JP4618225B2 - Belt type continuously variable transmission - Google Patents

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 face the two movable sheaves in the axial direction and form a V-shaped groove between the movable sheave and the belt, On the other hand, it is composed of a clamping pressure generating hydraulic chamber that generates a belt clamping pressure. The belt is wound around a V-shaped groove formed in each of the primary pulley and the secondary pulley.

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

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

JP 2001-323978 A

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

  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, a belt wound around each pulley and transmitting a driving force from a driving source, and each pulley are formed by hydraulic pressure. A clamping pressure generating hydraulic chamber that generates a belt clamping pressure with respect to the belt, a partition member constituting one clamping pressure generating hydraulic chamber among the clamping pressure generating hydraulic chambers, and hydraulic oil in one clamping pressure generating hydraulic chamber Valve that opens when hydraulic fluid is supplied or hydraulic fluid is discharged from one clamping pressure generating hydraulic chamber and that rotates integrally with one pulley, and a hydraulic fluid supply / discharge valve is disposed And an actuator that forcibly opens the hydraulic oil supply / discharge valve. The hydraulic oil supply / discharge valve has a valve body and a valve body closing direction pressing force that presses the valve body in a valve closing direction. A valve body elastic member for acting on the valve body, Member is characterized by being arranged in an urged state between the valve arrangement member and the partition member through the valve body.

  According to the present invention, when changing the transmission gear ratio, for example, the hydraulic oil supply / discharge valve is forcibly opened by an actuator to supply hydraulic oil to one clamping pressure generating hydraulic chamber, or to The hydraulic oil is discharged from the pressure generating hydraulic chamber. On the other hand, when the gear ratio is fixed (constant), the hydraulic oil supply / discharge valve is not forcibly opened by the actuator, that is, the hydraulic oil supply / discharge valve is kept closed, and one of the clamping pressures is generated. Do not supply hydraulic oil to the hydraulic chamber. As a result, the hydraulic oil supply / discharge valve is closed, discharge of hydraulic oil from one clamping pressure generating hydraulic chamber is prohibited, and the hydraulic fluid is held in one clamping pressure generating hydraulic chamber. Therefore, even if the position of the movable sheave in the axial direction with respect to the fixed sheave is about to change, the position of the movable sheave in the axial direction with respect to the fixed sheave can be kept constant by changing the hydraulic pressure in one of the clamping pressure generating hydraulic chambers. it can. Accordingly, in order to maintain the position of the movable sheave in the axial direction with respect to the fixed sheave, it is not necessary to supply hydraulic oil to the one clamping pressure generating hydraulic chamber from the outside of the one clamping pressure generating hydraulic chamber. The hydraulic oil can be prevented from leaking from the sliding portion between the movable member and the movable member. Therefore, an increase in the driving loss of the oil pump can be suppressed.

  Further, according to the present invention, since the partition member constituting the one clamping pressure generating hydraulic chamber and the valve disposing member where the hydraulic oil supply / discharge valve is disposed are separate members, the partition member and the valve disposing member are integrated. In comparison, the workability of each member can be improved.

  Further, according to the present invention, the hydraulic oil supply / discharge valve is arranged not on the partition member but on the valve arrangement member which is a separate member from the partition member, and the valve element is interposed between the partition member and the valve arrangement member via the valve element. Since the elastic member is arranged in a biased state, an elastic member locking member such as a snap ring may not be provided. That is, the partition member can be shared as a member for disposing the valve body elastic member in a biased state. Therefore, the number of parts can be reduced, and downsizing and cost reduction can be achieved. Further, the valve body elastic member can be easily assembled.

  According to the present invention, in the belt-type continuously variable transmission, the partition wall member is formed with a recess protruding in the axial direction toward one clamping pressure generating hydraulic chamber, and the valve arrangement member is inserted into the recess. , Fixed in the axial direction.

  According to the present invention, the hydraulic pressure of one clamping pressure generating hydraulic chamber increases, the pressing force acting on the partition member by the hydraulic pressure of one clamping pressure generating hydraulic chamber increases, and the partition member tries to collapse, Since the valve arrangement member is inserted into the recess formed in the partition wall member and fixed in the axial direction, the valve arrangement member can support the partition wall member that is about to fall down. Therefore, the rigidity of the partition member can be improved, and the shift response can be improved.

  Moreover, since the valve arrangement member is inserted into the recess formed in the partition wall member and is fixed in the axial direction, the rigidity of the partition wall member can be improved, so that the partition wall member can be thinned. Therefore, the inertia by the partition member can be reduced. Thereby, transmission of the driving force from the driving source during acceleration can be increased.

  In the present invention, the belt-type continuously variable transmission further includes a partition fixing member that fixes the partition member in the axial direction, and the valve disposing member is sandwiched between the partition member and the partition fixing member. Thus, it is characterized by being fixed with respect to the axial direction.

  According to the present invention, in order to fix the valve arrangement member to the partition member in the axial direction, the valve arrangement member fixing member may not be provided. That is, the partition fixing member that fixes the partition member in the axial direction can be shared as a member for fixing the valve arrangement member in the axial direction. Therefore, the number of parts can be reduced, and downsizing and cost reduction can be achieved.

  Further, according to the present invention, since the valve arrangement member is sandwiched between the partition member and the partition fixing member, the pressing force acting on the partition member due to the hydraulic pressure of one of the clamping pressure generating hydraulic chambers is separated via the valve arrangement member. A fixing member will receive. Therefore, the partition fixing member can support the partition member that is about to fall through the valve arrangement member even if the partition member is about to fall down. Therefore, the rigidity of the partition member can be improved, and the shift response can be improved.

  The belt type continuously variable transmission according to the present invention can hold the hydraulic oil in one of the clamping pressure generating hydraulic chambers when the transmission gear ratio is fixed, so that an increase in driving loss of the oil pump can be suppressed. Play. In addition, since the partition member constituting one of the clamping pressure generating hydraulic chambers and the valve disposing member on which the hydraulic oil supply / discharge valve is disposed are separate members, the workability of each member can be improved. In addition, since the partition member can be shared as a member for arranging the valve body elastic member in a biased state, the number of parts can be reduced, and miniaturization and cost reduction can be achieved. There is an effect that can be.

  Hereinafter, 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, one pulley is a primary pulley and the other pulley is a secondary pulley, but one pulley may be a secondary pulley and the other pulley may be a primary pulley.

  FIG. 1 is a skeleton diagram of a belt type continuously variable transmission according to the present invention. FIG. 2 is a cross-sectional view of the main part of the primary pulley when the transmission gear ratio is fixed. 3A and 3B are diagrams illustrating the torque cam. FIG. 4 is a diagram illustrating a configuration example of the hydraulic oil supply control device. 5 to 8 are explanatory diagrams of the operation of the belt type continuously variable transmission when the gear ratio is changed.

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

  A torque converter 30 is housed inside the transaxle housing 21. On the other hand, inside the case constituted by the transaxle case 22 and the transaxle rear cover 23, a primary pulley 50 and a secondary pulley 60 which are two pulleys constituting the belt type continuously variable transmission 1 according to the present invention, a partition wall A primary partition 54 that is a member, a primary hydraulic chamber 55 that is one clamping pressure generating hydraulic chamber, a valve arrangement member 56, a partition fixing member 58 that fixes the primary partition 54 in the axial direction, and a secondary hydraulic chamber 64 The hydraulic oil supply / discharge valve 70, the actuator 80, and the belt 110 are accommodated. Reference numeral 40 is a forward / reverse switching mechanism, 90 is a final speed reducer that transmits the driving force of the internal combustion engine 10 to the wheels 120, 100 is a power transmission path, 130 is a hydraulic oil supply control device, and 140 is an ECU (Engine Control Unit). is there.

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

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

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

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

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

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

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

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

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

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

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

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

  The primary pulley 50 of the belt type continuously variable transmission 1 is one of the pulleys, and transmits the output torque from the internal combustion engine 10 transmitted through the forward / reverse switching mechanism 40 to the secondary pulley 60 through the belt 110. is there. 1-4, 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, a primary hydraulic chamber 55, a valve arrangement member 56, And a cover member 57.

  As shown in FIG. 2, the primary pulley shaft 51 is rotatably supported by pulley bearings 111 and 112. Further, the primary pulley shaft 51 is formed with a supply / discharge side main passage 51a and a drive side main passage 51b that open only at both ends in the axial direction. Here, the pulley bearing 112 is fixed by being sandwiched between a step portion of the transaxle rear cover 23 and a stopper plate (not shown) fixed to the transaxle rear cover 23.

  The supply / discharge side main passage 51a constitutes a part of the hydraulic oil supply / discharge path for supplying hydraulic oil to the primary hydraulic chamber 55 which is one clamping pressure generating hydraulic chamber and for discharging the hydraulic oil from the primary hydraulic chamber 55. Is. The supply / discharge-side main passage 51 a is formed on the primary fixed sheave side and communicates with an oil passage R <b> 7 (described later) of the hydraulic oil supply control device 130. In the supply / discharge side main passage 51a, the hydraulic oil supplied from the hydraulic oil supply control device 130 to the primary hydraulic chamber 55 flows in, and the hydraulic oil discharged from the primary hydraulic chamber 55 flows in. Accordingly, the supply / discharge-side main passage 51a allows the hydraulic oil supplied or discharged between the hydraulic oil supply control device 130 and the primary hydraulic chamber 55 to pass therethrough. The supply / discharge-side main passage 51a communicates with the shaft-side communication passage 51c in the vicinity of the tip.

  The shaft side communication passage 51c constitutes a part of the hydraulic oil supply / discharge path. The shaft side communication passage 51c communicates with the space portion T1 by having one end portion communicating with the supply / discharge side main passage 51a and the other end portion opening to the outer peripheral surface of the primary pulley shaft 51. Here, the shaft side communication passage 51c is formed at a plurality of locations (for example, three locations) at equal intervals on the circumference.

  The space T1 constitutes a part of the hydraulic oil supply / discharge path. The space portion T <b> 1 is formed between the primary movable sheave 53 and the primary pulley shaft 51. That is, the space T1 is formed between the inner peripheral surface of the primary movable sheave 53, that is, the surface that slides in the axial direction with respect to the primary pulley shaft 51 of the primary movable sheave 53 and the outer peripheral surface of the primary pulley shaft 51. Has been. The space portion T1 has a ring shape, the radially inner end portion (lower end portion in the figure) communicates with each shaft-side communication passage 51c, and the other end portion in the axial direction (the left end portion in the figure). It communicates with the space T2.

  The space portion T2 constitutes a part of the hydraulic oil supply / discharge path. The space portion T <b> 2 is formed by the primary partition wall 54, the primary movable sheave 53, and the primary pulley shaft 51. The space T2 has a ring shape, and the radially inner end (the lower end in the figure) communicates with the space T1, and the radially outer end communicates with the partition wall side communication passage 54e. . That is, the supply / discharge side main passage 51a communicates with the partition wall side communication passage 54e via the shaft side communication passages 51c and the space portions T1 and T2.

  The drive-side main passage 51 b supplies hydraulic oil to a later-described drive hydraulic chamber 81 of the actuator 80 and discharges the hydraulic oil from the drive hydraulic chamber 81. The drive side main passage 51b is formed on the side opposite to the primary fixed sheave side, and the insertion portion 23a of the transaxle rear cover 23 is inserted therein. Here, the insertion portion 23a is formed with a first communication passage 23b having one end communicating with the drive side main passage 51b and the other end communicating with an oil passage R8 (described later) of the hydraulic oil supply control device 130. ing. Accordingly, the drive side main passage 51b communicates with the oil passage R8 of the hydraulic oil supply control device 130 via the first communication passage 23b. In the drive side main passage 51b, the hydraulic oil supplied from the hydraulic oil supply control device 130 to the drive hydraulic chamber 81 flows in, and the hydraulic oil discharged from the drive hydraulic chamber 81 flows in. Accordingly, the hydraulic fluid supplied or discharged between the hydraulic oil supply control device 130 and the drive hydraulic chamber 81 passes through the drive side main passage 51b. Further, the drive-side main passage 51b communicates with the shaft-side communication passage 51d in the vicinity of the tip.

  The shaft-side communication passage 51d constitutes a part of the hydraulic oil supply / discharge path. One end portion communicates with the drive side main passage 51b, and the other end portion opens to the outer peripheral surface of the primary pulley shaft 51, thereby communicating with the space portion T3. Here, the shaft side communication passage 51d is formed at a plurality of locations (for example, three locations) at equal intervals on the circumference.

  The space portion T3 is formed between the primary partition wall 54 and the primary pulley shaft 51. That is, the space portion T3 is formed between the inner peripheral surface of the primary partition wall 54 (the inner peripheral surface of the radially inner protruding portion 54b) and the outer peripheral surface of the primary pulley shaft 51. The space T3 has a ring shape, and the radially inner side (lower end portion in the figure) communicates with each shaft side communication passage 51d, and the radially outer side (upper end portion in the figure) communicates with the partition wall side of the primary partition wall 54. It communicates with the passage 54f. That is, the drive side main passage 51b communicates with the partition wall side communication passage 54f via each shaft side communication passage 51d and the space T3. Note that a communication portion seal member such as a seal ring may be provided between the inner peripheral surface of the primary partition wall 54 and the outer peripheral surface of the primary pulley shaft 51 with the space T3 interposed therebetween.

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

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

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

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

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

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

  As shown in FIG. 2, the primary movable sheave 53 includes a cylindrical portion 53a and an annular portion 53b. The cylindrical portion 53 a is formed around the same rotational axis as the primary pulley shaft 51. The annular portion 53b is formed so as to protrude radially outward from an end portion of the cylindrical portion 53a on the primary fixed sheave side. The primary movable sheave 53 is axially connected to the primary pulley shaft 51 by spline-fitting a spline 53c formed on the inner peripheral surface of the cylindrical portion 53a and a spline 51f formed on the outer peripheral surface of the primary pulley shaft 51. It is slidably supported on. Between the primary fixed sheave 52 and the primary movable sheave 53, that is, between the surface of the primary fixed sheave 52 that faces the primary movable sheave 53 and the surface of the primary movable sheave 53 that faces the primary fixed sheave 52. Primary grooves 110a are formed. A space between the spline 53c and the spline 51f is also included in the space T1. Further, a notch 53e is formed at the other end (right end in the figure) of the primary movable sheave 53 in the axial direction. Therefore, even if the other end portion in the axial direction of the primary movable sheave 53 slides to the other in the axial direction with respect to the primary pulley shaft 51, even if it contacts or is close to the primary partition wall 54, Communication between the space T1 and the space T2 is maintained.

  The primary partition 54 is a partition member and constitutes a primary hydraulic chamber 55 that is one clamping pressure generating hydraulic chamber. As shown in FIG. 2, the primary partition wall 54 is an annular member, and is arranged around the same rotational axis as the primary pulley shaft 51. The primary partition 54 is disposed so as to face the primary fixed sheave 52 in the axial direction with the primary movable sheave 53 interposed therebetween. The primary partition wall 54 is provided so as to rotate integrally with the primary pulley shaft 51 by spline fitting with the primary pulley shaft 51. The primary partition wall 54 is sandwiched between the stepped portion formed on the primary pulley shaft 51 and the partition fixing member 58 fixed to the primary pulley shaft 51 together with the cover member 57 and the pulley bearing 112, so that the primary pulley shaft 51. Is fixed in the axial direction.

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

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

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

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

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

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

  The primary hydraulic chamber 55 is one clamping pressure generating hydraulic chamber, and as shown in FIG. 2, by pressing the primary movable sheave 53 toward the primary fixed sheave side, the primary pulley 50, that is, the V-shaped primary groove 110a. A belt clamping pressure is generated with respect to the belt 110 wound around the belt. The primary hydraulic chamber 55 is a space formed by the primary movable sheave 53 and the primary partition wall 54 (mainly, the concave portion 54c and the radially outer protruding portion 54d). Here, for example, a seal ring is provided between the protrusion 53d of the primary movable sheave 53 and the radially outer protrusion 54d of the primary partition 54, and between the cylindrical portion 53a of the primary movable sheave 53 and the recess 54c of the primary partition 54. A primary hydraulic chamber seal member S1 is provided. Accordingly, the space formed by the primary movable sheave 53 as the primary hydraulic chamber 55 and the primary partition wall 54 is sealed by the primary hydraulic chamber seal member S1.

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

  The valve arrangement member 56 is for arranging the hydraulic oil supply / discharge valve 70 and is formed separately from the primary partition wall 54 which is a partition member. The valve arrangement member 56 has a cylindrical shape, is arranged in the primary partition wall 54, and is fixed to the primary partition wall 54. Here, the valve arrangement member 56 is inserted into a recess 54c formed to protrude toward the primary hydraulic chamber side of the primary partition wall 54, which is a partition member, and is a snap that is a valve arrangement member fixing member that is inserted into and fixed to the recess 54c. It is fixed with respect to the axial direction by a ring 59. Therefore, the primary partition wall 54 is a separate member because the primary partition wall 54 which is a partition member constituting the primary hydraulic chamber 55 which is one clamping pressure generating hydraulic chamber and the valve arrangement member 56 where each hydraulic oil supply / discharge valve 70 is disposed. Compared with the case where the valve arrangement member 56 and the valve arrangement member 56 are integrated, the workability of each member can be improved. Further, when the primary partition wall 54 and the valve arrangement member 56 are integrated, the thickness of the member increases. However, since the primary partition wall 54 and the valve arrangement member 56 are separate members, an increase in the thickness of the member is suppressed. It is possible to reduce the weight. In addition, when the primary partition wall 54 and the valve arrangement member 56 are integrated, it is necessary to remove the thickness of the member in order to reduce the weight. Since it is a separate member, an increase in the number of man-hours during processing can be suppressed. Further, when the primary partition wall 54 and the valve arrangement member 56 are integrated, a high-strength material is used in consideration of sealing performance between a later-described valve body 71 and a valve seat surface 72 of each hydraulic oil supply / discharge valve 70. Although it is necessary, since the primary partition wall 54 and the valve arrangement member 56 are separate members, a material having a lower strength than the material constituting the valve arrangement member 56 can be used as the material constituting the primary partition wall 54, and the low Cost can be reduced.

  The valve arrangement member 56 is formed with a valve arrangement passage 56a extending in the axial direction at a central portion in the radial direction. The valve arrangement passage 56a constitutes a part of the hydraulic oil supply / discharge path. The valve arrangement passage 56a has one end portion (right side end portion in the figure) communicating with the space portion T6, and the other end portion (left end portion in the figure) is closed inside the valve arrangement member 56, so that the arrangement side communication is established. It communicates with the passage 56b. The valve arrangement passage 56 a is formed with an annular valve seat surface 72 that is closed by a valve body 71 (described later) of the hydraulic oil supply / discharge valve 70. Here, the valve seat surface 72 is formed in the vicinity of one end of the valve arrangement passage 56a. The valve arrangement passage 56a is formed corresponding to each partition-side storage portion 54h of the primary partition 54. Accordingly, the valve arrangement passage 56a is formed at a plurality of locations (for example, three locations) at equal intervals on the circumference. A hydraulic oil supply / discharge valve 70 is arranged in each valve arrangement passage 56a.

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

  The space T7 constitutes a part of the hydraulic oil supply / discharge path. The space portion T7 is formed by the valve arrangement member 56 and the primary partition wall 54. The space T7 has a ring shape, and the radially inner end (the lower end in the figure) communicates with each partition wall side communication passage 54e, and the radially outer end communicates with each valve arrangement passage 56a. is doing. That is, here, the hydraulic oil supply / discharge path includes the supply / discharge side main passage 51a, the shaft side communication passages 51c, the space portions T1 and T2, the partition wall side communication passages 54e, the space portion T7, the arrangement side communication passages 56b, The valve arrangement passages 56a, the spaces T6, and the opening holes 54i communicate with each other.

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

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

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

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

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

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

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

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

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

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

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

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

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

  The hydraulic oil supply / discharge valve 70 opens when supplying hydraulic oil to the primary hydraulic chamber 55 that is one clamping pressure generating hydraulic chamber, and also when discharging hydraulic oil from the primary hydraulic chamber 55. It will also open the valve. As shown in FIGS. 2, 5, and 7, the hydraulic oil supply / discharge valve 70 supplies hydraulic oil, which is a hydraulic fluid, from the outside of the primary hydraulic chamber 55, that is, from the primary pulley 50 to the primary hydraulic chamber 55, 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. The hydraulic oil supply / discharge valve 70 is arranged on the valve arrangement member 56. That is, the hydraulic oil supply / discharge valve 70 rotates integrally with the primary pulley 50 that is one pulley.

  The hydraulic oil supply / discharge valve 70 includes a valve body 71, a valve seat surface 72, and a valve body elastic member 73. Each valve element 71 has a spherical shape, is disposed closer to the primary hydraulic chamber than the valve seat surface 72, and has a diameter larger than the inner diameter of the valve seat surface 72. The valve seat surface 72 has a tapered shape that inclines radially outward as it goes toward the primary fixed sheave side (from the other end of the valve arrangement passage 56a to one end). When the valve element 71 contacts the valve seat surface 72, the communication between the valve arrangement passage 56a and the space portion T6 is blocked, that is, the communication between the hydraulic oil supply / discharge path and the primary hydraulic chamber 55 is blocked. The supply / discharge valve 70 is closed. Further, when the valve element 71 is separated from the valve seat surface 72, the valve arrangement passage 56a and the space portion T6 are communicated with each other, that is, the hydraulic oil supply / discharge path and the primary hydraulic chamber 55 are communicated with each other. 70 is opened. That is, each hydraulic oil supply / discharge valve 70 opens in the valve opening direction and closes in the valve closing direction.

  The valve body elastic member 73 is a valve body valve closing direction pressing force generating means, and applies a valve body valve closing direction pressing force to the valve body 71 to press the valve body 71 in the valve closing direction. The valve body elastic member 73 is, for example, a coil spring, and a part thereof is housed in the partition-side storage portion 54 h of the primary partition wall 54. The valve body elastic member 73 is disposed in a state of being urged between the partition wall side storage portion 54 h and the valve body surface 72 via the valve body 71. That is, the valve body elastic member 73 is arranged in a state of being biased between the valve arrangement member 56 and the primary partition wall 54 that is a partition wall member via the valve body 71. Thereby, the valve body elastic member 73 generates a valve closing biasing force, and the valve closing biasing force is an elastic member pressing force in a direction in which the valve body 71 contacts the valve seat surface 72, that is, a valve closing direction. It acts on the valve body 71 as the valve body closing direction pressing force. That is, the valve body 71 is pressed against the valve seat surface 72, and each hydraulic oil supply / discharge valve 70 functions as a check valve. Accordingly, each hydraulic oil supply / discharge valve 70 can be opened in the direction in which the hydraulic oil is supplied to the primary hydraulic chamber 55 which is one clamping pressure generating hydraulic chamber, that is, in the valve opening direction.

  Accordingly, each hydraulic oil supply / discharge valve 70 is disposed not on the primary partition wall 54 which is a partition member but on a valve disposition member 56 which is a separate member from the primary partition wall 54, and the primary partition wall 54 and the valve disposition member 56 via the valve body 71. In order to dispose the valve body elastic member 73 in a biased state, an elastic member locking member such as a snap ring may not be provided. That is, the primary partition wall 54 can be shared as a member for disposing the valve body elastic member 73 in a biased state. Therefore, the number of parts can be reduced, and the belt-type continuously variable transmission 1 can be reduced in size and cost. Further, the valve body elastic member 73 can be easily assembled to the belt type continuously variable transmission 1.

  The actuator 80 forcibly opens the hydraulic oil supply / discharge valve 70. The actuator 80 includes a drive hydraulic chamber 81 and a piston 82. Reference numeral 83 denotes a piston elastic member, 84 denotes a cancel chamber, and 85 denotes an elastic member holding member that holds the piston elastic member.

  The drive hydraulic chamber 81 is supplied with hydraulic oil, and controls the opening / closing valve of the hydraulic oil supply / discharge valve 70 by the pressure of the supplied hydraulic oil, that is, the hydraulic pressure P2 of the drive hydraulic chamber 81. . The drive hydraulic chamber 81 is formed between a pressure receiving member 82 a (described later) of the piston 82, the primary partition wall 54, and the cover member 57. The drive hydraulic chamber 81 is a ring-shaped space, and hydraulic oil is supplied from the hydraulic oil supply control device 130 via the drive-side main passage 51b. Accordingly, a piston valve opening direction pressing force is applied to the piston 82 by the hydraulic pressure P <b> 2 of the drive hydraulic chamber 81. Here, between the pressure receiving member 82a and the primary partition wall 54 and the cover member 57, for example, a drive hydraulic chamber seal member S4 such as a seal ring is provided. In other words, the space formed by the cover member 57 constituting the drive hydraulic chamber 81, the primary partition wall 54, and the pressure receiving member 82a of the piston 82 is sealed by the drive hydraulic chamber seal member S4.

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

  The pressure receiving member 82 a is supported by the primary partition wall 54 and the cover member 57 so as to be slidable in the sliding direction, that is, in the axial direction with respect to the drive hydraulic chamber 81. The pressure receiving member 82a receives the hydraulic pressure P2 of the drive hydraulic chamber 81. Since the pressure receiving member 82a is formed in a ring shape, the pressure receiving area, which is the area where the pressure receiving member 82a receives the hydraulic pressure P2 of the drive hydraulic chamber 81, can be increased. Thereby, even if the hydraulic pressure P2 of the drive hydraulic chamber 81, that is, the pressure of the hydraulic fluid supplied to the drive hydraulic chamber 81 is low, each hydraulic oil supply / discharge valve 70 can be forcibly opened. Accordingly, it is possible to suppress an increase in driving loss of an oil pump 132, which will be described later, of the hydraulic oil supply control device 130. The pressure receiving member 82a is slid in one of the axial directions, that is, one of the sliding directions with respect to the driving chamber hydraulic pressure 81, that is, in the valve opening direction, by the piston valve opening direction pressing force acting by the hydraulic pressure P2 of the driving hydraulic chamber 81. Move. The pressure receiving member 82a has a pressure receiving side storage portion 82c. One end portion (right end portion in the figure) of the pressure receiving side storage portion 82c opens to one side surface (right side surface in the figure) of both side surfaces in the axial direction of the pressure receiving member 82a, and communicates with the cancel chamber 84. The other end (the left end in the figure) is closed inside the pressure receiving member 82a. Here, the pressure-receiving side storage portion 82 c is formed to face each arrangement side storage portion 56 d of the valve arrangement member 56.

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

  The piston elastic member 83 is a piston valve closing direction pressing force generating means. The piston elastic member 83 is arranged in a state of being biased between the arrangement-side storage portion 56d and the pressure-receiving side storage portion 82c. Here, the piston elastic member 83 has a piston urging force even when the piston 82 is positioned in the most other direction of the axial direction which is the other direction among the sliding directions with respect to the drive chamber hydraulic pressure 81, that is, in the most valve closing direction. Arranged to occur. Therefore, the piston elastic member 83 generates a piston urging force, and the piston urging force causes the pressure receiving member 82a of the piston 82 to move in the other direction of the axial direction which is the other direction of the sliding direction with respect to the drive hydraulic chamber 81, that is, The elastic member pressing force in the valve closing direction acts on the pressure receiving member 82a as the piston valve closing direction pressing force. Thus, the piston 82 does not have to slide in the other sliding direction by the valve closing direction pressing force applied to the valve body 71 by the valve closing biasing force generated by the valve body elastic member 73.

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

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

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

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

  Therefore, like the conventional belt-type continuously variable transmission, in order to maintain the position of the primary movable sheave 53 in the axial direction with respect to the primary fixed sheave 52, one hydraulic pressure generating hydraulic chamber is supplied from the hydraulic oil supply control device 130. When the hydraulic oil is continuously supplied to the primary hydraulic chamber 55, hydraulic oil having a predetermined pressure exists in the hydraulic oil supply / discharge path from the hydraulic oil supply control device 130 to the primary hydraulic chamber 55. . The hydraulic oil supply / discharge path includes a plurality of sliding portions between the stationary member and the movable member. When the transmission gear ratio is fixed, hydraulic oil of a predetermined pressure is moved from the sliding portion to the outside of the hydraulic oil supply / discharge path. There was a risk of leakage. The stationary member is a member that does not rotate, slide, or the like among the members constituting the belt type continuously variable transmission 1-1. For example, a transaxle housing 21, a transaxle case 22, and a transaxle rear cover 23 of the transaxle 20. On the other hand, the movable member is a member that rotates, slides, and the like among the members constituting the belt type continuously variable transmission 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 according to the present invention, each hydraulic oil supply / discharge valve 70 is disposed between the primary hydraulic chamber 55 and the sliding portion. That is, when each hydraulic oil supply / discharge valve 70 is maintained in the closed state and the hydraulic oil is held in the primary hydraulic chamber 55, the primary hydraulic chamber 55 and each hydraulic oil supply / discharge valve 70 are interposed. There is no sliding portion between the fixed member and the movable member. Thereby, since it can suppress that hydraulic oil leaks from this sliding part, the increase in the power loss of the oil pump 132 of the hydraulic oil supply control apparatus 130 can be suppressed. In order to forcibly open the hydraulic oil supply / discharge valve 70, the hydraulic pressure P2 of the drive hydraulic chamber 81 of the actuator 80 is used. However, the present invention is not limited to this. Force may be used.

  The piston 82 includes two members, a pressure receiving member 82a and a pressing member 82b. Therefore, when the pressure receiving member 82a tries to rotate relative to the primary pulley 50, the pressing member 82b can be prevented from rotating relative to the primary pulley 50 together with the pressure receiving member 82a. Thereby, the assembly | attachment precision of the pressing member 82b and the sliding support hole 56c of the primary pulley 50 can be improved, and a sealing performance can be improved. Moreover, since the deflection of the pressing member 82b can be suppressed and the generation of stress can be suppressed, the durability can be improved.

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

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

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

  The differential case 91 is rotatably supported by bearings 97 and 98. A ring gear 99 is provided on the outer periphery of the differential case 91, and the ring gear 99 is engaged with the final drive pinion 105. The pinion shaft 92 is attached to the hollow portion of the differential case 91. The differential pinions 93 and 94 are rotatably attached to the pinion shaft 92. The side gears 95 and 96 are meshed with both the differential pinions 93 and 94. The side gears 95 and 96 are fixed to the drive shafts 121 and 122, respectively.

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

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

  The hydraulic oil supply control device 130 supplies hydraulic oil to a hydraulic oil supply portion that requires supply of hydraulic oil in a vehicle on which the belt type continuously variable transmission 1 and the internal combustion engine 10 are mounted. When supplying the hydraulic oil to the primary hydraulic chamber 55 that is one clamping pressure generating hydraulic chamber, the hydraulic oil supply control device 130 supplies the hydraulic oil by the communication between the primary pulley 50 and the hydraulic oil supply / discharge path. The hydraulic oil is supplied to the primary hydraulic chamber 55 via the discharge path. Further, when the hydraulic oil supply control device 130 discharges the hydraulic oil from the primary hydraulic chamber 55, the primary hydraulic chamber 55 and the hydraulic oil supply / discharge path communicate with each other, whereby the primary hydraulic pressure is supplied via the hydraulic oil supply / discharge path. The hydraulic oil is also discharged from the chamber 55. Further, the hydraulic oil supply control device 130 supplies hydraulic oil to the drive hydraulic chamber 81.

  As shown in FIG. 4, the hydraulic oil supply control device 130 supplies hydraulic oil to the primary hydraulic chamber 55, the secondary hydraulic chamber 64, the drive hydraulic chamber 81, and the like. It also controls the gear ratio of the belt type continuously variable transmission 1 by controlling the discharge flow rate. In the figure, the hydraulic oil supply portion excluding the primary hydraulic chamber 55, the secondary hydraulic chamber 64, and the drive hydraulic chamber 81 (the above-described hydraulic oil supply portion and the income within the transaxle 20 such as the belt-type continuously variable transmission 1). The illustration of the lubricated part (for example, a stationary part having a sliding part between the movable parts, a movable part or a movable part having a sliding part between the stationary parts) is omitted. As shown in FIG. 4, the hydraulic oil supply control device 130 includes an oil pan 131, an oil pump 132, a line pressure control device 133, a constant pressure control device 134, a primary hydraulic chamber control device 135, and a drive hydraulic chamber use. A control device 136 and a secondary hydraulic chamber control device 137 are configured.

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

  The oil pump 132 is connected to the cancel chamber 84 via, for example, an oil passage R1 and a branch oil passage R11. Here, the oil pump 132 passes through the oil passage R1, the branch oil passage R11, the second communication passage 23d, the space portion T4, the shaft side communication passage 51e, the space portion T5, the cover side communication passage 57a, and the partition wall side communication passage 54g. Are connected to the primary hydraulic chamber 55. Therefore, hydraulic oil is always supplied from the hydraulic oil supply control device 130 to the cancel chamber 84. Here, although the cancel chamber 84 is connected to the oil pump 132, it may be connected to a return passage for returning oil supplied to a lubrication portion (not shown) to the oil pan 131.

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

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

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

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

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

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

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

  The supply-side flow rate control valve 135c controls the supply flow rate of the hydraulic oil supplied to the primary hydraulic chamber 55. The supply-side flow rate control valve 135c includes a first port 135k, a second port 135l, a third port 135m, a fourth port 135n, a control hydraulic chamber 135o, a spool 135p, and a spool elastic member 135q. ing. As described above, the first port 135k is connected to the second port 135f of the supply side control valve 135a. The second port 135l is connected to the line pressure control device 133 as described above. The third port 135m is connected to the primary hydraulic chamber 55 via an oil passage R7. Here, the third port 135m includes the oil passage R7 and the hydraulic oil supply / discharge passage (supply / discharge side main passage 51a, each shaft side communication passage 51c, space portions T1, T2, each partition wall side communication passage 54e, space portion T7, Each arrangement side communication passage 56b, each valve arrangement passage 56a, the space T6 and each opening hole 54i) are connected to the primary hydraulic chamber 55. The fourth port 135n is connected to the second port 135i of the discharge side control valve 135b as described above. In addition, as shown in the figure, between the second port 135f of the supply-side control valve 135a and the first port 135k of the supply-side flow control valve 135c, the line pressure controller 133 and the second of the supply-side flow control valve 135c An orifice, that is, a throttle is provided between the port 135l and the hydraulic oil flowing into the supply-side flow control valve 135c from the supply-side control valve 135a and the hydraulic oil flowing into the supply-side flow control valve 135c from the line pressure control device 133. The pressure or flow rate may be adjusted.

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

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

  The discharge side flow control valve 135d controls the discharge flow rate of the hydraulic oil discharged from the primary hydraulic chamber 55. The discharge-side flow rate control valve 135d includes a first port 135r, a second port 135s, a third port 135t, a fourth port 135u, a control hydraulic chamber 135v, a spool 135w, and a spool elastic member 135x. ing. As described above, the first port 135r is connected to the second port 135i of the discharge-side control valve 135b. The second port 135s is connected to the oil pan 131 via the merging oil path R52, the merging oil path R51, and the oil path R5. That is, the second port 135s is released to atmospheric pressure. The third port 135t is connected to the primary hydraulic chamber 55 via a branch oil passage R71 and an oil passage R7. In the first embodiment, the third port 135t includes the branch oil passage R71, the oil passage R7, and the hydraulic oil supply / discharge passage (supply / discharge side main passage 51a, each shaft side communication passage 51c, space T1, T2, each partition wall side. The primary hydraulic chamber 55 is connected via the communication passage 54e, the space portion T7, each arrangement side communication passage 56b, each valve arrangement passage 56a, the space portion T6, and each opening hole 54i). As described above, the fourth port 135u is connected to the second port 135f of the supply side control valve 135a. As shown in the figure, an orifice, that is, a throttle is provided between the second port 135i of the discharge-side control valve 135b and the first port 135r of the discharge-side flow control valve 135d, and the discharge is made from the discharge-side control valve 135b. The pressure or flow rate of the hydraulic oil flowing into the side flow rate control valve 135d may be adjusted.

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

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

  The drive hydraulic chamber control device 136 adjusts the hydraulic pressure P2 of the drive hydraulic chamber 81. As described above, the constant pressure PS is introduced from the constant pressure control device 134 into the drive hydraulic chamber control device 136. Further, the drive hydraulic chamber control device 136 is connected to the drive hydraulic chamber 81 via an oil passage R8. Here, the drive hydraulic chamber control device 136 includes the drive hydraulic chamber 81 via the oil passage R8, the first communication passage 23b, the drive side main passage 51b, the shaft side communication passage 51d, the space T3, and the partition wall side communication passage 54f. Connected with. The drive hydraulic chamber control device 136 includes an ON / OFF valve (not shown). The drive hydraulic chamber control device 136 is electrically connected to the ECU 140 and controls ON / OFF of the ON / OFF valve by a control signal from the ECU 140. The drive hydraulic chamber control device 136 is ON-controlled, that is, when the ON / OFF valve is turned ON, the branch oil passage R32 and the oil passage R8 communicate with each other and are introduced into the drive hydraulic chamber control device 136. The constant pressure PS is introduced into the drive hydraulic chamber 81, and the hydraulic pressure P2 in the drive hydraulic chamber 81 becomes the constant pressure PS. On the other hand, when the drive hydraulic chamber control device 136 is OFF-controlled, that is, when the ON / OFF valve is turned OFF, the communication between the branch oil path R32 and the oil path R8 is blocked and the oil path R8 is externally connected. The hydraulic pressure P2 in the drive hydraulic chamber 81 becomes atmospheric pressure. Here, the constant pressure PS is equal to or higher than the hydraulic pressure at which the hydraulic oil supply / discharge valve 70 can be opened by the hydraulic pressure P2 of the drive hydraulic chamber 81 at least when the hydraulic pressure P2 of the drive hydraulic chamber 81 becomes the constant pressure PS. It is.

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

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

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

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

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

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

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

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

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

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

  The drive hydraulic chamber control device 136 is ON-controlled by the ECU 140. Accordingly, the constant pressure PS introduced into the drive hydraulic chamber control device 136 is introduced into the drive hydraulic chamber 81, and the hydraulic pressure P2 of the drive hydraulic chamber 81 becomes the constant pressure PS. The actuator 80 opens a valve element by subtracting a differential pressing force obtained by subtracting a piston closing direction pressing force acting on the piston 82 by the piston elastic member 83 from a piston opening direction pressing force acting on the piston 82 by the hydraulic pressure P2 of the driving hydraulic chamber 81. A valve-direction pressing force is applied to each valve body 71 of each hydraulic oil supply / discharge valve 70. Here, as described above, when the hydraulic pressure P2 of the drive hydraulic chamber 81 becomes a constant pressure PS, the actuator 80 causes the hydraulic oil supply / discharge valve 70 to be driven by the hydraulic pressure P2 of the drive hydraulic chamber 81. Since the valve can be opened, the valve body closing direction pressing force is exceeded. Therefore, as shown in FIG. 5, the hydraulic oil supply / discharge valve 70 is opened by moving the valve body 71 in the valve opening direction with respect to the primary partition wall 54 by the actuator 80.

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

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

  As described above, each hydraulic oil supply / discharge valve 70 is forcibly opened by the actuator 80. Therefore, hydraulic oil introduced into the supply-side flow control valve 135c at the line pressure PL (when an orifice is provided between the line pressure control device 133 and the second port 135l of the supply-side flow control valve 135c, The hydraulic fluid inserted with the pressure adjusted from the line pressure PL) is controlled by the supply flow rate control valve 135c to the supply flow rate based on the reduction gear ratio and the shift speed, as shown by the arrow B in FIG. Then, it flows into the supply / discharge side main passage 51a of the hydraulic oil supply / discharge path via the oil passage R7. The hydraulic fluid that has flowed into the supply / discharge side main passage 51a flows from the supply / discharge side main passage 51a to the shaft side communication passages 51c, the space portions T1 and T2, the partition wall side communication passages 54e, the space portion T7, and the arrangement side communication passages 56b. The primary hydraulic chamber 55 is supplied through the valve arrangement passages 56a, the space T6, and the opening holes 54i. That is, when supplying hydraulic oil to the primary hydraulic chamber 55 which is one clamping pressure generating hydraulic chamber, the hydraulic oil supply / discharge valve 70 is not opened by the supply pressure of the hydraulic oil supplied to the primary hydraulic chamber 55. May be. Therefore, in order to increase the supply pressure of the hydraulic oil supplied to the primary hydraulic chamber 55, an increase in the line pressure PL introduced into the supply-side flow rate control valve 135c by the line pressure control device 133 can be suppressed. . The hydraulic oil P1 in the primary hydraulic chamber 55 is raised by the hydraulic oil supplied via the hydraulic oil supply / discharge valve 70, the pressing force for pressing the primary movable sheave 53 toward the primary fixed sheave side is increased, and the primary movable sheave 53 is Slides toward the primary fixed sheave side in the axial direction. As a result, the contact radius of the belt 110 in the primary pulley 50 is increased, the contact radius of the belt 110 in the secondary pulley 60 is decreased, the transmission ratio is decreased, and the reduced transmission ratio is obtained.

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

  The drive hydraulic chamber control device 136 is ON-controlled by the ECU 140. Accordingly, the constant pressure PS introduced into the drive hydraulic chamber control device 136 is introduced into the drive hydraulic chamber 81, and the hydraulic pressure P2 of the drive hydraulic chamber 81 becomes the constant pressure PS. The actuator 80 opens a valve element by subtracting a differential pressing force obtained by subtracting a piston closing direction pressing force acting on the piston 82 by the piston elastic member 83 from a piston opening direction pressing force acting on the piston 82 by the hydraulic pressure P2 of the driving hydraulic chamber 81. A valve-direction pressing force is applied to each valve body 71 of each hydraulic oil supply / discharge valve 70. Here, as described above, when the hydraulic pressure P2 of the drive hydraulic chamber 81 becomes a constant pressure PS, the actuator 80 causes the hydraulic oil supply / discharge valve 70 to be driven by the hydraulic pressure P2 of the drive hydraulic chamber 81. Since the valve can be opened, the valve body closing direction pressing force is exceeded. Accordingly, as shown in FIG. 7, the hydraulic oil supply / discharge valve 70 is opened by the actuator 80 moving the valve element 71 in the valve opening direction with respect to the primary partition wall 54.

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

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

  As described above, each hydraulic oil supply / discharge valve 70 is forcibly opened by the actuator 80. Therefore, as shown by the arrow D in FIG. 7, the hydraulic oil in the primary hydraulic chamber 55 is transferred from the primary hydraulic chamber 55 to each opening hole 54i of the hydraulic oil supply / discharge path, the space T6, each valve arrangement passage 56a, each arrangement. It flows into the supply / discharge side main passage 51a through the side communication passage 56b, the space portion T7, the partition wall side communication passages 54e, the space portions T2 and T1, and the shaft side communication passages 51c. The hydraulic oil in the primary hydraulic chamber 55 that has flowed into the supply / discharge-side main passage 51a flows into the discharge-side flow rate control valve 135d via the oil passage R7 and the branch oil passage R71, and is increased by the discharge-side flow rate control valve 135d. And the discharge flow rate based on the shift speed and discharged to the outside of the oil pan 131, that is, the primary hydraulic chamber 55 via the merged oil passages R52, R51 and the oil passage R5. Accordingly, the hydraulic oil is discharged from the primary hydraulic chamber 55 via each hydraulic oil supply / discharge valve 70, whereby the hydraulic pressure P1 of the primary hydraulic chamber 55 decreases, and the primary movable sheave 53 is pushed toward the primary fixed sheave side. The pressure decreases, and the primary movable sheave 53 slides in the axial direction on the side opposite to the primary fixed sheave side. Thereby, the contact radius of the belt 110 in the primary pulley 50 decreases, the contact radius of the belt 110 in the secondary pulley 60 increases, the transmission ratio is increased, and the increased transmission ratio is obtained.

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

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

The drive hydraulic chamber control device 136 is OFF-controlled by the ECU 140. Accordingly, the drive hydraulic chamber 81 is released to the atmospheric pressure, and the hydraulic pressure P2 of the drive hydraulic chamber 81 is almost the atmospheric pressure P _OFF . Thereby, only the piston valve closing direction pressing force by the piston elastic member 83 acts on the pressure receiving member 82a of the piston 82, so that the pressure receiving member 82a slides in the other direction, that is, the valve closing direction. As a result, the valve body opening direction pressing force does not act on the valve body 71 of each hydraulic oil supply / discharge valve 70, and only the valve body closing direction pressing force acts, and the valve body 71 is closed. And the hydraulic oil supply / discharge valve 70 is closed.

  The supply-side control valve 135a of the primary hydraulic chamber control device 135 is duty-controlled by the ECU 140 to control the supply flow rate of hydraulic oil to the primary hydraulic chamber 55 by the supply-side flow rate control valve 135c. When duty control is performed by the ECU 140, the supply-side control valve 135a maintains OFF as shown in FIG. 4, and the control hydraulic chamber 135o of the supply-side flow rate control valve 135c and the fourth port 135u of the discharge-side flow rate control valve 135d. To almost atmospheric pressure. Accordingly, the supply-side flow rate control valve 135c is maintained in a state where only the spool closing direction pressing force acts on the spool 135p, so that the spool 135p is positioned in the most other direction in the moving direction. The communication between 135l and the third port 135m is substantially cut off. As a result, the supply-side flow rate control valve 135c is maintained in a substantially closed state, and the supply flow rate of hydraulic oil to the primary hydraulic chamber 55 becomes substantially zero. As a result, the supply of hydraulic oil to the primary hydraulic chamber 55 via each hydraulic oil supply / discharge valve 70 is prohibited.

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

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

  Further, when the speed ratio is changed and when the speed ratio is fixed, the hydraulic pressure P1 of the primary hydraulic chamber 55, which is one clamping pressure generating hydraulic chamber, may increase. Accordingly, the pressing force acting on the primary partition wall 54 may increase due to the hydraulic pressure P1 of the primary hydraulic chamber 55. When the pressing force acting on the primary partition 54 is increased, the primary partition 54, particularly the portion formed integrally with the radially outer protrusion 54d (the radially outer portion of the recess 54c) among the radially outer protrusion 54d and the recess 54c. Tries to fall into the opposite side of the primary hydraulic chamber. However, in the belt-type continuously variable transmission 1 of the present invention, the valve arrangement member 56 is inserted into the recess 54 c formed in the primary partition wall 54 and is fixed to the axial direction by the snap ring 59. Therefore, the valve arrangement member 56 can support the primary partition wall 54 that tends to fall to the opposite side to the primary hydraulic chamber side due to an increase in the hydraulic pressure P1 of the radial primary hydraulic chamber 55. Thereby, the rigidity of the primary partition 54 can be improved, and the shift response of the belt type continuously variable transmission 1 can be improved.

  Further, as described above, the valve arrangement member 56 is inserted into the concave portion 54c formed in the primary partition wall 54, and is fixed in the axial direction by the snap ring 59 that is a fixing member for the valve arrangement member. Since the rigidity of 54 can be improved, the primary partition 54 can be made thin. Therefore, the inertia by the primary partition 54 can be reduced. Thereby, the transmission efficiency of the driving force from the driving source at the time of acceleration of the vehicle on which the belt type continuously variable transmission 1 is mounted, that is, the output torque of the internal combustion engine 10 can be increased.

  In the above embodiment, the valve arrangement member 56 is fixed in the axial direction by the snap ring 59 inserted and fixed to the primary partition wall 54, but the present invention is not limited to this. FIG. 9 is a diagram showing another schematic configuration example of the primary pulley according to the present invention. As shown in the figure, the valve arrangement member 56 may be fixed with respect to the axial direction by being sandwiched between the primary partition wall 54 and the partition wall fixing member 58.

  The valve arrangement member 56 has a fixed protrusion 56e formed on the other side surface (the left side surface in the drawing) of both side surfaces in the axial direction. The fixed protrusion 56e has a cylindrical shape and is formed to protrude from the radially inner end of the other side surface to the other in the axial direction. The valve arrangement member 56 is disposed in the primary partition wall 54 and is fixed by being sandwiched between the primary partition wall 54 and the partition wall fixing member 58. Here, the valve arrangement member 56 is inserted into the recess 54c of the primary partition wall 54, which is a partition member, and the fixed protrusion 56e contacts the cover member 57, so that the recess 54c, the cover member 56, and the pulley bearing 112 are connected. Through the partition wall fixing member 58. Therefore, the valve arrangement member 56 is fixed with respect to the axial direction.

  Further, the fixed protrusion 56e is formed with a notch 56f and an arrangement side communication hole 56g. The notch 56f is formed at the tip end of the fixed protrusion 56e, that is, the other end in the axial direction (the left end of the figure. The notch 56f has a radially inner end connected to each partition wall side. The passage 54f communicates with a space formed by the primary partition 54, the fixed protrusion 56e, and the cover member 57, and the radially outer end communicates with the drive hydraulic chamber 81. The notch 54e. Here, a plurality of locations (for example, 3 locations) are formed at equal intervals on the circumference, so that the drive-side main passage 51b has each shaft-side communication passage 51d, space T3, and each partition-side communication passage 54f. In addition, the drive hydraulic chamber 81 communicates with each other through the notches 56f.

  Further, the arrangement side communication hole 56g has a radially inner end communicating with the space T8 and a radially outer end communicating with the cancel chamber 84. Here, the arrangement side communication holes 56g are formed at a plurality of locations (for example, three locations) at equal intervals on the circumference. The space T8 is formed by the fixed protrusion 56e of the valve arrangement member 56 and the primary partition wall 54. The space T8 has a ring shape, and the radially inner end (the lower end in the figure) communicates with each partition wall communication passage 54g, and the radially outer end communicates with each arrangement-side communication hole 56g. is doing. Accordingly, the cancel-side main passage 23c includes the second communication passages 23d, the space portions T4, the shaft-side communication passages 51e, the space portions T5, the cover-side communication passages 57a, the partition wall-side communication passages 54g, the space portions T8, and the respective portions. The cancel chamber 84 communicates with the arrangement side communication hole 56g.

  As described above, the valve arrangement member 56 is sandwiched between the primary partition wall 54, which is a partition member, and the partition wall fixing member 58 via the cover member 57 and the pulley bearing 112. Therefore, the valve arrangement member 56 is fixed in the axial direction. It is not necessary to provide the snap ring 59 which is a valve body fixing member for this purpose. That is, the partition fixing member 58 that fixes the primary partition 54 in the axial direction can be shared as a member for fixing the valve arrangement member 56 in the axial direction. Therefore, the number of parts can be reduced, and downsizing and cost reduction can be achieved. Moreover, the valve body elastic member 73 can be assembled | attached easily.

  Further, since the valve arrangement member 56 is sandwiched between the primary partition wall 54 and the partition wall fixing member 58, the pressing force acting on the primary partition wall 54 by the hydraulic pressure P1 of the primary hydraulic chamber 55 which is one clamping pressure generating hydraulic chamber is The partition fixing member 58 is received via the member 56. Therefore, the partition fixing member 58 can support the primary partition 54 that tends to fall down on the side opposite to the primary hydraulic chamber side by the increase in the hydraulic pressure P1 of the radial primary hydraulic chamber 55 via the valve arrangement member 56. Thereby, the rigidity of the primary partition 54 can be improved, and the shift response of the belt type continuously variable transmission 1 can be improved.

  Moreover, since the rigidity of the primary partition 54 can be improved as described above, the primary partition 54 can be made thin. Therefore, the inertia by the primary partition 54 can be reduced. Thereby, the transmission efficiency of the driving force from the driving source at the time of acceleration of the vehicle on which the belt type continuously variable transmission 1 is mounted, that is, the output torque of the internal combustion engine 10 can be increased.

  Furthermore, each notch 56f and each arrangement side communication hole 56g that communicate directly with the drive hydraulic chamber 81 and the cancel chamber 84 are formed in the cylindrical fixed protrusion 56. Therefore, the opening for connecting the drive side main passage 51d and the cancel side main passage 23c to the drive hydraulic chamber 81 and the cancel chamber 84 can be formed at an arbitrary position. Thereby, the freedom degree of design can be improved.

It is a skeleton figure of the belt type continuously variable transmission concerning the present invention. It is principal part sectional drawing of the primary pulley at the time of gear ratio fixation. It is a figure which shows a torque cam. It is operation | movement explanatory drawing of a torque cam. It is a figure which shows the structural example of a hydraulic-oil supply control apparatus. It is operation | movement explanatory drawing of the belt type continuously variable transmission at the time of gear ratio change. It is operation | movement explanatory drawing of the belt type continuously variable transmission at the time of gear ratio change. It is operation | movement explanatory drawing of the belt type continuously variable transmission at the time of gear ratio change. It is operation | movement explanatory drawing of the belt type continuously variable transmission at the time of gear ratio change. It is a figure which shows the other schematic structural example of the primary pulley concerning this invention.

Explanation of symbols

1 Belt type continuously variable transmission 10 Internal combustion engine (drive source)
20 Transaxle 23c Cancel side main passage 30 Torque converter 40 Forward / reverse switching mechanism 50 Primary pulley 51 Primary pulley shaft 51a Supply / discharge side main passage 51b Drive side main passage 52 Primary fixed sheave 53 Primary movable sheave 54 Primary partition wall (partition wall member)
54a Cylindrical portion 54b Radially inner projecting portion 54c Recessed portion 54d Radially outer projecting portion 55 Primary hydraulic chamber (one clamping pressure generating hydraulic chamber)
56 Valve arrangement member 56a Valve arrangement passage 56e Fixed protrusion 57 Cover member 57a Cover side communication passage 57b Axial protrusion 57c Restriction protrusion 58 Bulkhead fixing member 59 Snap ring 60 Secondary pulley 64 Secondary hydraulic pressure chamber (other clamping pressure generating hydraulic pressure Room)
DESCRIPTION OF SYMBOLS 70 Hydraulic oil supply discharge valve 71 Valve body 72 Valve seat surface 73 Valve body elastic member 80 Actuator 81 Drive hydraulic chamber 82 Piston 82a Pressure receiving member 82b Press member 83 Piston elastic member 84 Cancel chamber 85 Elastic member holding member 90 Final reduction gear 100 Power Transmission path 110 Belt 112 Pulley bearing 120 Wheel 130 Hydraulic oil supply controller 131 Oil pan 132 Oil pump 133 Line pressure controller 134 Constant pressure controller 135 Primary hydraulic chamber controller 136 Drive hydraulic chamber controller 137 Secondary hydraulic chamber Control device 140 ECU
S1 Primary hydraulic chamber seal member S2, S3 Communication portion seal member S4 Drive hydraulic chamber seal member S5 Cancel chamber seal member

Claims (3)

Two pulleys,
A belt that is wound around each pulley and transmits a driving force from a driving source;
A clamping pressure generating hydraulic chamber formed in each pulley and generating a belt clamping pressure with respect to the belt by hydraulic pressure;
Of each of the clamping pressure generating hydraulic chambers, a partition member constituting one clamping pressure generating hydraulic chamber;
When supplying hydraulic fluid to the one clamping pressure generating hydraulic chamber or when discharging hydraulic fluid from the one clamping pressure generating hydraulic chamber, the hydraulic fluid is opened and rotated integrally with the one pulley. A valve,
A valve arrangement member in which the hydraulic oil supply / discharge valve is arranged;
An actuator for forcibly opening the hydraulic oil supply / discharge valve;
With
The hydraulic oil supply / discharge valve includes a valve body and a valve body elastic member that applies a valve body closing direction pressing force to the valve body to press the valve body in a valve closing direction.
The belt-type continuously variable transmission, wherein the valve body elastic member is arranged in a state of being urged between the valve arrangement member and the partition member via the valve body. The partition member is formed with a recess protruding in a direction toward the one clamping pressure generating hydraulic chamber in the axial direction,
The belt-type continuously variable transmission according to claim 1, wherein the valve arrangement member is inserted into the recess and is fixed with respect to the axial direction. A partition fixing member for fixing the partition member in the axial direction;
The belt-type continuously variable transmission according to claim 1 or 2, wherein the valve arrangement member is fixed in an axial direction by being sandwiched between the partition member and the partition fixing member.

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