JP4924522B2 - 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. There are two types of transmissions: a continuously variable transmission that controls the gear ratio steplessly (continuously) and a stepped transmission that controls the gear ratio stepwise (discontinuously). Here, the continuously variable transmission has two pulleys, namely, a primary pulley to which driving force from a driving source is transmitted, a secondary pulley that changes and outputs output torque transmitted to the primary pulley, and a transmission to the primary pulley. There is a belt-type continuously variable transmission that includes a belt that transmits the generated driving force to a secondary pulley. The primary pulley and the secondary pulley are two pulley shafts arranged in parallel, a primary pulley shaft and a secondary pulley shaft, and two movable sheaves (primary movable sheave, secondary secondary) that slide in the axial direction on each pulley shaft, respectively. Two fixed sheaves (primary fixed sheave and secondary fixed sheave) that face the two movable sheaves in the axial direction and form a V-shaped groove between the movable sheave and the belt It is constituted by 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.

  The clamping pressure generating hydraulic chamber, for example, like the belt type continuously variable transmission described in Patent Document 1, presses the movable sheave to the fixed sheave side by the hydraulic pressure of the clamping pressure generating hydraulic chamber, and This generates belt clamping pressure.

JP 2001-323978 A

  By the way, in the belt-type continuously variable transmission described in Patent Document 1 as described above, for example, by holding the hydraulic pressure of the clamping pressure generating hydraulic chamber at a predetermined hydraulic pressure, the movable sheave is moved in the axial direction with respect to the fixed sheave. In some cases, the movement ratio is restricted and the gear ratio is fixed by holding the position of the movable sheave in the axial direction constant with respect to the fixed sheave. For example, a more appropriate gear ratio can be obtained even when the transmission ratio is fixed. Control was desired.

  Accordingly, an object of the present invention is to provide a belt type continuously variable transmission capable of appropriately controlling a gear ratio.

  In order to achieve the above object, a belt type continuously variable transmission according to a first aspect of the present invention includes two pulleys, a belt wound around each of the pulleys and transmitting a driving force from a driving source, A clamping pressure generating hydraulic chamber that is formed in a pulley and generates a belt clamping pressure with respect to the belt by hydraulic pressure, and a hydraulic oil supply / discharge valve that opens in a direction to supply the hydraulic oil to one of the clamping pressure generating hydraulic chambers; An actuator for forcibly opening the hydraulic oil supply / discharge valve by sliding the piston in one of the sliding directions relative to the drive hydraulic chamber by the hydraulic pressure of the drive hydraulic chamber; When the hydraulic oil supply / discharge valve is opened, the hydraulic oil is supplied to the one clamping pressure generating hydraulic chamber via the hydraulic oil supply / discharge passage, or the hydraulic oil is discharged from the one clamping pressure generating hydraulic chamber. Hydraulic oil supply / discharge control means for controlling the gear ratio at the same time, and determination means for determining whether the hydraulic oil supply / discharge valve can be forcibly opened by the actuator when the gear ratio is changed. The hydraulic oil supply / discharge control means includes the hydraulic oil supply before the valve opening when the determination means determines that the hydraulic oil supply / discharge valve can be forcibly opened by the actuator. The hydraulic pressure of the discharge passage is increased.

  In the belt-type continuously variable transmission according to the second aspect of the invention, the determination means supplies and discharges the hydraulic oil by the actuator based on the hydraulic pressure of the one clamping pressure generating hydraulic chamber and the hydraulic pressure of the driving hydraulic chamber. It is determined whether or not the valve can be forcibly opened.

  In the belt type continuously variable transmission according to a third aspect of the invention, the hydraulic oil supply / discharge control means is determined by the determination means to be able to forcibly open the hydraulic oil supply / discharge valve by the actuator. When the gear ratio is changed to the decreasing side, the hydraulic pressure of the hydraulic oil supply / discharge passage is increased before the valve opening, while when the gear ratio is changed to the increasing side, the opening is started. The hydraulic pressure in the hydraulic oil supply / discharge passage before the valve is prohibited from increasing.

  The belt-type continuously variable transmission according to the invention of claim 4 further comprises tension reducing means for reducing the tension of the belt when the hydraulic oil supply / discharge valve cannot be forcibly opened by the actuator. Features.

  In a belt type continuously variable transmission according to a fifth aspect of the present invention, the tension reducing means reduces the hydraulic pressure of the other clamping pressure generating hydraulic chamber.

  In a belt type continuously variable transmission according to a sixth aspect of the present invention, the tension reducing means reduces output torque from the drive source.

  In the belt-type continuously variable transmission according to the invention according to claim 7, the determination means includes at least an output torque from the driving source, an input rotational speed of a pulley to which a driving force from the driving source is input among the pulleys, It is determined whether or not the hydraulic oil supply / discharge valve can be forcibly opened by the actuator based on one of the hydraulic pressure of the other clamping pressure generating hydraulic chamber and the gear ratio. To do.

  In the belt type continuously variable transmission according to an eighth aspect of the invention, the hydraulic oil supply / discharge control means reduces the hydraulic pressure in the hydraulic oil supply / discharge passage after the hydraulic oil supply / discharge valve is closed. .

  According to the belt type continuously variable transmission according to the present invention, there is provided a determination means for determining whether or not the hydraulic oil supply / discharge valve can be forcibly opened by the actuator when the transmission gear ratio is changed. The discharge control means raises the hydraulic pressure of the hydraulic oil supply / discharge passage before opening the valve when it is determined by the determination means that the hydraulic oil supply / discharge valve can be forcibly opened by the actuator. The gear ratio can be controlled.

  Hereinafter, the present invention will be described in detail with reference to the drawings. In addition, this invention is not limited by the following embodiment. In addition, constituent elements in the following embodiments include those that can be easily assumed by those skilled in the art or that are substantially the same. Here, an internal combustion engine (a gasoline engine, a diesel engine, an LPG engine, or the like) is used as a drive source for generating 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. However, one pulley may be a secondary pulley and the other pulley may be a primary pulley.

(Embodiment 1)
FIG. 1 is a skeleton diagram of a belt-type continuously variable transmission according to Embodiment 1 of the present invention, and FIG. 2 is a diagram when the gear ratio of the belt-type continuously variable transmission according to Embodiment 1 of the present invention is fixed (valve closed state). FIG. 3-1 and FIG. 3-2 are views showing a torque cam of a belt-type continuously variable transmission according to Embodiment 1 of the present invention, and FIG. 4 is Embodiment 1 of the present invention. It is a figure which shows the structural example of the hydraulic-oil supply / discharge control apparatus of the belt-type continuously variable transmission which concerns on.

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

  A torque converter 30 is housed inside the transaxle housing 21. On the other hand, inside the case constituted by the transaxle case 22 and the transaxle rear cover 23, a primary pulley 50 and a secondary pulley 60 which are two pulleys constituting the belt type continuously variable transmission 1-1 according to the first embodiment. A primary hydraulic chamber 55 that is one clamping pressure generating hydraulic chamber, a secondary hydraulic chamber 64 that is the other clamping pressure generating hydraulic chamber, a hydraulic oil supply / discharge valve 70, an actuator 80, and a belt 110. ing. In addition, 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 / discharge control device shown in FIG. Engine Control Unit), 150 is an input rotation speed sensor, and 160 is an output rotation speed sensor.

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

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

  The turbine 32 is disposed so as to face the pump 31. The turbine 32 is disposed inside the hollow shaft 36 and is attached to an input shaft 38 that can rotate 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 portion, and the hydraulic fluid is supplied as the hydraulic fluid from the hydraulic oil supply / discharge control device 130 that supplies the hydraulic oil to the hydraulic oil supply portion. Yes.

  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. Then, the output torque (engine torque) from the internal combustion engine 10 transmitted to the turbine 32 is transmitted to the input shaft 38. That is, the torque converter 30 increases the output torque from the internal combustion engine 10 via the input shaft 38 and transmits it to the belt type continuously variable transmission 1-1. In the above, the stator 33 can change the flow of hydraulic fluid circulating between the pump 31 and the turbine 32 to obtain a predetermined torque characteristic.

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

  As shown in FIG. 1, the forward / reverse switching mechanism 40 transmits the output torque (engine torque) transmitted from the internal combustion engine 10 via the torque converter 30 to the primary pulley 50 of the belt type continuously variable transmission 1-1. To do. 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 a hydraulic oil supply / discharge 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 / discharge control device 130 to a brake piston (not shown) which is a hydraulic oil supply portion. When the reverse brake 43 is ON, the switching carrier 47 is fixed to the transaxle case 22 so that each pinion 45 cannot revolve around the sun gear 44. When the reverse brake 43 is OFF, the switching carrier 47 is released, and each pinion 45 can revolve around the sun gear 44.

  The primary pulley 50 of the belt-type continuously variable transmission 1-1 is one pulley, and the output torque from the internal combustion engine 10 transmitted through the forward / reverse switching mechanism 40 is transmitted to the secondary pulley 60 by the belt 110. Is. As shown in FIGS. 1 and 2, the primary pulley 50 includes a primary pulley shaft 51, a primary fixed sheave 52, a primary movable sheave 53, a primary partition wall 54, a primary hydraulic chamber 55, and a cover member 56. Has been.

  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 are opened 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 passage that supplies the hydraulic oil to the primary hydraulic chamber 55 that is one clamping pressure generating hydraulic chamber and discharges the hydraulic oil from the primary hydraulic chamber 55. Is. The supply / discharge-side main passage 51a is formed on the primary fixed sheave side and communicates with an oil passage R7 (described later) of the hydraulic oil supply / discharge control device 130. In the supply / discharge side main passage 51a, hydraulic oil supplied from the hydraulic oil supply / discharge control device 130 to the primary hydraulic chamber 55 flows in, and 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 / discharge 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 passage. 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. In the first embodiment, 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 passage. 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 cylindrical shape, and its radially inner end (lower end in the figure) communicates with each shaft-side communication passage 51c, and the other end in the axial direction (the left end in the figure). It communicates with the space T2.

  The space T2 constitutes a part of the hydraulic oil supply / discharge passage. The space portion T <b> 2 is formed between the primary partition wall 54, the primary movable sheave 53, and the primary pulley shaft 51. That is, the space T2 includes an inner peripheral surface (a radially inner surface of the portion where the hydraulic oil supply / discharge valve 70 is formed) and the outer peripheral surface of the primary movable sheave 53 (the outer periphery of the primary movable sheave 53). It is formed between the outer peripheral surface of the primary pulley shaft 51 and the outer peripheral surface of the other side (left side in the figure) in the axial direction of the seal member S1 for the primary hydraulic chamber described later. 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-side communication passage 54b of the primary partition 54. Communicate. That is, the supply / discharge side main passage 51a communicates with the partition wall side communication passage 54b 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 communicates with an oil passage R8 described later of the hydraulic oil supply / discharge control device 130. In the drive side main passage 51b, the hydraulic oil supplied from the hydraulic oil supply / discharge control device 130 to the drive hydraulic chamber 81 flows in, and the hydraulic oil discharged from the drive hydraulic chamber 81 flows in. Therefore, the hydraulic fluid supplied or discharged between the hydraulic oil supply / discharge control device 130 and the drive hydraulic chamber 81 passes through the drive-side main passage 51b. Further, the drive-side main passage 51b communicates with the shaft-side communication passage 51d in the vicinity of the tip.

  The shaft-side communication passage 51d communicates with the space T3 by having one end communicating with the drive-side main passage 51b and the other end opening on the outer peripheral surface of the primary pulley shaft 51. In the first embodiment, 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 T <b> 3 is formed between the inner peripheral surface (innermost peripheral surface) of the primary partition wall 54 and the outer peripheral surface of the primary pulley shaft 51. The space portion 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 communication passage 54e. is doing. That is, the drive side main passage 51b communicates with the partition wall side communication passage 54e 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.

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

  As shown in FIG. 2, the primary movable sheave 53 includes a cylindrical portion 53a and an annular portion 53b. The cylindrical portion 53 a is formed around the same rotational axis as the primary pulley shaft 51. The annular portion 53b is formed so as to protrude radially outward from the end portion of the cylindrical portion 53a on the primary fixed sheave side. The primary movable sheave 53 is axially connected to the primary pulley shaft 51 by spline-fitting a spline 53c formed on the inner peripheral surface of the cylindrical portion 53a and a spline 51e 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 51e 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 wall 54 is a member in which the hydraulic oil supply / discharge valve 70 is disposed and the drive hydraulic chamber 81 of the primary pulley 50 that is one pulley. As shown in FIG. 2, the primary partition wall 54 is an annular member, and is arranged around the same rotational axis as the primary pulley shaft 51. The primary partition 54 is disposed so as to face the primary fixed sheave 52 in the axial direction with the primary movable sheave 53 interposed therebetween. The primary partition wall 54 is provided so as to rotate integrally with the primary pulley shaft 51 by spline fitting with the primary pulley shaft 51.

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

  The partition wall side communication passage 54b constitutes a part of the hydraulic oil supply / discharge passage. The partition wall side communication passage 54b has one end portion (end portion in the radial direction in the figure) communicating with the valve arrangement passage 54a, and the other end portion (in the radial direction in the drawing) on the inner peripheral surface of the primary partition wall 54. Open and communicate with the space T2. In the first embodiment, the valve arrangement passage 54a and the partition wall side communication passage 54b are formed at a plurality of locations (for example, three locations) at equal intervals on the circumference as shown in FIG. Accordingly, the supply / discharge side main passage 51a communicates with the primary hydraulic chamber 55 via the shaft side communication passages 51c, the space portions T1 and T2, the partition wall side communication passages 54b, and the valve arrangement passages 54a. That is, in the first embodiment, the hydraulic oil supply / discharge passage is configured by the supply / discharge side main passage 51a, the shaft side communication passages 51c, the spaces T1 and T2, the partition wall side communication passage 54b, and the valve arrangement passage 54a. In the first embodiment, the partition wall side communication passage 54b is formed such that the radially inner end extends in the other direction (the left side in the figure) in the axial direction.

  The primary partition wall 54 is formed with a sliding support hole 54c on the same axis as each valve arrangement passage 54a. Each sliding support hole 54c has one end portion (right end portion in the figure) communicating with the valve arrangement passage 54a and the other end portion (left end portion in the figure) circumferentially on the outer peripheral surface of the primary partition wall 54. Are opened in a notch 54d formed continuously. In the first embodiment, the other end portion of each sliding support hole 54c is opened to a surface facing one side surface (the right side surface in the figure) in the axial direction of a pressure receiving member 82a of a piston 82 described later of the actuator 80. ing.

  The partition wall side communication passage 54e has one end portion (an end portion on the radially outer side in the figure) opened to the cutout portion 54d, and the other end portion (the inner side in the radial direction in the figure) is the inner peripheral surface (the outermost surface) of the primary partition wall 54. It opens to the inner peripheral surface) and communicates with the space T3. In the first embodiment, the other end of the partition wall side communication passage 54e is opened to a surface constituting the drive hydraulic chamber 81 in the outer peripheral surface of the primary partition wall 54 constituting the notch 54d. In the first embodiment, the partition-side communication passage 54e is formed at a plurality of locations (for example, three locations) at equal intervals on the circumference. Accordingly, the drive-side main passage 51b communicates with the notch portion 54d, that is, the drive hydraulic chamber 81 via each shaft-side communication passage 51d, the space T3, and the partition wall-side communication passage 54e.

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

  The primary hydraulic chamber 55 is supplied with hydraulic oil from the hydraulic oil supply / discharge control device 130 that has flowed into the supply / discharge side main passage 51 a of the primary pulley shaft 51. The primary hydraulic chamber 55 slides the primary movable sheave 53 in the axial direction by the pressure of the hydraulic oil supplied from the hydraulic oil supply / discharge control device 130, that is, the hydraulic pressure P1 of the primary hydraulic chamber 55, and makes the primary movable sheave 53 primary. The fixed sheave 52 is approached or separated. 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 1-1.

  The cover member 56 is a member that constitutes the drive hydraulic chamber 81. The cover member 56 has a ring shape and is disposed between the primary partition wall 54 and the pulley bearing 112, that is, in the notch 54d. The cover member 56 has a radially inner end in contact with the outer peripheral surface of the primary partition wall 54 and a radially outer end in contact with the pressure receiving member 82a of the piston 82 via the piston seal member S2. The cover member 56 is formed with a circumferentially continuous seal surface at the radially inner end and the inner peripheral surface of the primary partition wall 54. Here, in Embodiment 1, the sealing surface is formed in the axial direction.

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

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

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

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

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

  The secondary hydraulic chamber 64 is supplied with hydraulic oil from the hydraulic oil supply / discharge control device 130 that has flowed into a hydraulic oil passage (not shown) of the secondary pulley shaft 61 via a hydraulic fluid supply hole (not shown). The hydraulic fluid is supplied to the secondary hydraulic chamber 64, and the secondary movable sheave 63 is slid in the axial direction by the pressure of the hydraulic fluid supplied from the hydraulic fluid supply / discharge control device 130, that is, the hydraulic pressure of the secondary hydraulic chamber 64. The sheave 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. And a plurality of disk-shaped discs arranged between the first engaging portion 63b and the second engaging portion 67a. The transmission member 68 is configured.

  The intermediate member 67 is formed integrally with the secondary partition wall 65 or is fixed to the secondary partition wall 65, and can rotate relative to the secondary pulley shaft 61 and the secondary movable sheave 63 on the secondary pulley shaft 61 by the pulley bearing 113 and the bearing 115. It is supported by. The intermediate member 67 is fixed to the input shaft 101 of the power transmission path 100 by, for example, spline fitting. That is, the output torque 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. 3B. The portion 63b and the second engaging portion 67a are changed to a separated state. As a result, the torque cam 66 generates a belt clamping pressure with respect to the belt 110 in the secondary pulley 60.

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

  The hydraulic oil supply / discharge valve 70 is a valve that opens in a direction to supply hydraulic oil to the primary hydraulic chamber 55 that is one clamping pressure generating hydraulic chamber. The hydraulic oil supply / discharge valve 70 is forcibly opened by the actuator 80 when supplying hydraulic oil to the primary hydraulic chamber 55 that is one clamping pressure generating hydraulic chamber and when discharging hydraulic oil from the primary hydraulic chamber 55. It is something to be made. As shown in FIG. 2, the hydraulic oil supply / discharge valve 70 is an operation that is a working fluid from the outside of the primary hydraulic chamber 55 that is one clamping pressure generating hydraulic chamber, that is, from the outside of the primary pulley 50 to the primary hydraulic chamber 55. The oil is supplied, the hydraulic oil is discharged from the primary hydraulic chamber 55 to the outside of the primary pulley 50, and the hydraulic oil in the primary hydraulic chamber 55 is retained. In the first embodiment, the hydraulic oil supply / discharge valve 70 is disposed in each valve arrangement passage 54a formed in the primary partition wall 54 of the primary pulley 50 which is one pulley (the hydraulic oil supply / discharge valve 70 is A plurality of locations (for example, 3 locations) are formed at equal intervals on the circumference). That is, each hydraulic oil supply / discharge valve 70 rotates integrally with the primary pulley 50 that is one pulley.

  Each hydraulic oil supply / discharge valve 70 is a ball type check valve, and includes a valve body 71, a valve seat surface 72, a valve body holding member 73, a valve body elastic member 74, and a snap ring 75. ing. 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 disposition passage 54a to one end). When the valve body 71 contacts the valve seat surface 72, the communication between the valve arrangement passage 54a and the primary hydraulic chamber 55 is shut off, and each hydraulic oil supply / discharge valve 70 is closed. Further, when the valve element 71 is separated from the valve seat surface 72, the valve arrangement passage 54a and the primary hydraulic chamber 55 are communicated with each other, and each hydraulic oil supply / discharge valve 70 is opened. That is, each hydraulic oil supply / discharge valve 70 opens in the valve opening direction and closes in the valve closing direction.

  The valve body holding member 73 is disposed at a position facing the valve seat surface 72 with the valve body 71 interposed therebetween. The valve body holding member 73 has an annular shape and is supported on the outer peripheral surface of the primary partition wall 54 on the primary hydraulic chamber side so as to be slidable in the axial direction. The valve body holding member 73 holds each valve body 71 by always contacting the valve body 71 of each hydraulic oil supply / discharge valve 70 by the valve closing biasing force generated by the valve body elastic member 74. Here, on the surface of the primary partition wall 54 facing the valve body holding member 73, each valve body 71 is in contact with each valve seat surface 72, and between the valve body holding member 73 and the primary partition wall 54. A recess 54f that is continuous in the circumferential direction is formed so that a gap is formed in the outer periphery.

  The valve body elastic member 74 is a valve body valve closing direction pressing force generating means. The valve body elastic member 74 is, for example, a disc spring, a snap ring 75 inserted and fixed to the outer peripheral surface of the primary partition wall 54 on the primary hydraulic chamber side via each valve body 71 and the valve body holding member 73, and a valve seat. It arrange | positions in the state urged | biased between the surfaces 72. FIG. Accordingly, the valve body elastic member 74 generates a valve closing biasing force, and the valve body elastic member 74 is closed as a valve body valve closing direction pressing force that is an elastic member pressing force in a direction in which the valve body 71 is in contact with the valve seat surface 72. A force acts on each valve body 71. As a result, each valve element 71 is pressed against each 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 of supplying hydraulic oil to the primary hydraulic chamber 55, which is one clamping pressure generating hydraulic chamber, that is, in the valve opening direction.

  The actuator 80 forcibly opens each hydraulic oil supply / discharge valve 70. The actuator 80 includes a drive hydraulic chamber 81 and a piston 82.

  The drive hydraulic chamber 81 is supplied with hydraulic oil, and controls the open / close valves of the hydraulic oil supply / discharge valves 70 by the pressure of the supplied hydraulic oil, that is, the hydraulic pressure P2 of the drive hydraulic chamber 81. is there. The drive hydraulic chamber 81 is formed between the piston 82, the primary partition wall 54, and the cover member 56 in the notch 54d. The drive hydraulic chamber 81 is a ring-shaped space, and hydraulic fluid is supplied from the hydraulic fluid supply / discharge control device 130 via the drive-side main passage 51b. Therefore, the piston valve opening direction pressing force acts on the piston 82 by the hydraulic pressure P <b> 2 of the drive hydraulic chamber 81.

  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 each hydraulic oil. The discharge valve 70 is forcibly opened. The piston 82 includes a pressure receiving member 82a and a pressing member 82b.

  The pressure receiving member 82a is slidably supported with respect to the drive hydraulic chamber 81 by a primary partition wall 54 and a cover member 56 which are support members in a sliding direction, that is, an axial direction. 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. Therefore, 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 / discharge 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 hydraulic chamber 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.

  Here, a piston seal member S2 such as an O-ring made of rubber is provided between the primary partition wall 54 and the cover member 56, which are support members, and the pressure receiving member 82a. That is, in the notch 54d, the space formed by the primary partition wall 54, the cover member 56, and the pressure receiving member 82a constituting the drive hydraulic chamber 81 is sealed by the piston seal member S2.

  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 54c of the primary partition wall 54, and is supported so as to be slidable in the axial direction with respect to each sliding support hole 54c. That is, each pressing member 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. . Note that the actuator 80 generates a piston closing direction pressing force for causing the piston 82 that slides in one of the sliding directions to slide in the other in the sliding direction by the hydraulic pressure P2 of the drive hydraulic chamber 81. Valve direction pressing force generation means may be provided separately. In this case, it is not necessary to slide the piston 82 in the other of the sliding directions by the valve closing direction pressing force applied to the valve element 71 by the valve closing biasing force generated by the valve element elastic member 74.

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

  In the first embodiment, each hydraulic oil supply / discharge valve 70 is an actuator regardless of whether hydraulic oil is supplied to the primary hydraulic chamber 55 that is one clamping pressure generating hydraulic chamber or when hydraulic oil is discharged from the primary hydraulic chamber 55. 80 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 valve opening direction pressing force acting on the piston 82 becomes the above valve body opening direction pressing force, and each valve body 71 Act on each. Accordingly, each hydraulic oil supply / discharge valve 70 moves in the valve opening direction with respect to the valve seat surface 72 when the valve body valve opening direction pressing force exceeds the valve body closing direction pressing force. The hydraulic oil supply / discharge valve 70 is forcibly opened. The valve body closing direction pressing force is closed to each valve body 71 by the elastic member pressing force acting on each valve body 71 by the valve closing biasing force generated by the valve body elastic member 74 and the hydraulic pressure P1 of the primary hydraulic chamber 55. Hydraulic oil closing direction pressing force acting in the valve direction.

  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 as long as the valve body opening direction pressing force acting on the valve body 71 does not exceed the valve body opening direction pressing force. The hydraulic oil in the primary hydraulic chamber 55 that is a hydraulic chamber is reliably held in the primary hydraulic chamber 55.

  Therefore, as in 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 pressure is supplied from the hydraulic oil supply / discharge control device 130. When hydraulic oil is continuously supplied to the primary hydraulic chamber 55, which is a chamber, hydraulic oil must be present at a predetermined pressure in the hydraulic oil supply / discharge passage from the hydraulic oil supply / discharge control device 130 to the primary hydraulic chamber 55. It becomes. The hydraulic oil supply / discharge passage includes a plurality of sliding portions between the stationary member and the movable member. When the transmission gear ratio is fixed, the hydraulic oil at a predetermined pressure flows from the sliding portion to the outside of the hydraulic oil supply / discharge passage. 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 in the member constituting the belt type continuously variable transmission 1-1. For example, the primary pulley shaft 51 or the like. Therefore, the sliding portion includes, for example, a portion where the primary pulley shaft 51 rotates with respect to the transaxle housing 21, the transaxle case 22, the transaxle rear cover 23, and the like of the transaxle 20.

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

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

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

  The belt 110 of the belt type continuously variable transmission 1-1 transmits the output torque 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 / discharge control device 130 supplies hydraulic oil to a hydraulic oil supply portion that requires supply of hydraulic oil in a vehicle in which the belt type continuously variable transmission 1-1 and the internal combustion engine 10 are mounted. . When each hydraulic oil supply / discharge valve 70 is forcibly opened by the actuator 80, the hydraulic oil supply / discharge control device 130 supplies hydraulic oil to the primary hydraulic chamber 55 which is one clamping pressure generating hydraulic chamber, or primary The gear ratio is controlled by discharging hydraulic oil from the hydraulic chamber 55. In addition, the hydraulic oil supply / discharge control device 130 supplies hydraulic oil to the drive hydraulic chamber 81.

  The hydraulic oil supply / discharge control device 130 is hydraulic oil supply / discharge control means, and supplies hydraulic oil to the primary hydraulic chamber 55, the secondary hydraulic chamber 64, the drive hydraulic chamber 81, etc., as shown in FIG. The transmission ratio of the belt type continuously variable transmission 1-1 is also controlled by controlling the supply flow rate of hydraulic oil and the discharge flow rate of hydraulic oil. In the figure, the hydraulic oil supply portion (excluding the above-described hydraulic oil supply portion and the hydraulic oil supply portion of the internal combustion engine 10 (for example, movable parts) is excluded from the primary hydraulic chamber 55, the secondary hydraulic chamber 64, and the drive hydraulic chamber 81. The illustration of a stationary part having a sliding part in between, a movable part or a movable part having a sliding part between stationary parts, a heated part or a driving device driven by oil) is omitted. The hydraulic oil supply / discharge 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, a drive hydraulic chamber control device 136, and a secondary. And a hydraulic chamber control device 137.

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

  The line pressure control device 133 adjusts the discharge pressure Pout of the oil pump 132 so that it becomes a predetermined line pressure PL. That is, the line pressure control device 133 adjusts the hydraulic pressure of the oil passage R1, which is the input hydraulic pressure, that is, the discharge pressure Pout, and sets the output hydraulic pressure from the line pressure control device 133 as the line pressure PL. The line pressure control device 133 is connected to a second port 135l of a supply-side flow rate control valve 135c, which will be described later, of the primary hydraulic chamber control device 135 via an oil passage R2, and is constant via an oil passage R2 and a branch oil passage R21. It is connected to the pressure control device 134, and is connected to the secondary hydraulic chamber control device 137 via the oil passage R2 and the branch oil passage R22. Therefore, the line pressure PL adjusted by the line pressure control device 133 is the second port 135l of the supply-side flow rate control valve 135c, the constant pressure control device 134, the drive hydraulic chamber control device 136, and the secondary hydraulic chamber control device 137. To be introduced. 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 an electromagnetic valve (not shown), for example, a linear solenoid valve, that regulates the pressure of the hydraulic oil discharged from the oil pump 132. The line pressure control device 133 is electrically connected to the ECU 140, and the line pressure PL can be regulated by controlling the valve opening degree of the linear solenoid valve by a control signal from the ECU 140.

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

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

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

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

  When the discharge-side control valve 135b is turned on, the first port 135h and the second port 135i communicate with each other. Accordingly, the constant pressure PS introduced into the discharge side control valve 135b is introduced into the first port 135r of the discharge side flow control valve 135d (see FIG. 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. Therefore, the discharge-side control valve 135b can regulate the control hydraulic chamber 135v of the discharge-side flow control valve 135d between a constant pressure PS and atmospheric pressure by a control signal from the ECU 140.

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

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

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

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

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

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

  The drive hydraulic chamber control device 136 adjusts the hydraulic pressure P2 of the drive hydraulic chamber 81. As described above, the constant pressure PS is introduced from the constant pressure control device 134 into the drive hydraulic chamber control device 136. Further, the drive hydraulic chamber control device 136 is connected to the drive hydraulic chamber 81 via an oil passage R8. In the first embodiment, the drive hydraulic chamber control device 136 is connected to the drive hydraulic chamber 81 via the oil passage R8 and the drive side main passage 51b. The drive hydraulic chamber control device 136 includes an ON / OFF valve (not shown). The drive hydraulic chamber control device 136 is electrically connected to the ECU 140 and controls ON / OFF of the ON / OFF valve by a control signal from the ECU 140. When the drive hydraulic chamber control device 136 is ON-controlled, that is, when the switching valve is turned on, the branch oil passage R32 and the oil passage R8 communicate with each other, and a constant pressure introduced into the drive hydraulic chamber control device 136 is reached. PS is introduced into the drive hydraulic chamber 81, and the hydraulic pressure P2 of the drive hydraulic chamber 81 becomes a 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.

  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 / discharge 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 / discharge control device 130 controls 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, thereby 80 forcibly opens each hydraulic oil supply / discharge valve 70, supplies hydraulic oil to the primary hydraulic chamber 55, which is one clamping pressure generating hydraulic chamber, or discharges hydraulic oil from the primary hydraulic chamber 55, and at least the belt It controls the gear ratio of the continuously variable transmission 1-1.

  The input rotation speed sensor 150 also constitutes a part of the gear ratio detection means. The input rotation speed sensor 150 detects an input rotation speed Nin of a pulley to which driving force from a driving source is input, that is, a primary pulley 50 to which output torque from the internal combustion engine 10 is input. The input rotation speed sensor 150 detects the rotation speed of the primary pulley shaft 51 of the primary pulley 50 and sets the rotation speed of the primary pulley shaft 51 as the input rotation speed Nin. The input rotation speed sensor 150 is connected to the ECU 140 as shown in FIG. Accordingly, the input rotational speed Nin detected by the input rotational speed sensor 150 is output to the ECU 140. The input rotational speed sensor 150 is not limited to the input rotational speed Nin that is the rotational speed of the primary pulley shaft 51. For example, the input rotational speed sensor 150 detects the engine rotational speed Ne of the internal combustion engine 10 and inputs it from the engine rotational speed Ne. The rotational speed Nin may be calculated.

  The output rotation speed sensor 160 also constitutes a part of the gear ratio detection means. The output rotation speed sensor 160 detects the output rotation speed Nout of the secondary pulley 60 to which the driving force from the drive source input to the primary pulley 50, that is, the output torque of the internal combustion engine 10 is transmitted via the belt 110. is there. In the first embodiment, the output rotation speed sensor 160 detects the rotation speed of the secondary pulley shaft 61 of the secondary pulley 60 and sets the rotation speed of the secondary pulley shaft 61 as the output rotation speed Nout. The output rotation speed sensor 160 is connected to the ECU 140 as shown in FIG. Therefore, the output rotation speed Nout detected by the output rotation speed sensor 160 is output to the ECU 140.

  Here, the ratio between the input rotational speed Nin detected by the input rotational speed sensor 150 and the output rotational speed Nout detected by the output rotational speed sensor 160 is the speed ratio of the belt type continuously variable transmission 1-1. . That is, the input rotation speed sensor 150 and the output rotation speed sensor 160 detect the gear ratio. Therefore, the ECU 140 receives the input speed Nγ detected by the input speed sensor 150 and the output speed Nout detected by the output speed sensor 160, so that the detected gear ratio γ is input. It becomes.

  Next, the operation of the belt type continuously variable transmission 1-1 according to the first embodiment will be described. First, general forward and reverse travel of the vehicle will be described. When the driver selects the 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 / discharge control device 130. The forward / reverse switching mechanism 40 is controlled. As a result, the input shaft 38 and the primary pulley shaft 51 are directly connected. That is, the sun gear 44 and the ring gear 46 of the planetary gear device 41 are directly connected, the primary pulley shaft 51 is rotated in the same direction as the rotation direction of the crankshaft 11 of the internal combustion engine 10, and the output torque from the internal combustion engine 10 is converted to the primary pulley. 50. The output torque from the internal combustion engine 10 transmitted to the primary pulley 50 is transmitted to the secondary pulley 60 via the belt 110 and rotates the secondary pulley shaft 61 of the secondary pulley 60.

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

  On the other hand, when the driver selects the reverse position by a shift position device (not shown) provided in the vehicle, the ECU 140 turns off the forward clutch 42 by the hydraulic oil supplied from the hydraulic oil supply / discharge control device 130, and reverse brakes. 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 that meshes with the ring gear 46 also rotates in the same direction as the input shaft 38, and the sun gear 44 that meshes with each pinion 45 moves to the input shaft 38. And rotate in the opposite direction. 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 1-1 is controlled via the hydraulic oil supply / discharge control device 130 so that the operating state of the internal combustion engine 10 is optimized. Here, the control of the gear ratio of the belt-type continuously variable transmission 1-1 includes changing the gear ratio and fixing the gear shift (gear ratio γ steady). The change of the gear ratio and the fixing of the gear ratio are performed by controlling the primary hydraulic chamber control device 135, the drive hydraulic chamber control device 136, and the secondary hydraulic chamber control device 137. The gear ratio control using the hydraulic oil supply / discharge control device 130 is performed every control cycle.

  Here, FIG. 5 is a cross-sectional view of the main part of the primary pulley when the gear ratio of the belt-type continuously variable transmission according to the first embodiment of the present invention is reduced (during upshift), and FIG. 6 is the first embodiment of the present invention. FIG. 7 is a diagram showing the operation of the hydraulic oil supply / discharge control apparatus when the gear ratio of the belt-type continuously variable transmission according to the present invention is reduced (during upshift), and FIG. FIG. 8 is a cross-sectional view of the main part of the primary pulley when the gear ratio is increased (during downshift), and FIG. It is a figure which shows operation | movement of a discharge control apparatus.

  The ECU 140 performs control to fix the gear ratio, that is, to make the gear ratio steady, when there is no need to change the gear ratio significantly, for example, when the running state of the vehicle is stable. When ECU 140 determines that the gear ratio is fixed, each hydraulic oil supply / discharge valve (reverse support valve) 70 is closed. That is, ECU 140 closes each hydraulic oil supply / discharge valve 70 to fix the gear ratio.

  Here, in the case where each hydraulic oil supply / discharge valve 70 is closed and the transmission gear ratio is fixed, that is, the transmission gear ratio is fixed in the closed valve state without supplying hydraulic oil to the primary hydraulic chamber 55 and this primary hydraulic pressure. The hydraulic oil is not discharged from the chamber 55, and the position of the primary movable sheave 53 in the axial direction with respect to the primary fixed sheave 52 is made constant, and the movement of the primary movable sheave 53 with respect to the primary fixed sheave 52 is restricted.

  When the transmission gear ratio is fixed in the closed state of each hydraulic oil supply / discharge valve 70, as shown in FIG. 2, each hydraulic oil supply / discharge valve 70 is closed and the primary hydraulic pressure via each hydraulic oil supply / discharge valve 70 is closed. The supply of hydraulic oil to the chamber 55 and the discharge of hydraulic oil from the primary hydraulic chamber 55 via each hydraulic oil supply / discharge valve 70 are prohibited. Specifically, the ECU 140 controls the drive hydraulic chamber control device 136 to be OFF.

When the drive hydraulic chamber control device 136 is OFF-controlled by the ECU 140, the drive hydraulic chamber 81 is released to atmospheric pressure, and the hydraulic pressure P2 of the drive hydraulic chamber 81 is almost atmospheric pressure P _OFF . Accordingly, 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 by the hydraulic pressure P1 of the valve body elastic member 74 and the primary hydraulic chamber 55 is applied. The valve body 71 moves in the valve closing direction and contacts the valve seat surface 72, and the hydraulic oil supply / discharge valves 70 are closed. Since only the valve body closing direction pressing force acts on the pressure receiving member 82a via each valve body 71 and each pressing member 82b, the piston 82 moves in the other direction of the sliding direction, that is, closes. Slides in the valve direction.

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

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

  As described above, when the gear ratio is fixed in the closed state of each hydraulic oil supply / discharge valve 70, the supply of hydraulic oil to the primary hydraulic chamber 55 and the discharge of hydraulic oil from the primary hydraulic chamber 55 are prohibited. The hydraulic oil in the primary hydraulic chamber 55 is retained. Here, since the belt tension of the belt 110 changes even when the gear ratio is fixed in the valve-closed state, the contact radius of the belt 110 in the primary pulley 50 tends to change, and the shaft of the primary movable sheave 53 with respect to the primary fixed sheave 52 The position in the direction may change. As described above, since the hydraulic oil is held in the primary hydraulic chamber 55, if the position of the primary movable sheave 53 in the axial direction with respect to the primary fixed sheave 52 is changed, the hydraulic pressure of 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. Thereby, when the transmission gear ratio is fixed in the valve-closed state, it is not necessary to drive the oil pump 132 in order 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. it can.

  Next, when the ECU 140 determines that the gear ratio is not fixed, the hydraulic oil supply / discharge valve 70 is opened with the hydraulic pressure P2 of the drive hydraulic chamber 81 set to the constant pressure PS. That is, the ECU 140 forcibly opens each hydraulic oil supply / discharge valve 70 by the actuator 80 in a state where the gear ratio is not fixed, that is, in a state where the gear ratio is changed. Specifically, the ECU 140 controls the drive hydraulic chamber control device 136 to be ON.

  When the drive hydraulic chamber control device 136 is ON-controlled by the ECU 140, 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 is constant pressure PS. It becomes. In the actuator 80, the piston valve opening direction pressing force acting on the piston 82 by the hydraulic pressure P2 of the drive hydraulic chamber 81 is transmitted from the piston 82 to the valve body 71 of each hydraulic oil supply / discharge valve 70, and the piston valve opening direction pressing force is controlled by the valve 80. It is made to act on the valve body 71 of each hydraulic oil supply / discharge valve 70 as the body opening direction pressing force. Accordingly, as shown in FIGS. 5 and 7, each hydraulic oil supply / discharge valve 70 is opened by moving the valve body 71 in the valve opening direction with respect to the valve seat surface 72 by the actuator 80.

  Next, as shown in FIG. 5, the ECU 140 performs gear ratio change control by the hydraulic oil supply / discharge control device 130. The gear ratio change control is mainly performed by supplying hydraulic oil from the hydraulic oil supply / discharge 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 / discharge 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. The 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, that is, the input rotation speed Nin, and the rotation speed of the secondary pulley 60, that is, the output rotation speed, is stepless. It is controlled (continuously).

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

  Here, the transmission ratio change control includes an upshift, that is, a transmission ratio decrease change control that decreases the transmission ratio, and a downshift, that is, a transmission ratio increase change control that increases the transmission ratio. Each will be described below.

  In gear ratio reduction change control (upshift control), hydraulic oil is supplied from the hydraulic oil supply / discharge control device 130 to the primary hydraulic chamber 55, and the primary movable sheave 53 is slid (moved) to the primary fixed sheave side. Is called. As shown in FIG. 5, the hydraulic oil is supplied from the hydraulic oil supply / discharge control device 130 to the primary hydraulic chamber 55 via each hydraulic oil supply / discharge valve 70 that is forcibly opened by the actuator 80. Specifically, ECU 140 calculates a reduction gear ratio and a gear shift speed, and outputs a gear ratio control signal based on these to hydraulic oil supply / discharge control device 130.

  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 moving directions, and the second port 135l and the third port 135m communicate with each other. As a result, the supply-side flow rate control valve 135c is opened, and the supply flow rate of 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 the 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 passage through the oil passage R7. The hydraulic oil that has flowed into the supply / discharge side main passage 51a passes through the supply / discharge side main passage 51a through the shaft-side communication passages 51c, the spaces T1 and T2, the partition wall-side communication passages 54b, and the valve arrangement passage 54a. It is supplied to the chamber 55. That is, when supplying hydraulic oil to the primary hydraulic chamber 55 that is one clamping pressure generating hydraulic chamber, the hydraulic oil that is the same as the hydraulic oil discharge valve is supplied by the hydraulic oil supply pressure Pin supplied to the primary hydraulic chamber 55. Each hydraulic oil supply / discharge valve 70 which is a supply valve may not be opened. 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 rises due to the hydraulic oil supplied via each hydraulic oil supply / discharge valve 70, the pressing force that presses the primary movable sheave 53 toward the primary fixed sheave side increases, and the primary movable sheave 53 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 the gear ratio increase change (downshift control), the hydraulic oil is discharged from the primary hydraulic chamber 55 via the hydraulic oil supply / discharge control device 130, and the primary movable sheave 53 is slid to the opposite side to the primary fixed sheave side ( To move). As shown in FIG. 7, the hydraulic oil is discharged from the primary hydraulic chamber 55 via each hydraulic oil supply / discharge valve 70 that is forcibly opened by the actuator 80. 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 / discharge control device 130.

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

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

  As described above, each hydraulic oil supply / discharge valve 70 is forcibly opened by the actuator 80. Accordingly, the hydraulic oil in the primary hydraulic chamber 55 is supplied from the primary hydraulic chamber 55 to the valve arrangement passage 54a of the hydraulic oil supply / discharge passage, the partition side communication passages 54b, and the space portions T1, T2 as shown by the arrow D in FIG. Then, it flows into the supply / discharge side main passage 51a through each shaft side communication passage 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.

  Here, in the belt-type continuously variable transmission 1-1 of the present embodiment, hydraulic fluid is supplied by the actuator 80 by the ECU 140 as a determination unit in the gear ratio fixed release control when the gear ratio is changed from the gear ratio fixed state. It is determined whether or not the forcible opening of the discharge valve 70 is possible, and the hydraulic oil supply / discharge control device 130 determines that the hydraulic oil supply / discharge valve 70 can be forcibly opened by the actuator 80 by the ECU 140. When this is done, an appropriate gear ratio control is realized by increasing the hydraulic pressure in the hydraulic oil supply / discharge passage before the hydraulic oil supply / discharge valve 70 is opened. Here, the hydraulic oil supply / discharge passage is, as described above, the supply / discharge side main passage 51a, the shaft side communication passages 51c, the spaces T1, T2, the partition wall side communication passages 54b, and the valve arrangement passages 54a. In other words, the hydraulic pressure of the hydraulic oil supply / discharge passage is the supply pressure Pin of hydraulic oil supplied to the primary hydraulic chamber 55.

  Here, FIG. 9-1 is a flowchart for explaining the gear ratio fixing control of the belt-type continuously variable transmission according to the first embodiment of the present invention, and FIG. It is a time chart explaining the transmission ratio fixed control of the step transmission, and the vertical axis indicates ON / OFF of the closing instruction of the hydraulic oil supply / discharge valve 70, the transmission ratio (γ), the hydraulic pressure (P2) of the drive hydraulic chamber 81, The supply pressure (Pin) of hydraulic oil supplied to the primary hydraulic chamber 55, the hydraulic pressure (Pd) of the secondary hydraulic chamber 64, and the horizontal axis are time axes.

  First, the gear ratio fixing control of the belt type continuously variable transmission 1-1 will be described with reference to FIGS. 9-1 and 9-2. This control routine is repeatedly executed at a control cycle of several ms to several tens of ms.

  First, the ECU 140 determines whether or not there is an instruction to close the hydraulic oil supply / discharge valve 70 (S0). That is, the ECU 140 determines whether or not it is necessary to perform the valve closing operation of the hydraulic oil supply / discharge valve 70 in order to fix the gear ratio. If it is determined that there is no instruction to close the hydraulic oil supply / discharge valve 70 (S0: No), the gear ratio fixing control is terminated. When it is determined that there is an instruction to close the hydraulic oil supply / discharge valve 70 (S0: Yes), the ECU 140 sets the valve closing instruction flag to ON (time t01 in FIG. 9-2).

  Next, the ECU 140 determines whether or not the current gear ratio is stable (S2). For example, the ECU 140 stabilizes the gear ratio when the absolute value of the deviation between the current actual gear ratio and the target gear ratio that is the target of the gear shift control is smaller than a predetermined value that is set in advance for a predetermined period. (Time t02 in FIG. 9-2). Here, the predetermined value and the predetermined period set in advance may be appropriately set to values that can distinguish whether the speed ratio is stable. The ECU 140 is not limited to this, and may determine whether or not the current speed ratio is stable by various known methods.

If it is determined that the current gear ratio is not stable (S2: No), this gear ratio fixing control is terminated. When it is determined that the current gear ratio is stable (S2: Yes), the ECU 140 performs a closing operation of the hydraulic oil supply / discharge valve 70 (S4). In other words, the ECU 140 controls the drive hydraulic chamber control device 136 to OFF to release the oil passage R8 to the outside, thereby releasing the drive hydraulic chamber 81 to atmospheric pressure, and the hydraulic pressure P2 of the drive hydraulic chamber 81 is substantially large. The atmospheric pressure P _OFF is reached (time t03 in FIG. 9-2). As a result, each hydraulic oil supply / discharge valve 70 is closed and the gear ratio is fixed.

Next, the ECU 140 determines whether or not the closing operation of the hydraulic oil supply / discharge valve 70 is completed (S6). For example, the ECU 140 closes the hydraulic oil supply / discharge valve 70 after the OFF control of the drive hydraulic chamber control device 136, that is, when a certain period of time has elapsed after the atmospheric pressure P _OFF is introduced into the dynamic hydraulic chamber 81. Is completed (time t04 in FIG. 9-2). When it is determined that the valve closing operation of the hydraulic oil supply / discharge valve 70 has not been completed (S6: No), that is, when a certain period of time has not elapsed after the OFF control of the drive hydraulic chamber control device 136, the ECU 140 Returning to S4, the subsequent processing is repeated.

When it is determined that the closing operation of the hydraulic oil supply / discharge valve 70 is completed (S6: Yes), that is, when a certain period of time has elapsed after the OFF control of the drive hydraulic chamber control device 136, the hydraulic oil supply / discharge control device 130, working oil supply and discharge passage hydraulic to a predetermined pressure Pl ₀ of (supply and discharge side main passage 51a, the shaft-side communicating passage 51c, the space portion T1, T2, each partition wall-side communication passage 54b and each valve disposed passageways 54a) The pressure is reduced, that is, the supply pressure Pin of the hydraulic oil supplied to the primary hydraulic chamber 55 is reduced (S8). Hydraulic oil supply and discharge control device 130, for example, sufficiently reduce the pressure to a lower predetermined pressure Pl ₀ than the pressure in the normal shift control supply pressure Pin (time t05 in FIG. 9-2), the fixed gear ratio control Exit. Thereby, since the load of the oil pump 132 can be reduced, an increase in driving loss of the oil pump 132 can be suppressed. As a result, fuel consumption can be improved.

  FIG. 10-1 is a flowchart for explaining the gear ratio fixed release control of the belt type continuously variable transmission according to the first embodiment of the present invention, and FIG. 5 is a time chart for explaining the gear ratio fixed release control of the machine, wherein the vertical axis indicates ON / OFF of the opening instruction of the hydraulic oil supply / discharge valve 70, the gear ratio (γ), the hydraulic pressure (P2) of the drive hydraulic chamber 81, the primary The supply pressure (Pin) of the hydraulic oil supplied to the hydraulic chamber 55, the hydraulic pressure (Pd) of the secondary hydraulic chamber 64, and the horizontal axis are time axes.

  Next, the gear ratio fixed release control of the belt type continuously variable transmission 1-1 will be described with reference to FIGS. 10-1 and 10-2. This control routine is repeatedly executed at a control cycle of several ms to several tens of ms.

  First, the ECU 140 determines whether or not there is an instruction to open the hydraulic oil supply / discharge valve 70 (S100). That is, ECU 140 determines whether or not it is necessary to perform the valve opening operation of hydraulic oil supply / discharge valve 70 in order to change the gear ratio from the gear ratio fixed state. If it is determined that there is no instruction to open the hydraulic oil supply / discharge valve 70 (S100: No), the gear ratio fixed release control is terminated. When it is determined that there is an instruction to open the hydraulic oil supply / discharge valve 70 (S100: Yes), the ECU 140 sets the valve opening instruction flag to ON (time t11 in FIG. 10-2).

  Next, the ECU 140 calculates the hydraulic pressure P1 of the primary hydraulic chamber 55 when the gear ratio is fixed when each hydraulic oil supply / discharge valve 70 is closed (S102). The ECU 140 operates based on, for example, the engine torque (output torque) Te generated by the internal combustion engine 10, the input rotational speed Nin detected by the input rotational speed sensor 150, the hydraulic pressure Pd of the secondary hydraulic chamber 64, the gear ratio γ, and the like. When the oil supply / discharge valve 70 is closed, the hydraulic pressure P1 confined in the primary hydraulic chamber 55 is estimated and calculated (time t12 in FIG. 10-2). Note that the ECU 140 is not limited to this, and may calculate the hydraulic pressure P1 of the primary hydraulic chamber 55 by various known methods.

  Next, the ECU 140 (determination means) determines whether or not the hydraulic oil supply / discharge valve 70 can be forcibly opened by the actuator 80 (S104). Here, the ECU 140 determines whether the hydraulic oil supply / discharge valve 70 can be forcibly opened by the actuator 80 based on the hydraulic pressure P1 of the primary hydraulic chamber 55 and the hydraulic pressure P2 of the drive hydraulic chamber 81 ( Time t13 in FIG. 10-2).

FIG. 11 is a diagram schematically showing a portion including the piston 82 of the actuator 80. The ECU 140 receives the hydraulic pressure P2 of the drive hydraulic chamber 81 when the constant pressure PS is input, the hydraulic pressure P1 of the primary hydraulic chamber 55, the piston pressure receiving area Ap of the pressure receiving member 82a of the piston 82, the valve body 71 and the valve seat surface 72. Supply of hydraulic fluid by the actuator 80 when the valve seal portion area Acv, which is the area of the seal portion, and the elastic member pressing force Pr by the valve closing biasing force generated by the valve body elastic member 74 satisfy the following relational expression (1): It is determined that the discharge valve 70 can be forcibly opened.

P2 · Ap> P1 · Acv + Pr (1)

That is, the ECU 140 determines that the valve body opening direction pressing force obtained by multiplying the hydraulic pressure P2 (PS) of the driving hydraulic chamber 81 and the piston pressure receiving area Ap when the constant pressure PS is input is the hydraulic pressure P1 of the primary hydraulic chamber 55 and the valve When the valve closing direction pressing force obtained by adding the elastic member pressing force Pr generated by the valve closing elastic force generated by the valve body elastic member 74 to the hydraulic oil closing direction pressing force multiplied by the seal portion area Acv is larger than the valve closing direction pressing force. It is determined that the hydraulic oil supply / discharge valve 70 can be forcibly opened by the actuator 80.

  If it is determined that the hydraulic oil supply / discharge valve 70 cannot be forcibly opened by the actuator 80 (S104: No), the gear ratio fixed release control is terminated.

  When it is determined that the hydraulic oil supply / discharge valve 70 can be forcibly opened by the actuator 80 (S <b> 104: Yes), the hydraulic oil supply / discharge control device 130 does not open the hydraulic oil supply / discharge valve 70. The hydraulic pressure of 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 communication passage 54b and each valve arrangement passage 54a) is increased, that is, the primary oil pressure is increased. The supply pressure Pin of hydraulic oil supplied to the chamber 55 is increased (S106). For example, the hydraulic oil supply / discharge control device 130 increases the supply pressure Pin to the vicinity of the hydraulic pressure P1 confined in the primary hydraulic chamber 55 when each hydraulic oil supply / discharge valve 70 is closed (FIG. 10-2). Time t14). As a result, the differential pressure between the hydraulic pressure P1 confined in the primary hydraulic chamber 55 and the supply pressure Pin decreases, and the hydraulic pressure P1 in the primary hydraulic chamber 55 fluctuates rapidly when each hydraulic oil supply / discharge valve 70 opens. Can be prevented. As a result, the shift shock when each hydraulic oil supply / discharge valve 70 is opened can be reduced, and the gear ratio can be controlled appropriately.

  Next, the ECU 140 performs an opening operation of the hydraulic oil supply / discharge valve 70 (S108). That is, the ECU 140 controls the drive hydraulic chamber control device 136 to be ON, 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 is constant. The pressure becomes PS (time t15 in FIG. 10-2). As a result, each hydraulic oil supply / discharge valve 70 is forcibly opened by the actuator 80, and the fixed gear ratio is released.

  Next, ECU 140 determines whether or not the gear ratio has changed, that is, whether or not the gear ratio has been changed (S110). The ECU 140 determines whether or not the speed ratio γ has changed based on, for example, the input rotation speed Nin detected by the input rotation speed sensor 150 and the output rotation speed Nout detected by the output rotation speed sensor 160. When it is determined that the gear ratio has not changed (S110: No), the ECU 140 repeatedly executes this process. When it is determined that the gear ratio has changed (from time t15 to time t16 in FIG. 10-2) (S110: Yes), the gear ratio fixed release control is terminated.

  According to the belt-type continuously variable transmission 1-1 according to the embodiment of the present invention described above, the primary pulley 50 and the secondary pulley 60 as two pulleys, and the primary pulley 50 and the secondary pulley 60 are wound around. A primary hydraulic chamber 55 and a secondary hydraulic chamber 64 that are formed in each of a belt 110 that transmits driving force from the internal combustion engine 10, a primary pulley 50, and a secondary pulley 60, and generates belt clamping pressure against the belt 110 by hydraulic pressure; The piston 82 is slid with respect to the drive hydraulic chamber 81 by the hydraulic oil supply / discharge valve 70 that opens in the direction of supplying hydraulic oil to the primary hydraulic chamber 55 as one clamping pressure generating hydraulic chamber and the hydraulic pressure of the drive hydraulic chamber 81. Actuator that forcibly opens hydraulic oil supply / discharge valve 70 by sliding in one of the directions When the hydraulic oil supply / discharge valve 70 is forcibly opened by the actuator 80 and the actuator 80, the hydraulic oil supply / discharge passage (the supply / discharge side main passage 51a, each shaft side communication passage 51c, the space portions T1, T2, A hydraulic oil supply / discharge control device that controls the gear ratio by supplying hydraulic oil to the primary hydraulic chamber 55 through the partition wall side communication passage 54b and the valve arrangement passages 54a) or by discharging the hydraulic oil from the primary hydraulic chamber 55. 130 and an ECU 140 that determines whether or not the hydraulic oil supply / discharge valve 70 can be forcibly opened by the actuator 80 when the gear ratio is changed. The hydraulic oil supply / discharge control device 130 is controlled by the ECU 140. When it is determined that the hydraulic oil supply / discharge valve 70 can be forcibly opened by the actuator 80, the hydraulic oil supply / discharge valve 70 is opened before the hydraulic oil supply / discharge valve 70 is opened. Raising the oil pressure of the passage.

  Therefore, in the gear ratio fixed release control when the gear ratio is changed from when the gear ratio is fixed, the ECU 140 determines whether the hydraulic oil supply / discharge valve 70 can be forcibly opened by the actuator 80, and the hydraulic oil When it is determined by the ECU 140 that the hydraulic oil supply / discharge valve 70 can be forcibly opened by the ECU 140, the supply / discharge control device 130 supplies the hydraulic oil supply / discharge before the hydraulic oil supply / discharge valve 70 is opened. By increasing the hydraulic pressure of the passage, the differential pressure between the hydraulic pressure P1 confined in the primary hydraulic chamber 55 and the supply pressure Pin is reduced, and when each hydraulic oil supply / discharge valve 70 is opened, the primary hydraulic chamber 55 It is possible to prevent the hydraulic pressure P1 from fluctuating rapidly. As a result, the shift shock when each hydraulic oil supply / discharge valve 70 is opened can be reduced, and the gear ratio can be controlled appropriately.

  Furthermore, according to the belt-type continuously variable transmission 1-1 according to the embodiment of the present invention described above, the ECU 140 uses the actuator 80 based on the hydraulic pressure in the primary hydraulic chamber 55 and the hydraulic pressure in the drive hydraulic chamber 81. It is determined whether the hydraulic oil supply / discharge valve 70 can be forcibly opened. Therefore, the ECU 140 determines that the valve body opening direction pressing force obtained by multiplying the hydraulic pressure P2 (PS) of the driving hydraulic chamber 81 and the piston pressure receiving area Ap when the constant pressure PS is input by the hydraulic pressure P1 of the primary hydraulic chamber 55 and the valve When the valve closing direction pressing force obtained by adding the elastic member pressing force Pr generated by the valve closing elastic force generated by the valve body elastic member 74 to the hydraulic oil closing direction pressing force multiplied by the seal portion area Acv is larger than the valve closing direction pressing force. It can be determined that the hydraulic oil supply / discharge valve 70 can be forcibly opened by the actuator 80.

  Furthermore, according to the belt-type continuously variable transmission 1-1 according to the embodiment of the present invention described above, the hydraulic oil supply / discharge control device 130 operates after the hydraulic oil supply / discharge valve 70 is closed. Decrease the oil pressure. Therefore, since the load of the oil pump 132 can be reduced, an increase in driving loss of the oil pump 132 can be suppressed. As a result, fuel consumption can be improved.

(Embodiment 2)
FIG. 12 is a flowchart for explaining the gear ratio fixed release control of the belt-type continuously variable transmission according to the second embodiment of the present invention, and FIG. 13 is the gear ratio of the belt-type continuously variable transmission according to the second embodiment of the present invention. It is a time chart explaining fixation release control. The belt-type continuously variable transmission according to the second embodiment has substantially the same configuration as the belt-type continuously variable transmission according to the first embodiment, but the first embodiment is different in that the hydraulic pressure in the hydraulic oil supply / discharge passage is not increased during downshifting. This is different from the belt type continuously variable transmission according to FIG. In addition, about the structure, effect | action, and effect which are common in embodiment mentioned above, while overlapping description is abbreviate | omitted as much as possible, the same code | symbol is attached | subjected. For the configuration of the main part, refer to FIGS.

  When the hydraulic oil supply / discharge control device 130 of the belt type continuously variable transmission 1-2 according to the second embodiment determines that the hydraulic oil supply / discharge valve 70 can be forcibly opened by the actuator 80 by the ECU 140. When the gear ratio is changed to the decreasing side, that is, in the case of an upshift, the hydraulic pressure in the hydraulic oil supply / discharge passage is increased before the hydraulic oil supply / discharge valve 70 is opened, while the gear ratio is increased. In the case of a change, that is, in the case of a downshift, the increase of the hydraulic pressure in the hydraulic oil supply / discharge passage before the opening of the hydraulic oil supply / discharge valve 70 is prohibited, thereby improving the shift response at the time of downshift. ing.

  The speed ratio fixed release control of the belt type continuously variable transmission 1-2 will be described with reference to FIGS. This control routine is repeatedly executed at a control cycle of several ms to several tens of ms.

  First, the ECU 140 determines whether or not there is an instruction to open the hydraulic oil supply / discharge valve 70 (S100). When it is determined that there is no instruction to open the hydraulic oil supply / discharge valve 70 (S100: No), this speed ratio fixation release control is terminated, and it is determined that there is an instruction to open the hydraulic oil supply / discharge valve 70 (S100: Yes), ECU 140 sets the valve opening instruction flag to ON (time t21 in FIG. 13).

  Next, the ECU 140 calculates the hydraulic pressure P1 of the primary hydraulic chamber 55 when the gear ratio is fixed when each hydraulic oil supply / discharge valve 70 is closed (S102, time t22 in FIG. 13).

  Next, the ECU 140 (determination means) determines whether or not the hydraulic oil supply / discharge valve 70 can be forcibly opened by the actuator 80 (S104, time t23 in FIG. 13).

  If it is determined that the hydraulic oil supply / discharge valve 70 cannot be forcibly opened by the actuator 80 (S104: No), the gear ratio fixed release control is terminated.

  When it is determined that the hydraulic oil supply / discharge valve 70 can be forcibly opened by the actuator 80 (S104: Yes), the ECU 140 determines that the opening instruction of the current hydraulic oil supply / discharge valve 70 is a downshift instruction. It is determined whether or not it is accompanied (S205, time t24 in FIG. 13).

  When it is determined that the current opening instruction of the hydraulic oil supply / discharge valve 70 does not accompany the downshift instruction, that is, it is determined that the hydraulic oil supply / discharge valve 70 accompanies the upshift instruction (S205: No), Before the hydraulic oil supply / discharge valve 70 is opened, the hydraulic oil supply pressure Pin supplied to the primary hydraulic chamber 55 is increased (S206), and the hydraulic oil supply / discharge valve 70 is opened (S108). . Then, ECU 140 determines whether or not the gear ratio has changed (S110), and when it is determined that the gear ratio has not changed (S110: No), this process is repeatedly executed to change the gear ratio. Is determined (S110: Yes), the gear ratio fixed release control is terminated.

  On the other hand, when it is determined that the opening instruction of the hydraulic oil supply / discharge valve 70 this time is accompanied by the downshift instruction (S205: Yes), the hydraulic oil supply / discharge control apparatus 130 Opening operation of the hydraulic oil supply / discharge valve 70 is prohibited without increasing the hydraulic pressure of the hydraulic oil supply / discharge passage before the valve is opened, that is, without increasing the supply pressure Pin of the hydraulic oil supplied to the primary hydraulic chamber 55. Is executed (S108, time t25 in FIG. 13).

  Then, ECU 140 determines whether or not the gear ratio has changed (S110), and when it is determined that the gear ratio has not changed (S110: No), this process is repeatedly executed to change the gear ratio. If it is determined (from time t25 to time t26 in FIG. 13) (S110: Yes), the gear ratio fixed release control is terminated.

  According to the belt-type continuously variable transmission 1-2 according to the embodiment of the present invention described above, the ECU 140 operates by the actuator 80 in the gear ratio fixed release control when the gear ratio is changed from when the gear ratio is fixed. It is determined whether or not the oil supply / discharge valve 70 can be forcibly opened, and the hydraulic oil supply / discharge control device 130 allows the ECU 140 to forcibly open the hydraulic oil supply / discharge valve 70 using the actuator 80. Is determined, the hydraulic pressure of the hydraulic oil supply / discharge passage is increased before the hydraulic oil supply / discharge valve 70 is opened, so that the differential pressure between the hydraulic pressure P1 confined in the primary hydraulic chamber 55 and the supply pressure Pin The hydraulic pressure P1 of the primary hydraulic chamber 55 can be prevented from abruptly changing when each hydraulic oil supply / discharge valve 70 is opened. As a result, the shift shock when each hydraulic oil supply / discharge valve 70 is opened can be reduced, and the gear ratio can be controlled appropriately.

  Furthermore, according to the belt-type continuously variable transmission 1-2 according to the embodiment of the present invention described above, the hydraulic oil supply / discharge control device 130 forces the ECU 140 to force the hydraulic oil supply / discharge valve 70 by the actuator 80. When it is determined that the valve can be opened, if the gear ratio is changed to a decreasing side, the hydraulic pressure in the hydraulic oil supply / discharge passage is increased before the hydraulic oil supply / discharge valve 70 is opened, while the gear ratio is changed. Is changed to an increase side, the increase of the hydraulic pressure in the hydraulic oil supply / discharge passage before the hydraulic oil supply / discharge valve 70 is opened is prohibited. Therefore, when the gear ratio is changed to the decreasing side, that is, hydraulic oil is supplied from the hydraulic oil supply / discharge control device 130 to the primary hydraulic chamber 55, and the primary movable sheave 53 is slid (moved) to the primary fixed sheave side. In the case of an upshift, the hydraulic shock in the hydraulic oil supply / discharge passage is increased before the hydraulic oil supply / discharge valve 70 is opened, thereby reducing a shift shock when each hydraulic oil supply / discharge valve 70 is opened. And the gear ratio can be controlled appropriately. On the other hand, when the gear ratio is changed to the increase side, that is, the hydraulic oil is discharged from the primary hydraulic chamber 55 via the hydraulic oil supply / discharge control device 130, and the primary movable sheave 53 is opposite to the primary fixed sheave side. In the case of a downshift that slides (moves), the hydraulic oil in the hydraulic oil supply / discharge passage is low by prohibiting the increase in hydraulic pressure in the hydraulic oil supply / discharge passage before the hydraulic oil supply / discharge valve 70 is opened. Therefore, the hydraulic oil can be quickly discharged to the outside, the responsiveness up to the start of the shift at the time of downshift can be improved, and the driver duty can be improved. At this time, since the hydraulic oil supply / discharge valve 70 is opened without increasing the hydraulic pressure in the hydraulic oil supply / discharge passage, it is not necessary to drive the oil pump 132. Increase can be suppressed. As a result, fuel consumption can be improved.

(Embodiment 3)
FIG. 14 is a flowchart for explaining secondary hydraulic pressure reduction control of the belt-type continuously variable transmission according to the third embodiment of the present invention. FIG. 15 is a secondary hydraulic pressure reduction control of the belt-type continuously variable transmission according to the third embodiment of the present invention. It is a time chart explaining control. The belt-type continuously variable transmission according to the third embodiment has substantially the same configuration as the belt-type continuously variable transmission according to the first embodiment, but it is impossible to forcibly open the hydraulic oil supply / discharge valve by the actuator. The belt type continuously variable transmission according to the first embodiment is different in that the belt tension is reduced. In addition, about the structure, effect | action, and effect which are common in embodiment mentioned above, while overlapping description is abbreviate | omitted as much as possible, the same code | symbol is attached | subjected. In addition, refer to FIG. 1 to FIG.

  In the belt-type continuously variable transmission 1-3 according to the third embodiment, when the hydraulic oil supply / discharge valve 70 cannot be forcibly opened by the actuator 80, the ECU 140 as the tension reducing unit reduces the tension of the belt 110. To do. More specifically, the ECU 140 reduces the tension of the belt 110 by reducing the hydraulic pressure Pd of the secondary hydraulic chamber 64 as the other clamping pressure generating hydraulic chamber.

  As described above, in the secondary pulley 60, the ECU 140 controls the secondary hydraulic chamber control device 137 to regulate the hydraulic pressure Pd of the secondary hydraulic chamber 64, and the belt is formed by the secondary fixed sheave 62 and the secondary movable sheave 63. The belt clamping pressure for clamping 110 is adjusted. Thereby, the belt tension of the belt 110 wound around the primary pulley 50 and the secondary pulley 60 is controlled. Here, the belt tension of the belt 110 is basically set to a magnitude corresponding to the engine torque which is the output torque of the internal combustion engine 10, and the hydraulic pressure Pd of the secondary hydraulic chamber 64 is also a magnitude corresponding to the engine torque. However, the hydraulic pressure Pd in the secondary hydraulic chamber 64 has some margin for engine torque. For this reason, the tension of the belt 110 can be reduced by reducing the hydraulic pressure Pd of the secondary hydraulic chamber 64 using the margin.

  If the tension of the belt 110 is reduced by reducing the hydraulic pressure Pd of the secondary hydraulic chamber 64, the reaction force acting on the primary movable sheave 53 from the belt 110 is also reduced. When the reaction force acting on the primary movable sheave 53 is reduced, the hydraulic pressure P1 of the hydraulic oil held in the primary hydraulic chamber 55 when the transmission ratio is fixed in the closed state of each hydraulic oil supply / discharge valve 70 is also reduced. As a result, the hydraulic oil valve closing direction pressing force obtained by multiplying the hydraulic pressure P1 of the primary hydraulic chamber 55 and the valve seal portion area Acv in the above formula (1) also decreases, and the valve element valve opening direction pressing force is reduced to the hydraulic oil valve closing direction. It becomes larger than the valve body closing direction pressing force obtained by adding the elastic member pressing force to the direction pressing force, and the hydraulic fluid supply / discharge valve 70 can be forcibly opened by the actuator 80, and the gear ratio can be changed. Become.

  The secondary hydraulic pressure reduction control of the belt type continuously variable transmission 1-3 will be described with reference to FIGS. 14 and 15. In this control routine, for example, when it is determined that the hydraulic fluid supply / discharge valve 70 cannot be forcibly opened by the actuator 80 in the gear ratio fixed release control (S104: No in FIG. 10-1), When it is determined that the ratio has not changed (S110: No in FIG. 10-1), the process is repeatedly executed at a control cycle of several ms to several tens of ms. In this control, the ECU 140 sets the valve opening instruction flag to ON, controls the drive hydraulic chamber control device 136 to be ON, and introduces the constant pressure PS into the drive hydraulic chamber 81.

  Then, ECU 140 determines whether or not the gear ratio has changed (S300). The ECU 140 determines whether or not the speed ratio γ has changed based on, for example, the input rotational speed Nin detected by the input rotational speed sensor 150 and the output rotational speed Nout detected by the output rotational speed sensor 160 ( Time t31 in FIG. When it is determined that the gear ratio has changed (S300: No), the secondary hydraulic pressure reduction control is terminated.

  When it is determined that the gear ratio has not changed (S300: Yes), that is, when it is determined that the opening operation of the hydraulic oil supply / discharge valve 70 has failed in the gear ratio fixed release control, the ECU 140 performs the secondary hydraulic chamber. It is determined whether the hydraulic pressure Pd of 64 is equal to or lower than the minimum pressure guard value (S302). When it is determined that the hydraulic pressure Pd in the secondary hydraulic chamber 64 is equal to or lower than the minimum pressure guard value (S302: Yes), the secondary hydraulic pressure reduction control is terminated.

  When it is determined that the hydraulic pressure Pd in the secondary hydraulic chamber 64 is greater than the minimum pressure guard value (S302: No), the ECU 140 controls the hydraulic oil supply / discharge control device 130 to gradually reduce the hydraulic pressure Pd in the secondary hydraulic chamber 64. (S304, time t32 in FIG. 15).

  Next, ECU 140 determines whether or not the gear ratio has changed (S306). The ECU 140 determines whether or not the speed ratio γ has changed based on, for example, the input rotation speed Nin detected by the input rotation speed sensor 150 and the output rotation speed Nout detected by the output rotation speed sensor 160 (FIG. 15). T33). When it is determined that the gear ratio has not changed (S306: No), the process returns to S302 and the subsequent processes are repeated.

  When it is determined that the gear ratio has changed (from time t34 to time t35 in FIG. 15) (S306: Yes), the ECU 140 controls the hydraulic oil supply / discharge control device 130 to reduce the hydraulic pressure Pd in the secondary hydraulic chamber 64. This is finished (S308, time t34 in FIG. 15), and this secondary hydraulic pressure reduction control is finished. As a result, the hydraulic oil supply / discharge valve 70 can be forcibly opened by the actuator 80, and the gear ratio can be changed.

  According to the belt-type continuously variable transmission 1-3 according to the embodiment of the present invention described above, the ECU 140 operates by the actuator 80 in the gear ratio fixed release control when the gear ratio is changed from when the gear ratio is fixed. It is determined whether or not the oil supply / discharge valve 70 can be forcibly opened, and the hydraulic oil supply / discharge control device 130 allows the ECU 140 to forcibly open the hydraulic oil supply / discharge valve 70 using the actuator 80. Is determined, the hydraulic pressure of the hydraulic oil supply / discharge passage is increased before the hydraulic oil supply / discharge valve 70 is opened, so that the differential pressure between the hydraulic pressure P1 confined in the primary hydraulic chamber 55 and the supply pressure Pin The hydraulic pressure P1 of the primary hydraulic chamber 55 can be prevented from abruptly changing when each hydraulic oil supply / discharge valve 70 is opened. As a result, the shift shock when each hydraulic oil supply / discharge valve 70 is opened can be reduced, and the gear ratio can be controlled appropriately.

  Furthermore, according to the belt-type continuously variable transmission 1-3 according to the embodiment of the present invention described above, when the forcible opening of the hydraulic oil supply / discharge valve 70 by the actuator 80 is impossible, the belt 110 An ECU 140 is provided as tension reducing means for reducing the tension. Therefore, by reducing the tension of the belt 110, the hydraulic oil pressure P1 of the hydraulic oil held in the primary hydraulic chamber 55 when the speed ratio is fixed in the closed state of each hydraulic oil supply / discharge valve 70 is also reduced. The hydraulic oil supply / discharge valve 70 can be forcibly opened by the actuator 80, and the gear ratio can be changed. As a result, the reliability of the belt type continuously variable transmission 1-3 can be improved.

  Furthermore, according to the belt-type continuously variable transmission 1-3 according to the embodiment of the present invention described above, the ECU 140 as the tension reducing unit decreases the hydraulic pressure Pd of the secondary hydraulic chamber 64. Therefore, the tension of the belt 110 can be reduced by reducing the hydraulic pressure Pd of the secondary hydraulic chamber 64.

(Embodiment 4)
FIG. 16 is a flowchart illustrating engine torque reduction control of a belt-type continuously variable transmission according to Embodiment 4 of the present invention, and FIG. 17 is engine torque reduction of the belt-type continuously variable transmission according to Embodiment 4 of the present invention. It is a time chart explaining control. The belt-type continuously variable transmission according to the fourth embodiment has substantially the same configuration as that of the belt-type continuously variable transmission according to the third embodiment, except that the belt tension is reduced by reducing the output torque from the drive source. This is different from the belt-type continuously variable transmission according to the third embodiment. In addition, about the structure, effect | action, and effect which are common in embodiment mentioned above, while overlapping description is abbreviate | omitted as much as possible, the same code | symbol is attached | subjected. In addition, refer to FIG. 1 to FIG.

  In the belt type continuously variable transmission 1-4 according to the fourth embodiment, when the hydraulic oil supply / discharge valve 70 cannot be forcibly opened by the actuator 80, the ECU 140 as the tension reducing unit reduces the tension of the belt 110. To do. More specifically, the hydraulic pressure Pd of the secondary hydraulic chamber 64, in other words, the belt tension of the belt 110 is basically set to a magnitude corresponding to the engine torque that is the output torque of the internal combustion engine 10 as described above. Therefore, the ECU 140 decreases the engine torque as the output torque from the internal combustion engine 10, and as a result, the hydraulic pressure Pd in the secondary hydraulic chamber 64 is reduced and the tension of the belt 110 is reduced.

  As described above, the hydraulic pressure Pd in the secondary hydraulic chamber 64 has some margin for engine torque, but this margin is used to reduce the hydraulic pressure Pd in the secondary hydraulic chamber 64. Even when the tension of the belt 110 is insufficiently reduced, by reducing the engine torque as in this embodiment, the hydraulic pressure Pd of the secondary hydraulic chamber 64 can be further reduced as a result. The tension of the belt 110 can be sufficiently reduced.

  The engine torque reduction control of the belt type continuously variable transmission 1-4 will be described with reference to FIGS. In this control routine, for example, when it is determined that the hydraulic fluid supply / discharge valve 70 cannot be forcibly opened by the actuator 80 in the gear ratio fixed release control (S104: No in FIG. 10-1), When it is determined that the ratio has not changed (S110: No in FIG. 10-1), the process is repeatedly executed at a control cycle of several ms to several tens of ms. In this control, the ECU 140 sets the valve opening instruction flag to ON, controls the drive hydraulic chamber control device 136 to be ON, and introduces the constant pressure PS into the drive hydraulic chamber 81.

  Then, ECU 140 determines whether or not the gear ratio has changed (S400, time t41 in FIG. 17). If it is determined that the gear ratio has changed (S400: No), the engine torque reduction control is terminated.

  When it is determined that the gear ratio has not changed (S400: Yes), that is, when it is determined that the opening operation of the hydraulic oil supply / discharge valve 70 has failed in the gear ratio fixed release control, the ECU 140 determines whether the internal combustion engine 10 And the engine torque Te is gradually reduced (S402, time t42 in FIG. 17).

  Next, the ECU 140 determines whether or not the gear ratio has changed (S404, time t43 in FIG. 17). When it is determined that the gear ratio has not changed (S404: No), the process returns to S402 and the subsequent processes are repeated.

  If it is determined that the gear ratio has changed (from time t44 to time t45 in FIG. 17) (S404: Yes), the ECU 140 controls the internal combustion engine 10 to end the decrease in the engine torque Te (S406, FIG. 17). At time t44), the engine torque reduction control is terminated. As a result, the hydraulic oil supply / discharge valve 70 can be forcibly opened by the actuator 80, and the gear ratio can be changed.

  According to the belt type continuously variable transmission 1-4 according to the embodiment of the present invention described above, the ECU 140 operates by the actuator 80 in the gear ratio fixed release control when the gear ratio is changed from when the gear ratio is fixed. It is determined whether or not the oil supply / discharge valve 70 can be forcibly opened, and the hydraulic oil supply / discharge control device 130 allows the ECU 140 to forcibly open the hydraulic oil supply / discharge valve 70 using the actuator 80. Is determined, the hydraulic pressure of the hydraulic oil supply / discharge passage is increased before the hydraulic oil supply / discharge valve 70 is opened, so that the differential pressure between the hydraulic pressure P1 confined in the primary hydraulic chamber 55 and the supply pressure Pin The hydraulic pressure P1 of the primary hydraulic chamber 55 can be prevented from abruptly changing when each hydraulic oil supply / discharge valve 70 is opened. As a result, the shift shock when each hydraulic oil supply / discharge valve 70 is opened can be reduced, and the gear ratio can be controlled appropriately.

  Furthermore, according to the belt-type continuously variable transmission 1-4 according to the embodiment of the present invention described above, by reducing the tension of the belt 110, the transmission gear ratio in the closed state of each hydraulic oil supply / discharge valve 70. Since the hydraulic oil pressure P1 of the hydraulic oil held in the primary hydraulic chamber 55 also decreases when the hydraulic pressure is fixed, the hydraulic oil supply / discharge valve 70 can be forcibly opened by the actuator 80, and the gear ratio can be changed. become. As a result, the reliability of the belt type continuously variable transmission 1-4 can be improved.

  Furthermore, according to the belt-type continuously variable transmission 1-4 according to the embodiment of the present invention described above, the ECU 140 as the tension reducing means reduces the engine torque of the internal combustion engine 10. Therefore, the tension of the belt 110 can be reduced by reducing the engine torque generated by the internal combustion engine 10. In addition, for example, even when the hydraulic pressure Pd of the secondary hydraulic chamber 64 is reduced and the tension of the belt 110 is not sufficiently reduced, by reducing the engine torque as in this embodiment, as a result The hydraulic pressure Pd of the secondary hydraulic chamber 64 can be further reduced, and the tension of the belt 110 can be sufficiently reduced.

(Embodiment 5)
FIG. 18 is a flowchart for explaining the gear ratio fixed release control of the belt-type continuously variable transmission according to the fifth embodiment of the present invention, and FIG. 19 is the gear ratio of the belt-type continuously variable transmission according to the fifth embodiment of the present invention. FIG. 20 is a time chart for explaining the unlocking control, and FIG. 20 is a diagram showing an example of a valve opening / decision map of the belt type continuously variable transmission according to the fifth embodiment of the present invention. The belt-type continuously variable transmission according to the fifth embodiment has substantially the same configuration as that of the belt-type continuously variable transmission according to the first embodiment, but it is possible to forcibly open the hydraulic oil supply / discharge valve by the actuator. Is different from the belt type continuously variable transmission according to the first embodiment. In addition, about the structure, effect | action, and effect which are common in embodiment mentioned above, while overlapping description is abbreviate | omitted as much as possible, the same code | symbol is attached | subjected. For the configuration of the main part, refer to FIGS.

  The ECU 140 as a determination unit of the belt-type continuously variable transmission 1-5 according to the fifth embodiment is a primary pulley to which at least engine torque (Te) as output torque from the internal combustion engine 10 and driving force from the internal combustion engine 10 are input. The hydraulic oil supply / discharge valve 70 can be forcibly opened by the actuator 80 based on any one of the input rotational speed (Nin) of 50, the hydraulic pressure (Pd) of the secondary hydraulic chamber 64 and the transmission gear ratio (γ). It is determined whether or not. For example, the ECU 140 determines whether or not the hydraulic oil supply / discharge valve 70 can be opened based on a valve open / disable map m01 for determining whether or not the hydraulic oil supply / discharge valve 70 shown in FIG. 20 is openable. To do. Here, the valve open / close map m01 is a map showing whether or not the hydraulic oil supply / discharge valve 70 can be opened in the relationship between the engine torque (Te) and the hydraulic pressure (Pd) of the secondary hydraulic chamber 64. Middle “○” indicates that valve opening is possible, and “×” indicates that valve opening is not possible. Here, the valve open / close map m01 is described based on the engine torque (Te) and the hydraulic pressure (Pd) of the secondary hydraulic chamber 64. However, the present invention is not limited to this. For example, the engine torque (Te) Further, the map may represent whether or not the hydraulic oil supply / discharge valve 70 can be opened using the input rotation speed (Nin), the hydraulic pressure (Pd) of the secondary hydraulic chamber 64, and the transmission gear ratio (γ) as parameters.

  The gear ratio fixed release control of the belt type continuously variable transmission 1-5 of this embodiment will be described with reference to FIGS. This control routine is repeatedly executed at a control cycle of several ms to several tens of ms.

  First, the ECU 140 determines whether or not there is an instruction to open the hydraulic oil supply / discharge valve 70 (S100). When it is determined that there is no instruction to open the hydraulic oil supply / discharge valve 70 (S100: No), this speed ratio fixation release control is terminated, and it is determined that there is an instruction to open the hydraulic oil supply / discharge valve 70 (S100: Yes), ECU 140 sets the valve opening instruction flag to ON (time t51 in FIG. 19).

  Next, the ECU 140 reads the valve open / close map m01 from a storage unit (not shown) (S502, time t52 in FIG. 19). Then, the ECU 140 (determination means) forces the hydraulic oil supply / discharge valve 70 by the actuator 80 based on, for example, the engine torque (Te) and the hydraulic pressure (Pd) of the secondary hydraulic chamber 64 based on the valve opening / possibility map m01. It is determined whether or not the valve can be opened (S504, time t53 in FIG. 19).

  If it is determined that the hydraulic oil supply / discharge valve 70 cannot be forcibly opened by the actuator 80 (S504: No), the gear ratio fixed release control is terminated.

  When it is determined that the hydraulic oil supply / discharge valve 70 can be forcibly opened by the actuator 80 (S <b> 504: Yes), the hydraulic oil supply / discharge control device 130 performs the operation before the hydraulic oil supply / discharge valve 70 is opened. The hydraulic oil supply pressure Pin supplied to the primary hydraulic chamber 55 is increased (S106, time t54 in FIG. 19), and the hydraulic oil supply / discharge valve 70 is opened (S108, time t55 in FIG. 19). . Then, ECU 140 determines whether or not the gear ratio has changed (S110), and when it is determined that the gear ratio has not changed (S110: No), this process is repeatedly executed to change the gear ratio. If it is determined (from time t55 to time t56 in FIG. 19) (S110: Yes), the gear ratio fixed release control is terminated.

  According to the belt-type continuously variable transmission 1-5 according to the embodiment of the present invention described above, the ECU 140 operates by the actuator 80 in the gear ratio fixed release control when the gear ratio is changed from when the gear ratio is fixed. It is determined whether or not the oil supply / discharge valve 70 can be forcibly opened, and the hydraulic oil supply / discharge control device 130 allows the ECU 140 to forcibly open the hydraulic oil supply / discharge valve 70 using the actuator 80. Is determined, the hydraulic pressure of the hydraulic oil supply / discharge passage is increased before the hydraulic oil supply / discharge valve 70 is opened, so that the differential pressure between the hydraulic pressure P1 confined in the primary hydraulic chamber 55 and the supply pressure Pin The hydraulic pressure P1 of the primary hydraulic chamber 55 can be prevented from abruptly changing when each hydraulic oil supply / discharge valve 70 is opened. As a result, the shift shock when each hydraulic oil supply / discharge valve 70 is opened can be reduced, and the gear ratio can be controlled appropriately.

  Furthermore, according to the belt-type continuously variable transmission 1-5 according to the embodiment of the present invention described above, the ECU 140 includes at least the engine torque (Te) as the output torque from the internal combustion engine 10 and the drive from the internal combustion engine 10. Based on any one of the input rotational speed (Nin) of the primary pulley 50 to which the force is input, the hydraulic pressure (Pd) of the secondary hydraulic chamber 64 and the transmission gear ratio (γ), It is determined whether forcible valve opening is possible. Therefore, it can be determined whether or not the hydraulic oil supply / discharge valve 70 can be forcibly opened by the actuator 80 according to the operating state of the belt type continuously variable transmission 1-5 or the internal combustion engine 10. Responsiveness is good and reliability can be improved. For example, when it is determined that the hydraulic oil supply / discharge valve 70 cannot be forcibly opened by the actuator 80 in the gear ratio fixed release control (S504: No), it is determined that the gear ratio has not changed. In the case (S110: No) or the like, when the tension of the belt 110 is reduced by reducing the engine torque of the internal combustion engine 10 or reducing the hydraulic pressure Pd of the secondary hydraulic chamber 64, etc. Therefore, the amount of decrease in the engine torque and the amount of pressure reduction of the hydraulic pressure Pd in the secondary hydraulic chamber 64 can be set, so that the hydraulic oil supply / discharge valve 70 can be forcibly opened by the actuator 80 with high responsiveness. The ratio can be changed.

  The belt-type continuously variable transmission according to the above-described embodiment of the present invention is not limited to the above-described embodiment, and various modifications can be made within the scope described in the claims. The belt type continuously variable transmission according to the embodiment of the present invention may be configured by combining a plurality of the embodiments described above.

  As described above, the belt-type continuously variable transmission according to the present invention can appropriately control the gear ratio, and is suitable for application to various belt-type continuously variable transmissions.

It is a skeleton figure of the belt type continuously variable transmission concerning Embodiment 1 of the present invention. It is principal part sectional drawing of the primary pulley at the time of gear ratio fixed of the belt-type continuously variable transmission which concerns on Embodiment 1 of this invention (valve closed state). It is a figure which shows the torque cam of the belt-type continuously variable transmission which concerns on Embodiment 1 of this invention. It is a figure which shows the torque cam of the belt-type continuously variable transmission which concerns on Embodiment 1 of this invention. It is a figure which shows the structural example of the hydraulic-oil supply / discharge control apparatus of the belt-type continuously variable transmission which concerns on Embodiment 1 of this invention. It is principal part sectional drawing of the primary pulley at the time of gear ratio reduction of the belt-type continuously variable transmission which concerns on Embodiment 1 of this invention (at the time of upshift). It is a figure which shows operation | movement of the hydraulic-oil supply / discharge control apparatus at the time of the gear ratio reduction (at the time of upshift) of the belt-type continuously variable transmission which concerns on Embodiment 1 of this invention. It is principal part sectional drawing of the primary pulley at the time of the gear ratio increase (at the time of downshift) of the belt-type continuously variable transmission which concerns on Embodiment 1 of this invention. It is a figure which shows operation | movement of the hydraulic-oil supply / discharge control apparatus at the time of the gear ratio increase (at the time of downshift) of the belt-type continuously variable transmission which concerns on Embodiment 1 of this invention. 3 is a flowchart illustrating transmission ratio fixing control of the belt type continuously variable transmission according to the first embodiment of the present invention. It is a time chart explaining gear ratio fixed control of the belt type continuously variable transmission which concerns on Embodiment 1 of this invention. 5 is a flowchart for explaining speed ratio fixed release control of the belt-type continuously variable transmission according to the first embodiment of the present invention. It is a time chart explaining the gear ratio fixed release control of the belt type continuously variable transmission according to the first embodiment of the present invention. It is the figure which showed typically the part containing the piston of the actuator of the belt-type continuously variable transmission which concerns on Embodiment 1 of this invention. It is a flowchart explaining the gear ratio fixed release control of the belt type continuously variable transmission according to the second embodiment of the present invention. It is a time chart explaining the gear ratio fixed release control of the belt type continuously variable transmission according to the second embodiment of the present invention. It is a flowchart explaining the secondary hydraulic pressure reduction control of the belt type continuously variable transmission according to the third embodiment of the present invention. It is a time chart explaining the secondary hydraulic pressure reduction control of the belt type continuously variable transmission according to the third embodiment of the present invention. It is a flowchart explaining the engine torque reduction control of the belt-type continuously variable transmission which concerns on Embodiment 4 of this invention. It is a time chart explaining the engine torque reduction control of the belt-type continuously variable transmission which concerns on Embodiment 4 of this invention. It is a flowchart explaining the gear ratio fixed cancellation | release control of the belt-type continuously variable transmission which concerns on Embodiment 5 of this invention. It is a time chart explaining gear ratio fixed release control of the belt type continuously variable transmission which concerns on Embodiment 5 of this invention. It is a figure which shows an example of the valve opening possibility map of the belt-type continuously variable transmission which concerns on Embodiment 5 of this invention.

Explanation of symbols

1-1, 1-2, 1-3, 1-4, 1-5 Belt type continuously variable transmission 10 Internal combustion engine (drive source)
20 transaxle 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 51c, d shaft side communication passage 52 primary fixed sheave 53 primary movable sheave 54 primary partition wall 54a valve arrangement Passage 54b, e Bulkhead side communication passage 54c Sliding support hole 54d Notch 54f Recess 55 Primary hydraulic chamber (one clamping pressure generating hydraulic chamber)
56 Cover member 60 Secondary pulley 64 Secondary hydraulic chamber (the other clamping pressure generating hydraulic chamber)
DESCRIPTION OF SYMBOLS 70 Hydraulic oil supply discharge valve 71 Valve body 72 Valve seat surface 73 Valve body holding member 74 Valve body elastic member 75 Snap ring 80 Actuator 81 Drive hydraulic chamber 82 Piston 82a Pressure receiving member 82b Press member 90 Final reduction gear 100 Power transmission path 110 Belt 112 Pulley bearing 120 Wheel 130 Hydraulic oil supply / discharge control device (hydraulic oil supply / discharge control means)
131 Oil pan 132 Oil pump 133 Line pressure control device 134 Constant pressure control device 135 Primary hydraulic chamber control device 136 Drive hydraulic chamber control device 137 Secondary hydraulic chamber control device 140 ECU (determination means, tension reduction means)
150 Input Rotational Speed Sensor 160 Output Rotational Speed Sensor S1 Primary Hydraulic Chamber Seal Member S2 Piston Seal Member

Claims (8)

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;
A hydraulic oil supply / discharge valve that opens in a direction to supply hydraulic oil to one of the clamping pressure generating hydraulic chambers;
An actuator for forcibly opening the hydraulic oil supply and discharge valve by sliding the piston in one of the sliding directions with respect to the drive hydraulic chamber by the hydraulic pressure of the drive hydraulic chamber;
When the hydraulic oil supply / discharge valve is forcibly opened by the actuator, the hydraulic oil is supplied to the one clamping pressure generation hydraulic chamber via the hydraulic oil supply / discharge passage, or from the one clamping pressure generation hydraulic chamber. Hydraulic oil supply / discharge control means for controlling the gear ratio by discharging hydraulic oil;
Determination means for determining whether the hydraulic oil supply / discharge valve can be forcibly opened by the actuator when the speed ratio is changed,
When the determination means determines that the hydraulic oil supply / discharge valve can be forcibly opened by the actuator, the hydraulic oil supply / discharge control means before the valve opens, the hydraulic oil supply / discharge passage It is characterized by increasing the hydraulic pressure of
Belt type continuously variable transmission. The determination means determines whether the hydraulic oil supply / discharge valve can be forcibly opened by the actuator based on the hydraulic pressure of the one clamping pressure generating hydraulic chamber and the hydraulic pressure of the driving hydraulic chamber. It is characterized by
The belt-type continuously variable transmission according to claim 1. The hydraulic oil supply / discharge control means, when the determination means determines that the hydraulic oil supply / discharge valve can be forcibly opened by the actuator, the gear ratio is changed to a decreasing side. The hydraulic pressure of the hydraulic oil supply / discharge passage is increased before the valve opening, while the hydraulic pressure of the hydraulic oil supply / discharge passage before the valve opening is increased when the gear ratio is changed to the increase side. Characterized by prohibition,
The belt-type continuously variable transmission according to claim 1 or 2. A tension reducing means for reducing the tension of the belt when the hydraulic oil supply / discharge valve cannot be forcibly opened by the actuator;
The belt-type continuously variable transmission according to any one of claims 1 to 3. The tension reducing means reduces the hydraulic pressure of the other clamping pressure generating hydraulic chamber,
The belt-type continuously variable transmission according to claim 4. The tension reducing means reduces the output torque from the drive source,
The belt type continuously variable transmission according to claim 4 or 5. The determination means includes at least an output torque of the driving source, an input rotation speed of a pulley to which a driving force from the driving source is input among the pulleys, a hydraulic pressure of the other clamping pressure generating hydraulic chamber, and a transmission ratio. Based on any one of the above, it is determined whether or not the hydraulic oil supply / discharge valve can be forcibly opened by the actuator.
The belt-type continuously variable transmission according to any one of claims 1 to 6. The hydraulic oil supply / discharge control means reduces the hydraulic pressure of the hydraulic oil supply / discharge passage after the hydraulic oil supply / discharge valve is closed,
The belt-type continuously variable transmission according to any one of claims 1 to 7.

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