JP2008101753A - Belt type continuously variable transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a belt type continuously variable transmission capable of inhibiting the increase of drive loss of an oil pump. <P>SOLUTION: The belt type continuously variable transmission is provided with a primary pulley 50, a secondary pulley, a belt 110 wound around the primary pulley 50 and the secondary pulley, a primary hydraulic pressure chamber 55, each working fluid supply discharge valve 70 permitting supply of working fluid to a primary hydraulic pressure chamber 55, controlling permission or prohibition of discharge of the working fluid from the primary hydraulic pressure chamber 55, and rotating as one unit with the primary pulley 50, and foreign matter collecting devices 81, 82. The foreign matter collection deices 81, 82 collect foreign matter included in the working fluid in the primary hydraulic pressure chamber 55 and the working fluid supplied to the primary hydraulic pressure chamber 55. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

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

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

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

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

JP 2001-323978 A

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

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

  In order to solve the above-described problems and achieve the object, in the present invention, two pulleys and a driving force from a driving source wound around each pulley and transmitted to one pulley are transmitted to the other pulley. A clamping pressure generating hydraulic chamber that is formed in each pulley and generates a belt clamping pressure with respect to the belt by hydraulic pressure, and the clamping pressure generating hydraulic chamber is one of the clamping pressure generating hydraulic chambers. A hydraulic oil supply valve that allows only hydraulic oil to be supplied and rotates integrally with the one pulley; and permits or prohibits discharge of the hydraulic oil from the one clamping pressure generating hydraulic chamber; A hydraulic oil discharge valve that rotates integrally with the hydraulic fluid, hydraulic fluid supply control means for controlling the transmission ratio by supplying the hydraulic oil to at least each of the clamping pressure generating hydraulic chambers, at least the hydraulic oil supply control means, pressure Characterized in that it and a foreign matter collecting means for collecting foreign substances contained in the hydraulic fluid present between the raw hydraulic chamber.

  According to this invention, when changing the gear ratio, the hydraulic oil supply control means supplies hydraulic oil to the clamping pressure generating hydraulic chamber or controls the hydraulic oil discharge valve to operate from the clamping pressure generating hydraulic chamber. Drain the oil. On the other hand, when the gear ratio is fixed (constant), the hydraulic oil discharge valve is controlled to prohibit the hydraulic oil from being discharged from the clamping pressure generating hydraulic chamber. That is, since the hydraulic oil supply valve only allows the hydraulic oil to be supplied to the clamping pressure generating hydraulic chamber, the hydraulic oil in the clamping pressure generating hydraulic chamber is held in the clamping pressure generating hydraulic chamber. . Therefore, even if the position of the movable sheave in the axial direction with respect to the fixed sheave is changed, the position of the movable sheave in the axial direction with respect to the fixed sheave can be maintained constant by changing the oil pressure in the one clamping pressure generating hydraulic chamber. Can do. Thus, in order to maintain the position of the movable sheave in the axial direction with respect to the fixed sheave, it is not necessary to supply hydraulic oil to the clamping pressure generating hydraulic chamber from outside the clamping pressure generating hydraulic chamber. The hydraulic oil can be prevented from leaking from the sliding portion. Thereby, an increase in driving loss of the oil pump can be suppressed.

  Here, in order to retain the hydraulic oil in one clamping pressure generating hydraulic chamber when the speed ratio is fixed, the sealing performance of the one clamping pressure generating hydraulic chamber is ensured, and one clamping pressure generating hydraulic chamber is secured. Therefore, leakage of hydraulic oil from the engine is suppressed. However, if the hydraulic oil held in one clamping pressure generating hydraulic chamber contains foreign matter such as friction powder, these foreign matters may reduce the sealing performance of the hydraulic oil supply valve or hydraulic oil discharge valve. There is. According to the present invention, the foreign matter contained in the hydraulic oil interposed between the hydraulic oil supply control means and the one clamping pressure generating hydraulic chamber, that is, the foreign matter contained in the hydraulic oil held in the one clamping pressure generating hydraulic chamber. Alternatively, the foreign matter contained in the hydraulic oil supplied to one clamping pressure generating hydraulic chamber is collected by the foreign matter collecting means. Accordingly, it is possible to reduce foreign matter contained in the hydraulic oil interposed between the hydraulic oil supply control means and one of the clamping pressure generating hydraulic chambers. Accordingly, it is possible to suppress a decrease in the sealing performance of the hydraulic oil supply valve and the hydraulic oil discharge valve, and it is possible to reliably hold the hydraulic oil in one clamping pressure generating hydraulic chamber.

  According to the present invention, in the belt type continuously variable transmission, the foreign matter collecting means rotates integrally with the one pulley.

  According to the present invention, since the foreign matter collecting means is provided so as to rotate integrally with one pulley, the fixing member of the hydraulic oil interposed between the hydraulic oil supply control means and the one clamping pressure generating hydraulic chamber is The foreign substance of the hydraulic oil which intervenes in one clamping pressure generation hydraulic chamber side rather than the sliding part with a movable member is collected. Therefore, since there is no sliding part between the fixed member and the movable member between the foreign matter collecting means and one of the clamping pressure generating hydraulic chambers, it is included in the hydraulic oil in which the foreign matter has been collected by the foreign matter collecting means. It is possible to suppress an increase in foreign matter. Accordingly, it is possible to suppress a decrease in the sealing performance of the hydraulic oil supply valve and the hydraulic oil discharge valve, and it is possible to reliably hold the hydraulic oil in one clamping pressure generating hydraulic chamber.

  According to the present invention, in the belt type continuously variable transmission, the foreign matter collecting means is a hydraulic oil through which hydraulic oil supplied to the one clamping pressure generating hydraulic chamber or the one clamping pressure hydraulic chamber passes. The collecting groove is formed in at least one of the passages.

  Here, centrifugal force acts on the hydraulic oil for operation in one clamping pressure generating hydraulic chamber or the hydraulic oil passing through the hydraulic oil passage by rotation of one pulley. Accordingly, the foreign matter contained in the hydraulic oil collects on the inner wall surface of one clamping pressure generating hydraulic chamber or the inner wall surface of the hydraulic oil passage. According to this invention, as the foreign matter collecting means, since the collecting groove is formed on the inner wall surface of one clamping pressure generating hydraulic chamber and the inner wall surface of the hydraulic oil passage, one pulley rotates, Foreign matter contained in the hydraulic oil can be collected.

  According to the present invention, in the belt type continuously variable transmission, the foreign matter collecting means is a hydraulic oil passage through which hydraulic oil supplied to the one clamping pressure generating hydraulic chamber or the one clamping pressure hydraulic chamber passes. It is the magnetic body arrange | positioned in at least any one of these, It is characterized by the above-mentioned.

  Here, the foreign matter contained in the hydraulic oil is mainly generated by the friction of the sliding portion between the fixed member and the movable member, and includes a magnetic material. According to the present invention, since the magnetic body is disposed in the one clamping pressure generating hydraulic chamber or the hydraulic oil passage as the foreign substance collecting means, the foreign substance of the magnetic substance contained in the hydraulic oil can be reliably collected. As a result, foreign substances contained in the hydraulic oil can be collected.

  According to the present invention, in the belt-type continuously variable transmission, the magnetic body is a magnetized snap ring, and the magnetized snap ring is disposed in the collecting groove.

  According to the present invention, the groove that holds the magnetized snap ring is the collection groove. Therefore, the magnetized snap ring can surely secure the foreign matter of the magnetic material, and one pulley is rotated by the collecting groove, so that the inner wall surface of one of the clamping pressure generating hydraulic chambers and the hydraulic oil Foreign matter that collects on the inner wall surface of the passage can be collected.

  In the belt-type continuously variable transmission according to the present invention, the belt-type continuously variable transmission includes a rotational force imparting unit that imparts a rotational force to the hydraulic oil and generates a flow toward the foreign matter collecting unit.

  According to the present invention, the rotational force applying means can positively make the flow of hydraulic oil toward the foreign matter collecting means as one pulley rotates. Accordingly, the foreign oil contained in the hydraulic oil is easily collected by the foreign matter collecting means due to the flow of the working oil in the vicinity of the foreign matter collecting means. As a result, foreign matter contained in the hydraulic oil interposed between the hydraulic oil supply control means and one of the clamping pressure generating hydraulic chambers can be further reduced, and the sealing performance of the hydraulic oil supply valve and hydraulic oil discharge valve is reduced. The hydraulic oil in one of the clamping pressure generating hydraulic chambers can be held more reliably.

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

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

  The belt type continuously variable transmission according to the present invention can prevent the hydraulic oil from being discharged from the clamping pressure generating hydraulic chamber when the transmission gear ratio is fixed, so that an increase in driving loss of the oil pump can be suppressed. . Further, since the foreign matter collecting means is provided, the hydraulic oil in one clamping pressure generating hydraulic chamber can be reliably held.

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

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

  As shown in FIG. 1, a transaxle 20 is disposed on the output side of the internal combustion engine 10 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 accommodated in the transaxle housing 21. On the other hand, inside the case constituted by the transaxle case 22 and the transaxle rear cover 23, a primary pulley 50 and a secondary pulley 60, which are two pulleys constituting the belt type continuously variable transmission 1 according to the present invention, The primary hydraulic chamber 55, the secondary hydraulic chamber 64, the hydraulic oil supply / discharge valve 70, the foreign matter collecting devices 81 and 82, the fins 83 and 84, and the belt 110 are accommodated. Yes. 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 control device that is hydraulic oil supply control means, and 140 is ECU (Engine Control Unit).

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

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

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

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

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

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

  An oil pump 26 is provided between the torque converter 30 and a forward / reverse switching mechanism 40 described later. The oil pump 26 supplies hydraulic oil to the hydraulic oil supply control device 130. The oil pump 26 includes a rotor 27, a hub 28, and a body 29. The oil pump 26 is connected to the pump 31 by a rotor 27 via a cylindrical hub 28. A body 29 is fixed to the transaxle case 22. The hub 28 is splined to the hollow shaft 36. Accordingly, the oil pump 26 is driven by the output torque from the internal combustion engine 10 being transmitted to the rotor 27 via the pump 31. That is, the oil pump 26 increases the discharge amount of the discharged hydraulic oil, that is, the hydraulic pressure of the hydraulic oil supplied to the hydraulic oil supply control device 130 increases as the rotational speed of the internal combustion engine 10 increases.

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

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

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

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

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

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

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

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

  As shown in FIG. 2, the primary pulley shaft 51 is rotatably supported by 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.

  The supply / discharge side main passage 51a is formed on the primary fixed sheave side, and is a hydraulic oil passage through which hydraulic oil supplied to the primary hydraulic chamber 55, which is one clamping pressure hydraulic chamber, passes. That is, the hydraulic oil supplied from the hydraulic oil supply control device 130 to the primary hydraulic chamber 55 flows into the supply / discharge side main passage 51a. Further, hydraulic oil discharged from the primary hydraulic chamber 55 flows into the supply / discharge-side main passage 51a. The supply / discharge-side main passage 51a is formed between a plurality of shaft-side communication passages 51c (three in the circumferential direction in this embodiment) formed in the vicinity of the front end portion and between the primary movable sheave 53 and the primary pulley shaft 51. This space portion T1 communicates with each partition wall side communication passage 54f described later. The shaft-side communication passage 51c and the space portion T1 communicate with each other via a spline 53c of the primary movable sheave 53 described later and a spline 51e of the primary pulley shaft 51.

  Further, the drive side main passage 51b is formed on the side opposite to the primary fixed sheave side, and hydraulic oil supplied from the hydraulic oil supply control device 130 to the drive hydraulic chamber 78 of each hydraulic oil supply / discharge valve 70 flows in. . Further, the primary pulley shaft 51 has a plurality of shaft side communication passages 51d that allow the hydraulic oil flowing into the drive side main passage 51b to flow into the space T2 formed between the primary partition wall 54 and the primary pulley shaft 51 (this implementation). In the example, it is formed in two places in the circumferential direction). Therefore, the drive-side main passage 51b is connected to each drive hydraulic chamber 78 (in this embodiment, in the circumferential direction) via each shaft-side communication passage 51d, the space T2, and each partition-side communication passage 54e described later of the primary partition 54. 3 places). A seal member S such as a seal ring is provided between the primary partition wall 54 and the primary pulley shaft 51 so as to sandwich the space T2. That is, the space T2 is sealed by the seal member S.

  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 this 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 has a spline 53c formed on the inner peripheral surface of the cylindrical portion 53a and a spline 51e formed on the outer peripheral surface of the primary pulley shaft 51. It is slidably supported in the axial direction. Between the primary fixed sheave 52 and the primary movable sheave 53, that is, between the surface of the primary fixed sheave 52 facing the primary movable sheave 53 and the surface of the primary movable sheave 53 facing the primary fixed sheave 52. A primary groove 110a having a shape is formed.

  As shown in FIG. 2, the primary partition wall 54 is an annular member, and is arranged around the same rotational axis as the primary pulley shaft 51. The primary partition 54 is disposed so as to face the primary fixed sheave 52 in the axial direction with the primary movable sheave 53 interposed therebetween. The primary partition wall 54 is configured to rotate integrally with the primary pulley shaft 51 by spline-fitting a spline 54g formed on the inner peripheral surface thereof and a spline 51g formed on the outer peripheral surface of the primary pulley shaft 51. Is provided.

  The primary partition wall 54 is formed with a supply / discharge passage 54a and a drive passage 54b in the vicinity of the central portion in the radial direction with a protrusion 54c interposed therebetween. One end portion (left end portion in the figure) of the supply / discharge passage 54a is open to the primary hydraulic chamber 55, and the other end portion (right end portion in the figure) is formed through a space T3 formed by the protrusion 54c. And communicated with the drive passage 54b. The drive passage 54b has one end (the left end in the figure) communicating with the supply / discharge passage 54a via the space T3, and the other end (the right end in the figure) is outside the primary partition wall 54. It is open. The supply / discharge passage 54a and the drive passage 54b have a cylindrical shape, and are formed at a plurality of locations on the circumference of the primary partition wall 54 at equal intervals (in this embodiment, three locations). A hydraulic oil supply / discharge valve 70 is disposed in each of the supply / discharge passage 54a and the drive passage 54b.

  The primary partition wall 54 is formed with partition wall side communication passages 54e and 54f corresponding to the supply / discharge passages 54a and the drive passages 54b, respectively (three in this embodiment). Each partition wall side communication passage 54e has one end communicating with the drive side main passage 51b via the space T2 and each shaft side communication passage 51d, and the other end is closed by a closing member 54h. Each partition-side communication passage 54e communicates with each drive passage 54b in the middle of the passage. That is, each partition wall side communication passage 54e is a part of each drive hydraulic chamber 78 described later, and does not open to the space T3 facing each drive hydraulic chamber 78 and each piston 77 therebetween. That is, each partition wall side communication passage 54e communicates only with each drive hydraulic chamber 78 in each drive passage 54b. Therefore, the hydraulic oil in the drive side main passage 51b flowing into each partition wall side communication passage 54e is supplied only to each drive hydraulic chamber 78.

  Each partition-side communication passage 54f has one end communicating with the drive-side main passage 51b via the space T3 and each shaft-side communication passage 51d, and the other end communicating with the space T3. Therefore, the hydraulic oil in the supply / discharge side main passage 51a flowing into each partition wall side communication passage 54f is supplied to each space T3.

  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 pulley shaft 51, the primary movable sheave 53, and the primary partition wall 54. Here, between the protrusion 53d of the primary movable sheave 53 and the primary partition wall 54 and between the cylindrical portion 53a of the primary movable sheave 53 and the primary pulley shaft 51, for example, a seal member S such as a seal ring is provided. ing. That is, the space formed by the primary pulley shaft 51, the primary movable sheave 53, and the primary partition wall 54 constituting the primary hydraulic chamber 55 is sealed by the seal member S.

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

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

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

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

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

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

  The secondary hydraulic chamber 64 is supplied with hydraulic oil from the hydraulic oil supply 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 oil supply control device 130, that is, the internal pressure of the secondary hydraulic chamber 64, and the secondary movable sheave 63 63 is moved toward or away from the secondary fixed sheave 62. Thus, the secondary hydraulic chamber 64 generates a belt clamping pressure with respect to the belt 110 by the internal pressure of the secondary hydraulic chamber 64, and maintains a constant contact radius of the belt 110 with respect to the primary pulley 50 and the secondary pulley 60.

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

  The intermediate member 67 is formed integrally with the secondary partition wall 65 or fixed to the secondary partition wall 65, and is supported by the bearings 113 and 115 so as to be relatively rotatable on the secondary pulley shaft 61 with respect to the secondary pulley shaft 61 and the secondary movable sheave 63. Has been. 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 bearing 113, relative rotation occurs between the secondary movable sheave 63 and the intermediate member 67. Then, as shown in FIG. 3A, the first engagement portion 63b and the second engagement portion 67a are brought close to each other by the plurality of transmission members 68, as shown in FIG. The portion 63b and the second engaging portion 67a are changed to a separated state. As a result, the torque cam 66 generates a belt clamping pressure with respect to the belt 110 in the secondary pulley 60.

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

  The hydraulic oil supply / discharge valve 70 is a hydraulic oil supply valve and a hydraulic oil discharge valve. In other words, the hydraulic oil supply / discharge valve 70 allows only hydraulic oil to be supplied to the primary hydraulic chamber 55 that is one clamping pressure generating hydraulic chamber, and allows or prohibits the hydraulic oil to be discharged from the primary hydraulic chamber 55. It is something to control. As shown in FIGS. 2, 4, and 5, the hydraulic oil supply / discharge valve 70 is connected to the primary hydraulic chamber 55 from the outside of the primary hydraulic chamber 55 that is one clamping pressure generating hydraulic chamber, that is, from the outside of the primary pulley 50. The hydraulic oil is supplied, the hydraulic oil is discharged from the primary hydraulic chamber 55 to the outside of the primary pulley 50, and the hydraulic oil in the primary hydraulic chamber 55 is retained. In this embodiment, the hydraulic oil supply / discharge valve 70 is provided corresponding to a supply / discharge passage 54a and a drive passage 54b formed in the primary partition wall 54 of the primary pulley 50, which is one pulley. The hydraulic oil supply / discharge valve 70 is provided at a plurality of positions on the circumference with respect to the primary partition wall 54, for example, at three equal intervals. 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 includes a ball type check valve and an actuator that opens the check valve by hydraulic pressure. Each of the ball type check valves is disposed in the supply / discharge passage 54 a and includes a valve body 71, a valve seat 72, an elastic member 73, a ring member 74, and a locking member 75. . Reference numeral 76 denotes a casing that is inserted into each supply / discharge passage 54 a and houses the valve body 71, the valve seat 72, the elastic member 73, the ring member 74, and the locking member 75.

  Each valve element 71 has a spherical shape, is disposed closer to the primary hydraulic chamber than the valve seat 72, and has a diameter larger than the inner diameter of the valve seat 72. The valve seat 72 has a cylindrical shape and is fixed by the protrusion 54 c and the casing 76. Each elastic member 73 is disposed in a state of being biased between the valve member 71 and the ring member 74 fixed to the supply / discharge passage 54 a by the locking member 75 via the valve body 71. Each elastic member 73 generates a valve closing urging force in a direction in which the valve body 71 comes into contact with the valve seat 72, and this valve closing urging force is a direction in which the valve body 71 comes into contact with the valve seat 72, that is, a valve closing direction. Each of the valve bodies 71 acts as a pressing force. Each locking member 75 has a disk shape, and an opening for allowing hydraulic oil to pass therethrough is formed at the center thereof.

  Here, when each hydraulic oil supply / discharge valve 70 is opened, the valve body valve opening direction pressing force which is a pressing force acting on the valve body 71 in the direction in which the valve body 71 moves away from the valve seat 72, that is, the valve opening direction. However, when the valve body 71 exceeds the valve body closing direction pressing force which is a pressing force acting on the valve body 71 in the direction in which the valve body 71 contacts the valve seat 72, that is, in the valve closing direction, the valve body 71 is separated from the valve seat 72. Done. The valve body opening direction pressing force is the pressure of the hydraulic oil supplied from the partition wall side communication passage 54e to the space portion T2, that is, the hydraulic pressure P2 of the space portion T2. On the other hand, the valve body closing direction pressing force includes the valve closing urging force and the hydraulic pressure P1 of the primary hydraulic chamber 55. Since the hydraulic pressure P1 of the primary hydraulic chamber 55 acts as a valve-closing pressing force on the valve body 71, the valve body 71 may be separated from the valve seat step portion 72 even if the hydraulic pressure P1 of the primary hydraulic chamber 55 rises. Absent. 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.

  Further, 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 chamber is supplied from the hydraulic oil supply control device 130. When the hydraulic oil is continuously supplied to the primary hydraulic chamber 55, the hydraulic oil of a predetermined pressure exists in the hydraulic oil supply path from the hydraulic oil supply control device 130 to the primary hydraulic chamber 55. The hydraulic oil supply path includes a plurality of sliding portions between the fixed member and the movable member. When the transmission gear ratio is fixed, hydraulic oil of a predetermined pressure is moved from the sliding portion to the outside of the hydraulic oil supply path. There was a risk of leakage. This fixing member is a member that does not rotate, slide, or the like among the members constituting the belt type continuously variable transmission 1. For example, a transaxle housing 21, a transaxle case 22, and a transaxle rear cover 23 of the transaxle 20. On the other hand, this movable member is a member that rotates, slides, etc. in the members constituting the belt type continuously variable transmission 1. For example, the primary pulley shaft 51 or the like. Therefore, the sliding portion includes, for example, a portion where the primary pulley shaft 51 rotates with respect to the transaxle housing 21, the transaxle case 22, the transaxle rear cover 23, and the like of the transaxle 20.

  In the belt type continuously variable transmission 1 according to this 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 26 can be suppressed.

  An actuator for opening each ball type check valve is disposed in the drive passage 54 b and is constituted by a piston 77 and a drive hydraulic chamber 78. The piston 77 moves the valve body 71 in the valve opening direction. The piston 77 is supported by each drive passage 54b so as to be slidable in the direction of the on-off valve. Each piston 77 has a cylindrical shape, and a valve body pressing projection 77a is formed at an end in the valve opening direction. Each valve body pressing projection 77a protrudes from the end in the valve opening direction of the drive passage 54b to each supply / discharge passage 54a via the space T2. Each of the valve body pressing projections 77a is slid in the valve opening direction by the piston valve opening direction pressing force acting on the piston 77 by the hydraulic pressure P3 of the drive hydraulic chamber 78. Contact. The piston valve opening direction pressing force acting on each piston 77 acts on each valve body 71 as the valve body valve opening direction pressing force. Therefore, even if this piston valve opening direction pressing force exceeds the valve body closing direction pressing force, each valve body 71 moves in the valve opening direction with respect to the valve seat 72, and each hydraulic oil supply / discharge valve 70 is moved. Open the valve. That is, each hydraulic oil supply / discharge valve 70 is forcibly opened in the direction in which the hydraulic oil is discharged from the primary hydraulic chamber 55 to the outside. Accordingly, the hydraulic oil supply / discharge valve 70 is the same as the hydraulic oil supply valve and the hydraulic oil discharge valve. Therefore, the hydraulic oil is supplied to the primary hydraulic chamber 55, which is one clamping pressure generating hydraulic chamber, The hydraulic oil can be discharged from the hydraulic chamber 55 and retained in the primary hydraulic chamber 55 with a single valve. Note that the hydraulic pressure P3 of the drive hydraulic chamber 78 is used to control the permission or prohibition of the discharge of hydraulic oil from the primary hydraulic chamber 55, which is one of the clamping pressure generating hydraulic chambers. Instead, rotational force such as a motor or electromagnetic force may be used.

  Each drive hydraulic chamber 78 is supplied with hydraulic oil, and the hydraulic oil supply / discharge valve 70 is controlled by the pressure of the supplied hydraulic oil, that is, the hydraulic pressure P3 of the drive hydraulic chamber 78. . Each hydraulic oil supply / discharge valve 70 is controlled by the hydraulic pressure P <b> 3 of the drive hydraulic chamber 78 to permit or prohibit the discharge of hydraulic oil from the primary hydraulic chamber 55. Each drive hydraulic chamber 78 is formed between the drive passage 54b, the partition wall side communication passage 54e, the piston 77, and the closing members 54d and h. The hydraulic oil is supplied to the drive hydraulic chambers 78 from the hydraulic oil supply controller 130 via the drive-side main passages 51b, the shaft-side communication passages 51d, the space portions T1, and the partition wall-side communication passages 54e. Therefore, the piston valve opening direction pressing force acts on each piston 77 by the hydraulic pressure P <b> 3 of each drive hydraulic chamber 78.

  The foreign matter collecting devices 81 and 82 are foreign matter collecting means, and are interposed between the hydraulic oil supply control device 130 that is hydraulic oil supply control means and the primary hydraulic chamber 55 that is one clamping pressure generating hydraulic chamber. Foreign matter contained in hydraulic oil is collected. That is, the foreign matter collecting devices 81 and 82 collect the foreign oil contained in the hydraulic fluid supplied to the primary hydraulic chamber 55 or the hydraulic fluid supplied to the primary hydraulic chamber 55, that is, the hydraulic fluid in the primary hydraulic chamber 55. Is.

  The foreign matter collecting device 81 collects foreign matter of hydraulic oil in the primary hydraulic chamber 55. The foreign matter collecting device 81 is provided in the primary hydraulic chamber 55. Accordingly, the foreign matter collecting device 81 rotates integrally with the primary pulley 50 that is one pulley. The foreign matter collecting device 81 includes a collecting groove 81a and a snap ring 81b.

  The collecting groove 81a is a foreign matter collecting means, and is formed in the primary hydraulic chamber 55 which is one clamping pressure generating hydraulic chamber. In this embodiment, the collection groove 81 a is formed on the primary fixed sheave side of the radially inner surface of the protruding portion 53 d of the primary movable sheave 53 constituting the primary hydraulic chamber 55. The collection groove 81a is formed to extend in the circumferential direction.

  The snap ring 81b is a foreign matter collecting means and is a magnetic body. The snap ring 81b is disposed in the primary hydraulic chamber 55 that is one clamping pressure generating hydraulic chamber. In this embodiment, the snap ring 81b is disposed in the primary hydraulic chamber 55 by being disposed in the collection groove 81a. That is, the collection groove 81a is used as a groove for holding the snap ring 81b. Therefore, when the collecting groove 81a and the snap ring 81b are provided in the primary hydraulic chamber 55 as foreign matter collecting means, the collecting groove 81a can be shared as a groove for holding the snap ring 81b. Thereby, size reduction and cost reduction can be achieved.

  The foreign matter collecting device 82 collects foreign matter of hydraulic oil supplied to the primary hydraulic chamber 55. The foreign matter collecting device 82 is provided in the supply / discharge-side main passage 51a of the primary pulley shaft 51, which is a working oil passage through which the working oil supplied to the primary hydraulic chamber 55 which is one clamping pressure hydraulic chamber passes. Yes. Accordingly, the foreign matter collecting device 82 rotates integrally with the primary pulley 50 that is one pulley. The foreign material collecting device 82 includes collecting grooves 82a and 82b and a snap ring 82c.

  The collection grooves 82a and 82b are foreign matter collection means and are formed in the supply / discharge side main passage 51a which is a hydraulic oil passage. In this embodiment, the collection groove 82a is formed on the inner wall surface in the vicinity of the step portion 51h formed in the supply / discharge side main passage 51a in the supply / discharge side main passage 51a. The collection groove 82b is formed in the inner wall surface on the primary fixed sheave side of the supply / discharge side main passage 51a with respect to the collection groove 82a. The collection grooves 82a and 82b are formed to extend in the circumferential direction. The distance between the collecting groove 82a and the collecting groove 82b is set in consideration of the length in the longitudinal direction of the fin 84 described later.

  The snap ring 82c is a foreign matter collecting means and is a magnetic body. The snap ring 82c is disposed in the supply / discharge side main passage 51a which is a hydraulic oil passage. In this embodiment, the snap ring 82c is arranged in the supply / discharge side main passage 51a by being arranged in the collection groove 82b. That is, the collection groove 82b is used as a groove for holding the snap ring 82c. Therefore, when the collecting groove 82b and the snap ring 82c are provided in the supply / discharge side main passage 51a as the foreign matter collecting means, the collecting groove 82b can be shared as a groove for holding the snap ring 82c. Thereby, size reduction and cost reduction can be achieved.

  The fin 83 is a rotational force imparting means, which imparts rotational force to the hydraulic oil supplied to the primary hydraulic chamber 55 that is one clamping pressure generating hydraulic chamber and generates a flow toward the foreign matter collecting device 81. is there. The fin 83 is provided in the primary hydraulic chamber 55. In this embodiment, a plurality of fins 83 (two in the circumferential direction in this embodiment) are provided on the radially outer side of the end face on the primary movable sheave side of the primary partition wall 54 constituting the primary hydraulic chamber 55. Each fin 83 protrudes from the radially inner side toward the radially outer side toward the primary movable sheave side, and the rotation direction of the primary pulley 50 that is one of the pulleys (in this embodiment, the belt type continuously variable transmission 1 is It is formed to project toward the primary movable sheave side in the opposite direction to the direction of rotation when the mounted vehicle moves forward. Accordingly, the hydraulic oil in the primary hydraulic chamber 55 flows along the fins 83 when the primary pulley 50 rotates in the rotation direction, particularly when the primary movable sheave 53 moves in the axial direction with respect to the primary fixed sheave 52. A rotational force in the rotational direction is applied, resulting in a spiral flow. As a result, the hydraulic oil in the primary hydraulic chamber 55 is directed toward the radially inner surface of the projecting portion 53d of the hydraulic oil primary movable sheave 53 as shown by an arrow A in FIG. The flow is directed toward the groove 81a and the snap ring 81b.

  The fins 84 are rotational force applying means that apply rotational force to the hydraulic oil supplied to the primary hydraulic chamber 55 and generate a flow toward the foreign matter collecting device 82. The fins 84 are provided in the supply / discharge side main passage 51a which is a hydraulic oil passage. In this embodiment, the fin 84 is inserted into the supply / discharge side main passage 51a and is held by a snap ring 82c disposed in the step portion 51h and the collection groove 82b of the supply / discharge side main passage 51a. The fins 84 are flat and twisted in the longitudinal direction. Therefore, the hydraulic oil that passes through the supply / discharge-side main passage 51a passes through the fin 84 in the direction toward the primary hydraulic chamber 55 and when the fin 84 passes in the direction toward the hydraulic oil supply control device 130. Since it flows along the fins 84, a rotational force is applied to form a spiral flow. As a result, the hydraulic oil in the primary hydraulic chamber 55 is directed toward the primary hydraulic chamber 55 and toward the inner wall surface of the supply / discharge-side main passage 51a as shown by an arrow C in FIG. The flow is directed toward the collection groove 82a of the device 82. Further, as shown by an arrow E shown in FIG. 5, the hydraulic oil in the primary hydraulic chamber 55 is directed toward the hydraulic oil supply control device 130 and toward the inner wall surface of the supply / discharge side main passage 51a, that is, foreign matter trapping. The flow is directed toward the collecting groove 82a of the collecting device 82.

  Therefore, the fins 83 and 84 can positively create a flow of hydraulic oil toward the foreign matter collecting devices 81 and 82 as the foreign matter collecting means by rotating the primary pulley 50 that is one pulley. Therefore, the foreign matter contained in the hydraulic oil can be easily collected by the foreign matter collecting devices 81 and 82 by the flow of the working oil in the vicinity of the foreign matter collecting devices 81 and 82.

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

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

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

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

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

  The hydraulic oil supply control device 130 is a hydraulic oil supply portion that requires supply of hydraulic oil in a vehicle in which the belt type continuously variable transmission 1 and the internal combustion engine 10 are mounted, for example, a primary hydraulic chamber 55, a secondary hydraulic chamber 64, The hydraulic oil is supplied to each drive hydraulic chamber 78 and other parts. The hydraulic oil supply control device 130 is connected to at least an ECU 140 that controls the operation of the internal combustion engine 10. The hydraulic oil supply control device 130 controls the hydraulic oil pressure supplied to the primary hydraulic chamber 55 and the hydraulic oil pressure supplied to each drive hydraulic chamber 78 based on the control signal of the gear ratio from the ECU 140. Thus, at least the gear ratio of the belt type continuously variable transmission 1 is controlled.

  The hydraulic oil supply control device 130 has a supply side path and a discharge side path communicating with the supply / discharge side main passage 51a, although not shown. The supply side path is a path that includes a pressure regulating valve that regulates the hydraulic pressure of the hydraulic oil, and supplies hydraulic oil whose hydraulic pressure is controlled to the primary hydraulic chamber 55 via the supply / discharge side main passage 51a. On the other hand, the discharge side path is a path that has an open / close valve that communicates with the outside and that discharges hydraulic fluid from the primary hydraulic chamber 55 via the supply / discharge side main passage 51a. Note that a part of the supply side path and a part of the discharge side path may be shared.

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

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

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

  Here, when the operation of the internal combustion engine 10 is controlled by the ECU 140, the oil pump 26 is driven by the driving force of the internal combustion engine 10. When the oil pump 26 is driven, pressurized hydraulic oil is supplied to the hydraulic oil supply control device 130, and the hydraulic oil pressurized from the hydraulic oil supply control device 130 is activated in each hydraulic oil supply portion. The oil is supplied to a hydraulic oil supply portion that requires oil.

  The ECU 140 also includes a map (for example, an optimal fuel consumption curve based on the engine speed and the throttle opening of the throttle valve) stored in the storage unit of the ECU 140 and conditions such as the vehicle speed and the accelerator opening of the driver. Based on the above, the gear ratio of the belt-type continuously variable transmission 1 is controlled via the hydraulic oil supply control device 130 so that the operation state of the internal combustion engine 10 is optimized. The control of the gear ratio of the belt type continuously variable transmission 1 includes changing the gear ratio and fixing the gear shift (gear ratio γ steady). The change of the gear ratio and the fixing of the gear ratio are performed by controlling the hydraulic pressure of the hydraulic oil by the hydraulic oil supply control device 130, so that the hydraulic pressure P1 of the primary hydraulic chamber 55 of the primary pulley 50 and the secondary hydraulic chamber 64 of the secondary pulley 60 are controlled. This is done by controlling the hydraulic pressure and the hydraulic pressure P3 of each drive hydraulic chamber 78.

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

  In the secondary pulley 60, the belt 110 is sandwiched between the secondary fixed sheave 62 and the secondary movable sheave 63 by controlling the hydraulic pressure in the secondary hydraulic chamber 64 with the hydraulic oil supplied from the hydraulic oil supply control device 130. The belt clamping pressure to be applied is adjusted. Thereby, the belt tension of the belt 110 wound around the primary pulley 50 and the secondary pulley 60 is controlled.

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

  The gear ratio reduction change is performed by supplying hydraulic oil from the hydraulic oil supply control device 130 to the primary hydraulic chamber 55 and sliding (moving) the primary movable sheave 53 toward the primary fixed sheave side. As shown in FIG. 4, each hydraulic oil supply / discharge valve 70 is opened to allow the hydraulic oil to be supplied from the hydraulic oil supply control device 130 to the primary hydraulic chamber 55. Specifically, ECU 140 calculates a reduction gear ratio and a transmission speed, and outputs a control signal for the transmission ratio based on these to hydraulic fluid supply control device 130. The hydraulic oil supply control device 130 adjusts and raises the hydraulic pressure of the hydraulic oil supplied to the primary hydraulic chamber 55 in order to set the transmission ratio of the belt-type continuously variable transmission 1 to the decreasing transmission ratio at the above-described transmission speed. Accordingly, the hydraulic pressure P2 of the space T3 increases, and the pressing force in the valve opening direction that acts on each valve element 71 by the hydraulic pressure P2 of the space T3 causes the hydraulic pressure P1 of the primary hydraulic chamber 55 and the valve closing of each elastic member 73 to The pressing force in the valve closing direction acting on each valve element 71 is exceeded by the urging force. Thereby, each valve body 71 moves in the valve opening direction, and each hydraulic oil supply / discharge valve 70 opens. That is, supply of the hydraulic oil to the primary hydraulic chamber 55 which is one clamping pressure generating hydraulic chamber by each hydraulic oil supply / discharge valve 70 is permitted.

  When supply of hydraulic oil to the primary hydraulic chamber 55 by each hydraulic oil supply / discharge valve 70 is permitted, the hydraulic oil whose hydraulic pressure is regulated by the hydraulic oil supply control device 130 is shown in FIG. Then, it flows into the supply / discharge side main passage 51a through a supply side passage (not shown), and from the supply / discharge side main passage 51a to the shaft side communication passage 51c, the space portion T1, the partition wall side communication passage 54f, the space portion T3 and the hydraulic oil supply / discharge It is supplied to the primary hydraulic chamber 55 via the valve 70 (supply / discharge passage 54a). At this time, the hydraulic oil supply control device 130 stops the supply of hydraulic oil from the hydraulic oil supply control device 130 to each drive hydraulic chamber 78, or the hydraulic pressure P3 of each drive hydraulic chamber 78 is changed to the hydraulic pressure of each drive hydraulic chamber 78. The valve opening direction pressing force acting on each valve body 71 via each piston 77 by P3 acts on each valve body 71 by the hydraulic pressure P1 of the primary hydraulic chamber 55 and the valve closing biasing force of each elastic member 73. The hydraulic pressure of the hydraulic oil supplied to each drive hydraulic chamber 78 is regulated so as not to exceed the pressing force. Here, each hydraulic oil supply / discharge valve 70 discharges the hydraulic oil from the primary hydraulic chamber 55 because the hydraulic oil supply control device 130 supplies the hydraulic oil to the primary hydraulic chamber 55 via a supply-side path (not shown). Is prohibited. Accordingly, the hydraulic oil P1 in the primary hydraulic chamber 55 is raised by the hydraulic oil supplied via each hydraulic oil supply / discharge valve 70, and the pressing force for pressing the primary movable sheave 53 toward the primary fixed sheave side is increased. The 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.

  At this time, hydraulic fluid passes in the direction toward the primary hydraulic chamber 55 in the supply / discharge side main passage 51a. Centrifugal force acts on the hydraulic oil passing through the supply / discharge-side main passage 51a as the primary pulley 50 rotates. Accordingly, foreign matter such as friction powder contained in the hydraulic oil collects on the inner wall surface of the supply / discharge side main passage 51a. Further, the hydraulic oil passing through the supply / discharge-side main passage 51a is given a rotational force by the fins 84 as shown by an arrow C shown in the figure, and a flow toward the collection groove 82a of the foreign material collection device 82 is generated. To do. Therefore, the collection groove 82a can collect the foreign matter contained in the hydraulic oil by the rotation of the primary pulley 50 or the application of rotational force by the fins 84.

  Further, centrifugal force acts on the hydraulic oil supplied to the primary hydraulic chamber 55 as the primary pulley 50 rotates. Accordingly, foreign matter such as friction powder contained in the hydraulic oil collects on the inner wall surface of the primary hydraulic chamber 55, that is, the radially inner surface of the protruding portion 53 d of the primary movable sheave 53. Further, the hydraulic oil in the primary hydraulic chamber 55 is given a rotational force by the fins 83 as shown by an arrow A shown in the figure, and the flow toward the collecting groove 81a and the snap ring 81b of the foreign matter collecting device 81 is flowed. appear. Therefore, the collection groove 81a can collect the foreign matters contained in the hydraulic oil when the primary pulley 50 rotates or when the rotational force is applied by the fins 83. Further, the snap ring 81b can attract and reliably collect magnetic foreign matters out of the foreign matters contained in the hydraulic oil by its magnetic force.

  In changing the gear ratio, the hydraulic oil is discharged from the primary hydraulic chamber 55 via the hydraulic oil supply control device 130, and the primary movable sheave 53 is slid (moved) to the opposite side of the primary fixed sheave side. Is called. First, as shown in FIG. 5, each hydraulic oil supply / discharge valve 70 is forcibly opened to allow the hydraulic oil to be discharged from the primary hydraulic chamber 55. Specifically, ECU 140 calculates an increase gear ratio and a gear shift speed, and outputs a gear ratio control signal based on these to hydraulic oil supply control device 130. The hydraulic oil supply control device 130 regulates and raises the hydraulic pressure of the hydraulic oil supplied to each drive hydraulic chamber 78 in order to set the transmission ratio of the belt-type continuously variable transmission 1 to the increased transmission ratio at the above-described transmission speed. . Accordingly, the hydraulic pressure P3 of each drive hydraulic chamber 78 rises, and the pressing force in the valve opening direction that acts on each valve element 71 via each piston 77 by each drive hydraulic chamber 78 is the hydraulic pressure P1 of the primary hydraulic chamber 55 and The pressing force in the valve closing direction acting on each valve element 71 is exceeded by the valve closing biasing force of each elastic member 73. Thereby, each valve body 71 moves in the valve opening direction, and each hydraulic oil supply / discharge valve 70 is forcibly opened. That is, the hydraulic oil is allowed to be discharged from the primary hydraulic chamber 55 which is one clamping pressure generating hydraulic chamber by each hydraulic oil supply / discharge valve 70.

  When the hydraulic oil is allowed to be discharged from the primary hydraulic chamber 55 by each hydraulic oil supply / discharge valve 70, the hydraulic oil in the primary hydraulic chamber 55 is supplied to the hydraulic oil supply / discharge valve 70 ( The hydraulic oil supply control device flows into the space portion T3 through the supply / discharge passage 54a) and from the space portion T3 through the partition wall side communication passage 54f, the space portion T1, the shaft side communication passage 51c, and the supply / discharge side main passage 51a. 130 flows. Here, the hydraulic oil supply control device 130 is switched from a supply-side path (not shown) to a discharge-side path when the gear ratio increase is changed. Accordingly, the hydraulic oil that has flowed into the hydraulic oil supply control device 130 is discharged to the outside, that is, outside the primary hydraulic chamber 55 via the discharge side outlet passage. That is, each hydraulic oil supply / discharge valve 70 is prohibited from supplying hydraulic oil to the primary hydraulic chamber 55. 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.

  At this time, in the supply / discharge side main passage 51a, the hydraulic oil passes in a direction toward the hydraulic oil supply control device 130. Since the centrifugal force acts on the hydraulic oil passing through the supply / discharge side main passage 51a as described above, the foreign matter contained in the hydraulic oil collects on the inner wall surface of the supply / discharge side main passage 51a. Further, the hydraulic oil passing through the supply / discharge side main passage 51a is given rotational force by the fins 84 as shown by an arrow E shown in FIG. A heading flow occurs. Accordingly, the collection groove 82b can collect foreign matter contained in the hydraulic oil by the rotation of the primary pulley 50 or the application of rotational force by the fins 84. Moreover, the snap ring 82c can adsorb | suck the foreign material of a magnetic body among the foreign materials contained in hydraulic fluid with the magnetic force, and can collect it reliably.

  Further, when the gear ratio is increased, the foreign matter contained in the hydraulic oil can be collected by the collecting groove 81a, and the foreign matter contained in the hydraulic oil can be collected by the snap ring 81b, as in the case of the reduction of the gear ratio described above. Among them, the foreign substance of the magnetic substance can be adsorbed and reliably collected.

  The speed ratio is fixed without supplying hydraulic oil to the primary hydraulic chamber 55 and without discharging hydraulic oil from the primary hydraulic chamber 55, and making the position of the primary movable sheave 53 in the axial direction relative to the primary fixed sheave 52 constant, This is performed by restricting the movement of the primary movable sheave 53 with respect to the primary fixed sheave 52. Note that the gear ratio is fixed, that is, the gear ratio is fixed when the ECU 140 determines that there is no need to change the gear ratio significantly, such as when the vehicle is in a stable running state. As shown in FIG. 2, the hydraulic oil supply / discharge valve 70 is maintained in a closed state, and the supply of hydraulic oil to the primary hydraulic chamber 55 and the discharge of hydraulic oil from the primary hydraulic chamber 55 are both prohibited. Specifically, the hydraulic oil supply control device 130 stops the supply of hydraulic oil to the primary hydraulic chamber 55. Further, the hydraulic oil supply control device 130 stops the supply of the hydraulic oil to each drive hydraulic chamber 78, or the pressing force for opening the valve bodies 71 of the hydraulic pressure P3 of each drive hydraulic chamber 78 is the valve bodies 71. The hydraulic pressure of the hydraulic oil supplied to each drive hydraulic chamber 78 is regulated so as not to act on the hydraulic pressure.

  In addition, even when the gear ratio is fixed, the foreign material contained in the hydraulic oil can be collected by the collecting groove 81a, and the snap ring 81b is activated, as in the case of the gear ratio being decreased and the gear ratio being increased. Among foreign matters contained in oil, magnetic foreign matters can be adsorbed and reliably collected.

  As described above, the hydraulic oil in the primary hydraulic chamber 55 is held by prohibiting the supply of the hydraulic oil to the primary hydraulic chamber 55 and the discharge of the hydraulic oil from the primary hydraulic chamber 55. Even when the gear ratio is fixed, the belt tension of the belt 110 changes, so that the contact radius of the belt 110 in the primary pulley 50 tends to change, and the position of the primary movable sheave 53 in the axial direction with respect to the primary fixed sheave 52 may change. is there. As described above, since the hydraulic oil is held in the primary hydraulic chamber 55, if the position of the primary movable sheave 53 in the axial direction with respect to the primary fixed sheave 52 is changed, the internal 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, the oil pump 26 does not have to be driven to supply the hydraulic oil to the primary hydraulic chamber 55, so that an increase in driving loss of the oil pump 26 can be suppressed.

  Further, when the belt type continuously variable transmission 1 is operated, the foreign matter contained in the hydraulic oil held in the primary hydraulic chamber 55 or the foreign matter contained in the hydraulic fluid supplied to the primary hydraulic chamber 55 81 and 82. Therefore, the foreign matter contained in the hydraulic oil interposed between the hydraulic oil supply control device 130 and the primary hydraulic chamber 55 can be reduced. Further, the foreign matter collecting devices 81 and 82 are provided so as to rotate integrally with the primary pulley 50, and of the hydraulic oil that is interposed between the hydraulic oil supply control device 130 and the primary hydraulic chamber 55, Foreign matter contained in the hydraulic oil that is present on the primary hydraulic chamber side with respect to the sliding portion with the movable member is collected. Therefore, since there is no sliding portion between the fixed member and the movable member between the foreign matter collecting devices 81 and 82 and the primary hydraulic chamber 55, the foreign matter collecting devices 81 and 82 act to collect the foreign matter. It can suppress that the foreign material contained in oil increases. As a result, it is possible to suppress a decrease in the sealing performance of the hydraulic oil supply / discharge valve 70, and to suppress leakage of hydraulic oil from the primary hydraulic chamber 55 when the speed ratio is fixed. The hydraulic oil can be reliably held, and the reliability is improved.

  Moreover, since the foreign material collection apparatuses 81 and 82 collect a foreign material with the centrifugal force which acts on hydraulic fluid when the primary pulley 50 rotates, it does not require motive power in order to collect a foreign material. Accordingly, the hydraulic oil in the primary hydraulic chamber 55 can be reliably held, and deterioration of the efficiency of the belt type continuously variable transmission 1 can be suppressed.

  In the above embodiment, the foreign matter collecting devices 81 and 82 are provided in both the primary hydraulic chamber 55 that is one clamping pressure generating hydraulic chamber and the supply / discharge side main passage 51a that is the hydraulic fluid passage. The invention is not limited to this, and may be provided in either one.

Moreover, the foreign material collection means concerning this invention is not limited to the foreign material collection devices 81 and 82 of the said Example. FIG. 6 is a diagram illustrating another configuration example of the foreign material collecting apparatus. As shown in the figure, a foreign matter collecting device 85 having a different configuration from the foreign matter collecting device 81 is provided in the primary hydraulic chamber 55.
The supply / discharge-side main passage 51a is provided with a foreign matter collecting device 86 having a configuration different from that of the foreign matter collecting device 82.

  The foreign matter collecting device 85 collects foreign matter of hydraulic oil in the primary hydraulic chamber 55 and rotates integrally with the primary pulley 50. The foreign matter collecting device 85 includes a collecting portion 85a, a magnetic body 85b, and a snap ring 85c.

  The collection part 85a is a foreign matter collection means, and is formed in the primary hydraulic chamber 55 which is one clamping pressure generating hydraulic chamber. In the same figure, the collection part 85a is a space part formed between the magnetic body 85b and the side surface on the opposite side of the primary fixed sheave side of the annular part 53b of the primary movable sheave 53 constituting the primary hydraulic chamber 55. . The collection part 85a is formed extending in the circumferential direction.

  The magnetic body 85b is a foreign matter collecting means. The magnetic body 85b has a ring shape and is disposed in the primary hydraulic chamber 55 that is one clamping pressure generating hydraulic chamber. The magnetic body 85b is disposed between a step portion (not shown) formed on the radially inner surface of the protruding portion 53d of the primary movable sheave 53 constituting the primary hydraulic chamber 55 and the snap ring 81b. The snap ring 85c is a groove (not shown) formed on the opposite side to the primary fixed sheave side of the stepped portion on the radially inner surface of the protruding portion 53d of the primary movable sheave 53 constituting the primary hydraulic chamber 55. Inserted and fixed to. In the foreign material collection apparatus 85, since the collection groove | channel is not formed as a foreign material collection means, the strength fall of the primary movable sheave 53 can be suppressed. Moreover, cost reduction can be achieved.

  The foreign matter collecting device 86 collects foreign matter of hydraulic oil supplied to the primary hydraulic chamber 55 and rotates integrally with the primary pulley 50. The foreign matter collecting device 86 includes a collecting groove 86a, a magnetic body 86b, and a snap ring 86c.

  The collection groove 86a is a foreign matter collection means, and is formed in the supply / discharge side main passage 51a which is a hydraulic oil passage. In the figure, the collection groove 86a is formed on the inner wall surface of the supply / discharge side main passage 51a. The collection part 85a is formed extending in the circumferential direction.

  The magnetic body 86b is a foreign matter collecting means, and is disposed in the supply / discharge side main passage 51a which is a hydraulic oil passage. In the figure, the magnetic body 86b has a ring shape, and is inserted into the collecting groove 86a so as to cover the bottom of the collecting groove 86a. The snap ring 86c is inserted and fixed in the collecting groove 86a, thereby fixing the magnetic body 86b in the collecting groove 86a.

  Moreover, in the said Example, although the fins 83 and 84 corresponding to each foreign material collection apparatus 81 and 82 were each provided, this invention is not limited to this, As shown to the same figure, it does not provide a fin. May be.

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

  In the above embodiment, the hydraulic oil supply valve and the hydraulic oil discharge valve are made the same by the hydraulic oil supply / discharge valve 70, but the hydraulic oil supply valve and the hydraulic oil discharge valve may be provided separately. In this case, the hydraulic oil supply / discharge valve 70 is used as the hydraulic oil discharge valve, and the hydraulic oil supply valve is provided to rotate integrally with the separate primary pulley 50. For example, a check valve that opens only in the direction in which the hydraulic oil is directed to the primary hydraulic chamber 55 is supplied to the primary hydraulic chamber 55 through a path where the primary hydraulic chamber 55 and the supply / discharge-side main passage 51a communicate with each other via the primary movable sheave 53. Provide as a valve. For example, the hydraulic oil supply valve is provided on the primary movable sheave 53 and the primary pulley shaft 51. The primary partition wall 54 is formed with a discharge passage that communicates each space T3 and the outside of the primary pulley 50, instead of the partition wall side communication passage 54f. The hydraulic oil supply control device 130 includes only a supply side path (not shown).

  As a result, when the gear ratio is decreased, the hydraulic oil supply valve is opened by the hydraulic pressure of the hydraulic oil supplied from the hydraulic oil supply control device 130, so that the hydraulic oil is supplied to the primary hydraulic chamber 55. Further, when the gear ratio is increased, the hydraulic oil supply / discharge valve 70 is forcibly opened by the hydraulic pressure P3 of each drive hydraulic chamber 78, so that the hydraulic oil in the primary hydraulic chamber 55 is discharged to the outside through the discharge passage. Discharged.

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

Explanation of symbols

1 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 52 Primary fixed sheave 53 Primary movable sheave 54 Primary partition wall 55 Primary hydraulic chamber (one clamping pressure generating hydraulic chamber)
60 Secondary pulley 64 Secondary hydraulic chamber (the other clamping pressure generating hydraulic chamber)
70 Hydraulic oil supply / discharge valve (hydraulic oil supply valve, hydraulic oil discharge valve)
81, 82, 85, 86 Foreign matter collecting device (foreign matter collecting means)
81a, 82a, 82b, 86a Collection groove 81b, 82c Snap ring (magnetic material)
83, 84 fins (rotational force applying means)
85a Collection part 85b, 86b Magnetic body 85c, 86c Snap ring 90 Final reduction gear 100 Power transmission path 110 Belt 120 Wheel 130 Hydraulic oil supply control device (hydraulic oil supply means)
140 ECU

Claims (7)

Two pulleys,
A belt that is wound around each pulley and transmits a driving force from a driving source transmitted to one pulley to the other pulley;
A clamping pressure generating hydraulic chamber formed in each pulley and generating a belt clamping pressure with respect to the belt by hydraulic pressure;
A hydraulic oil supply valve that allows only hydraulic oil to be supplied to one of the clamping pressure generating hydraulic chambers among the clamping pressure generating hydraulic chamber, and rotates integrally with the one pulley;
A hydraulic oil discharge valve that controls permission or prohibition of discharge of the hydraulic oil from the one clamping pressure generating hydraulic chamber, and rotates integrally with the one pulley;
Hydraulic oil supply control means for supplying the hydraulic oil to at least each of the clamping pressure generating hydraulic chambers and controlling a gear ratio;
Foreign matter collecting means for collecting foreign matter contained in the hydraulic oil interposed between at least the hydraulic oil supply control means and the one clamping pressure generating hydraulic chamber;
A belt-type continuously variable transmission.   The belt-type continuously variable transmission according to claim 1, wherein the foreign matter collecting means rotates integrally with the one pulley.   The foreign matter collecting means is a collecting groove formed in at least one of the one clamping pressure generating hydraulic chamber or a hydraulic fluid passage through which hydraulic oil supplied to the one clamping pressure hydraulic chamber passes. The belt-type continuously variable transmission according to claim 2.   The foreign matter collecting means is a magnetic body disposed in at least one of the one clamping pressure generating hydraulic chamber or a hydraulic fluid passage through which hydraulic fluid supplied to the one clamping pressure hydraulic chamber passes. The belt-type continuously variable transmission according to claim 2 or 3. The magnetic body is a magnetized snap ring,
The belt-type continuously variable transmission according to claim 4, wherein the magnetized snap ring is disposed in the collecting groove.   The belt-type continuously variable machine according to any one of claims 1 to 5, further comprising a rotational force applying unit that applies a rotational force to the hydraulic oil and generates a flow toward the foreign matter collecting unit. transmission.   The belt-type continuously variable transmission according to any one of claims 1 to 6, wherein the hydraulic oil supply valve and the hydraulic oil discharge valve are the same.

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