to the ends thereof. The wheels 130 and 130 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 150 turns off the forward clutch 42 with the hydraulic oil supplied from the hydraulic oil supply control device 140, and 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 111, the intermediate shaft 112, the differential case 101, the drive shafts 131, 132, 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.

  Further, ECU 150 is based on conditions such as the speed of the vehicle and the accelerator opening of the driver and a map (for example, an optimal fuel consumption curve based on the engine speed and the throttle opening) stored in the storage unit of ECU 150. Thus, the gear ratio of the belt-type continuously variable transmission 1-1 is controlled so that the operating state of the internal combustion engine 10 is optimized. The control of the gear ratio of the belt-type continuously variable transmission 1-1 includes changing the gear ratio and fixing the gear shift (gear ratio γ steady). The change of the gear ratio and the fixing of the gear ratio are performed by controlling at least the hydraulic pressure P1 of the primary hydraulic chamber 55, which is the positioning hydraulic chamber of the primary pulley 50, and the hydraulic pressure P3 of the drive hydraulic chamber 82.

  The change of the gear ratio is mainly caused by the supply of hydraulic fluid from the hydraulic fluid supply control device 140 to the primary hydraulic chamber 55 or the discharge of hydraulic fluid from the primary hydraulic chamber 55 to the outside of the primary pulley 50. Sliding in the axial direction of the primary pulley shaft 51, the distance between the primary fixed sheave 52 and the primary movable sheave 53, that is, the width of the primary groove 120a is adjusted. As a result, the contact radius of the belt 120 in the primary pulley 50 changes, and the speed ratio, which is the ratio between the rotation speed of the primary pulley 50 and the rotation speed of the secondary pulley 60, is controlled steplessly (continuously). The gear ratio is fixed mainly by prohibiting the discharge of hydraulic fluid from the primary hydraulic chamber 55 to the outside of the primary pulley 50.

  In the secondary pulley 60, the secondary fixed sheave 62 and the secondary movable sheave 62 are controlled by controlling the hydraulic pressure of the hydraulic oil supplied from the hydraulic oil supply control device 140 to the secondary hydraulic chamber 64 by a not-shown clamping pressure regulating valve. 63, the secondary side belt clamping pressure for clamping the belt 120 is adjusted. Thereby, the belt tension of the belt 120 wound between 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 140 to the primary hydraulic chamber 55 and sliding (moving) the primary movable sheave 53 toward the primary fixed sheave side. As shown in FIG. 5, the hydraulic oil supply valve 70 is opened to allow the hydraulic oil to be supplied from the hydraulic oil supply control device 140 to the primary hydraulic chamber 55. Specifically, ECU 150 calculates a reduction gear ratio and a transmission speed, and outputs a control signal for the transmission ratio based on these to hydraulic oil supply controller 140. The hydraulic oil supply control device 140 controls the clamping pressure regulating valve 144 and supplies it to the first flow path 54a so that the transmission ratio of the belt-type continuously variable transmission 1-1 is reduced at the above-described transmission speed. Increase the hydraulic oil pressure. Accordingly, the hydraulic pressure P2 rises in the first flow path 54a, and the operating pressure F1 acting on the valve body 71 is increased by the hydraulic pressure P2 of the first flow path 54a.

  At this time, the hydraulic oil supply control device 140 controls the pressure adjusting valve 145 to adjust the hydraulic pressure of the hydraulic oil from the hydraulic oil supply control device 140 to the drive hydraulic chamber 82. Here, the piston valve opening direction pressing force F4 is applied to the piston 81 by the hydraulic pressure P3 of the drive hydraulic chamber 82. In other words, the valve opening / closing device 80 causes the piston valve opening direction pressing force F4 to act on the piston 81 when the hydraulic oil is supplied to the primary hydraulic chamber 55, so that the piston valve opening direction pressing force F4 is applied to the hydraulic oil supply valve 70. The valve element 71 is operated as a valve element opening direction pressing force in the valve opening direction. Accordingly, when hydraulic oil is supplied to the primary hydraulic chamber 55, the combined pressure of the hydraulic oil pressing force F1 and the piston valve opening direction pressing force F4 becomes the valve body valve opening direction pressing force. Thus, the valve body opening direction pressing force acts on the valve body 71 by the elastic member pressing force F2 acting on the valve body 71 by the valve closing biasing force of the valve body elastic member 73 and the hydraulic pressure P1 of the primary hydraulic chamber 55. When the valve body closing direction pressing force combined with the hydraulic oil pressing force F3 is exceeded, the valve body 71 moves in the valve opening direction, and the hydraulic oil supply valve 70 opens. That is, the hydraulic oil supply valve 70 allows the hydraulic oil to be supplied to the primary hydraulic chamber 55 that is one positioning hydraulic chamber.

  Here, the hydraulic oil supply control device 140 is configured so that the hydraulic pressure P3 of the drive hydraulic chamber when the hydraulic oil is supplied to the primary hydraulic chamber 55 is less than the hydraulic pressure P3 of the drive hydraulic chamber 82 that can open the discharge flow rate control valve 90. In the first embodiment, the pressure of the hydraulic oil supplied to the drive hydraulic chamber 82 is regulated by the pressing pressure regulating valve 145 so as to be less than PA. When the hydraulic pressure P3 of the drive hydraulic chamber 82 is increased, the piston valve opening direction pressing force F4 is increased, and the spool valve opening direction pressing force F6 acting on the spool 91 of the discharge flow rate control valve 90 is also increased. Accordingly, when the increased spool opening direction pressing force F6 exceeds the spool closing direction pressing force F5, the discharge flow rate control valve 90 is opened. However, since the hydraulic pressure P3 in the drive hydraulic chamber at the time of supplying the hydraulic oil to the primary hydraulic chamber 55 is less than the hydraulic pressure P3 in the drive hydraulic chamber 82 that can open the discharge flow rate control valve 90, the piston 81 is used. Even if the valve opening / closing device 80 causes the valve opening direction pressing force F4 to act on the valve body 71 as the valve body opening direction pressing force, the discharge flow rate control valve 90 maintains the closed state. Therefore, it is possible to suppress the hydraulic oil supplied to the primary hydraulic chamber 55 from leaking from the hydraulic oil discharge channel, that is, the discharge channel 54m. When the hydraulic pressure of the drive hydraulic chamber 82 that can open the discharge flow rate control valve 90 is larger than the hydraulic pressure of the drive hydraulic chamber 82 that can open the hydraulic oil supply valve 70, the primary hydraulic chamber 55. The hydraulic pressure P3 of the drive hydraulic chamber at the time of supplying the hydraulic oil to the hydraulic oil is set to the hydraulic pressure of the drive hydraulic chamber 82 at which the hydraulic oil supply valve 70 can open. As a result, the hydraulic oil supply valve 70 can be opened by the hydraulic pressure P3 of the drive hydraulic chamber.

  When supply of the hydraulic oil to the primary hydraulic chamber 55 by the hydraulic oil supply valve 70 is permitted, the pressure is regulated by the clamping pressure regulating valve 144 of the hydraulic oil supply control device 140 as shown by an arrow A in FIG. The hydraulic oil is supplied from the supply side passage 51a to the primary hydraulic chamber 55 through the communication passages 51c and 54k and the first flow passage 54a. At this time, as described above, the discharge flow rate control valve 90 causes the spool valve opening direction pressing force F6 to act on the spool 91 by the hydraulic pressure P3 of the drive hydraulic chamber 82, but the spool valve closing direction pressing force to act on the spool 91. F5 is located in the most valve closing direction with respect to the second flow path 54b, and the first main body portion 91c is positioned to face the first communication flow path 54d. Therefore, the valve closed state is maintained and the second flow path 54b is maintained. The communication between the first communication flow path 54d and the discharge flow path 54m via is blocked. Therefore, the hydraulic oil supplied from the hydraulic oil supply control device 140 to the primary hydraulic chamber 55 is prohibited from being discharged through the first communication channel 54d, the second channel 54b, and the discharge channel 54m. The hydraulic oil P1 in the primary hydraulic chamber 55 rises due to the hydraulic oil supplied through the supply valve 70, the pressing force that pushes the primary movable sheave 53 toward the primary fixed sheave side rises, and the primary movable sheave 53 moves in the axial direction. Among them, it slides to the primary fixed sheave side. As a result, the contact radius of the belt 120 in the primary pulley 50 increases, the contact radius of the belt 120 in the secondary pulley 60 decreases, the gear ratio is reduced, and the reduction gear ratio is obtained.

  The gear ratio increase is changed by discharging hydraulic oil from the primary hydraulic chamber 55 and sliding (moving) the primary movable sheave 53 to the side opposite to the primary fixed sheave side. First, as shown in FIG. 6, the hydraulic oil supply valve 70 is forcibly opened to allow the hydraulic oil to be discharged from the primary hydraulic chamber 55. Then, the discharge flow rate of the hydraulic oil discharged from the primary hydraulic chamber 55 is controlled by the discharge flow rate control valve 90. Specifically, ECU 150 calculates an increase gear ratio and a gear shift speed, and outputs a gear ratio control signal based on these to hydraulic oil supply controller 140. The hydraulic oil supply control device 140 controls the pressing pressure regulating valve 145 to be supplied to the drive hydraulic chamber 82 so that the transmission ratio of the belt-type continuously variable transmission 1-1 is increased at the above-described transmission speed. Increase hydraulic oil pressure. Accordingly, the hydraulic pressure P3 of the drive hydraulic chamber 82 rises above the above-described hydraulic pressure PA, and the piston valve opening that acts on the valve body 71 as a valve body opening direction pressing force via the piston 81 by the hydraulic pressure P3 of the drive hydraulic chamber 82. The direction pressing force F4 includes an elastic member pressing force F2 acting on the valve body 71 by the valve closing biasing force of the valve body elastic member 73 and a hydraulic oil pressing force F3 acting on the valve body 71 by the hydraulic pressure P1 of the primary hydraulic chamber 55. The combined valve body closing direction pressing force will be exceeded. As a result, the valve body 71 moves in the valve opening direction, and the hydraulic oil supply valve 70 is forcibly opened by the valve opening / closing device 80. That is, the valve opening / closing device 80 allows the hydraulic oil to be discharged from the primary hydraulic chamber 55 that is one positioning hydraulic chamber by the hydraulic oil supply valve 70.

  At this time, the spool valve-opening direction pressing force F6 acting on the spool 91 by the hydraulic pressure P3 (hydraulic pressure from the hydraulic pressure PA to PB) of the raised drive hydraulic chamber 82 is caused by the valve closing biasing force of the spool elastic member 92. This exceeds the spool valve closing direction pressing force F5 acting on the valve. Here, the discharge flow rate control valve 90 corresponds to the amount of movement (stroke amount) in the valve opening direction of the spool 91 from the state where the spool 91 is positioned in the most valve closing direction with respect to the second flow path 54b. The discharge flow path area formed by the tapered surface 91b and the first communication flow path 54d increases. When the amount of movement described above is equal to or greater than a predetermined amount, the positional relationship of the spool 91 with respect to the first communication channel 54d is such that the first main body portion 91c of the spool 91 faces the first communication channel 54d. The taper surface 91b changes to a positional relationship facing the first communication channel 54d. Accordingly, the discharge flow rate control valve 90 controls the discharge flow rate of the hydraulic oil from the primary hydraulic chamber 55, which is one positioning hydraulic chamber, to the outside.

  When the hydraulic oil is allowed to be discharged from the primary hydraulic chamber 55 by the hydraulic oil supply valve 70 and the discharge flow rate of the hydraulic oil is controlled by the discharge flow rate control valve 90, as shown by an arrow B in FIG. The hydraulic oil in the hydraulic chamber 55 flows into the discharge channel 54m through the first channel 54a, the first communication channel 54d, and the second channel 54b. The hydraulic oil that has flowed into the discharge passage 54m is discharged to the outside of the primary pulley 50. At this time, the hydraulic oil discharged from the primary hydraulic chamber 55 flows into the second flow path 54b orthogonal to the first communication flow path 54d via the first communication flow path 54d. Here, the spool 91 of the discharge flow rate control valve 90 is supported by the second flow path 54b so as to be slidable in the direction of the on-off valve. In other words, the discharge flow rate control valve 90 of the primary pulley 50 that is one pulley that rotates integrally, when the hydraulic oil supply valve 70 is opened, the hydraulic pressure of the primary pulley 50 that is one positioning hydraulic chamber is in the direction of the on-off valve. It is arranged at a position where it does not act. Accordingly, the hydraulic pressure P1 of the primary hydraulic chamber 55 when the hydraulic oil is discharged from the primary hydraulic chamber 55 changes when the hydraulic oil is discharged from the primary hydraulic chamber 55, so that the primary hydraulic chamber flowing into the second flow path 54b. Even if the pressure of the hydraulic oil discharged from 55 changes, the position of the spool 91 in the on-off valve direction with respect to the second flow path 54b is difficult to be displaced. Thereby, the discharge flow rate control valve 90 can suppress the change of the discharge flow rate due to the change of the hydraulic pressure P1 of the primary hydraulic chamber 55, and can discharge the hydraulic oil stably. Can be improved. Further, since it is not necessary to perform feedback control based on the change of the hydraulic pressure P1 of the primary hydraulic chamber 55 in order to suppress the influence of the change of the hydraulic pressure P1 of the primary hydraulic chamber 55 on the discharge flow rate, the control is simplified. be able to. Moreover, cost reduction can be achieved.

  At this time, the hydraulic oil supply control device 140 closes the clamping pressure regulating valve 144. This is to prevent the hydraulic oil discharged from the primary hydraulic chamber 55 from returning to the hydraulic oil supply control device 140 via the communication passage 54k, the space T1, the communication passage 51c, and the supply-side passage 51a. That is, the hydraulic oil supply valve 70 prohibits the supply of hydraulic oil to the primary hydraulic chamber 55. Accordingly, the hydraulic oil P1 in the primary hydraulic chamber 55 is reduced by being discharged from the hydraulic oil from the primary hydraulic chamber 55 via the hydraulic oil supply valve 70 while the discharge flow rate is controlled by the discharge flow control valve 90, and the primary movable. The pressing force that presses the sheave 53 toward the primary fixed sheave side decreases, and the primary movable sheave 53 slides in the axial direction opposite to the primary fixed sheave side. As a result, the contact radius of the belt 120 in the primary pulley 50 decreases, the contact radius of the belt 120 in the secondary pulley 60 increases, the transmission ratio is increased, and the increased transmission ratio is obtained. A check valve may be provided in a flow path for supplying hydraulic oil from the hydraulic oil supply control device 140 to the primary hydraulic chamber 55, for example, in the supply side passage 51a of the primary pulley shaft 51. This check valve opens only in the direction in which the hydraulic oil is supplied from the hydraulic oil supply control device 140 to the primary hydraulic chamber 55. Therefore, it is possible to suppress the hydraulic oil discharged from the primary hydraulic chamber 55 from returning to the hydraulic oil supply control device 140 by the check valve when the transmission ratio increase is changed.

  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 made steady when the ECU 150 determines that there is no need to change the gear ratio significantly, such as when the running state of the vehicle is stable. As shown in FIG. 2, the hydraulic oil supply valve 70 is maintained in a closed state, and the supply of hydraulic oil to the primary hydraulic chamber 55 and the discharge of hydraulic oil from the primary hydraulic chamber 55 are both prohibited. Specifically, the hydraulic oil supply control device 140 closes the clamping pressure regulating valve 144 and stops the supply of hydraulic oil from the hydraulic oil supply control device 140 to the first flow path 54a. Further, the hydraulic oil supply control device 140 closes the pressing pressure regulating valve 145 to stop the supply of hydraulic oil from the hydraulic oil supply control device 140 to the drive hydraulic chamber 82, or the hydraulic pressure of the drive hydraulic chamber 82. The pressure of the hydraulic oil supplied to the drive hydraulic chamber 82 so that the spool valve opening direction pressing force F6 acting on the spool 91 by the hydraulic pressure P3 of the driving hydraulic chamber 82 does not exceed the spool closing direction pressing force F5. The pressure is regulated by the pressure regulating valve 145.

  Here, since the belt tension of the belt 120 changes even when the transmission ratio is fixed, the contact radius of the belt 120 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 is changed. May change. As described above, since the hydraulic oil is held in the primary hydraulic chamber 55, if the position of the primary movable sheave 53 in the axial direction with respect to the primary fixed sheave 52 is changed, the pressure of the primary hydraulic chamber 55 is changed. However, the position of the primary movable sheave 53 in the axial direction with respect to the primary fixed sheave 52 is maintained constant. Therefore, 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, the hydraulic pressure P1 of the primary hydraulic chamber 55 is not increased by supplying hydraulic oil to the primary hydraulic chamber 55 from the outside. May be. As a result, when the speed ratio is fixed, it is not necessary to drive the oil pump 142 in order to supply the hydraulic oil to the primary hydraulic chamber 55, so that an increase in power loss of the oil pump 142 can be suppressed.

  As described above, in the belt-type continuously variable transmission 1-1 according to the first embodiment, the hydraulic oil discharge valve is not provided separately, and the primary hydraulic chamber 55, which is one positioning hydraulic chamber, is provided by one valve. The hydraulic oil can be supplied, the hydraulic oil can be discharged from the primary hydraulic chamber 55, and the hydraulic oil can be held in the primary hydraulic chamber 55.

  Further, when hydraulic fluid is supplied to the primary hydraulic chamber 55 that is one of the positioning hydraulic chambers, the valve opening / closing device 80 that is the valve opening / closing means has a valve body opening direction pressing force in the valve opening direction of the hydraulic oil supply valve 70. In order to cause the piston valve opening direction pressing force F4 to act on the valve body 71 of the hydraulic oil supply valve 70, the hydraulic oil supply valve 70 is opened, that is, the valve body valve can be moved in the valve opening direction. The direction pressing force is determined by the piston valve opening direction pressing force F4 by the valve opening / closing device 80 and the pressure of the hydraulic oil supplied to the primary hydraulic chamber 55, that is, the hydraulic pressure P2 of the first flow path 54a and the first communication flow path 54d. The hydraulic oil pressing force F1 which is the valve body opening direction pressing force acting on the valve body 71 is combined. Therefore, when supplying hydraulic oil to the primary hydraulic chamber 55, the hydraulic oil supply valve 70 is compared with the case where the valve opening direction pressing force F <b> 4 by the valve opening / closing device 80 does not act on the valve body 71 of the hydraulic oil supply valve 70. The hydraulic oil pressing force F1 for opening the valve can be reduced. As a result, when the hydraulic oil is supplied to the primary hydraulic chamber 55, the influence of the elastic member pressing force F2 when the hydraulic oil supply valve 70 is opened can be reduced, so that the operation supplied to the primary hydraulic chamber 55 is performed. The oil supply pressure can be reduced. Further, since the disc-shaped valve body 71 is in surface contact with the valve body protrusion 72 when the hydraulic oil supply valve 70 is closed, the sealing performance is superior to a spherical valve body that is in line contact with the valve body. Can be improved. However, since the valve body 71 is in surface contact, the valve body opening direction pressing force for opening the hydraulic oil supply valve 70 is higher than in the case of using a valve body that is in line contact. In the present invention, since the valve body opening direction pressing force is a combination of the piston valve opening direction pressing force F4 and the hydraulic oil pressing force F1, even if the valve body opening direction pressing force becomes high, the primary hydraulic chamber Compared with the case where the piston valve opening direction pressing force F4 does not act on the valve body 71 of the hydraulic oil supply valve 70 when supplying the hydraulic oil to the hydraulic oil 55, the hydraulic oil pressing force for opening the hydraulic oil supply valve 70 F1 can be reduced. Thereby, the sealing performance of the hydraulic oil supply valve 70 can be improved, and the supply pressure of the hydraulic oil supplied to the primary hydraulic chamber 55 can be reduced. Further, in the belt-type continuously variable transmission 1-1, the case where the hydraulic oil pressure is most required is when the gear ratio reduction is changed. Therefore, the maximum discharge pressure of the oil pump 142 of the hydraulic oil supply control device 140 can be reduced. Thereby, an increase in driving loss of the oil pump 142 can be further suppressed.

  In the first embodiment, the pressing force acting on the spool 91 of the discharge flow rate control valve 90 in the valve closing direction is the elasticity acting on the spool 91 in the valve closing direction by the valve closing biasing force generated by the spool elastic member 92. Only the spool valve closing direction pressing force F5, which is a member pressing force, is provided, but the present invention is not limited to this. FIG. 7 is another configuration example of the discharge flow rate control valve according to the first embodiment.

  As shown in the figure, a tip 91e protruding in the valve opening direction is formed at the end of the spool 91 of the discharge flow rate control valve 90 in the valve opening direction. The tip 91e is exposed to the primary hydraulic chamber 55, which is one positioning hydraulic chamber, through a communication hole 54p formed at the end of the second flow path 54b in the valve opening direction. Here, the front end portion 91e is formed on the spool 91 so that the front end surface 91f can always be exposed to the primary hydraulic chamber 55 even if the spool 91 slides in the on-off valve direction with respect to the second flow path 54b. ing. The communication hole 54p and the tip 91e are sealed by a seal member S provided in the communication hole 54p.

  Therefore, the hydraulic oil pressing force F7, which is the pressing force in the valve closing direction of the spool 91, acts on the spool 91 as the spool valve closing direction pressing force by the hydraulic pressure P1 of the primary hydraulic chamber 55. That is, the spool valve opening direction pressing force F6 is applied to the spool 91 by the valve closing biasing force of the spool elastic member 92, and the hydraulic oil pressing force F7 is applied to the spool 91 by the hydraulic pressure P1 of the primary hydraulic chamber 55. The exhaust flow rate control valve 90 is opened by exceeding the spool valve closing direction pressing force.

  When the hydraulic pressure P1 of the primary hydraulic chamber 55 is low, the hydraulic oil pressing force F7 acting on the spool 91 is reduced as compared to the case where the hydraulic pressure P1 is high. Accordingly, the amount of movement of the spool 91 of the discharge flow rate control valve 90 that moves in the valve opening direction with the same spool valve opening direction pressing force F6 increases as the hydraulic pressure P1 of the primary hydraulic chamber 55 decreases. That is, when the hydraulic pressure P1 of the primary hydraulic chamber 55 is low, the spool valve opening direction pressing force F6 for fully opening the discharge flow rate control valve 90 can be reduced as compared with the case where the hydraulic pressure P1 is high. As shown in FIG. 4, the hydraulic pressure P3 of the drive hydraulic chamber 82 that allows the spool valve opening direction pressing force F6 for fully opening the discharge flow rate control valve 90 to act on the spool 91 is the hydraulic pressure P1 of the primary hydraulic chamber 55. It can be reduced to a lower case (PC in the figure) than in a higher case (PB in the figure). As a result, the spool valve opening direction pressing force, that is, the spool valve opening direction pressing force F6 by the hydraulic pressure P3 of the drive hydraulic chamber 82 in this embodiment 1, is changed according to the hydraulic pressure P1 of the primary hydraulic chamber 55 which is one positioning hydraulic chamber. can do.

  In the first embodiment, the pair of hydraulic oil supply valve 70 and valve opening / closing device 80 and the discharge flow rate control valve 90 are arranged on the same normal line of the primary pulley 50 that is one pulley. Is not limited to this. The pair of hydraulic oil supply valve 70 and valve opening / closing device 80 and the discharge flow rate control valve 90 may be disposed on different normal lines of the primary pulley 50. For example, the pair of hydraulic oil supply valve 70 and valve opening / closing device 80 and the discharge flow rate control valve 90 may be arranged so as to face each other while the primary pulley 50 is rotating. In this case, the pair of hydraulic oil supply valve 70 and valve opening / closing device 80 and the discharge flow rate control valve 90 are preferably arranged so as to suppress the eccentric rotation of the primary pulley 50.

  Next, the belt type continuously variable transmission 1-2 according to the second embodiment will be described. FIG. 8 is a diagram illustrating a configuration example of a hydraulic oil supply valve, a valve opening / closing device, and a discharge flow rate control valve according to the second embodiment. 9 and 10 are explanatory diagrams of the operation of the belt-type continuously variable transmission when the gear ratio is changed. 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 a hydraulic oil supply valve 160, a valve opening / closing device 170, and a discharge flow rate. The control valve 180 is formed on the same axis. The basic configuration of the belt-type continuously variable transmission 1-2 according to the second embodiment is substantially the same as the basic configuration of the belt-type continuously variable transmission 1-1 according to the first embodiment. The description is omitted.

  As shown in FIG. 8, the primary partition 54 has an opening 54q and a common channel 54r. A valve seat protrusion 162 is formed between the opening 54q and the common flow path 54r.

  The opening 54q is formed in the axial direction, that is, in the opening / closing valve direction of the hydraulic oil supply valve 160 and the discharge flow rate control valve 180. The openings 54q are formed at a plurality of positions on the circumference with respect to the primary partition wall 54, for example, at three equal intervals. The opening 54q has a cylindrical shape, an end in the valve closing direction communicates with the common flow path 54r via the valve seat protrusion 162, and an end in the valve opening direction in the valve opening direction of the primary partition wall 54. The side surface, that is, the primary hydraulic chamber 55 is opened.

  The common flow path 54r is formed in the axial direction, that is, in the opening / closing valve direction of the hydraulic oil supply valve 160 and the discharge flow rate control valve 180. The common flow path 54r is formed at a plurality of positions on the circumference with respect to the primary partition wall 54, for example, three positions at equal intervals. The common flow path 54r has a cylindrical shape, an end in the valve closing direction is closed by the closing member 56, and an end in the valve opening direction communicates with the opening 54q through the valve seat protrusion 162. . The common channel 54r has a space T3 at the center in the opening / closing valve direction. The space T3 has a ring shape covering the outer periphery of the common flow path 54r, and communicates with the communication path 54k. That is, the common flow path 54r communicates with the supply side passage 51a via the space portion T3, the communication passage 54k, the space portion T1, and the communication passage 51c, and is supplied from the hydraulic oil supply control device 140 to the supply side passage 51a. Inflow of hydraulic fluid.

  The discharge channel 54m has one end communicating with a position in the valve closing direction rather than the space T3 of the common channel 54r, and the other end connected to the outer peripheral surface of the primary partition wall 54, that is, outside. Communicate. Further, one end of the release passage 54n communicates with the vicinity of the end of the common flow path 54r in the valve opening direction, and the other end communicates with the outer peripheral surface of the primary partition wall 54, that is, the outside. .

  The hydraulic oil supply valve 160 allows only supply of hydraulic oil to the primary hydraulic chamber 55 that is one positioning hydraulic chamber. As shown in FIGS. 7 to 9, the hydraulic oil supply valve 160 is an operation that is a working fluid from the primary hydraulic chamber 55 that is one positioning hydraulic chamber, that is, from the outside of the primary pulley 50 to the primary hydraulic chamber 55. The 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 valve 160 is provided corresponding to the common flow path 54r formed in the primary partition wall 54 of the primary pulley 50 that is one of the pulleys. That is, the primary partition wall 54 is provided at a plurality of locations on the circumference, for example, three locations at equal intervals. The hydraulic oil supply valve 160 includes a valve body 161, the above-described valve seat protrusion 162, a valve body elastic member 163, and a locking member 164. Reference numeral 165 denotes a fixing pin that fixes the valve body 161 to the piston 171 of the valve opening / closing device 170.

  The valve body 161 has a disk shape and a diameter larger than the diameter of the inner diameter of the valve seat protrusion 162. The valve body 161 is disposed in the opening 54q so that the axial direction is parallel to the on-off valve direction. When the valve body 161 contacts the valve seat protrusion 162, the end portion in the valve closing direction communicating with the common flow path 54r of the opening 54q is closed, and the hydraulic oil supply valve 160 is closed. Further, when the valve element 161 is separated from the valve seat protrusion 162, the opening 54q and the common flow path 54r communicate with each other, and the hydraulic oil supply valve 160 is opened. That is, the hydraulic oil supply valve 160 opens in the opening 54q in the valve opening direction and closes in the valve closing direction.

  The valve body elastic member 163 is piston valve closing direction pressing means. The valve body elastic member 163 is arranged in a state of being biased between the locking member 164 fixed to the opening 54q and the valve body protrusion 162 via the valve body 161. The valve body elastic member 163 generates a valve closing urging force. This valve closing urging force causes the pressing force in the direction in which the valve body 161 contacts the valve seat protrusion 162, that is, the elastic member pressing force F9 is the valve body. It acts on the valve body 161 as a pressing force in the valve closing direction. Accordingly, the valve body 161 is pressed against the valve seat protrusion 162, and the hydraulic oil supply valve 160 functions as a check valve. The locking member 164 has a disk shape, and an opening for allowing hydraulic oil to pass therethrough is formed at the center thereof.

  The valve opening / closing device 170 is a valve opening / closing means, and controls the allowance or prohibition of the discharge of hydraulic oil from the primary hydraulic chamber 55. The valve opening / closing device 170 forcibly opens the hydraulic oil supply valve 160. In the second embodiment, the valve opening / closing device 170 is provided corresponding to the common flow path 54r formed in the primary partition wall 54 of the primary pulley 50, which is one pulley. Accordingly, the valve opening / closing device 170 is provided at a plurality of positions on the circumference with respect to the primary partition wall 54, for example, three positions at equal intervals. That is, the valve opening / closing device 170 rotates integrally with the primary pulley 50 that is one pulley. The valve opening / closing device 170 includes a piston 171 and a drive hydraulic chamber 172.

  The piston 171 moves the valve body 161 in the opening / closing valve direction. The piston 171 is supported by the common flow path 54r so as to be slidable in the on-off valve direction. In the second embodiment, the common flow path 54r is slidably supported with respect to the inner peripheral surface of the spool 181 of the discharge flow rate control valve 180 that is slidably supported in the opening / closing valve direction. The piston 171 has a cylindrical shape, and an end in the valve opening direction protrudes from the valve seat protrusion 162. The outer diameter of the end in the valve opening direction of the piston 171 is such that the end in the valve opening direction can slide in the opening / closing valve direction with respect to the valve seat protrusion 162 and the opening through the valve seat protrusion 162 is open. It is set with respect to the inner diameter of the valve seat protrusion 162 so that the communication between the portion 54q and the common flow path 54r is blocked (including a case where the flow is substantially blocked). The end of the piston 171 in the valve opening direction is fixed to the valve body 161 by a fixing pin 165. That is, the piston 171 moves in the opening / closing valve direction together with the valve body 161.

  The piston 171 has a first communication passage 171a and a second communication passage 171b. The first communication passage 171a is formed at the center of the piston 171 in the opening / closing valve direction. Both end portions of the first communication passage 171 a are open to the outer peripheral surface of the piston 171. The first communication passage 171a communicates with the space portion T3 through a communication hole 181e described later of the discharge flow rate control valve 180 when the hydraulic oil supply valve 160 is closed. That is, when the hydraulic oil supply valve 160 is closed, the hydraulic fluid supplied from the hydraulic oil supply control device 140 to the supply-side passage 51a is connected to the first communication passage 171a in the communication passage 51c, the space portion T1, and the communication passage 51k. Then, it flows in through the space T3 and the communication hole 181e.

  The second communication passage 171 b is formed in parallel with the opening / closing valve direction of the piston 171. The second communication passage 171b is closed by a valve body 161 whose end in the valve closing direction communicates with the first communication passage 171a and whose end in the valve opening direction is fixed to the end of the piston 171 in the valve opening direction. Has been. Here, a plurality of communication holes 171c (for example, four at regular intervals) are formed on the outer peripheral surface in the vicinity of the end of the piston 171 in the valve opening direction. The second communication passage 171b communicates with the communication hole 171c. That is, the hydraulic fluid supplied from the hydraulic fluid supply control device 140 that has flowed into the first communication passage 171a to the supply-side passage 51a flows into the second communication passage 171b.

  Here, when the hydraulic oil supply valve 160 is opened, the valve body valve opening direction pressing force which is a pressing force acting on the valve body 161 in the direction in which the valve body 161 moves away from the valve seat protrusion 162, that is, the valve opening direction. However, the valve body 161 exceeds the valve body closing direction pressing force, which is the pressing force acting on the valve body 161 in the valve contact direction in the valve closing direction, that is, the valve closing direction. This is done by leaving 162. As the valve body opening direction pressing force, the pressure of the hydraulic fluid supplied from the communication passage 54k to the first communication passage 171a to the second communication passage 171b, that is, the second communication passage 171b (of the hydraulic oil supply valve 160) is normally set. In the closed state, there is a hydraulic pressure F8 that acts on the valve body 161 by the hydraulic pressure P4 of the space formed between the valve seat protrusion 162 and the valve body 161 via the communication hole 171c. . On the other hand, as the valve body closing direction pressing force, the elastic member pressing force F9 acting on the valve body 16 by the valve closing biasing force, and the hydraulic oil pressing force F10 acting on the valve body 161 by the hydraulic pressure P1 of the primary hydraulic chamber 55. And are included. Since the hydraulic pressure P1 of the primary hydraulic chamber 55 acts as a pressing force in the valve closing direction on the valve body 161, the valve body 161 is separated from the valve seat protrusion 162 even when the hydraulic pressure P1 of the primary hydraulic chamber 55 rises. There is no. Therefore, the closed state of the hydraulic oil supply valve 160 is maintained unless the valve body valve opening direction pressing force acting on the valve body 161 exceeds the valve body valve opening direction pressing force. The hydraulic oil in the primary hydraulic chamber 55 is securely held in the primary hydraulic chamber 55.

  Similar to the first embodiment, in the belt type continuously variable transmission 1-2 according to the second embodiment, the hydraulic oil supply valve 160 is disposed between the primary hydraulic chamber 55 and the sliding portion. . That is, when the hydraulic oil supply valve 160 is maintained in the closed state and the hydraulic oil is held in the primary hydraulic chamber 55, the above-described fixing is performed between the primary hydraulic chamber 55 and the hydraulic oil supply valve 160. There is no sliding part between the member and the movable member. Thereby, since it is possible to suppress the hydraulic oil from leaking from the sliding portion, it is possible to suppress an increase in power loss of the oil pump 142.

  Further, the piston 171 has a valve opening direction pressing force F11 acting on the circular end surface 171d of the piston 171 in the valve closing direction by the hydraulic pressure P5 of the driving hydraulic chamber 172. Works. Therefore, when the piston valve opening direction pressing force F11 exceeds the valve body closing direction pressing force, the valve body 161 moves in the valve opening direction with respect to the valve seat protrusion 162, and the hydraulic oil supply valve 160 is opened. I speak. That is, the hydraulic oil supply valve 160 is forcibly opened in the direction in which the hydraulic oil is discharged from the primary hydraulic chamber 55 to the outside.

  The drive hydraulic chamber 172 is supplied with hydraulic oil, and controls the hydraulic oil supply valve 160 and the discharge flow rate control valve 180 by the pressure of the supplied hydraulic oil, that is, the hydraulic pressure P5 of the drive hydraulic chamber 172. It is. That is, the hydraulic oil supply valve 160 is controlled by the hydraulic pressure P5 of the drive hydraulic chamber 172 to permit or prohibit the discharge of the hydraulic fluid from the primary hydraulic chamber 55 by the valve opening / closing device 170. Further, the discharge flow rate control valve 180 is controlled by the hydraulic pressure P5 of the drive hydraulic chamber 172. The drive hydraulic chamber 172 is formed between the common flow path 54r, the end surface 171d of the piston 171 in the valve closing direction, the end surface 181f of the spool 181 in the valve closing direction, and the closing member 56. Therefore, the piston valve opening direction pressing force F11 acts on the piston 171 and the spool valve opening direction pressing force F12 acts on the spool 181 by the hydraulic pressure P5 of the drive hydraulic chamber 172.

  The discharge flow rate control valve 180 controls the discharge flow rate of the hydraulic oil discharged from the primary hydraulic chamber 55 which is one positioning hydraulic chamber by the hydraulic oil supply valve 160. In the second embodiment, the discharge flow rate control valve 180 is provided corresponding to the common flow path 54r formed in the primary partition wall 54 of the primary pulley 50 that is one pulley. That is, the primary partition wall 54 is provided at a plurality of locations on the circumference, for example, three locations at equal intervals. The discharge flow control valve 180 includes a spool 181 and a spool elastic member 182.

  The spool 181 has a cylindrical shape, and is supported by the common flow path 54r so as to be slidable in the on-off valve direction so that its axial direction is parallel to the on-off valve direction. The spool 181 supports the piston 171 of the valve opening / closing device 170 so as to be slidable in the direction of the opening / closing valve. The spool 181 is formed with a throttle portion 181a continuous in the circumferential direction in the vicinity of the center portion in the opening / closing valve direction. A tapered surface 181b whose diameter increases in the valve opening direction is formed on the valve opening direction side of the throttle portion 181a. Here, the diameter of the first main body portion 181c on the valve opening direction side of the throttle portion 181a of the spool 181 is such that the first main body portion 181c can slide in the on-off valve direction with respect to the common flow path 54r. It is set with respect to the inner diameter of the common flow path 54r so that the communication between the portion T3 and the release passage 54n is blocked (including the case where the part T3 is almost blocked). The diameter of the second main body portion 181d in the valve closing direction relative to the throttle portion 181a of the spool 181 is such that the second main body portion 181d can slide in the on-off valve direction with respect to the common flow path 54r. It is set with respect to the inner diameter of the common flow path 54r so that the communication between the space portion T3 via the 54r and the discharge flow path 54m is blocked (including a case where the discharge flow path 54m is substantially blocked). In addition, a plurality of communication holes 181e are formed in the vicinity of the narrowed portion 181a in the first main body portion 181c. The communication hole 181e passes through the outer peripheral surface and the inner peripheral surface of the spool 181. The communication hole 181e faces the space T3 in the opening / closing valve direction when the spool 181 is positioned in the most valve closing direction with respect to the common flow path 54r, and the hydraulic oil supply valve 160 is closed in the circumferential direction. It is formed at a position facing both ends of the first communication passage 171a of the piston 171 in the valve state.

  Here, when the spool 181 is positioned in the most valve closing direction with respect to the common flow path 54r, the space T3 is positioned to face only the communication hole 181e. Accordingly, the communication between the first communication passage 171a via the space T3 and the common flow path 54r and the discharge flow path 54m is blocked, and the discharge flow rate control valve 180 is closed. Further, when the spool 181 is slid with respect to the common flow path 54r in the valve opening direction from the state where the spool 181 is positioned in the most valve closing direction, the space T3 is formed into the tapered surface 181b and the tapered surface 181b of the throttle part 181a. The position is opposite to the communication hole 181e. Therefore, the communication between the space T3 via the common flow path 54r and the discharge flow path 54m is released, and the discharge flow rate control valve 180 is opened. Further, the discharge flow rate control valve 180 is a hydraulic fluid that flows into the discharge flow path 54m from the space portion T3 via the common flow path 54r according to the discharge flow path area formed by the tapered surface 181b and the space portion T3. It controls the discharge flow rate.

  The spool elastic member 182 is spool valve closing direction pressing means. The spool elastic member 182 is arranged in a state of being biased between the end portion of the common flow path 54r in the valve opening direction and the spool 181. The spool elastic member 182 generates a valve closing urging force, and an elastic member pressing force that causes only the communication hole 181e of the spool 181 to slide to a position facing the space T3 by this valve closing urging force causes the spool valve closing direction. It acts on the spool 181 as the pressing force F13.

  Here, when the discharge flow rate control valve 180 is opened, the spool opening direction pressing force F12 that is the pressing force acting on the spool 181 in the valve opening direction is the pressing force acting on the spool 181 in the valve closing direction. This is done by sliding the spool 181 to a position where the spool valve closing direction pressing force F13 is exceeded and the tapered surface 181b faces the space T3. The spool valve opening direction pressing force F12 is the hydraulic pressure P5 of the drive hydraulic chamber 172 that acts on the ring-shaped end surface 181f of the spool 181 in the valve closing direction. On the other hand, the spool closing direction pressing force F13 is an elastic member pressing force acting on the spool 181 by the valve closing biasing force.

  Further, the discharge flow rate control valve 180 is provided in the drive hydraulic chamber 172 that can forcibly open the hydraulic oil supply valve 160 when the hydraulic oil supply valve 160 is opened by the hydraulic pressure P5 of the drive hydraulic chamber 172. The valve is set to open at a hydraulic pressure equal to or higher than the hydraulic pressure P5. That is, the discharge flow rate control valve 180 has a discharge flow rate at a hydraulic pressure equal to or higher than the hydraulic pressure at which the hydraulic oil supply valve 160 can be opened when the hydraulic pressure P1 of the primary hydraulic chamber 55 is maximum, as in the first embodiment. It is set to be controlled. Thus, by controlling the hydraulic pressure P5 of one drive hydraulic chamber 172, the hydraulic oil discharge valve 160 can be opened and the discharge flow rate can be controlled by the discharge flow rate control valve 180. Therefore, it is possible to allow or prohibit the discharge of the hydraulic oil in the primary hydraulic chamber 55, which is one positioning hydraulic chamber, and control the discharge flow rate with a simple configuration.

  Here, the working oil supply flow path for supplying the working oil to the primary hydraulic chamber 55, which is one positioning hydraulic chamber, in this second embodiment is connected to the supply side passage 51a, the communication passage 51c, the space portion T1, and the communication portion. The passage 54k, the space T3, the communication hole 181e, the first communication path 171a, the second communication path 171b, the communication hole 171c, and the opening 54q are configured. In the second embodiment, the hydraulic oil discharge passage for discharging the hydraulic oil from the primary hydraulic chamber 55, which is one positioning hydraulic chamber, includes a common flow passage 54r and a discharge passage 54m.

  Next, the operation of the belt type continuously variable transmission 1-2 according to the second embodiment will be described. General forward and reverse travel of the vehicle is the same as that of the belt-type continuously variable transmission 1-1 according to the first embodiment, and thus description thereof is omitted. As for the gear ratio decrease change, the gear ratio increase change, and the gear ratio fixation, the same parts as those of the belt type continuously variable transmission 1-1 according to the first embodiment will be described in a simplified manner.

  The gear ratio reduction change is performed by supplying hydraulic oil from the hydraulic oil supply control device 140 to the primary hydraulic chamber 55 and sliding (moving) the primary movable sheave 53 toward the primary fixed sheave side. As shown in FIG. 9, the hydraulic oil supply valve 160 is opened to allow the hydraulic oil to be supplied from the hydraulic oil supply control device 140 to the primary hydraulic chamber 55. Specifically, ECU 150 calculates a reduction gear ratio and a transmission speed, and outputs a control signal for the transmission ratio based on these to hydraulic oil supply controller 140. The hydraulic oil supply control device 140 increases the hydraulic pressure of the hydraulic oil supplied to the second communication passage 171b. Accordingly, the hydraulic pressure P4 of the second communication passage 171b increases, and the hydraulic oil pressure F8 acting on the valve body 161 is increased by the hydraulic pressure P4 of the second communication passage 171b.

  At this time, the hydraulic oil supply control device 140 controls the pressing force regulating valve 145 to apply the piston valve opening direction pressing force F11 to the piston 171 by the hydraulic pressure P5 of the driving hydraulic chamber 172. That is, the valve opening / closing device 170 applies the piston valve-opening direction pressing force F11 to the piston 171 when supplying the hydraulic oil to the primary hydraulic chamber 55, so that the piston valve-opening direction pressing force F11 is applied to the hydraulic oil supply valve 160. The valve body 161 is fixed to the piston 171 via a fixing pin 165 as the valve body opening direction pressing force in the valve opening direction. Therefore, when hydraulic fluid is supplied to the primary hydraulic chamber 55, the combined pressure of the hydraulic fluid pressing force F8 and the piston valve opening direction pressing force F11 becomes the valve body valve opening direction pressing force. Thus, the valve body opening direction pressing force acts on the valve body 161 by the elastic member pressing force F9 that acts on the valve body 161 by the valve closing biasing force of the valve body elastic member 163 and the hydraulic pressure P1 of the primary hydraulic chamber 55. When the valve body closing direction pressing force combined with the hydraulic oil pressing force F10 is exceeded, the valve body 161 moves in the valve opening direction, and the hydraulic oil supply valve 160 opens. That is, the hydraulic oil supply valve 160 allows the hydraulic oil to be supplied to the primary hydraulic chamber 55 that is one positioning hydraulic chamber.

  Here, the hydraulic oil supply control device 140 is configured so that the hydraulic pressure P5 of the drive hydraulic chamber 172 when the hydraulic oil is supplied to the primary hydraulic chamber 55 can open the discharge flow rate control valve 180. The pressure of the hydraulic oil supplied to the drive hydraulic chamber 172 is regulated by the pressing pressure regulating valve 145 so as to be less than the value. Since the hydraulic pressure P5 of the drive hydraulic chamber 172 at the time of supplying the hydraulic oil to the primary hydraulic chamber 55 is less than the hydraulic pressure P5 of the drive hydraulic chamber 172 that can open the discharge flow rate control valve 180, via the piston 171, Even when the valve opening / closing device 170 applies the piston valve opening direction pressing force F11 to the valve body 161 as the valve body opening direction pressing force, the discharge flow rate control valve 180 maintains the closed state. Therefore, it is possible to suppress the hydraulic oil supplied to the primary hydraulic chamber 55 from leaking from the hydraulic oil discharge channel, that is, the discharge channel 54m.

  When supply of the hydraulic oil to the primary hydraulic chamber 55 by the hydraulic oil supply valve 160 is allowed, the pressure is regulated by the clamping pressure regulating valve 144 of the hydraulic oil supply control device 140 as shown by an arrow C in FIG. The hydraulic oil is supplied to the primary hydraulic chamber 55 from the second communication passage 171b through the communication hole 171c. At this time, the discharge flow rate control valve 180 maintains the closed state as in the first embodiment, and the hydraulic oil supplied from the hydraulic oil supply control device 140 to the primary hydraulic chamber 55 is the space T3, the common flow path. It is prohibited to be discharged through 54r and the discharge flow path 54m. Accordingly, the hydraulic oil P1 in the primary hydraulic chamber 55 is increased by the hydraulic oil supplied via the hydraulic oil supply valve 160, 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 120 in the primary pulley 50 increases, the contact radius of the belt 120 in the secondary pulley 60 decreases, the gear ratio is reduced, and the reduction gear ratio is obtained.

  The gear ratio increase is changed by discharging hydraulic oil from the primary hydraulic chamber 55 and sliding (moving) the primary movable sheave 53 to the side opposite to the primary fixed sheave side. First, as shown in FIG. 10, the hydraulic oil supply valve 160 is forcibly opened to allow the hydraulic oil to be discharged from the primary hydraulic chamber 55. Then, the discharge flow rate of the hydraulic oil discharged from the primary hydraulic chamber 55 is controlled by the discharge flow rate control valve 180. Specifically, ECU 150 calculates an increase gear ratio and a gear shift speed, and outputs a gear ratio control signal based on these to hydraulic oil supply controller 140. The hydraulic oil supply control device 140 increases the hydraulic pressure of the hydraulic oil supplied to the drive hydraulic chamber 172. Accordingly, the hydraulic pressure P5 in the drive hydraulic chamber 180 rises above the hydraulic pressure at which the discharge flow rate control valve 180 can be opened, and the valve body 161 opens the valve body 161 via the piston 171 by the hydraulic pressure P5 in the drive hydraulic chamber 182. The piston valve opening direction pressing force F11 acting as the pressing force acts on the valve body 161 by the elastic member pressing force F9 acting on the valve body 161 by the valve closing biasing force of the valve body elastic member 163 and the hydraulic pressure P1 of the primary hydraulic chamber 55. The valve body closing direction pressing force combined with the hydraulic oil pressing force F10 is exceeded. As a result, the valve body 161 moves in the valve opening direction, and the hydraulic oil supply valve 160 is forcibly opened by the valve opening / closing device 170. That is, the valve opening / closing device 170 allows the hydraulic oil to be discharged from the primary hydraulic chamber 55 that is one positioning hydraulic chamber by the hydraulic oil supply valve 160.

  At this time, the spool valve-opening direction pressing force F12 acting on the spool 181 by the raised hydraulic pressure P5 of the drive hydraulic chamber 172 is the spool valve-closing direction pressing force F12 acting on the spool 181 by the valve closing biasing force of the spool elastic member 182. It will exceed. Here, the discharge flow rate control valve 180 tapers in accordance with the amount of movement (stroke amount) in the valve opening direction of the spool 181 from the state in which the spool 181 is positioned closest to the common flow path 54r. The discharge flow path area formed by the surface 181b and the space T3 will increase. When the amount of movement is equal to or greater than a predetermined amount, the positional relationship of the spool 181 with respect to the space portion T3 is such that only the communication hole 181e of the spool 181 faces the space portion T3. Changes to a positional relationship facing the space T3. Accordingly, the discharge flow rate control valve 180 controls the discharge flow rate of the hydraulic oil from the primary hydraulic chamber 55 which is one positioning hydraulic chamber to the outside.

  When the hydraulic oil is allowed to be discharged from the primary hydraulic chamber 55 by the hydraulic oil supply valve 160 and the discharge flow rate of the hydraulic oil is controlled by the discharge flow rate control valve 180, as shown by an arrow D in FIG. The hydraulic oil in the hydraulic chamber 55 flows into the space T3 from the opening 54q via the communication hole 171c, the second communication flow path 171b, the first communication flow path 171a, and the communication hole 171e, and passes through the common flow path 54r. Flow into the discharge channel 54m. The hydraulic oil that has flowed into the discharge passage 54m is discharged to the outside of the primary pulley 50. Here, the discharge flow rate control valve 180 of the primary pulley 50 that is one pulley that rotates integrally, when the hydraulic oil supply valve 160 is opened, the hydraulic pressure of the primary pulley 50 that is one positioning hydraulic chamber is in the on-off valve direction. It is arranged at a position that does not act on. Accordingly, the hydraulic pressure P1 of the primary hydraulic chamber 55 when the hydraulic oil is discharged from the primary hydraulic chamber 55 changes when the hydraulic oil is discharged from the primary hydraulic chamber 55, so that the primary hydraulic chamber 55 flowing into the common flow path 54r. Even if the pressure of the hydraulic oil discharged from the cylinder changes, the position of the spool 181 in the on-off valve direction with respect to the common flow path 54r becomes difficult to be displaced. As a result, the discharge flow rate control valve 180 can suppress the change in the discharge flow rate due to the change in the hydraulic pressure P1 of the primary hydraulic chamber 55 and can discharge the hydraulic oil stably. Can be improved. Further, since it is not necessary to perform feedback control based on the change of the hydraulic pressure P1 of the primary hydraulic chamber 55 in order to suppress the influence of the change of the hydraulic pressure P1 of the primary hydraulic chamber 55 on the discharge flow rate, the control is simplified. be able to. Moreover, cost reduction can be achieved.

  At this time, the hydraulic oil supply control device 140 closes the clamping pressure regulating valve 144. This is to prevent the hydraulic oil discharged from the primary hydraulic chamber 55 from returning to the hydraulic oil supply control device 140. That is, the hydraulic oil supply valve 160 prohibits the supply of hydraulic oil to the primary hydraulic chamber 55. Accordingly, the hydraulic fluid P1 in the primary hydraulic chamber 55 is reduced by being discharged from the hydraulic fluid from the primary hydraulic chamber 55 via the hydraulic oil supply valve 160 while the discharge flow rate is controlled by the discharge flow control valve 180, and the primary movable. The pressing force that presses the sheave 53 toward the primary fixed sheave side is reduced, and the primary movable sheave 53 slides in the axial direction opposite to the primary fixed sheave side. As a result, the contact radius of the belt 120 in the primary pulley 50 decreases, the contact radius of the belt 120 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. As shown in FIG. 8, the hydraulic oil supply valve 160 is maintained in a closed state, and both the supply of hydraulic oil to the primary hydraulic chamber 55 and the discharge of hydraulic oil from the primary are prohibited. Specifically, the hydraulic oil supply control device 140 closes the clamping pressure regulating valve 144 and stops the supply of hydraulic oil from the hydraulic oil supply control device 140 to the second communication flow path 171b. Further, the hydraulic oil supply control device 140 closes the pressing pressure regulating valve 145 to stop the supply of hydraulic oil from the hydraulic oil supply control device 140 to the drive hydraulic chamber 172, or the hydraulic pressure of the drive hydraulic chamber 172. The pressure of the hydraulic fluid supplied to the drive hydraulic chamber 182 so that the spool valve opening direction pressing force F12 acting on the spool 181 by the hydraulic pressure P5 of the driving hydraulic chamber 172 does not exceed the spool closing direction pressing force F13. The pressure is regulated by the pressure regulating valve 145.

  As described above, since the hydraulic oil is held in the primary hydraulic chamber 55, the primary hydraulic chamber 55 has the primary hydraulic chamber 55 in order to maintain a constant position in the axial direction of the primary movable sheave 53 with respect to the primary fixed sheave 52. It is not necessary to increase the pressure of the primary hydraulic chamber 55 by supplying hydraulic oil from the outside. As a result, when the speed ratio is fixed, it is not necessary to drive the oil pump 142 in order to supply the hydraulic oil to the primary hydraulic chamber 55, so that an increase in power loss of the oil pump 142 can be suppressed.

  As described above, in the belt-type continuously variable transmission 1-2 according to the second embodiment, the hydraulic oil discharge valve is separately provided as in the belt-type continuously variable transmission 1-1 according to the first embodiment. Rather, the hydraulic oil is supplied to the primary hydraulic chamber 55 which is one positioning hydraulic chamber, the hydraulic oil is discharged from the primary hydraulic chamber 55, and the hydraulic oil is held in the primary hydraulic chamber 55 by one valve. Can do.

  As in the first embodiment, when the hydraulic oil is supplied to the primary hydraulic chamber 55, the valve opening direction pressing force is a combination of the piston opening direction pressing force F11 and the hydraulic oil pressing force F8. Therefore, the hydraulic oil pressing force F8 for opening the hydraulic oil supply valve 160 is made smaller than when the piston valve opening direction pressing force F11 is not applied to the valve body 161 of the hydraulic oil supply valve 160. be able to. As a result, when hydraulic fluid is supplied to the primary hydraulic chamber 55, the influence of the elastic member pressing force F9 when the hydraulic fluid supply valve 160 is opened can be reduced, so that the operation supplied to the primary hydraulic chamber 55 is performed. The oil supply pressure can be reduced. Further, as in the first embodiment, the sealing performance of the hydraulic oil supply valve 160 can be improved, and the supply pressure of the hydraulic oil supplied to the primary hydraulic chamber 55 can be reduced. Further, as in the first embodiment, an increase in the driving loss of the oil pump 142 can be further suppressed.

  In the belt type continuously variable transmission 1-2 according to the second embodiment, the hydraulic oil supply valve 160 and the discharge flow rate control valve 180 are arranged on the same axis, that is, a pair of hydraulic oil supply valves 160 and The discharge flow rate control valve 180 is integrated with the primary pulley 50, which is one pulley that rotates integrally. Therefore, the size can be reduced.

  Further, since the pair of hydraulic oil supply valves 160 and the discharge flow rate control valve 180 are integrated, the volume of the portion through which the hydraulic oil passes from the primary hydraulic chamber 55 to the discharge flow path 54m as compared with a separate case is reduced. Can be small. Therefore, a change in gear ratio and a shock when only the hydraulic oil supply valve 160 is opened can be reduced. Thereby, feeling can be improved.

  Next, a belt type continuously variable transmission 1-3 according to a third embodiment will be described. FIG. 11 is a diagram illustrating a configuration example of a hydraulic oil supply valve, a valve opening / closing device, and a discharge flow rate control valve according to the third embodiment. 12 and 13 are explanatory diagrams of the operation of the belt-type continuously variable transmission when the gear ratio is changed. The belt-type continuously variable transmission 1-3 according to the third embodiment differs from the belt-type continuously variable transmission 1-2 according to the second embodiment in that the spool 211 forcibly opens the hydraulic oil supply valve 190. It is a point that is a piston. The basic configuration of the belt-type continuously variable transmission 1-3 according to the third embodiment is substantially the same as the basic configuration of the belt-type continuously variable transmission 1-2 according to the second embodiment. The description is omitted.

  The hydraulic oil supply valve 190 allows only the supply of hydraulic oil to the primary hydraulic chamber 55 which is one positioning hydraulic chamber. As shown in FIGS. 11 to 13, the hydraulic oil supply valve 190 is an operation that is a working fluid from the outside of the primary hydraulic chamber 55 that is one positioning hydraulic chamber, that is, from the outside of the primary pulley 50 to the primary hydraulic chamber 55. The 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 third embodiment, the hydraulic oil supply valve 190 is provided corresponding to the common flow path 54r formed in the primary partition wall 54 of the primary pulley 50, which is one pulley. That is, the primary partition wall 54 is provided at a plurality of locations on the circumference, for example, three locations at equal intervals. The hydraulic oil supply valve 190 includes a valve body 191, a valve seat 192, a valve body elastic member 193, a ring-shaped member 194, and a locking member 195.

  The valve body 191 has a spherical shape and a diameter larger than the diameter of the valve seat 192. Moreover, this valve body 191 is arrange | positioned at the opening part 54q. The valve seat 192 is disposed in contact with the end face 54s of the common flow path 54r in the valve opening direction. The valve seat 192 has a ring shape, and the diameter of the valve seat 192 extends from the end surface 54s in the valve opening direction toward the end surface in the valve closing direction (from the opening side toward the common flow path side). A decreasing valve seat taper surface 192a is formed. When the valve body 191 contacts the valve seat taper surface 192a of the valve seat 192, the communication between the opening 54q and the common flow path 54r is cut off, and the hydraulic oil supply valve 190 is closed. Further, when the valve body 191 is separated from the valve seat 192, the opening 54q and the common flow path 54r communicate with each other, and the hydraulic oil supply valve 190 is opened. That is, the hydraulic oil supply valve 190 opens at the opening 54q in the valve opening direction and closes in the valve closing direction.

  The valve body elastic member 193 is disposed in a state of being biased between the valve body 191 and the ring-shaped member 194 fixed to the opening 54q by the locking member 195 via the valve body 191. The valve body elastic member 193 generates a valve closing biasing force, and this valve closing biasing force causes the pressing force in the direction in which the valve body 191 contacts the valve seat 192, that is, the elastic member pressing force F15 is the valve body valve closing valve. It acts on the valve body 191 as a directional pressing force. As a result, the valve body 191 is pressed against the valve seat 192, and the hydraulic oil supply valve 190 functions as a check valve. Further, the locking member 195 has a disc shape, and an opening for allowing hydraulic oil to pass therethrough is formed at the center thereof.

  The guide member 200 is disposed in the common flow path 54r. The guide member 200 has a cylindrical shape, and is disposed in a state where an end portion in the valve opening direction is in contact with the valve seat 192 of the hydraulic oil supply valve 190. A guide-side tapered surface 200a whose diameter increases from the valve closing direction to the valve opening direction (from the common flow path side to the opening side) is formed on the inner peripheral surface of the guide member 200. A communication portion 200b that communicates the outer peripheral surface and the inner peripheral surface at the end in the valve opening direction is formed. This communication part 200b connects the space part T5 and the communication path 54k through the space part T6. In addition, the guide member 200 is formed with a communication portion 200c that connects the outer peripheral surface and the inner peripheral surface in the vicinity of the end in the valve closing direction. The communication part 200c communicates the space part T5 and the discharge flow path 54m via the space part T7. Here, the space portion T <b> 5 includes a valve body 191, a guide member 200, and a spool 211.

  Here, when the hydraulic oil supply valve 190 is opened, the valve body opening direction pressing force, which is the pressing force acting on the valve body 191 in the direction in which the valve body 191 moves away from the valve seat 192, that is, the valve opening direction, The valve body 191 exceeds the valve body closing direction pressing force, which is the pressing force acting on the valve body 191 in the direction in which the valve body 191 contacts the valve seat protrusion 192, that is, the valve closing direction, and the valve body 191 is separated from the valve seat 192. Done in As the valve body opening direction pressing force, there is usually a hydraulic oil pressure supplied to the space portion T5 from the communication passage 54k, that is, a hydraulic oil pressure F14 that acts on the valve body 191 by the hydraulic pressure P6 of the space portion T5. . On the other hand, as the valve body closing direction pressing force, the elastic member pressing force F15 acting on the valve body 191 by the valve closing urging force and the hydraulic oil pressing force F16 acting on the valve body 191 by the hydraulic pressure P1 of the primary hydraulic chamber 55. And are included. Since the hydraulic pressure P1 of the primary hydraulic chamber 55 acts as a pressing force in the valve closing direction on the valve body 191, even if the hydraulic pressure P1 of the primary hydraulic chamber 55 rises, the valve body 191 separates from the valve seat protrusion 192. There is no. Therefore, as long as the valve body valve opening direction pressing force acting on the valve body 191 does not exceed the valve body valve opening direction pressing force, the closed state of the hydraulic oil supply valve 190 is maintained. The hydraulic oil in the primary hydraulic chamber 55 is securely held in the primary hydraulic chamber 55.

  The discharge flow rate control valve 210 controls the discharge flow rate of the hydraulic oil discharged from the primary hydraulic chamber 55 which is one positioning hydraulic chamber by the hydraulic oil supply valve 190. Further, the discharge flow rate control valve 210 is a valve opening / closing means, and controls permission or prohibition of discharge of hydraulic oil from the primary hydraulic chamber 55. In the third embodiment, the discharge flow rate control valve 210 is provided corresponding to the common flow path 54r formed in the primary partition wall 54 of the primary pulley 50 that is one of the pulleys. That is, the primary partition wall 54 is provided at a plurality of locations on the circumference, for example, three locations at equal intervals. The discharge flow rate control valve 210 includes a spool 211, a drive hydraulic chamber 212, and a spool elastic member 213.

  The spool 211 has a cylindrical shape, and is supported by the common channel 54r so as to be slidable in the opening / closing valve direction via the guide member 200 so that the axial direction thereof is parallel to the opening / closing valve direction. In the spool 211, a throttle portion 211a that is continuous in the circumferential direction is formed in the vicinity of the center portion in the opening / closing valve direction. A spool-side tapered surface 211b whose diameter increases from the valve closing direction to the valve opening direction (from the common flow path side to the opening side) is formed on the valve opening direction side of the throttle portion 211a. Here, the diameter of the first main body portion 211c closer to the valve opening direction than the throttle portion 211a of the spool 211 is such that the first main body portion 211c can slide in the opening / closing valve direction with respect to the guide member 200, and this space portion. It is set with respect to the inner diameter of the guide member 200 so that the communication between T5 and the discharge channel 54m is blocked (including a case where the discharge channel 54m is almost blocked). The diameter of the second main body portion 211d in the valve closing direction relative to the throttle portion 211a of the spool 211 is such that the second main body portion 211d can slide in the on-off valve direction with respect to the guide member 200, and a piston portion 211f described later. It is set with respect to the inner diameter of the guide member 200 so that the communication between the space between the guide member 200 and the discharge channel 54m is blocked (including the case where it is substantially blocked). The diameter of the piston portion 211f in the valve closing direction relative to the second main body portion 211d of the spool 211 is such that the piston portion 211f can slide in the on-off valve direction with respect to the common flow path 54r, and the drive hydraulic chamber 212, It is set with respect to the inner diameter of the common flow path 54r so that the communication with the discharge flow path 54m is blocked (including a case where the communication is substantially blocked).

  Further, the spool 211 is formed with a valve body pressing projection 211e protruding in the valve opening direction at an end in the valve opening direction. The valve body pressing projection 211e is formed at a position where it can contact the valve body 191 through the valve seat 192. The valve body pressing projection 211e contacts the valve body 191 by sliding the spool 211 in the valve opening direction by the piston valve opening direction pressing force F16 acting on the spool 211 by the hydraulic pressure P7 of the drive hydraulic chamber 212. To do. The spool valve opening direction pressing force F17 acting on the spool 211 acts on the valve body 191 as the valve body valve opening direction pressing force. Therefore, even when the spool valve opening direction pressing force F17 exceeds the valve body closing direction pressing force, the valve body 191 moves in the valve opening direction with respect to the valve seat 192, and the hydraulic oil supply valve 190 opens. To do. That is, the hydraulic oil supply valve 190 is forcibly opened in the direction in which the hydraulic oil is discharged from the primary hydraulic chamber 55 to the outside.

  Here, when the spool 211 is positioned in the most valve-closing direction with respect to the common channel 54r, only the first main body portion 211c faces the guide-side tapered surface 200a of the guide member 200. Accordingly, the communication between the space portion T5 and the discharge flow path 54m is blocked through the communication portion 200c and the space portion T7, and the discharge flow rate control valve 210 is closed. Further, the spool 211 slides with respect to the common flow path 54r in the valve opening direction from the state where the spool 211 is located in the most valve closing direction with respect to the common flow path 54r, and the spool side taper surface 211b is guided by the guide member 200. Opposite to the side tapered surface 200a. Therefore, the communication between the space portion T5 and the discharge flow path 54m is released via the communication portion 200c and the space portion T7, and the discharge flow rate control valve 210 is opened. Further, the discharge flow rate control valve 210 has a space through the communication portion 200c and the space portion T7 in accordance with the discharge flow path area formed by the spool-side tapered surface 211b and the guide-side tapered surface 200a of the guide member 200. The discharge flow rate of the hydraulic oil flowing into the discharge flow path 54m from the part T5 is controlled. In the hydraulic oil supply valve 190, before the spool side tapered surface 211b faces the guide side tapered surface 200a of the guide member 200, the valve body pressing projection 211e contacts the valve body 191, and the valve body 191 is opened. The valve is opened to move in the valve direction. That is, the hydraulic oil supply valve 190 is opened before the spool-side tapered surface 211b and the guide-side tapered surface 200a of the guide member 200 face each other, that is, before the discharge flow rate control valve 210 is opened.

  The drive hydraulic chamber 212 is supplied with hydraulic oil, and controls the hydraulic oil supply valve 190 and the discharge flow rate control valve 210 by the pressure of the supplied hydraulic oil, that is, the hydraulic pressure P7 of the drive hydraulic chamber 212. It is. In other words, the hydraulic oil supply valve 190 is controlled by the hydraulic pressure P7 of the drive hydraulic chamber 212 to permit or prohibit the discharge of the hydraulic oil from the primary hydraulic chamber 55 by the discharge flow rate control valve 210. Further, the discharge flow rate control valve 210 has its discharge flow rate controlled by the hydraulic pressure P 7 of the drive hydraulic chamber 212. The drive hydraulic chamber 212 is formed between the common flow path 54r, the end surface 211g of the spool 211 in the valve closing direction, and the closing member 56. Accordingly, the spool valve opening direction pressing force F17 acts on the spool 211 by the hydraulic pressure P7 of the drive hydraulic chamber 212.

  The spool elastic member 213 is a spool valve closing direction pressing unit. The spool elastic member 213 is arranged in a state of being biased between the step portion 54t of the common flow path 54r and the piston portion 211f via the guide member 200. The spool elastic member 213 generates a valve closing urging force, and an elastic member pressing force F18 that slides only the first main body portion 211c of the spool 211 to a position facing the guide-side tapered surface 200a by the valve closing urging force. Acts on the spool 211 as the spool valve closing direction pressing force.

  Here, when the discharge flow rate control valve 210 is opened, the spool opening direction pressing force F17, which is the pressing force acting on the spool 211 in the valve opening direction, is the pressing force acting on the spool 211 in the valve closing direction. This is performed by sliding the spool 211 to a position where a certain spool closing direction pressing force is exceeded and the spool side tapered surface 211b is opposed to the guide side tapered surface 200a. This spool opening direction pressing force F17 is the hydraulic pressure P7 of the drive hydraulic chamber 212 acting on the end surface 211g of the spool 211 in the valve closing direction. On the other hand, the spool closing direction pressing force includes an elastic member pressing force F18 acting on the spool 211 by the valve closing biasing force and an elastic member pressing force F15 acting on the valve body 191 by the valve closing biasing force of the valve body elastic member 193. And hydraulic oil pressing force F16 acting on the valve body 191 by the hydraulic pressure P1 of the primary hydraulic chamber 55 is included.

  Further, the discharge flow rate control valve 210 is provided in the drive hydraulic chamber 212 that can forcibly open the hydraulic oil supply valve 190 when the hydraulic oil supply valve 190 is opened by the hydraulic pressure P7 of the drive hydraulic chamber 212. The valve is set to open at a hydraulic pressure equal to or higher than the hydraulic pressure P5. That is, the discharge flow rate control valve 210 has a discharge flow rate at a hydraulic pressure higher than the hydraulic pressure at which the hydraulic oil supply valve 190 can be opened when the hydraulic pressure P1 of the primary hydraulic chamber 55 is maximum, as in the first embodiment. It is set to be controlled. Thus, by controlling the hydraulic pressure P7 of one drive hydraulic chamber 212, the hydraulic oil discharge valve 190 can be opened and the discharge flow rate can be controlled by the discharge flow rate control valve 210. Therefore, it is possible to allow or prohibit the discharge of the hydraulic oil in the primary hydraulic chamber 55, which is one positioning hydraulic chamber, and control the discharge flow rate with a simple configuration.

  Here, the working oil supply flow path for supplying the working oil to the primary hydraulic chamber 55, which is one positioning hydraulic chamber, is connected to the supply side passage 51a, the communication passage 51c, the space portion T1, and the communication in this third embodiment. The passage 54k, the space portion T6, the communication portion 200b, the space portion T5, and the opening portion 54q are configured. In the third embodiment, the hydraulic oil discharge passage for discharging the hydraulic oil from the primary hydraulic chamber 55, which is one positioning hydraulic chamber, is configured by the communication portion 200c, the space portion T7, and the discharge passage 54m. ing.

  Next, the operation of the belt type continuously variable transmission 1-3 according to the third embodiment will be described. General forward and reverse travel of the vehicle is the same as that of the belt-type continuously variable transmission 1-2 according to the second embodiment, and thus description thereof is omitted. In addition, about the gear ratio decrease change, the gear ratio increase change, and the gear ratio fixation, the same part as the belt-type continuously variable transmission 1-2 according to the second embodiment will be described in a simplified manner.

  The gear ratio reduction change is performed by supplying hydraulic oil from the hydraulic oil supply control device 140 to the primary hydraulic chamber 55 and sliding (moving) the primary movable sheave 53 toward the primary fixed sheave side. As shown in FIG. 9, the hydraulic oil supply valve 190 is opened to allow the hydraulic oil to be supplied from the hydraulic oil supply control device 140 to the primary hydraulic chamber 55. Specifically, ECU 150 calculates a reduction gear ratio and a transmission speed, and outputs a control signal for the transmission ratio based on these to hydraulic oil supply controller 140. The hydraulic oil supply control device 140 increases the hydraulic pressure of the hydraulic oil supplied to the space T5. Accordingly, the hydraulic pressure P6 of the space portion T5 increases, and the hydraulic oil pressing force F14 acting on the valve body 191 increases due to the hydraulic pressure P6 of the space portion T5.

  At this time, the hydraulic oil supply control device 140 controls the pressing force regulating valve 145 to apply the spool valve opening direction pressing force F17 to the spool 211 by the hydraulic pressure P7 of the driving hydraulic chamber 212. That is, the discharge flow rate control valve 210 causes the spool valve opening direction pressing force F17 to act on the spool 211 when supplying the hydraulic oil to the primary hydraulic chamber 55, so that the spool valve opening direction pressing force F17 is applied to the hydraulic oil supply valve. The valve body 191 is acted on the valve body 191 through the valve body pressing protrusion 211e of the spool 211 as a valve body opening direction pressing force 190. Accordingly, when hydraulic fluid is supplied to the primary hydraulic chamber 55, the combined pressure of the hydraulic fluid pressing force F14 and the spool valve opening direction pressing force F17 becomes the valve body valve opening direction pressing force. Thus, the valve body opening direction pressing force acts on the valve body 191 by the elastic member pressing force F15 acting on the valve body 191 by the valve closing biasing force of the valve body elastic member 193 and the hydraulic pressure P1 of the primary hydraulic chamber 55. The valve element 191 is opened by exceeding the valve element closing direction pressing force obtained by combining the hydraulic oil pressing force F16 to be applied and the elastic member pressing force F18 acting on the spool 211 by the valve closing biasing force of the spool elastic member 213. The hydraulic oil supply valve 190 opens in the direction. That is, the hydraulic oil supply valve 190 allows hydraulic oil to be supplied to the primary hydraulic chamber 55 that is one positioning hydraulic chamber.

  Here, the hydraulic oil supply control device 140 is configured so that the hydraulic pressure P7 of the drive hydraulic chamber 212 when the hydraulic oil is supplied to the primary hydraulic chamber 55 is less than the hydraulic pressure at which the discharge flow rate control valve 210 can be opened. The pressure of the hydraulic oil supplied to the drive hydraulic chamber 212 is regulated by the pressing pressure regulating valve 145. Since the hydraulic pressure P7 of the drive hydraulic chamber 212 at the time of supplying the hydraulic oil to the primary hydraulic chamber 55 is less than the hydraulic pressure P7 of the drive hydraulic chamber 212 that can open the discharge flow rate control valve 210, via the spool 211, Even if the discharge flow rate control device 211 causes the valve opening direction pressing force F17 to act on the valve body 191 as the valve body opening direction pressing force, the discharge flow rate control valve 210 remains closed. Therefore, it is possible to suppress the hydraulic oil supplied to the primary hydraulic chamber 55 from leaking from the hydraulic oil discharge channel, that is, the discharge channel 54m.

  When supply of the hydraulic oil to the primary hydraulic chamber 55 by the hydraulic oil supply valve 190 is allowed, the pressure is adjusted by the clamping pressure regulating valve 144 of the hydraulic oil supply control device 140 as shown by an arrow E in FIG. The hydraulic oil is supplied from the space T5 to the primary hydraulic chamber 55. At this time, in the discharge flow rate control valve 210, the spool 211 is moved in the valve opening direction by the spool valve opening direction pressing force F17. However, as in the second embodiment, the valve closing state is maintained and the hydraulic oil supply control device 140 is maintained. The hydraulic oil supplied to the primary hydraulic chamber 55 is prohibited from being discharged through the space portion T5, the communication portion 200c, the space portion T7, and the discharge flow path 54m. Accordingly, the hydraulic oil P1 in the primary hydraulic chamber 55 is raised by the hydraulic oil supplied via the hydraulic oil supply valve 190, 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 120 in the primary pulley 50 increases, the contact radius of the belt 120 in the secondary pulley 60 decreases, the gear ratio is reduced, and the reduction gear ratio is obtained.

  The gear ratio increase is changed by discharging hydraulic oil from the primary hydraulic chamber 55 and sliding (moving) the primary movable sheave 53 to the side opposite to the primary fixed sheave side. First, as shown in FIG. 13, the hydraulic oil supply valve 190 is forcibly opened to allow the hydraulic oil to be discharged from the primary hydraulic chamber 55. Then, the discharge flow rate of the hydraulic oil discharged from the primary hydraulic chamber 55 is controlled by the discharge flow rate control valve 210. Specifically, ECU 150 calculates an increase gear ratio and a gear shift speed, and outputs a gear ratio control signal based on these to hydraulic oil supply controller 140. The hydraulic oil supply control device 140 increases the hydraulic pressure of the hydraulic oil supplied to the drive hydraulic chamber 212. Accordingly, the hydraulic pressure P7 in the drive hydraulic chamber 212 rises above the hydraulic pressure at which the discharge flow rate control valve 210 can be opened, and the valve body 191 opens to the valve body 191 via the spool 211 by the hydraulic pressure P7 in the drive hydraulic chamber 212. The spool valve opening direction pressing force F17 acting as a pressing force is applied to the valve body 191 by the elastic member pressing force F15 acting on the valve body 191 by the valve closing biasing force of the valve body elastic member 193 and the hydraulic pressure P1 of the primary hydraulic chamber 55. The spool valve opening direction pressing force, which is the sum of the operating hydraulic pressure F16 acting and the elastic member pressing force F18 acting on the spool 211 due to the valve closing biasing force of the spool elastic member 213, is exceeded. As a result, the valve body 191 moves in the valve opening direction, and the hydraulic oil supply valve 190 is forcibly opened by the discharge flow rate control valve 210. That is, the discharge flow rate control valve 210 allows the hydraulic oil to be discharged from the primary hydraulic chamber 55 that is one positioning hydraulic chamber by the hydraulic oil supply valve 190.

  At this time, the spool valve-opening direction pressing force F17 acting on the spool 211 by the increased hydraulic pressure P7 of the driving hydraulic chamber 212 exceeds the spool valve-closing direction pressing force. Here, the discharge flow rate control valve 210 has a spool side in accordance with the amount of movement (stroke amount) in the valve opening direction of the spool 211 from the state in which the spool 211 is positioned closest to the common flow path 54r. The discharge channel area formed by the tapered surface 211b and the guide-side tapered surface 200a is increased. When the amount of movement is equal to or greater than a predetermined amount, the positional relationship of the spool 211 with respect to the guide member 200 is such that only the first main body portion 211c of the spool 211 faces the guide-side tapered surface 200a. It changes to the positional relationship facing the guide-side tapered surface 200a. Therefore, the discharge flow rate control valve 211 controls the discharge flow rate of the hydraulic oil from the primary hydraulic chamber 55 which is one positioning hydraulic chamber to the outside.

  When the hydraulic oil is allowed to be discharged from the primary hydraulic chamber 55 by the hydraulic oil supply valve 190 and the discharge flow rate of the hydraulic oil is controlled by the discharge flow rate control valve 210, as shown by an arrow G in FIG. The hydraulic oil in the hydraulic chamber 55 flows into the discharge flow path 54m from the opening 54q through the space portion T5, the communication portion 200c, and the space portion T7. The hydraulic oil that has flowed into the discharge passage 54m is discharged to the outside of the primary pulley 50.

  At this time, the hydraulic oil supply control device 140 closes the clamping pressure regulating valve 144. This is to prevent the hydraulic oil discharged from the primary hydraulic chamber 55 from returning to the hydraulic oil supply control device 140. That is, the hydraulic oil supply valve 190 prohibits the supply of hydraulic oil to the primary hydraulic chamber 55. Accordingly, the hydraulic fluid P1 in the primary hydraulic chamber 55 is reduced by being discharged from the hydraulic fluid from the primary hydraulic chamber 55 via the hydraulic oil supply valve 190 while the discharge flow rate is controlled by the discharge flow control valve 210, and the primary movable. The pressing force that presses the sheave 53 toward the primary fixed sheave side is reduced, and the primary movable sheave 53 slides in the axial direction opposite to the primary fixed sheave side. As a result, the contact radius of the belt 120 in the primary pulley 50 decreases, the contact radius of the belt 120 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. As shown in FIG. 11, the hydraulic oil supply valve 190 is maintained in the closed state, and the supply of hydraulic oil to the primary hydraulic chamber 55 and the discharge of hydraulic oil from the primary hydraulic chamber 55 are both prohibited. Specifically, the hydraulic oil supply control device 140 closes the clamping pressure regulating valve 144 and stops the supply of hydraulic oil from the hydraulic oil supply control device 140 to the space T5. Further, the hydraulic oil supply control device 140 closes the pressing pressure regulating valve 145 to stop the supply of hydraulic oil from the hydraulic oil supply control device 140 to the drive hydraulic chamber 212 or the hydraulic pressure of the drive hydraulic chamber 212. In order to prevent the spool valve opening direction pressing force F17 acting on the spool 211 by the hydraulic pressure P7 of the driving hydraulic chamber 212 from exceeding the valve body closing direction pressing force and the spool closing direction pressing force, The pressure of the supplied hydraulic oil is regulated by the pressing pressure regulating valve 145.

  As described above, since the hydraulic oil is held in the primary hydraulic chamber 55, the primary hydraulic chamber 55 has the primary hydraulic chamber 55 in order to maintain a constant position in the axial direction of the primary movable sheave 53 with respect to the primary fixed sheave 52. It is not necessary to increase the pressure of the primary hydraulic chamber 55 by supplying hydraulic oil from the outside. As a result, when the speed ratio is fixed, it is not necessary to drive the oil pump 142 in order to supply the hydraulic oil to the primary hydraulic chamber 55, so that an increase in power loss of the oil pump 142 can be suppressed.

  As described above, in the belt-type continuously variable transmission 1-3 according to the third embodiment, the hydraulic oil discharge valve is separately provided as in the belt-type continuously variable transmission 1-2 according to the second embodiment. Rather, the hydraulic oil is supplied to the primary hydraulic chamber 55 which is one positioning hydraulic chamber, the hydraulic oil is discharged from the primary hydraulic chamber 55, and the hydraulic oil is held in the primary hydraulic chamber 55 by one valve. Can do.

  Similarly to the second embodiment, when the hydraulic oil is supplied to the primary hydraulic chamber 55, the valve opening direction pressing force is a combination of the spool opening direction pressing force F17 and the hydraulic oil pressing force F14. Therefore, compared with the case where the spool valve opening direction pressing force F17 is not applied to the valve body 191 of the hydraulic oil supply valve 190, the hydraulic oil pressing force F14 for opening the hydraulic oil supply valve 190 is reduced. be able to. Accordingly, when the hydraulic oil is supplied to the primary hydraulic chamber 55, the influence of the elastic member pressing force F15 when the hydraulic oil supply valve 190 is opened can be reduced, so that the operation supplied to the primary hydraulic chamber 55 is performed. The oil supply pressure can be reduced. Further, similarly to the second embodiment, an increase in driving loss of the oil pump 142 can be further suppressed.

  Similarly to the belt type continuously variable transmission 1-2 according to the second embodiment, the hydraulic oil supply valve 190 and the discharge flow rate control valve 210 are arranged on the same axis, that is, a pair of hydraulic oil supply valves 190. And the discharge flow rate control valve 210 are integrated and arranged in the primary pulley 50, which is one pulley that rotates integrally, so that the size can be reduced. In addition, since the pair of hydraulic oil supply valves 190 and the discharge flow rate control valve 210 are integrated, the volume of the portion through which the hydraulic oil passes from the primary hydraulic chamber 55 to the discharge flow path 54m as compared with a separate case is reduced. Can be small. Therefore, it is possible to reduce a change in gear ratio and a shock when only the hydraulic oil supply valve 190 is opened. Thereby, feeling can be improved.

  In the first to third embodiments, the hydraulic oil supply valves 70, 160, 190, the valve opening / closing devices 80, 170, and the discharge flow control valves 90, 180, 210 are pulleys whose axial direction, that is, the opening / closing valve direction is one pulley. The primary partition wall 54 is disposed so as to be parallel to the axial direction of the primary pulley 50, but the present invention is not limited to this. For example, the hydraulic oil supply valves 70, 160, 190, the valve opening / closing devices 80, 170, and the discharge flow control valves 90, 180, 210 are twisted with respect to the axial direction of the primary pulley 50 whose opening / closing valve direction is one pulley. You may arrange | position to the primary partition 54 so that it may become a position. Accordingly, the hydraulic oil supply valves 70, 160, 190, the valve opening / closing devices 80, 170, and the discharge flow rate control valves 90, 180, 210 can be prevented from projecting in the axial direction of the primary pulley 50. The influence of the hydraulic oil supply valves 70, 160, 190, the valve opening / closing devices 80, 170 and the discharge flow control valves 90, 180, 210 on the axial length can be reduced. Thereby, the increase in the axial direction length of the primary pulley 50 can be suppressed, the primary pulley 50 can be miniaturized, and the belt-type continuously variable transmissions 1-1 to 1-3 can be miniaturized. be able to.

It is a skeleton figure of the belt type continuously variable transmission concerning this invention. FIG. 3 is a cross-sectional view of a main part of the primary pulley according to the first embodiment. 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 hydraulic pressure of a drive hydraulic chamber, and the valve opening state of a valve. It is operation | movement explanatory drawing of the belt type continuously variable transmission at the time of gear ratio change. It is operation | movement explanatory drawing of the belt type continuously variable transmission at the time of gear ratio change. It is a figure which shows the other structural example of the discharge flow control valve concerning Example 1. FIG. It is a figure which shows the structural example of the hydraulic-oil supply valve concerning Example 2, a valve opening / closing apparatus, and a discharge flow control valve. It is operation | movement explanatory drawing of the belt type continuously variable transmission at the time of gear ratio change. It is operation | movement explanatory drawing of the belt type continuously variable transmission at the time of gear ratio change. It is a figure which shows the structural example of the hydraulic-oil supply valve concerning Example 3, a valve opening / closing apparatus, and a discharge flow control valve. It is operation | movement explanatory drawing of the belt type continuously variable transmission at the time of gear ratio change. It is operation | movement explanatory drawing of the belt type continuously variable transmission at the time of gear ratio change.

Explanation of symbols

1-1 to 1-3 Belt type continuously variable transmission 10 Internal combustion engine (drive source)
20 Transaxle 30 Torque converter 40 Forward / reverse switching mechanism 50 Primary pulley (one pulley)
51 Primary pulley shaft 51a Supply side passage 51b Drive side passage 51c, d Communication passage 51e, f Spline 52 Primary fixed sheave 53 Primary movable sheave 53a Cylindrical portion 53b Annular portion 53c Spline 53d Protruding portion 54 Primary partition 54a First flow passage 54b First passage 54b 2 flow path 54c 3rd flow path 54d 1st communication flow path 54e 2nd communication flow path 54f Spline 54g-j Closing member 54k, l Communication path 54m Discharge flow path 54n, o Release path 54p Communication hole 54q Opening 54r Common flow Road 54t Step part 55 Primary hydraulic chamber (positioning hydraulic chamber)
60 Secondary pulley 70 Hydraulic oil supply valve 71 Valve body 72 Valve seat protrusion 73 Valve body elastic member 74 Locking member 80 Valve opening / closing device (valve opening / closing means)
81 Piston 81a Valve body pressing protrusion 82 Drive hydraulic chamber 90 Discharge flow rate control valve 91 Spool 91a Throttle portion 91b Tapered surface 91c First main body portion 91d Second main body portion 91e Tip portion 91f Tip surface 92 Spool elastic member (spool valve closing direction) Pressing means)
DESCRIPTION OF SYMBOLS 100 Final reduction gear 110 Power transmission path 120 Belt 130 Wheel 140 Hydraulic oil supply control apparatus 141 Oil tank 142 Oil pump 143 Pressure regulator 144 Nipping pressure regulating valve 145 Pushing pressure regulating valve 150 ECU
160 Hydraulic oil supply valve 161 Valve body 162 Valve seat protrusion 163 Valve body elastic member 164 Locking member 165 Fixed pin 170 Valve opening / closing device (valve opening / closing means)
171 Piston 171a First communication passage 171b Second communication passage 171c Communication hole 171d End face in the valve closing direction 180 Discharge flow control valve 181 Spool 181a Restriction portion 181b Tapered surface 181c First main body portion 181d Second main body portion 181e Communication hole 181f End face 182 Spool elastic member (spool valve closing direction pressing means)
190 hydraulic oil supply valve 191 valve body 192 valve seat 193 valve body elastic member 194 ring-shaped member 195 locking member 200 guide member 200a guide side taper surface 200b communication portion 200c communication portion 210 discharge flow rate control valve (valve opening / closing means)
211 Spool (piston)
211a Restriction part 211b Spool side taper surface 211c 1st main-body part 211d 2nd main-body part 211e Valve body press protrusion part 211f Piston part 211g End face of valve closing direction T1-T7 Space part

Claims (8)

Two pulleys,
A belt that is wound around each pulley and transmits a driving force from a driving source transmitted to one pulley to the other pulley;
A positioning hydraulic chamber formed on each pulley and pressing the movable sheave toward the fixed sheave by hydraulic pressure;
Among the positioning hydraulic chambers, a hydraulic fluid supply flow path for supplying hydraulic fluid to one positioning hydraulic chamber;
A hydraulic oil discharge passage that communicates with the hydraulic oil supply passage and discharges the hydraulic oil from the one positioning hydraulic chamber;
A hydraulic oil supply valve disposed in the hydraulic oil supply flow path, allowing only the hydraulic oil to be supplied to the one positioning hydraulic chamber, and rotating integrally with the one pulley;
A valve opening / closing means for controlling permission or prohibition of discharge of the hydraulic oil from the one positioning hydraulic chamber by forcibly opening the hydraulic oil supply valve;
The hydraulic oil supply flow valve disposed in the hydraulic oil discharge passage and opened by the valve opening / closing means controls the discharge flow rate of the hydraulic oil discharged from the one positioning hydraulic chamber, and is integrated with the one pulley. A rotating discharge flow control valve;
With
The valve opening / closing means causes a valve body opening direction pressing force in a valve opening direction of the hydraulic oil supply valve to act on the valve body of the hydraulic oil supply valve when the hydraulic oil is supplied to the one positioning hydraulic chamber. A belt type continuously variable transmission. The valve opening / closing means includes
A drive hydraulic chamber to which the hydraulic oil is supplied;
A piston that is slidably supported in the on-off valve direction of the hydraulic oil supply valve, and that acts on the valve body in the valve body opening direction pressing force by the hydraulic pressure of the drive hydraulic chamber;
The belt-type continuously variable transmission according to claim 1, comprising: The discharge flow rate control valve includes a spool that is slidably supported in the on-off valve direction,
3. The belt according to claim 2, wherein the spool controls the discharge flow rate when a spool valve opening direction pressing force in a valve opening direction of the discharge flow rate control valve is acted on by a hydraulic pressure of the drive hydraulic chamber. Type continuously variable transmission.   The hydraulic pressure of the drive hydraulic chamber that causes the valve body to act on the valve body in the valve body opening direction pressing force when supplying the hydraulic oil to the one positioning hydraulic chamber can open the discharge flow rate control valve. The belt-type continuously variable transmission according to claim 3, wherein the belt-type continuously variable transmission is less than the hydraulic pressure of the drive hydraulic chamber.   The belt-type continuously variable transmission according to claim 4, wherein the hydraulic oil supply valve and the discharge flow rate control valve are arranged on the same axis.   The belt-type continuously variable transmission according to claim 5, wherein the spool is the piston.   7. The discharge flow control valve according to claim 3, wherein the spool closing direction pressing force in the valve closing direction of the spool due to the hydraulic pressure of the one positioning hydraulic chamber acts on the spool. The belt type continuously variable transmission described in 1.   The belt-type continuously variable transmission according to claim 7, wherein a tip portion of the spool in the valve opening direction is exposed to one positioning hydraulic chamber.

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