JP2008051177A - Torque cam device and belt-driven continuously variable transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a torque cam device and a belt-driven continuously variable transmission, which can implement the optimal thrust development notwithstanding the drive state. <P>SOLUTION: The torque cam device comprises a first cam device 71 comprising a first input side cam member 71a and a first output side cam member 71b, a second cam device 72 comprising a second input side cam member 72a and a second output side cam member 72b integrally formed with the first input side cam member 71a, and having the second input side cam member 72a supported to be axially movable for the second output side cam member 72b, and a cam hydraulic chamber 73 (second cam hydraulic chamber 73b) to apply cam pressing force to press the second input side cam member 72a in the direction to contact the second output side cam member 72b out of the axial direction to the second input side cam member 72a. The cam hydraulic chamber 73 comprises a cam hydraulic chamber element 75 fastened between the first output side cam member 71b and a cam guide member 76 to guide to axially move the second input side cam member 72a. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a torque cam device and a belt type continuously variable transmission, and more particularly to a torque cam device and a belt type continuously variable transmission that use separate cam devices for driving and driven (reverse driving). is there.

  There are various torque cam devices. However, the input cam member is brought into contact with the drive cam surface formed on the output cam member, and the input cam member moves along the drive cam surface. Some perform torque transmission. In this torque cam device, both cam members are formed in a ring shape and the drive cam surface is formed in the circumferential direction, so that not only torque can be transmitted but also thrust can be generated in one of the axial directions. Some of them can be used, and such a torque cam device is used in a transmission of a vehicle, particularly a belt type continuously variable transmission.

  A torque cam device used in a belt-type continuously variable transmission is generally disposed between a secondary pulley and a final reduction gear, and transmits output torque, which is an output of the engine, from the secondary pulley to the final reduction gear via a cam roller. Become. At this time, the thrust generated in one of the axial directions becomes the belt clamping pressure of the secondary pulley, and the belt wound between the primary pulley and the secondary pulley can be clamped. Here, in the torque cam device of the belt-type continuously variable transmission, a driven force or a reverse driving force is generated in addition to a normal driving force that is an output torque for moving the vehicle forward. This driven force is a resistance torque in the same direction as the driving force transmitted from the final reduction gear side, for example, when an engine brake is used. The reverse driving force is an output torque in a direction opposite to the driving force transmitted from the secondary pulley side in order to move the vehicle backward. For this reason, in a torque cam device used for a belt type continuously variable transmission, it is necessary to transmit a driven force during driving or a reverse driving force during reverse driving via a cam roller in addition to the driving cam surface. Therefore, the driven cam surface is formed in the circumferential direction on the output cam member. This driven cam surface is formed so as to be arranged alternately with the driving cam surface in the circumferential direction.

  In a torque cam device in which a driving cam surface and a driven cam surface are formed, when the driving state is switched from driving to driving (during reverse driving) or from driving (reverse driving) to driving The object to be contacted by the input side cam member is switched from the driving cam surface to the driven cam surface or from the driven cam surface to the driving cam surface. When the driving state is switched, the input side cam member and the output side cam member rotate relative to each other in the circumferential direction, so that the input side cam member separates from one cam surface and contacts the other cam surface. .

  Conventionally, for example, a torque cam device as shown in Patent Document 1 has been proposed. A conventional torque cam device disclosed in Patent Document 1 includes a first cam surface that contacts a cam roller and a cam member guided by a long groove and a pin so as to be movable only in the axial direction with respect to a cylindrical portion provided with the first cam surface. And a second cam surface provided on the cam member so as to be inclined in a direction opposite to the first cam surface and contacting the cam roller. This conventional torque cam device is used for a belt-type continuously variable transmission.

  In this torque cam device, a cam roller is sandwiched between a first cam surface and a second cam surface by a compression force in a compression spring disposed in the axial direction. That is, the contact between the cam roller and the cam surface is not separated regardless of the driving state of the torque cam device. Therefore, in the conventional torque cam device, the contact between the cam roller and the cam surface is not separated regardless of the driving state of the torque cam device.

JP 63-210458 A

  However, when a conventional torque cam device as shown in Patent Document 1 transmits a driven force or a reverse driving force, a thrust in one of the axial directions is generated between the cam roller and the cam member. Here, the direction in which this thrust is generated is the same as the direction in which the compression spring is compressed. Therefore, if the generated thrust exceeds the compression force of the compression spring, the compression spring is compressed, and there is a possibility that the optimum belt clamping pressure cannot be generated. That is, there is a possibility that the optimum thrust cannot be generated at the time of driven or reverse driving force, or excessive thrust is generated. Therefore, in order to generate the optimum belt clamping pressure, it is conceivable to generate the cam pressing force that presses in the direction in which the thrust is generated by the internal pressure in the cam hydraulic chamber. In addition, in the method of generating cam pressing force by the internal pressure in the cam hydraulic chamber, the driving state is switched, especially when the driving state is switched under a transient condition from driving to driving and from driving to driving. It is thought that the shock can be reduced.

  Therefore, the present invention has been made in view of the above, and is a torque cam capable of realizing at least one of generation of an optimum thrust regardless of a driving state or reduction of a shock when the driving state is switched. An object of the present invention is to provide a device and a belt type continuously variable transmission.

  In order to solve the above-described problems and achieve the object, the torque cam device according to the present invention includes a first input-side cam member and a first output-side cam member. The first output cam member is supported so as to be relatively rotatable in the circumferential direction, and a positive driving force during positive driving is transmitted and axial direction by contact between the first input cam member and the first output cam member. A first cam device that generates thrust in one direction, a second input cam member, and a second output cam member formed integrally with the first input cam member. The side cam member and the second output side cam member are supported so as to be relatively rotatable in the circumferential direction, and the second input side cam member is supported so as to be movable in the axial direction with respect to the second output side cam member; The second input side cam member and the second output side cam A second cam device that transmits a driven force at the time of driving or a reverse driving force at the time of reverse driving and generates thrust in one of the axial directions by contact with the member; and the second input side cam member A cam hydraulic chamber that causes the second input cam member to act on the second input cam member that presses the second input cam member in the axial direction in the direction of contacting the second output cam member. It is characterized by comprising a cam hydraulic chamber constituting member fixed between a first output cam member and a cam guide member for guiding the movement of the second input cam member in the axial direction.

  According to this invention, the second input cam member can be brought into contact with the second output cam member by the cam pressing force generated by the internal pressure of the cam hydraulic chamber acting on the second input cam member. Accordingly, since the second input side cam member and the second output side cam member can be kept away from each other when driven or reversely driven, an optimum thrust can be generated.

  Here, when the driving state of the torque cam device is switched from driving to driven or from driving to reverse driving, an impact force acts on the second cam device. However, during driving, the second input cam member can be brought into contact with the second output cam member by the cam pressing force acting on the second input cam member due to the internal pressure of the cam hydraulic chamber, and the cam hydraulic pressure Since the chamber can act as a damper, the impact force acting on the second cam device can be suppressed when the driving state is switched. Thereby, the fall of durability can be suppressed.

  Further, since the cam hydraulic chamber is formed by using a part of the first cam device and the second cam device, the structure of the cam hydraulic chamber may be complicated to form the cam hydraulic chamber. May be difficult. However, according to the present invention, the cam hydraulic chamber constituting member is fixed between the first output cam member and the cam guide member for guiding the movement of the second input cam member in the axial direction. Therefore, the cam hydraulic component is subjected to a force that moves in the axial direction due to the internal pressure of the cam hydraulic chamber, but the movement in the axial direction can be restricted by the first output cam member and the cam guide member. Thereby, the cam hydraulic component can be fixed in the axial direction with a simple configuration.

  According to the present invention, in the torque cam device, the second input side cam member extends to an inner peripheral surface of the second input side cam member on an end surface facing the cam hydraulic chamber constituting member in the axial direction. An end face groove is formed.

  According to the present invention, in the torque cam device, the second input side cam member extends to an inner peripheral surface of the second input side cam member on an end surface facing the cam hydraulic chamber constituting member in the axial direction. An end face recess is formed.

  According to these inventions, even if the end face of the second input side cam member facing the cam hydraulic chamber constituent member in the axial direction is in contact with the cam hydraulic chamber constituent member, the hydraulic oil supplied to the cam hydraulic chamber is the end face. It flows into the groove or the end surface recess. Therefore, even if the second input side cam member is in contact with the cam hydraulic chamber constituent member, the hydraulic oil can be quickly supplied between the second input cam member and the cam hydraulic chamber constituent member. Thereby, even when the second input side cam member is in contact with the cam hydraulic chamber constituting member, the pressure receiving area of the second input side cam member can be secured, so that the operation response of the second cam device is improved. Can do.

  According to the present invention, in the torque cam device, the end surface recess is formed in the end surface and communicates with an end surface outer peripheral groove extending to the outer peripheral surface of the second input side cam member.

  According to this invention, the hydraulic fluid that has flowed into the end surface recess also flows into the end surface outer circumferential groove. Accordingly, even when the second input side cam member is in contact with the cam hydraulic chamber constituting member, the pressure receiving area of the second input side cam member can be further ensured, so that the operation response of the second cam device is further improved. be able to.

  According to the present invention, in the torque cam device, hydraulic fluid is interposed between the second input cam member and the cam guide member between the second input cam member and the cam hydraulic chamber constituent member. The supplied second cam member is characterized in that an inner peripheral surface groove communicating with the end surface groove is formed on the inner peripheral surface.

  According to the present invention, in the torque cam device, hydraulic fluid is interposed between the second input cam member and the cam guide member between the second input cam member and the cam hydraulic chamber constituent member. The supplied second cam member is characterized in that an inner peripheral surface groove that communicates with the end surface recess is formed on the inner peripheral surface.

  According to these inventions, when the hydraulic oil supplied to the cam hydraulic chamber from between the second input side cam member and the cam guide member is supplied to the end surface groove or the end surface recess, the second input side cam member and The hydraulic oil supplied to the cam hydraulic chamber also flows into an inner peripheral groove formed between the cam guide member and the cam guide member. Therefore, the working oil can be quickly flowed into the end face groove or the end face recess. Therefore, the operation response of the second cam device can be further improved.

  According to the present invention, in the torque cam device, between the inner peripheral surface of the first output cam member and the shaft that rotates integrally with the first input cam member and the second output cam member, A bearing that rotatably supports the first output cam with respect to the shaft and a seal member that seals the cam hydraulic chamber are arranged to have the same diameter.

  According to the present invention, the seal member is disposed between the first output cam member that rotates relative to the rotating shaft and the shaft that is supported by the bearing. Therefore, the clearance of the portion to be sealed is properly maintained, and the sealing member can be prevented from being dragged or bitten during operation.

  According to the present invention, in the torque cam device, the seal member is disposed on the cam hydraulic chamber side with respect to the shaft support member of the bearing.

  Here, at the time of assembling the torque cam device, the first output cam member is inserted into a shaft to which a bearing is previously attached. The insertion direction at this time is the direction toward the first input side cam member, that is, the cam hydraulic chamber side. According to this invention, since the seal member is disposed on the cam hydraulic chamber side with respect to the shaft support member of the bearing, when the first output side cam member is inserted into the shaft, the seal member first comes into contact with the shaft support member. . Therefore, the first output cam member can contact the seal member while being centered with respect to the shaft. Thereby, the biting of the seal member during assembly of the torque cam device can be suppressed.

  In the belt type continuously variable transmission according to the present invention, at least two pulley shafts arranged in parallel and transmitting the driving force from the driving source to one of the two pulley shafts are respectively provided on the two pulley shafts. Two pulleys comprising two movable sheaves sliding in the direction, two fixed sheaves facing the two movable sheaves in the axial direction, respectively, and transmission to any one of the two pulleys A belt that transmits the driving force from the drive source to the other pulley, and the torque cam device that generates a belt clamping pressure between the movable sheave and the fixed sheave.

  According to the present invention, the belt-type continuously variable transmission is configured using the torque cam device, and the thrust generated by the torque cam device is used as the belt clamping pressure. Therefore, the optimum belt clamping pressure can be generated. Also, the cam hydraulic component can be fixed in the axial direction with a simple configuration.

  In the torque cam device and the belt type continuously variable transmission according to the present invention, since the second input cam member is brought into contact with the second output cam member by the cam pressing force generated by the cam hydraulic chamber, the optimum thrust (belt clamping pressure) ) Can be produced. In addition, at least one of the reduction of the shock at the time of switching of the driving state can be realized. In addition, the cam hydraulic component can be fixed in the axial direction with a simple configuration.

  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, in the following embodiment, a case where the torque cam device according to the present invention is used in a belt type continuously variable transmission will be described. In the belt-type continuously variable transmission, the torque cam device according to the present invention is used to generate a belt clamping pressure with respect to the belt wound around the secondary pulley. 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, but the invention is not limited to this. An electric motor may be used as a drive source.

  FIG. 1 is a skeleton diagram of a belt type continuously variable transmission including a torque cam device according to the present invention. FIG. 2 is a diagram illustrating a configuration example of the torque cam device when the speed ratio is minimum. FIG. 3 is a diagram illustrating a configuration example of the torque cam device at the maximum gear ratio. 4 is a cross-sectional view taken along the line II of FIG. FIG. 5A is a diagram illustrating an operation state of the first cam device when the speed ratio is minimum. FIG. 5B is a diagram illustrating an operation state of the second cam device when the speed ratio is minimum. FIG. 6A is a diagram illustrating an operation state of the first cam device when the speed ratio is maximum. FIG. 6B is a diagram illustrating an operation state of the second cam device when the speed ratio is maximum. 5A is a sectional view taken along the line II-II in FIG. 2, FIG. 5-2 is a sectional view taken along the line III-III in FIG. 2, FIG. 6-1 is a sectional view taken along the line IV-IV in FIG. FIG. Further, the driving force F1 and the driven force F2 in this embodiment are assumed to be generated clockwise when the torque cam device is viewed from the power transmission shaft side in FIGS. The reverse driving force F3 in this embodiment is assumed to be generated counterclockwise when the torque cam device is viewed from the power transmission shaft side in FIGS.

  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 that are two pulleys constituting the belt type continuously variable transmission 1 according to the present invention, and a primary pulley A primary hydraulic chamber 54 that generates belt clamping pressure in the pulley 50, a secondary hydraulic chamber 64 that generates belt clamping pressure in the secondary pulley 60, the torque cam device 70 according to the present invention, and the belt 100 are housed. Reference numeral 40 denotes a forward / reverse switching mechanism, 80 denotes a final reduction gear that transmits the driving force of the internal combustion engine 10 to the wheels 110, and 90 denotes a power transmission path.

  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 supplied with hydraulic oil as a hydraulic fluid from a hydraulic oil supply control device (not shown).

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

  An oil pump 26 included in a hydraulic oil supply control device (not shown) is provided between the torque converter 30 and a forward / reverse switching mechanism 40 described later. 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. Therefore, the oil pump 26 can be driven because the output torque from the internal combustion engine 10 is transmitted to the rotor 27 via the pump 31.

  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 to a hollow portion (not shown) of the input shaft 38 from a hydraulic oil supply control device (not shown). 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 to a brake piston (not shown) from a hydraulic oil supply control device (not shown). When the reverse brake 43 is ON, the switching carrier 47 is fixed to the transaxle case 22 so that each pinion 45 cannot revolve around the sun gear 44. When the reverse brake 43 is OFF, the switching carrier 47 is released, and each pinion 45 can revolve around the sun gear 44.

  The primary pulley 50 of the belt-type continuously variable transmission 1 is one pulley, and the output torque from the internal combustion engine 10 transmitted via the forward / reverse switching mechanism 40 is transmitted by the belt 100 to the secondary pulley 60 which is the other pulley. To communicate. As shown in FIG. 1, the primary pulley 50 includes a primary pulley shaft 51, a primary fixed sheave 52, a primary movable sheave 53, and a belt-type continuously variable transmission that generates belt clamping pressure on the primary pulley 50. And a primary hydraulic chamber 54 that changes the transmission ratio of 1.

  The primary pulley shaft 51 is rotatably supported by bearings 101 and 102. Further, the primary pulley shaft 51 has a hydraulic oil passage (not shown) inside, and hydraulic oil supplied from the hydraulic oil supply control device (not shown) to the primary hydraulic chamber 54 flows into the hydraulic oil passage.

  The primary fixed sheave 52 is provided to rotate integrally with the primary pulley shaft 51 so as to face 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 provided on the outer periphery of the primary pulley shaft 51.

  The primary movable sheave 53 is spline-fitted to the primary pulley shaft 51 so as to be slidable in the axial direction on the primary pulley shaft 51. 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 100a having a shape is formed.

  The primary hydraulic chamber 54 is configured by a back surface 53 a opposite to the surface facing the primary fixed sheave 52 of the primary movable sheave 53, and a disk-shaped primary partition wall 55 fixed to the primary pulley shaft 51. On the back surface 53a of the primary movable sheave 53, an annular protrusion 53b that protrudes in one axial direction, that is, protrudes toward the transaxle rear cover 23 is formed. On the other hand, the primary partition wall 55 is formed with an annular protrusion 55a that protrudes in the other axial direction, that is, toward the primary movable sheave 53 side. A seal member for a primary hydraulic chamber (not shown) such as a seal ring is provided between the projecting portion 53b and the projecting portion 55a. That is, the back surface 53a of the primary movable sheave 53 constituting the primary hydraulic chamber 54 and the primary partition wall 55 are sealed by the seal member.

  The primary hydraulic chamber 54 is supplied with hydraulic oil flowing into a hydraulic oil passage (not shown) of the primary pulley shaft 51 via a hydraulic oil supply hole (not shown). In other words, the hydraulic oil supply control device (not shown) supplies hydraulic oil to the primary hydraulic chamber 54, and the primary movable sheave 53 is slid in the axial direction by the internal pressure of the primary hydraulic chamber 54, and the primary movable sheave 53 is made primary. The fixed sheave 52 is approached or separated. The primary hydraulic chamber 54 is wound around the primary groove 100 a by applying a movable sheave pressing force that presses the primary movable sheave 53 in the axial direction to the primary movable sheave 53 by the hydraulic oil supplied to the primary hydraulic chamber 54. A belt clamping pressure is applied to the belt 100 to be hung, and the axial position of the primary movable sheave 53 with respect to the primary fixed sheave 52 is changed. Thereby, the primary hydraulic chamber 54 has a function as a gear ratio changing means for changing 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 100 to the final speed reducer 80 of the belt type continuously variable transmission 1. As illustrated in FIG. 1, the secondary pulley 60 includes a secondary pulley shaft 61, a secondary fixed sheave 62, and a secondary movable sheave 63.

  As illustrated in FIGS. 1 to 3, the secondary pulley shaft 61 is rotatably supported by bearings 103 and 104. The secondary pulley shaft 61 has a hydraulic oil passage 61a formed therein. The working oil that is the working fluid supplied to the cam hydraulic chamber 73 from a working oil supply control device (not shown) flows into the working oil passage 61a.

  The secondary fixed sheave 62 is provided to rotate integrally with the secondary pulley shaft 61 so as to face the 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 provided on the outer periphery of the secondary pulley shaft 61.

  The secondary movable sheave 63 includes a cylindrical portion 63a and an annular portion 63b. The cylindrical portion 63 a is formed around the same rotation axis as the secondary pulley shaft 61. The annular portion 63b is formed to project radially outward from an end portion of the cylindrical portion 63a in the fixed sheave direction. The secondary movable sheave 63 has a spline 63c formed on the inner peripheral surface of the cylindrical portion 63a and a spline 61b formed on the outer peripheral surface of the secondary pulley shaft 61. It is slidably supported in the axial direction. 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 100b having a shape is formed.

  The torque cam device 70 includes a first cam device 71, a second cam device 72, and a cam hydraulic chamber 73, as shown in FIGS. In addition, 74 is a fixing member, 75 is a cam hydraulic chamber constituent member, 76 is a cam guide member, 77 is a secondary partition, 78 is a pressing elastic member, and 79 is a parking gear.

  The first cam device 71 includes a first input cam member 71a and a first output cam member 71b. The first cam device 71 transmits a driving force F1 and generates thrust in one of the axial directions (hereinafter simply referred to as “fixed sheave direction”).

  The first input side cam member 71a protrudes in the power transmission shaft direction from the radially outer portion of the side surface in the other direction (hereinafter simply referred to as “power transmission shaft direction”) in the axial direction of the fixed member 74. Is formed. Here, the fixing member 74 has a ring shape, and the side surface in the fixed sheave direction is fixed to the side surface in the power transmission shaft direction of the secondary movable sheave 63. That is, the first input side cam member 71 a is provided integrally with the secondary movable sheave 63 via the fixed member 74. A plurality of (for example, 3 to 4) first input cam members 71 a are formed in the circumferential direction with respect to the secondary movable sheave 63. Here, in this embodiment, the first input side cam member 71a is configured separately from the secondary movable sheave 63, but may be integrally formed.

  The first input cam member 71a is a protruding member having a tip formed in an arc shape. As shown in FIGS. 5A and 6A, the first input side cam member 71a may be fixed to the fixing member 74. However, the first input side cam member 71a and the first output side cam member In order to reduce resistance when the 71b rotates relative to each other in the circumferential direction, it is preferable that the fixing member 74 is rotatably supported. The first input side cam member 71a has a first input side cam surface 71c that contacts the first output side cam surface 71d on the outer periphery.

  The first output cam member 71b is a ring-shaped member having an L-shaped axial cross section. Specifically, the radially inner end of the first output side cam member 71b is rotatably supported by the secondary pulley shaft 61 by bearings 103 and 105. Here, the bearing 103 includes an inner peripheral surface of the first output cam member 71b and a secondary pulley shaft 61 that is a shaft that rotates integrally with the first input cam member 71a and a second output cam member 72b described later. Arranged between. The bearing 103 includes a shaft support member 103a and an inner race 103b. The inner race 103 b has a ring shape and is attached to the outer periphery of the secondary pulley shaft 61. The shaft support member 103a is inserted into a recess formed in the inner race 103b so as to be rotatable in the axial direction with respect to the inner race 103b. Further, the shaft support member 103a is in contact with the inner peripheral surface of the first output side cam member 71b so as to be rotatable in the axial direction. Thus, the bearing 103 supports the first output cam member 71b so as to be rotatable in the axial direction with respect to the secondary pulley shaft 61. The bearing 105 is disposed between the side surface of the first output side cam member 71 b in the power transmission shaft direction and the fixed member 61 c fixed to the secondary pulley shaft 61. The bearing 105 includes a shaft support member 105a and an inner race 105b. The inner race 105 b has a ring shape and is attached to the outer periphery of the secondary pulley shaft 61. The shaft support member 105a is inserted into a recess formed in the inner race 105b so as to be rotatable in the circumferential direction with respect to the inner race 105b. The shaft support member 105a is in contact with the side surface of the power transmission shaft of the first output cam member 71b so as to be rotatable in the circumferential direction. Accordingly, the bearing 105 supports the first output-side cam member 71b so as to be rotatable in the circumferential direction with respect to the secondary pulley shaft 61. That is, the first output cam member 71b is restricted from moving in the power transmission shaft direction in the axial direction by the fixing member 61c fixed to the secondary pulley shaft 61 via the bearing 105.

  Further, the first output side cam member 71b has a first output side cam surface 71d in contact with the first input side cam surface 71c of the first input side cam member 71a at the end portion in the stationary sheave direction on the radially outer side. , Projecting in the fixed sheave direction. The first output-side cam surface 71d is an inclined surface that is inclined so as to rise in the direction in which the secondary movable sheave 63 rotates by the driving force F1 (see FIGS. 5-1 and 6-1). The shape and cam angle of the first output cam surface 71d are determined based on the magnitude of the driving force F1 transmitted by the first cam device 71, the magnitude of the thrust to be generated, and the like.

  The first output cam member 71b has a plurality of cam side engaging projections 71e formed on the side surface in the power transmission shaft direction in the circumferential direction. On the other hand, a plurality of shaft-side engaging protrusions 91a are formed at the end of the power transmission shaft 91 in the fixed sheave direction so as to face each cam-side engaging protrusion 71e. Each of the cam side engaging protrusions 71e and each of the shaft side engaging protrusions 91a are engaged with each other. That is, as described above, the first input side cam member 71a is fixed to the secondary movable sheave 63 that rotates integrally with the secondary pulley shaft 61 via the fixed member 74, and the first output side cam member 71b is fixed to the secondary pulley shaft. 61 is connected to a power transmission shaft 91 different from 61. Therefore, the first input side cam member 71a and the first output side cam member 71b are supported so as to be relatively rotatable in the circumferential direction.

  The first input cam surface 71c of the first input cam member 71a and the first output of the first output cam member 71b are caused by the relative rotation of the first input cam member 71a and the first output cam member 71b. The side cam surface 71d comes into contact, and the driving force F1 is transmitted from the secondary pulley 60 to the power transmission shaft 91 via the first cam device 71 (see FIGS. 5-1 and 6-1). When the first cam device 71 transmits the driving force F1, as described above, the fixing member 61c causes the first output cam member 71b to move in the direction of the power transmission axis with respect to the first input cam member 71a. Therefore, a thrust that attempts to move the secondary movable sheave 63 toward the secondary fixed sheave 62 is generated in the secondary movable sheave 63.

  The second cam device 72 includes a second input side cam member 72a and a second output side cam member 72b. The second cam device 72 transmits the driven force F2 or the reverse driving force F3 and generates a thrust in the fixed sheave direction.

  The second input side cam member 72a has a ring shape, and is disposed on the radially inner side with respect to the first output side cam member 71b. The second input side cam member 72a is disposed between the first output side cam member 71b and the cam guide member 76 fixed to the first output side cam member 71b by welding W at one place. As shown in FIG. 3, the second input side cam member 72a has a helical spline 72f formed on the inner peripheral surface thereof. Here, as shown in the figure, the cam guide member 76 has a ring shape having an outer peripheral surface facing the inner peripheral surface of the second input side cam member, and the outer peripheral surface has the same shape as the helical spline 72f. A helical spline 76a is formed. The helical spline 72f of the second input side cam member 72a and the helical spline 76a of the cam guide member 76 are spline-fitted. These helical splines 72f and 76a are twisted in the direction in which the secondary pulley 60 rotates by the driving force F1. Accordingly, when the second input cam member 72a moves in one axial direction relative to the second output cam member 72b, that is, in the fixed sheave direction, the second input cam member 72a moves relative to the second output cam member 72b. Thus, the first output cam member 71b rotates in the same direction as the first input cam member 71a by the driving force F1 during driving. A gap (not shown) is formed between the second input side cam member 72a and the cam guide member 76, that is, between the helical splines 72f and 76a. Accordingly, the hydraulic oil supplied to the cam hydraulic chamber 73 is supplied from the first cam hydraulic chamber 73a (to be described later) of the cam hydraulic chamber 73 to the second cam hydraulic chamber 73b through this gap.

  Further, the second input side cam member 72a is in contact with a second output side cam surface 72d (to be described later) of the second output side cam member 72b at an end in the fixed sheave direction on the radially outer side. Is formed so as to protrude in the fixed sheave direction. The second input side cam surface 72a rises in a direction opposite to the direction in which the second input side cam member 72a rotates by the driven force F2, that is, in the direction in which the secondary movable sheave 63 rotates by the reverse driving force F3. The inclined surface is inclined (see FIGS. 5-2 and 6-2). The shape and cam angle of the second input side cam surface 72a are determined based on the magnitude of the driven force F2 and the reverse driving force F3 transmitted by the second cam device 72, the magnitude of the thrust to be generated, and the like. Is.

  An end face groove 72g is formed on an end face of the second input cam member 72a facing the cam hydraulic chamber constituting member 75 in the axial direction, that is, an end face 72e in the power transmission shaft direction. In this embodiment, a plurality of (for example, eight) end face grooves 72g are formed at equal intervals in the circumferential direction of the end face 72e. Each end face groove 72e is formed in the radial direction. Each end face groove 72e is formed such that one end extends to the inner peripheral surface of the second input side cam member 72a and the other end extends to the outer peripheral surface of the second input side cam member 72a. Yes.

  An inner peripheral surface groove 72h is formed on the inner peripheral surface of the second input side cam member 72a. In this embodiment, a plurality (for example, eight) of inner peripheral surface grooves 72h are formed at equal intervals in the circumferential direction of the end surface 72e. Each inner peripheral groove 72h is formed in the axial direction. Each inner peripheral surface groove 72h has one end portion extending to the end surface in the fixed sheave direction of the second input side cam member 72a, and the other end portion being an end surface in the power transmission shaft direction of the second input side cam member 72a. It extends to 72e. Each inner peripheral surface groove 72h is formed such that the other end communicates with each end surface groove 72g. Accordingly, when the hydraulic oil supplied to the cam hydraulic chamber 73 (first cam hydraulic chamber 73a described later) from between the second input side cam member 72a and the cam guide member 76 is supplied to the end face groove 72g, The hydraulic oil supplied to the cam hydraulic chamber 73 (first cam hydraulic chamber 73a) also flows into the inner circumferential groove 72h formed between the two-input-side cam member 72a and the cam guide member 76. Therefore, compared with the case where hydraulic fluid flows into the end surface groove 72g only from the gap (not shown) between the helical splines 72f and 76a, the hydraulic fluid can be quickly flowed into the end surface groove 72g. Thereby, the operation response of the second cam device 72 can be improved immediately after the cold start when the viscosity of the hydraulic oil is high. The second input cam member 72a has an auxiliary partition wall 72i fixed to an end portion in the fixed sheave direction on the radially inner side. The auxiliary partition wall 72i has a ring shape, and an end portion in the power transmission shaft direction is fixed to the second input side cam member 72a.

  The second output cam member 72b is formed to project in the power transmission shaft direction from the radially inner portion of the side surface of the fixed member 74 in the power transmission shaft direction. That is, the second output cam member 72b is formed integrally with the first input cam member 71a on the radially inner side of the first input cam member 71a, and is connected to the secondary movable sheave via the fixed member 74. 63 is integrally provided. A plurality of (for example, 3 to 4) second output cam members 72 b are formed in the circumferential direction with respect to the secondary movable sheave 63. Here, in this embodiment, the second output cam member 72a is configured separately from the secondary movable sheave 63, but may be integrally formed.

  The second output cam member 72b is a protruding member having a tip formed in an arc shape. Here, in this embodiment, the axis line of the first input side cam member 71a and the axis line of the second output side cam member 72b are located on one normal line of a circle centered on the center line OO. . The second output side cam member 72b may be fixed to the fixing member 74 as shown in FIGS. 5-2 and 6-2, but the second input side cam member 72a and the second output side In order to reduce resistance when the cam member 72b is relatively rotated in the circumferential direction, it is preferable that the cam member 72b is rotatably supported by the fixing member 74.

  As described above, the second input side cam member 72a is connected to the power transmission shaft 91 different from the secondary pulley shaft 61 via the cam guide member 76 and the first output side cam member 71b that are spline-fitted, and the second The output cam member 72b is fixed to a secondary movable sheave 63 that rotates integrally with the secondary pulley shaft 61 via a fixed member 74. Therefore, the second input cam member 72a and the second output cam member 72b are supported so as to be relatively rotatable in the circumferential direction.

  The second input cam surface 71c of the second input cam member 71a and the second output of the second output cam member 72b are caused by the relative rotation of the second input cam member 72a and the second output cam member 72b. The driven force F <b> 2 transmitted to the power transmission shaft 91 via the second cam device 72 is transmitted to the secondary pulley 60 through the second cam device 72, and reversely from the secondary pulley 60 via the second cam device 72. The driving force F3 is transmitted to the power transmission shaft 91 (see FIGS. 5-2 and 6-2). Further, when the second cam device 72 transmits the driven force F2 and the reverse driving force F3, the movement of the second input cam member 72a in the power transmission shaft direction with respect to the second output cam member 72b will be described later. Since the internal pressure of the cam hydraulic chamber 73 to be controlled, particularly the internal pressure of the second cam hydraulic chamber 73b, is restricted, the thrust that moves the secondary movable sheave 63 toward the secondary fixed sheave 62 is driven by the secondary movable sheave 62. Occurs in the sheave 63.

  Here, the first cam device 71 that transmits a driving force F1 larger than the driven force F2 and the reverse driving force F3 is disposed on the outer side in the radial direction than the second cam device 72. Therefore, compared with the case where the first cam device 71 is disposed on the radially inner side of the second cam device 72, the tangential force on the first output cam surface 71d when transmitting the same driving force F1 is reduced. can do. Thereby, the durability of the first output cam surface 71d is improved, and the durability of the torque cam device 70 and the belt type continuously variable transmission 1 can be improved. Further, since the cam angle of the first output side cam surface 71d can be made gentle relative to the circumferential direction, the length of the first output side cam member 71b in the axial direction can be shortened, and the torque cam device 70 and The belt type continuously variable transmission 1 can be reduced in size.

  The cam hydraulic chamber 73 generates a cam pressing force that presses at least the second input cam member 72a in a direction in which the second input cam member 72a contacts the second output cam member 72b in the axial direction, that is, in the fixed sheave direction. The cam hydraulic chamber 73 is provided with the first cam device 71. In this embodiment, the cam hydraulic chamber 73 a is formed on the radially inner side of the first cam device 71. The cam hydraulic chamber 73 is surrounded by a cam hydraulic chamber constituting member 75, a second input cam member 72a, an auxiliary partition wall 72i, a secondary partition wall 77, a secondary movable sheave 63, and a first output side cam member 71b. It is a space formed. That is, the cam hydraulic chamber 73 is formed by the first cam device 71 and a part of the second cam device 72. The cam hydraulic chamber 73 includes a first cam hydraulic chamber 73a and a second cam hydraulic chamber 73b.

  The first cam hydraulic chamber 73a mainly generates a belt pressing force that presses the secondary movable sheave 63 in the fixed sheave direction, is radially inward from the first output cam member 71b, and further includes a second cam. It is formed radially inward from the hydraulic chamber 73b. The first cam hydraulic chamber 73a is surrounded by a second input cam member 72a, an auxiliary partition wall 72i, a secondary partition wall 77, a secondary movable sheave 63, a first output side cam member 71b, and a cam guide member 76. This is a space formed. The first cam hydraulic chamber 73a communicates with the hydraulic oil passage 61a through the hydraulic oil supply hole 61d.

  Here, the secondary partition wall 77 is a ring-shaped member having an L-shaped cross section in the axial direction, and is disposed radially inward of the fixing member 74. The secondary partition wall 77 includes a disk part 77a and a protruding part 77b. The disk portion 77 a has a side surface in the fixed sheave direction fixed to a side surface in the power transmission shaft direction of the secondary movable sheave 63. The protruding portion 77b is formed so as to protrude in the direction of the power transmission shaft from the radially outer portion of the side surface of the disk portion 77a in the power transmission shaft direction. The secondary partition wall 77 is fixed to the secondary movable sheave 63 so that the outer peripheral surface of the protrusion 77b faces the inner peripheral surface of the auxiliary partition wall 72i.

  In addition, a pressing elastic member 78 is disposed in the first cam hydraulic chamber 73a. The pressing elastic member 78 is, for example, a spring, a side surface of the fixed sheave of the first output side cam member 71b that forms the first cam hydraulic chamber 73a, and a cylindrical portion of the secondary partition wall 77 that forms the first cam hydraulic chamber 73a. 77a is arranged in a biased state between the side surface in the power transmission shaft direction of 77a. Accordingly, the secondary movable sheave 63 is subjected to an auxiliary pressing force in the fixed sheave direction by the biasing force generated by the pressing elastic member 78. This auxiliary pressing force causes a minimum belt clamping pressure to act on the belt 100 wound around the secondary groove 100b even if the internal pressure of the cam hydraulic chamber 73a, particularly the internal pressure of the first cam hydraulic chamber 73a is reduced. It is.

  The second cam hydraulic chamber 73b mainly generates a cam pressing force that presses the second input cam member 72a in the fixed sheave direction, and is radially inward of the first output cam member 71b. The first cam hydraulic chamber 73a is formed radially outside. The second cam hydraulic chamber 73 b is a space formed by being surrounded by the cam hydraulic chamber constituting member 75, the second input side cam member 72 a, and the cam guide member 76. The second cam hydraulic chamber 73b is connected to the first cam hydraulic chamber 73a through a gap (not shown) formed between the second input cam member 72a and the cam guide member 76, that is, between the helical splines 72f and 76a. Communicated with.

  Here, the cam hydraulic chamber constituting member 75 is a ring-shaped member having an L-shaped cross section in the axial direction, and is disposed so as to face the inner peripheral surface of the first output side cam member 71b. The cam hydraulic chamber constituting member 75 includes a disc part 75a and a protruding part 75b. The disk portion 75a has a side surface in the power transmission shaft direction that contacts the inner peripheral surface of the first output side cam member 71b, and a side surface in the fixed sheave direction that faces the end surface 72e of the second input side cam member 72a. The protruding portion 75b is formed to protrude in the fixed sheave direction from the radially outer portion of the side surface in the fixed sheave direction of the disk portion 75a. As for this protrusion part 75b, the outer peripheral surface in the radial direction outer side contacts the inner peripheral surface of the 1st output side cam member 71b, and the inner peripheral surface in the radial direction inner side opposes the outer peripheral surface of the 2nd input side cam member 72a. In the cam hydraulic chamber constituting member 75, the end portion on the radially inner side of the disc portion 75a is sandwiched between the inner peripheral surface of the first output cam member 71b and the end portion of the cam guide member 76 in the power transmission shaft direction. It is. Here, since the cam guide member 76 is fixed to the first output side cam member 71b by the welding W as described above, the cam hydraulic chamber constituting member 75 has the first output side cam member 71b and the cam guide member 76. It is fixed between. Therefore, the cam hydraulic component 75 is restricted from moving in the axial direction by the first output cam member 71b and the cam guide member 76 even if a force that moves in the axial direction due to the internal pressure of the cam hydraulic chamber 73 is applied. Yes. As a result, the cam hydraulic component 75 can be fixed in the axial direction with a simple configuration. Further, even when the first output cam member 71b and the cam hydraulic chamber constituting member 75 are made of different materials and it is difficult to fix the cam hydraulic chamber constituting member 75 to the first output cam member 71b by welding. The cam hydraulic component 75 can be fixed in the axial direction with a simple configuration. Therefore, the number of parts can be reduced and the ease of assembly can be improved. The cam hydraulic chamber constituting member 75 is fixed so that a gap is formed between the outer peripheral surface on the radially outer side of the projecting portion 75b and the inner peripheral surface of the first output side cam member 71b. preferable. Thereby, the hydraulic fluid leaking from the cam hydraulic chamber 73 can be discharged to the outside, and the stress in the weld W portion can be relieved.

  The cam hydraulic chamber 73 is sealed to the outside by cam hydraulic chamber seal members S1, S2, S3. The cam hydraulic chamber seal members S1 to S3 are formed of, for example, a ring-shaped seal ring.

  The cam hydraulic chamber seal member S1 is a seal member according to the present invention, and rotates together with the inner peripheral surface of the first output cam member 71b and the first input cam member 71a and the second output cam member 72b. Between the shaft, that is, the secondary pulley shaft 61, the first output side cam member 71 b is disposed with the same diameter as the bearing 103 that rotatably supports the secondary pulley shaft 61. In this embodiment, the cam hydraulic chamber seal member S1 is inserted into a recess formed in the outer peripheral surface of the inner race 103b of the bearing 103, and is disposed with the same diameter as the shaft support member 103a. Here, as described above, the secondary pulley shaft 61 in which the first input cam member 71a rotates integrally via the fixed member 74 and the secondary movable sheave 63 and the first output cam member 71b rotate relative to each other. That is, the cam hydraulic chamber seal member S1 is disposed between the first output cam member 71b and the inner race 103b that rotate relative to the inner race 103b fixed to the secondary pulley shaft 61. Therefore, the clearance of the portion to be sealed can be properly maintained. As a result, dragging of the cam hydraulic chamber seal member S1 and biting during operation of the belt-type continuously variable transmission 1 can be suppressed.

  The cam hydraulic chamber seal member S1 is disposed on one side in the axial direction with respect to the shaft support member 103a of the bearing 103, that is, on the fixed sheave direction side. When the belt-type continuously variable transmission 1 is assembled, particularly when the torque cam device 70 is assembled, the first output-side cam member 71b is inserted into the secondary pulley shaft 61 to which the bearing 103 is previously attached. The insertion direction at this time is a direction toward the first input side cam member 71a, that is, a fixed sheave direction. That is, when the torque cam device 70 is assembled, when the first output cam member 71b is inserted into the secondary pulley shaft 61, the cam hydraulic chamber seal member S1 is fixed in the fixed sheave direction with respect to the shaft support member 103a of the bearing 103. Since it is arranged on the side, it contacts the shaft support member 103a. Accordingly, the first output cam member 71b can contact the cam hydraulic chamber seal member S1 while being centered with respect to the secondary pulley shaft 61. Thereby, the biting of the cam hydraulic chamber seal member S1 during assembly of the torque cam device 70 can be suppressed. Further, when the belt type continuously variable transmission 1 is operated, the gap between the recess of the inner race 103a into which the cam hydraulic chamber seal member S1 is inserted and the first output cam member 71b is the recess of the shaft support member 103a. Since it is formed in the vicinity, it is properly held. Therefore, biting during operation can be suppressed.

  The cam hydraulic chamber sealing member S2 is disposed between the secondary partition wall 77 and the auxiliary partition wall 72i. The cam hydraulic chamber sealing member S3 is disposed between the cam hydraulic chamber constituting member 75 and the second input cam member 72a.

  As shown by an arrow A in FIGS. 2 and 3, the cam hydraulic chamber 73 is supplied with the operation oil supplied from the operation oil supply control device to the operation oil passage 61 a of the secondary pulley shaft 61 through the operation oil supply hole 61 d. Oil is supplied. Thereby, first, hydraulic fluid is supplied to the first cam hydraulic chamber 73 a of the cam hydraulic chamber 73. The hydraulic oil supply control device supplies hydraulic oil to the first cam hydraulic chamber 73a, and the secondary movable sheave 63 is slid in the axial direction via the secondary partition wall 77 by the hydraulic pressure of the supplied hydraulic oil, so that the secondary movable The sheave 63 is moved toward or away from the secondary fixed sheave 62. The first cam hydraulic chamber 73a is operated by applying a movable sheave pressing force that presses the secondary movable sheave 63 in the axial direction to the secondary movable sheave 63 by the hydraulic oil supplied to the first cam hydraulic chamber 73a. A part of the function of generating a belt clamping pressure with respect to the belt 100 wound around the groove 100b and maintaining a constant contact radius of the belt 100 with respect to the primary pulley 50 and the secondary pulley 60 is assumed.

  Further, as shown by the arrow B in FIGS. 2 and 3, the hydraulic oil supplied to the first cam hydraulic chamber 73a is interposed between the second input side cam member 72a and the cam guide member 76, that is, the helical spline 72f, It is supplied to the second cam hydraulic chamber 73b through a gap (not shown) formed between 76a. That is, the hydraulic oil supply control device supplies hydraulic oil to the second cam hydraulic chamber 73b via the first cam hydraulic chamber 73a, and the second input cam member 72a is moved by the internal pressure of the second cam hydraulic chamber 73b. The second input cam member 72a is rotated relative to the second output cam member 72b in the circumferential direction, and the second output cam member 72a is moved relative to the second output cam member 72b in the axial direction to thereby output the second input cam member 72a to the second output. The side cam member 72b is approached or separated. The second cam hydraulic chamber 73b generates a cam pressing force that presses the second input cam member 72a in one axial direction, that is, the fixed sheave direction, by the hydraulic oil supplied to the second cam hydraulic chamber 73b. By acting on the second input cam member 72a, the second cam device 72 can generate thrust in the fixed sheave direction. Accordingly, the second cam hydraulic chamber 73b also generates a belt clamping pressure against the belt 100 wound around the secondary groove 100b via the second cam device 72, and the contact radius of the belt 100 with respect to the primary pulley 50 and the secondary pulley 60 is increased. It bears a part of the function to maintain constant.

  The parking gear 79 is formed on the outer periphery of the first output cam member 71 b of the first cam device 71. Therefore, in the belt-type continuously variable transmission 1, the parking gear need not be provided separately. Since the parking gear 79 is formed on the first output cam member 71b located on the outermost side of the torque cam device 70, the surface pressure of the gear can be reduced. As a result, the torque cam device 70 and the belt type continuously variable transmission 1 can be reduced in size and cost. Further, since the first output cam member 71b is thinned to form the parking gear 79 on the first output cam member 71b, the weight can be reduced, the inertia is reduced, and the acceleration performance is improved. can do.

  A power transmission path 90 is disposed between the secondary pulley 60 and the final reduction gear 80. The power transmission path 90 includes a power transmission shaft 91 and an intermediate shaft 92 parallel to the secondary pulley shaft 61, a counter drive pinion 93, a counter driven gear 94, and a final drive pinion 95. The power transmission shaft 91 is rotatably supported by bearings 106 and 107. The intermediate shaft 92 is rotatably supported by bearings 108 and 109. The counter drive pinion 93 is fixed to the power transmission shaft 91. The counter driven gear 94 is fixed to the intermediate shaft 92 and meshed with the counter drive pinion 93. Further, the final drive pinion 95 is fixed to the intermediate shaft 92.

  The final speed reducer 80 of the belt type continuously variable transmission 1 transmits the output torque from the internal combustion engine 10 transmitted through the power transmission path 90 from the wheels 110 and 110 to the road surface. The final reduction gear 80 includes a differential case 81 having a hollow portion, a pinion shaft 82, differential pinions 83 and 84, and side gears 85 and 86.

  The differential case 81 is rotatably supported by bearings 87 and 88. A ring gear 89 is provided on the outer periphery of the differential case 81, and the ring gear 89 is engaged with the final drive pinion 95. The pinion shaft 82 is attached to the hollow portion of the differential case 81. The differential pinions 83 and 84 are rotatably attached to the pinion shaft 82. The side gears 85 and 86 are meshed with both of the differential pinions 83 and 84. The side gears 85 and 86 are fixed to the drive shafts 111 and 112, respectively.

  The drive shafts 111 and 112 have side gears 85 and 86 fixed to one end thereof, respectively, and wheels 110 and 110 are attached to the other end thereof.

  The belt 100 of the belt type continuously variable transmission 1 transmits the output torque from the internal combustion engine 10 transmitted via the primary pulley 50 to the secondary pulley 60. As shown in FIG. 1, the belt 100 is wound between a primary groove 100 a of the primary pulley 50 and a secondary groove 100 b of the secondary pulley 60. The belt 100 is an endless belt composed of a number of metal pieces and a plurality of steel rings.

  Next, the operation of the belt type continuously variable transmission 1 including the torque cam device 70 according to the present invention will be described. First, general forward and reverse travel of the vehicle will be described. When a driver selects a forward position by a shift position device (not shown) provided in the vehicle, an ECU (Engine Control Unit) (not shown) is operated by a forward clutch 42 by hydraulic oil supplied from a hydraulic oil supply control device (not shown). Is turned on, the reverse brake 43 is turned off, 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 100 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 to the torque cam device 70. The output torque transmitted to the torque cam device 70, that is, the driving force F1, is transmitted to the power transmission shaft 91 of the power transmission path 90. The output torque transmitted to the power transmission shaft 91 is transmitted to the intermediate shaft 92 via the counter drive pinion 93 and the counter driven gear 94, and rotates the intermediate shaft 92. The output torque transmitted to the intermediate shaft 92 is transmitted to the differential case 81 of the final reduction gear 80 via the final drive pinion 95 and the ring gear 89, and the differential case 81 is rotated. The output torque from the internal combustion engine 10 transmitted to the differential case 81 is transmitted to the drive shafts 111 and 112 via the differential pinions 83 and 84 and the side gears 85 and 86, and to the wheels 110 and 110 attached to the ends thereof. Then, the wheels 110 and 110 are rotated, 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 (not shown) turns off the forward clutch 42 with the hydraulic oil supplied from the hydraulic oil supply control device (not shown). 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 that meshes with the ring gear 46 also rotates in the same direction as the input shaft 38, and the sun gear 44 that meshes with each pinion 45 And rotate in the opposite direction. That is, the primary pulley shaft 51 connected to the sun gear 44 rotates in the direction opposite to the input shaft 38. Thereby, the secondary pulley shaft 61 of the secondary pulley 60 rotates in the opposite direction to the case where the driver selects the forward position.

  The output torque of the internal combustion engine 10 transmitted to the secondary pulley 60, that is, the reverse driving force F3 is transmitted to the torque cam device 70. The output torque transmitted to the torque cam device 70 is transmitted to the power transmission shaft 91 of the power transmission path 90, and the power transmission shaft 91 rotates in the opposite direction to the case where the driver selects the forward position. Then, the intermediate shaft 92, the differential case 81, the drive shafts 111, 112, and the like rotate in the opposite direction to the case where the driver selects the forward position, and the vehicle moves backward.

  The ECU (not shown) includes various conditions such as the vehicle speed and the driver's accelerator opening, and a map (for example, an optimal fuel consumption curve based on the engine speed and the throttle opening) stored in the storage unit of the ECU. Based on the above, the gear ratio of the belt-type continuously variable transmission 1 is controlled so that the operating state of the internal combustion engine 10 is optimized. The control of the gear ratio of the belt type continuously variable transmission 1 includes changing the gear ratio and fixing the gear ratio (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 hydraulic oil supplied from a hydraulic oil supply control device (not shown) to the primary hydraulic chamber 54 that generates belt clamping pressure in the primary pulley 50. The change in the gear ratio is mainly performed by adjusting the distance between the primary fixed sheave 52 and the primary movable sheave 53, that is, the width of the primary groove 100a, by sliding the primary movable sheave 53 in the axial direction of the primary pulley shaft 51. Is done. As a result, the contact radius of the belt 100 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).

  For example, when a large torque is not required, for example, when the vehicle is traveling at high speed, the primary movable sheave 53 is adjusted closest to the primary fixed sheave 52, that is, the width of the primary groove 100a is adjusted to the minimum. Thereby, the contact radius of the belt 100 in the primary pulley 50 is maximized, the contact radius of the belt 100 in the secondary pulley 60 is minimized, and the speed ratio is minimized. Accordingly, when the speed ratio is minimum, the width between the secondary fixed sheave 62 and the secondary movable sheave 63 is maximized. Therefore, as shown in FIG. 5-1, the first input cam member 71a of the first cam device 71 The width with respect to the first output cam member 71b is minimized.

  Further, when a large torque is required at the time of starting the vehicle, etc., the primary movable sheave 53 is adjusted so as to be farthest from the primary fixed sheave 52, that is, the width of the primary groove 100a is maximized. As a result, the contact radius of the belt 100 in the primary pulley 50 is minimized, the contact radius of the belt 100 in the secondary pulley 60 is maximized, and the gear ratio is maximized. Accordingly, when the speed ratio is maximum, the width between the secondary fixed sheave 62 and the secondary movable sheave 63 is minimum. Therefore, as shown in FIG. 6A, the first input cam member 71a of the first cam device 71 The width with respect to the 1st output side cam member 71b becomes the maximum.

  On the other hand, in the secondary pulley 60, by controlling the hydraulic pressure of the hydraulic oil supplied from the hydraulic oil supply control device (not shown) to the cam hydraulic chamber 73, the internal pressure of the first cam hydraulic chamber 73a of the cam hydraulic chamber 73 and the second pressure are controlled. The internal pressure of the cam hydraulic chamber 73b is controlled. Accordingly, a movable sheave pressing force is applied to the secondary movable sheave 63 by the internal pressure of the first cam hydraulic chamber 73a, and a thrust is generated in the second cam device 72 by the internal pressure of the second cam hydraulic chamber 73b. Adjustment of the belt clamping pressure with respect to the belt 100 to be wound is performed. As a result, the tension of the belt 100 wound between the primary pulley 50 and the secondary pulley 60 is controlled.

  Next, the operation of the torque cam device 70 will be described. In the hydraulic oil supply control device (not shown) in the above embodiment, the force (driving force F1, driven) that the internal pressure of the first cam hydraulic chamber 73a and the internal pressure of the second cam hydraulic chamber 73b of the cam hydraulic chamber 73 acts on the torque cam device 70. Control is performed so that the belt clamping pressure corresponding to the magnitude of the force F2 and the reverse driving force F3) can be generated.

  First, the torque cam device 70 during driving will be described. As shown in FIGS. 5A and 5B, in the torque cam device 70 during driving, the output torque of the internal combustion engine 10 in the direction to advance the vehicle transmitted to the secondary movable sheave 63 is the first driving force F1. It is transmitted to the input side cam member 71a. The driving force F1 causes the first input cam member 71a to rotate in the direction in which the driving force F1 acts with respect to the first output cam member 71b, so that the first input cam surface 71c and the first output cam The cam surface 71d comes into contact. Then, the driving force F1 is transmitted from the first input cam member 71a to the first output cam member 71b via the first input cam surface 71c and the first output cam surface 71d. That is, the first cam device 71 transmits the driving force F1 during driving.

  Here, a first input between the first input cam surface 71c and the first input cam surface 71d is caused by the driving force F1 transmitted from the first input cam member 71a to the first output cam member 71b. A force is generated in a direction in which the side cam member 71a and the first output side cam member 71b are separated from each other. However, as described above, the first output side cam member 71b is restricted from moving in the axial direction. A thrust in the fixed sheave direction is generated in the input side cam member 71a. That is, the first cam device 71 can transmit the driving force F1 during driving and can generate thrust in the fixed sheave direction. The generated thrust in the fixed sheave direction acts on the secondary movable sheave 63 as a force in a direction in which the secondary movable sheave 63 is directed in the fixed sheave direction. Therefore, the belt 100 between the secondary movable sheave 63 and the secondary fixed sheave 62 is In contrast, a belt clamping pressure is generated.

  At this time, when the driving force F <b> 1 is applied to the torque cam device 70 during driving, the hydraulic oil supply control device (not shown) is secondary through the fixed member 74 by the thrust in the fixed sheave direction generated by the first cam device 71. The movable sheave pressing force acting on the movable sheave 63, the movable sheave pressing force in the fixed sheave direction acting on the secondary movable sheave 63 by the internal pressure of the first cam hydraulic chamber 73a, and the secondary movable sheave via the secondary partition wall 77 by the pressing member. The hydraulic pressure in the cam hydraulic chamber 73 is controlled so that the sum of the auxiliary pressing forces acting on the belt 63 becomes a belt clamping pressure that prevents the belt 100 from slipping even when the torque cam device 70 transmits the driving force F1.

  At this time, the hydraulic fluid supplied to the first cam hydraulic chamber 73a of the cam hydraulic chamber 73 is also supplied to the second cam hydraulic chamber 73b. Here, the internal pressure of the second cam hydraulic chamber 73b at the time of driving is a cam pressing force that can always bring the second input cam member 72a into contact with the second output cam member 72b. It becomes more than the pressure which can be made to act on. As a result, the second input cam member 72a tends to move in the fixed sheave direction with respect to the second output cam member 72b as shown in FIGS. The second input side cam member 72a and the second output side cam member 72b are always in contact with each other. That is, when viewed from the radial direction, the first input cam member 71a and the second output cam member 72b are connected to the first output cam surface 71d of the first output cam member 71b and the second input cam member, respectively. The state is sandwiched between the second input side cam surface 72c of 72a.

  Here, when the gear ratio of the belt-type continuously variable transmission 1 is changed during driving, the secondary movable sheave 63 is moved along with the movement of the secondary movable sheave 63 in the axial direction with respect to the secondary fixed sheave 62 as described above. The first input side cam member 71a formed integrally with 63 also moves in the axial direction, and the width between the first input side cam member 71a and the first output side cam member 71b is as shown in FIGS. As shown in -1, it changes between the minimum width at the minimum speed ratio and the maximum width at the maximum speed ratio.

  At this time, since the second output cam member 72b is formed integrally with the first input cam member 71a, the second output cam member 72b also extends in the axial direction of the secondary movable sheave 63 with respect to the secondary fixed sheave 62. It moves in the axial direction as it moves. As described above, in the torque cam device 70 during driving, the cam pressing force acts on the second input side cam member 72a due to the internal pressure of the second cam hydraulic chamber 73b. Therefore, the helical spline of the second input side cam member 72a 72 f slides along the helical spline 76 a of the cam guide member 76, so that the second input side cam member 72 a moves in the axial direction along the guide of the cam guide member 76.

  Therefore, for example, when the speed ratio of the belt type continuously variable transmission 1 is changed from the minimum to the maximum, as shown in FIGS. 5-2 and 6-2, the second input side is controlled by the internal pressure of the second cam hydraulic chamber 73b. When the cam pressing force acts on the cam member 72a, the second input cam member 72a moves in the fixed sheave direction while maintaining the contact between the second input cam member 72a and the second output cam member 72b. At the same time, the first output cam member 71b is rotated in the same direction as the first output cam member 71a by the driving force F1 during driving of the second output cam member 72b. That is, the second input-side cam member 72a follows the change in the relative position in the circumferential direction and the axial direction of the first input-side cam member 71a and the first output-side cam member 71b at the time of driving. The relative position with respect to the cam member 72b can be changed.

  Here, in the torque cam device 70, the driving state may be switched from driving to driven or reverse driving force. Since the driving force F1 is transmitted to the first input side cam member 71a, the resistance torque transmitted to the power transmission shaft 91 is the second input side cam member as the driven force F2 in the same direction as the driving force F1. When shifting to the driven state transmitted to 72a, the driven force F2 transmitted to the second input side cam member 72a is the same as that of the second input side cam member 72a at the time of driving regardless of the gear ratio as described above. Since the contact with the second output side cam member 72b is maintained, it is instantaneously transmitted to the second output side cam member 72b via the second input side cam surface 72c and the second output side cam surface 72d. Further, the output torque of the internal combustion engine 10 in the direction in which the vehicle transmitted to the secondary pulley 60 moves backward from the time when the driving force F1 is transmitted to the first input side cam member 71a is the second output as the reverse driving force F3. In the case of shifting during the reverse drive transmitted to the side cam member 72b, the reverse drive force F3 transmitted to the second output side cam member 72b is the second input side cam regardless of the gear ratio as described above during the drive. Since the contact between the member 72a and the second output cam member 72b is maintained, it is instantaneously transmitted to the second input cam member 72a via the second output cam surface 72d and the second input cam surface 72c. The power is transmitted to the power transmission shaft 91 through the first output cam member 71b.

  Next, the torque cam device 70 when driven will be described. As shown in FIGS. 5-2 and 6-2, in the driven torque cam device 70, the resistance torque transmitted to the power transmission shaft 91 is transmitted as the driven force F2 to the second input side cam member 72a. The The driven force F2 causes the second input cam member 72a to rotate with respect to the second output cam member 72b in the direction in which the driven force F2 acts. The output side cam surface 72d comes into contact. The driven force F2 is transmitted from the second input cam member 72a to the second output cam member 72b via the second input cam surface 72c and the second output cam surface 72d. That is, the second cam device 72 transmits the driven force F2 when driven.

  Next, the torque cam device 70 during reverse driving will be described. As shown in FIGS. 5-2 and 6-2, in the torque cam device 70 in the reverse drive, the output torque of the internal combustion engine 10 in the direction of moving the vehicle reversely transmitted to the secondary movable sheave 63 is the reverse drive force F3. It is transmitted to the second output side cam member 72b. The reverse output force F3 causes the second output side cam member 72b to rotate in the direction in which the reverse drive force F3 acts with respect to the second input side cam member 72a. The input side cam surface 72c comes into contact. Then, the reverse driving force F3 is transmitted from the second output cam member 72b to the second input cam member 72a via the second output cam surface 72d and the second input cam surface 72c. That is, the second cam device 72 transmits the reverse driving force F3 during reverse driving.

  At this time, when the driving force F2 in the driven state or the reverse driving force F3 in the reverse driving acts on the torque cam device 70, the hydraulic oil supply control device (not shown) operates in the fixed sheave direction generated by the first cam device 71. The movable sheave pressing force that acts on the secondary movable sheave 63 via the fixed member 74 by the thrust of the shaft, the movable sheave pressing force in the fixed sheave direction that acts on the secondary movable sheave 63 by the internal pressure of the first cam hydraulic chamber 73a, and the pressing member Thus, the sum of the auxiliary pressing forces acting on the secondary movable sheave 63 via the secondary partition wall 77 becomes a belt clamping pressure that prevents the belt 100 from slipping even when the torque cam device 70 transmits the driven force F2 or the reverse driving force F3. The hydraulic pressure in the cam hydraulic chamber 73 is controlled.

  Here, in the belt type continuously variable transmission 1 at the time of the minimum gear ratio, the second output cam member 72b is located most in the power transmission shaft direction. At this time, the end surface 72e of the second input side cam member 72a contacts the side surface in the fixed sheave direction of the cylindrical portion 75a of the cam hydraulic chamber constituting member 75. That is, the pressure receiving area of the second input cam member 72a when the speed ratio is minimum is significantly smaller than when the end surface 72e of the second input cam member 72a and the cam hydraulic chamber constituting member 75 are separated from each other. . Therefore, the operation response of the second cam device 72 may be reduced. However, since a plurality of end surface grooves 72g are formed in the end surface 72e of the second input side cam member 72a of the torque cam device 70 according to the present invention, the first cam hydraulic chamber 73a supplies the second cam hydraulic chamber 73b. Even if the end surface 72e of the second input side cam member 72a is in contact with the cam hydraulic chamber constituting member 75, the hydraulic oil supplied to the second cam hydraulic chamber 73b flows into the end surface groove 72g. Therefore, even if the second input side cam member 72a is in contact with the cam hydraulic chamber constituting member 75, the hydraulic fluid can be quickly supplied between the second input side cam member 72a and the cam hydraulic chamber constituting member 75. . Thereby, even when the end surface 72e of the second input side cam member 72a is in contact with the cam hydraulic chamber constituting member 75, the pressure receiving area of the second input side cam member 72a can be ensured. The hydraulic oil can be supplied smoothly to the second cam device 72 and the operation response of the second cam device 72 can be improved. Therefore, since the slip of the belt 100 can be suppressed, the durability of the belt 100 can be improved.

  In addition, the driving state may be switched from driven to driving. The resistance torque transmitted to the power transmission shaft 91 is transmitted to the second input side cam member 72a as the driven force F2 in the same direction as the driving force F1, and the driving force F1 is applied to the first input side cam member 71a from the driven state. Since the hydraulic oil supply control device (not shown) can apply the cam pressing force corresponding to the driven force F2 to the second input side cam member 72a when driven, when the shift is made during the drive during which the pressure is transmitted. Regardless of the magnitude of the driven force F2, the second input side cam member 72a can be restricted from moving in the axial direction with respect to the second output side cam member 72b. That is, even when driven, since the contact between the first input cam member 71a and the first output cam member 71b is maintained regardless of the gear ratio, the first input cam member 71a is transmitted to the first input cam member 71a. The driving force F1 is instantaneously transmitted to the first output cam member 71b via the first input cam surface 71c and the first output cam surface 71d.

  Further, the driving state may be switched from reverse driving to driving. The driving force applied to the first input side cam member 71a from the time of reverse driving when the output torque of the internal combustion engine 10 transmitted to the secondary pulley 60 in the reverse direction is transmitted to the second output side cam member 72b as the reverse driving force F3. In the case of shifting during the driving in which F1 is transmitted, the hydraulic oil supply control device (not shown) can apply the cam pressing force corresponding to the reverse driving force F3 to the second input side cam member 72a during the reverse driving. Therefore, regardless of the magnitude of the reverse driving force F3, the second output side cam member 72b can be restricted from moving in the axial direction with respect to the second input side cam member 72a. That is, even during reverse driving, the contact between the first input side cam member 71a and the first output side cam member 71b is maintained regardless of the gear ratio, so that the signal is transmitted to the first input side cam member 71a. The driving force F1 is instantaneously transmitted to the first output cam member 71b via the first input cam surface 71c and the first output cam surface 71d.

  As described above, the second input cam member 72a is moved to the second output cam member 72b by the cam pressing force acting on the second input cam member 72a by the internal pressure of the second cam hydraulic chamber 73b of the cam hydraulic chamber 73. Can be contacted. Accordingly, the second input side cam member 72a and the second output side cam member 72b can be kept away from each other when driven or reversely driven, so that an optimum thrust can be generated. Further, when the driving state of the torque cam device 70 is switched from driving to driven or from driving to reverse driving, an impact force, that is, a shock acts on the second cam device 72. However, even during driving, the second input cam member 72a is turned into the second output cam member 72b by the cam pressing force that the second cam hydraulic chamber 73b of the cam hydraulic chamber 73 acts on the second input cam member 72a. Since the cam hydraulic chamber 73 can act as a damper, the shock acting on the second cam device 72 can be suppressed when the drive state is switched. Thereby, the fall of the durability of the torque cam apparatus 70 can be suppressed.

  In the above-described embodiment, the plurality of end surface grooves 72g are formed on the end surface 72e of the second input side cam member 72a, but the present invention is not limited to this. FIG. 7 is a diagram illustrating a configuration example of another second input-side cam member. As shown in the figure, an end surface recess 72j is formed on the end surface 72e of the second input side cam member 72a. In this embodiment, the end surface recess 72j is formed in a portion excluding the outer peripheral end of the end surface 72e. The end surface recess 72j is formed to extend to the inner peripheral surface of the second input side cam member 72a. That is, the end surface recess 72j is formed in communication with each inner peripheral surface groove 72h. Accordingly, the hydraulic oil supplied from the first cam hydraulic chamber 73a to the second cam hydraulic chamber 73b is not affected even if the end surface 72e of the second input cam member 72a is in contact with the cam hydraulic chamber constituting member 75. The hydraulic oil supplied to the hydraulic chamber 73b flows into the end surface recess 72j. Therefore, even if the second input side cam member 72a is in contact with the cam hydraulic chamber constituting member 75, the hydraulic fluid can be quickly supplied between the second input side cam member 72a and the cam hydraulic chamber constituting member 75. . Thereby, even when the end surface 72e of the second input side cam member 72a is in contact with the cam hydraulic chamber constituting member 75, the pressure receiving area of the second input side cam member 72a can be ensured. The hydraulic oil can be supplied smoothly to the second cam device 72 and the operation response of the second cam device 72 can be improved. Therefore, since the slip of the belt 100 can be suppressed, the durability of the belt 100 can be improved.

  Further, the end surface 72e may be formed with an end surface outer peripheral groove 72k extending to the outer peripheral surface on the radially outer side of the second input side cam member 72a. In this embodiment, a plurality of (for example, eight) end face outer peripheral grooves 72k are formed at equal intervals in the circumferential direction of the end face 72e. Each end face outer peripheral groove 72k is formed in the radial direction. Each end surface outer peripheral groove 72k is formed such that one end portion extends to the outer peripheral surface on the radially outer side of the second input side cam member 72a and the other end portion extends to an end surface recess 72j formed in the end surface 72e. Has been. That is, each end surface outer peripheral groove 72k is formed to communicate with the end surface recess 72j. Therefore, the hydraulic oil that has flowed into the end surface recess 72j also flows into each end surface outer circumferential groove 72k. Accordingly, even when the second input side cam member 72a is in contact with the cam hydraulic chamber constituting member 75, the pressure receiving area of the second input side cam member 72a can be further secured. Oil can be supplied more smoothly, and the operation response of the second cam device 72 can be further improved.

  As described above, the torque cam device according to the present invention is useful for a belt-type continuously variable transmission, and is particularly suitable for realizing generation of optimum thrust regardless of a driving state.

It is a skeleton figure of a belt type continuously variable transmission provided with a torque cam device concerning this invention. It is a figure which shows the structural example of the torque cam apparatus at the time of the minimum gear ratio. It is a figure which shows the structural example of the torque cam apparatus at the time of gear ratio maximum. It is II sectional drawing of FIG. It is a figure which shows the operation state of the 1st cam apparatus in the time of the minimum gear ratio. It is a figure which shows the operation state of the 2nd cam apparatus at the time of the minimum gear ratio. It is a figure which shows the operation state of the 1st cam apparatus at the time of the maximum gear ratio. It is a figure which shows the operation state of the 2nd cam apparatus at the time of gear ratio maximum. It is a figure which shows the structural example of another 2nd input side cam member.

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 hydraulic chamber 55 primary bulkhead 60 secondary pulley 61 secondary pulley shaft 62 secondary fixed sheave 63 secondary movable sheave 70 torque cam Device 71 First cam device 71a First input side cam member 71b First output side cam member 71c First input side cam surface 71d First output side cam surface 71e Cam side engagement protrusion 72 Second cam device 72a Second input side Cam member 72b Second output side cam member 72c Second input side cam surface 72d Second output side cam surface 72e End surface 72f Helical spline 72g End surface groove 72h Inner peripheral surface groove 72i Auxiliary partition wall 72j End surface recess 72k Surface outer peripheral groove 73 Cam hydraulic chamber 73a First cam hydraulic chamber 73b Second cam hydraulic chamber 74 Fixed member 75 Cam hydraulic chamber constituent member 76 Cam guide member 76a Helical spline 77 Secondary partition wall 78 Pressing elastic member 79 Parking gear 80 Final reduction gear 90 Power transmission path 91 Power transmission shaft 100 Belt 110 Wheel S1 to S3 Seal member for cam hydraulic chamber

Claims (9)

A first input side cam member and a first output side cam member, the first input side cam member and the first output side cam member are supported so as to be relatively rotatable in the circumferential direction; A first cam device that transmits a positive driving force during positive driving and generates a thrust in one of the axial directions by contact between the cam member and the first output cam member;
A second input side cam member; and a second output side cam member formed integrally with the first input side cam member, wherein the second input side cam member and the second output side cam member are circumferentially arranged. The second input-side cam member and the second output-side cam member are supported so as to be relatively rotatable, and the second input-side cam member is supported so as to be movable in the axial direction with respect to the second output-side cam member. A second cam device that transmits a driven force at the time of driving or a reverse driving force at the time of reverse driving and generates thrust in one of the axial directions by contact with
A cam hydraulic chamber that applies a cam pressing force to the second input cam member to press the second input cam member in a direction in which the second input cam member contacts the second output cam member in the axial direction;
With
The cam hydraulic chamber is constituted by a cam hydraulic chamber constituting member fixed at least between a first output cam member and a cam guide member for guiding the movement of the second input cam member in the axial direction. A torque cam device.   The second input-side cam member is formed with an end surface groove extending to an inner peripheral surface of the second input-side cam member on an end surface facing the cam hydraulic chamber constituting member in the axial direction. The torque cam device according to claim 1. Between the second input side cam member and the cam hydraulic chamber constituting member, hydraulic oil is supplied from between the second input side cam member and the cam guide member,
3. The torque cam device according to claim 2, wherein the second input side cam member has an inner peripheral surface groove communicating with the end surface groove on the inner peripheral surface. 4.   The second input-side cam member is formed with an end surface recess extending to the inner peripheral surface of the second input-side cam member on an end surface facing the cam hydraulic chamber constituting member in the axial direction. The torque cam device according to claim 1.   5. The torque cam device according to claim 4, wherein the end surface recess communicates with an end surface outer peripheral groove that is formed in the end surface and extends to an outer peripheral surface of the second input side cam member. Between the second input side cam member and the cam hydraulic chamber constituting member, hydraulic oil is supplied from between the second input side cam member and the cam guide member,
6. The torque cam device according to claim 4, wherein the second input side cam member is formed with an inner peripheral surface side groove communicating with the end surface concave portion on the inner peripheral surface.   Between the inner peripheral surface of the first output cam member and a shaft that rotates integrally with the first input cam member and the second output cam member, the first output cam member is moved with respect to the shaft. The torque cam device according to any one of claims 1 to 6, wherein a bearing that is rotatably supported and a seal member that seals the cam hydraulic chamber are arranged with the same diameter.   The torque cam device according to claim 7, wherein the seal member is disposed on the cam hydraulic chamber side with respect to the shaft support member of the bearing. at least,
Two pulley shafts arranged in parallel and transmitting driving force from a driving source to one of them, two movable sheaves each sliding in the axial direction on the two pulley shafts, and the two movable sheaves Two pulleys comprising two fixed sheaves facing each other in the axial direction,
A belt for transmitting the driving force from the driving source transmitted to one of the two pulleys to the other pulley;
The torque cam device according to any one of claims 1 to 8, wherein a belt clamping pressure is generated between the movable sheave and the fixed sheave.
A belt-type continuously variable transmission.

Images