JP2006291999A - Torque cam device and belt type continuously variable transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a torque cam device suppressing a degradation of durability caused by the changeover of a driving state, and also to provide a belt-type continuously variable transmission. <P>SOLUTION: The torque cam device comprises: a first cam device 71 having facing driving cam surfaces (an input side driving cam surface 71a and an output side driving cam surface 71b) relatively rotatable in a circumferential direction, and generating thrust in an axial direction by driving force F1 when driving; a second cam device having facing driven cam surfaces (an input side driven cam surface 72a and an output side driven cam surface 72b) relatively rotatable in the circumferential direction, and generating thrust in the axial direction by driven force F2, F3 when driven; a cam roller 73 contacting the facing driving cam surfaces when driving, and contacting the facing driven cam surfaces when driven; and elastic members 74, 74 applying force P1, P2 to the facing driven cam surfaces to rotate the facing driven cam surfaces in a direction to contact the cam roller 73 when driving. <P>COPYRIGHT: (C)2007,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 using a cam roller and a belt type continuously variable transmission.

  Some torque cam devices use cam rollers as rolling elements. In the torque cam device using the cam roller, torque is transmitted by the cam roller contacting cam surfaces formed on the input member and the output member so as to face each other. Some of these torque cam devices can not only transmit torque but also generate thrust in the axial direction by forming opposing cam surfaces in the circumferential direction. It is used for a machine, particularly a belt type continuously variable transmission.

  A torque cam device used for 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 the axial direction becomes the belt clamping pressure of the secondary pulley, and the belt can be clamped. Here, in the torque cam device of the belt type continuously variable transmission, a driven force is generated in addition to the driving force that is an output torque for moving the vehicle forward. As this driven force, there is an output torque in the direction opposite to the driving force transmitted from the secondary pulley side in order to reverse the vehicle, or a resistance torque in the same direction as the driving force from the final reduction gear side, for example, when using an engine brake. is there. For this reason, in a torque cam device used in a belt-type continuously variable transmission, it is necessary to transmit a driven force during driving via a cam roller in addition to the opposing cam surface. Therefore, the input cam and the output member are formed so that the driven cam surfaces face each other. The driven cam surface is formed on the input member and the output member on the circumferential direction in which the driving cam surface is formed. That is, the driving cam surface and the driven cam surface are alternately formed on the input member and the output member 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 or from driving to driving, the object to be contacted by the cam roller is driven from the driving cam surface. It changes from a cam surface or a driven cam surface to a driving cam surface. When this driving state is switched, the cam roller is separated from one opposing cam surface, and when it comes into contact with the opposing cam surface in the other direction, impact torque is generated in the input member and output member, and the durability of the cam surface is increased. May decrease, and the durability of the torque cam device may decrease.

  Conventionally, 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 that is 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 the direction opposite to the first cam surface and contacting the cam roller. This conventional torque cam device is used in a belt type continuously variable transmission.

  In this torque cam device, the cam roller is sandwiched between the first cam surface and the second cam surface by the compression force of the compression spring arranged 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, regardless of the driving state of the torque cam device A, the contact between the cam roller and the cam surface does not leave.

JP 63-210458 A

  However, in order to guide the cam member in the axial direction relative to the cylindrical portion, a sliding gap is formed in the circumferential direction between the long groove and the pin. That is, there is a backlash in the circumferential direction between the long groove and the pin. Therefore, when the driving state of the torque cam device A is switched, the long groove and the pin are contacted in the circumferential direction, and thus a collision torque is generated. As a result, the durability of the long groove and the pin is lowered, and there is a possibility that the deterioration of the durability of the torque cam cannot be suppressed.

  Therefore, the present invention has been made in view of the above, and an object thereof is to provide a torque cam device and a belt-type continuously variable transmission that can suppress a decrease in durability due to switching of a driving state. It is.

  In order to solve the above-described problems and achieve the object, the torque cam device according to the present invention has opposing drive cam surfaces that can rotate at least in the circumferential direction, and thrust in the axial direction by the driving force during driving. A first cam device that generates a thrust, a second cam device that has an opposed driven cam surface that is relatively rotatable in the circumferential direction, and generates a thrust in an axial direction by a driven force when driven, and the drive A rolling element that sometimes contacts the opposing driving cam surface and contacts the opposing driven cam surface during the driving; and the opposing driven cam surface that faces the opposing driven cam surface during the driving. And buffer means for applying a force for rotating in a direction to contact the rolling element.

  According to the present invention, in the torque cam device, the buffer means is disposed between the first cam device and the second cam device, and the driven cam surface facing the opposite driving cam surface. It is characterized by applying a force in the direction in which the two approach.

  The rolling element is preferably a cam roller.

  According to these inventions, the opposing driven cam surface is applied with a force in a direction approaching the opposing driving cam surface by the buffering means, so that the opposing driving cam surface contacts the rolling element. Even during driving, it is always in contact with the rolling element. Therefore, when the driving state of the torque cam device is switched from driving to driven, the opposing driving cam surface and the opposing driven cam surface are not separated from the rolling element, so that impact torque is generated. Can be suppressed. Also, when the driving state of the torque cam device is switched from driven to driven, the driven cam surface and the rolling element do not separate from each other, and the opposing driving cam surface and the rolling element are difficult to separate by the buffer means. The occurrence of impact torque can be suppressed. Thus, when the driving state of the torque cam device is switched, it is possible to suppress the generation of impact torque between the cam surface and the rolling element, and it is possible to suppress a decrease in durability due to the switching of the driving state.

  According to the present invention, in the torque cam device, the first cam device has an opposing auxiliary driven cam surface, and a driven force input to the second cam device at the time of driving is a predetermined value or more. Then, the opposing auxiliary driven cam surface and the rolling element come into contact with each other.

  According to the present invention, the driven cam at the time of driving changes the relative position of the second cam device with respect to the first cam device, and when the driving force at the time of driving becomes equal to or greater than a predetermined value, The rolling element in contact with the surface comes into contact with the opposing auxiliary driven cam surface. Therefore, when the driven force at the time of driving becomes a predetermined value or more, the relative position of the second cam device to the first cam device does not change. Therefore, it is possible to maintain a change in responsiveness within a certain range when the driven force changes during driving.

  In the torque cam device according to the present invention, the driven cam surface and the auxiliary driven cam surface have the same cam angle.

  According to the present invention, when the driven force during driving is equal to or greater than a predetermined value, both the opposed driven cam surface and the opposing auxiliary driven cam surface are always in contact with the rolling elements. That is, the driven force during driving is transmitted by both the first cam device and the second cam device. Therefore, even if an excessive driven force is input to the torque cam device, the auxiliary driven cam surface of the first cam device can transmit a part of the excessive driven force. The durability of the two-cam device can be improved. Further, since the cam angle of the opposed driven cam surface and the opposed auxiliary driven cam surface is the same, the auxiliary driven surface facing the opposed driven cam surface when the relative position of the second cam device with respect to the first cam device changes. The rolling elements can be prevented from being bitten by the difference in cam angle with the drive cam surface.

  According to the present invention, in the torque cam device, the rolling element is divided into a first rolling element that contacts the opposing driving cam surface and a second rolling element that contacts the opposing driven cam surface. It is characterized by.

  According to the present invention, in the torque cam device, the rolling element is in contact with the opposing driving cam surface and the opposing auxiliary driven cam surface, and the opposing driven cam surface. It is divided into a second rolling element.

  According to these inventions, the rolling elements can be divided into the first rolling element that contacts at least the opposing driving cam surface and the second rolling element that contacts the opposing driven cam surface, and can rotate separately. . Therefore, the rotation direction can be made different between the first rolling element in contact with the opposed driving cam surface and the second rolling element in contact with the opposed driven cam surface. Thereby, since the increase in resistance at the time of rotation of a rolling element can be suppressed, the fall of the transmission efficiency of a driving force and a to-be-driven force can be suppressed.

  According to the present invention, in the torque cam device, the rolling element further includes a rolling element rotating shaft, and the rolling element rotating shaft supports the first rolling element and the second rolling element so as to be relatively rotatable. It is characterized by that.

  According to this invention, the 1st rolling element and the 2nd rolling element can rotate relatively centering on a rolling element rotating shaft. Therefore, relative movement between the first rolling element and the second rolling element can be suppressed during driving and driven. Thereby, the fall of durability of a rolling element 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, since the belt type continuously variable transmission is configured using the torque cam device, it is possible to suppress a decrease in durability.

  In the torque cam device and the belt type continuously variable transmission according to the present invention, since the driven cam surface opposed to the rolling element by the buffering means is in contact with the rolling element by the buffering means, the deterioration of the durability due to the switching of the driving state is suppressed. There is an effect that can be done.

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

  A torque converter 30 is accommodated in the transaxle housing 21. On the other hand, inside the case constituted by the transaxle case 22 and the transaxle rear cover 23, a primary pulley 50 and a secondary pulley 60 which are two pulleys constituting the belt type continuously variable transmission 1 according to the present invention, and a primary A primary oil chamber 54 for generating belt clamping pressure in the pulley 50, a secondary oil chamber 64 for generating 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 about the same axis as the crankshaft 11. That is, the turbine 32 can rotate about the same axis as the crankshaft 11 together with the input shaft 38.

  A stator 33 is disposed between the pump 31 and the turbine 32 via a one-way clutch 39. The one-way clutch 39 is fixed to the transaxle housing 21. A lockup clutch 34 is disposed between the turbine 32 and the front cover 37, and the lockup clutch 34 is connected to an input shaft 38 via a damper device 35. The casing formed by the pump 31 and the front cover 37 is 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 described later. In the above, the stator 33 can change the flow of hydraulic fluid circulating between the pump 31 and the turbine 32 to obtain a predetermined torque characteristic.

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

  An oil pump 26 is provided between the torque converter 30 and a forward / reverse switching mechanism 40 described later. The oil pump 26 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 a primary pulley shaft 51 of a primary pulley 50 described later. Accordingly, the output torque from the internal combustion engine 10 transmitted to the sun gear 44 is transmitted to the primary pulley shaft 51.

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

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

  The forward clutch 42 is ON / OFF controlled by hydraulic oil supplied 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 a brake piston (not shown) supplied with hydraulic oil 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 transmits the output torque from the internal combustion engine 10 transmitted through the forward / reverse switching mechanism 40 to the secondary pulley 60 by a belt 100 described later. 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 oil 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 the hydraulic oil supplied from the hydraulic oil supply control device (not shown) to the primary oil chamber 54 flows into the hydraulic oil passage.

  The primary fixed sheave 52 is integrally provided on the outer periphery of the primary pulley shaft 51 so as to face the primary movable sheave 53. The primary movable sheave 53 is splined to the primary pulley shaft 51 so as to be slidable on the primary pulley shaft 51 in the axial direction. Between the primary fixed sheave 52 and the primary movable sheave 53, that is, between the surface of the primary fixed sheave 52 that faces the primary movable sheave 53 and the surface of the primary movable sheave 53 that faces the primary fixed sheave 52. A primary groove 100a having a shape is formed.

  The primary oil 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 (not shown) such as a seal ring is provided between the protrusion 53b and the protrusion 55a. That is, the back surface 53a of the primary movable sheave 53 constituting the primary oil chamber 54 and the primary partition wall 55 are sealed by the seal member.

  The primary oil chamber 54 is supplied with hydraulic oil flowing into a hydraulic oil passage (not shown) of the secondary pulley shaft 61 through a hydraulic oil supply hole (not shown). That is, the hydraulic oil supply control device supplies hydraulic oil to the primary oil chamber 54, and the primary movable sheave 53 is slid in the axial direction by the pressure of the supplied hydraulic oil, so that the primary movable sheave 53 is primary fixed. It approaches or separates from the sheave 52. The primary oil chamber 54 generates a belt clamping pressure with respect to the belt 100 wound around the primary groove 100 a by applying an axial pressing force to the primary movable sheave 53 by the hydraulic oil supplied to the primary oil chamber 54. The axial position of the primary movable sheave 53 with respect to the primary fixed sheave 52 is changed. Thus, the primary oil 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 shown in FIG. 1, the secondary pulley 60 includes a secondary pulley shaft 61, a secondary fixed sheave 62, a secondary movable sheave 63, and a secondary oil chamber 64 that generates belt clamping pressure on the secondary pulley 60. ing.

  The secondary pulley shaft 61 is rotatably supported by bearings 103 and 104. Further, the secondary pulley shaft 61 has a hydraulic oil passage (not shown) inside, and the hydraulic oil that is a hydraulic fluid supplied from the hydraulic oil supply control device (not shown) to the secondary oil chamber 64 is provided in the hydraulic oil passage. Flows in.

  The secondary fixed sheave 62 is integrally provided on the outer periphery of the secondary pulley shaft 61 so as to face the secondary movable sheave 63. The secondary movable sheave 63 is spline-fitted to the secondary pulley shaft 61 so as to be slidable on the secondary pulley shaft 61 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. Reference numeral 66 denotes a parking brake gear.

  The secondary oil chamber 64 is configured by a back surface 63 a opposite to the surface facing the secondary fixed sheave 62 of the secondary movable sheave 63, and a disk-shaped secondary partition wall 65 fixed to the secondary pulley shaft 61. On the back surface 63a of the secondary movable sheave 63, an annular protrusion 63b that protrudes in the other axial direction, that is, protrudes toward the final reduction gear 80, is formed. On the other hand, the secondary partition wall 65 is formed with an annular projecting portion 65a projecting in one axial direction, that is, projecting toward the secondary movable sheave 63 side. A seal member (not shown) such as a seal ring is provided between the protrusion 63b and the protrusion 65a. That is, the back surface 63a of the secondary movable sheave 63 constituting the secondary oil chamber 64 and the secondary partition wall 65 are sealed by a seal member (not shown).

  The secondary oil chamber 64 is supplied with hydraulic oil flowing into a hydraulic oil passage (not shown) of the secondary pulley shaft 61 through a hydraulic oil supply hole (not shown). That is, the hydraulic oil supply control device supplies hydraulic oil to the secondary oil chamber 64, and the secondary movable sheave 63 is slid in the axial direction by the pressure of the supplied hydraulic oil, and the secondary movable sheave 63 is moved to the secondary fixed sheave. 62 is approached or separated. The secondary oil chamber 64 generates a belt clamping pressure with respect to the belt 100 wound around the secondary groove 100 b by applying an axial pressing force to the secondary movable sheave 63 by the hydraulic oil supplied to the secondary oil chamber 64. The contact radius of the belt 100 with respect to the primary pulley 50 and the secondary pulley 60 is kept constant.

  FIGS. 2-1 to 2-3 are diagrams showing a configuration example of the torque cam device according to the present invention. FIGS. 2-1 to 2-3 are views showing the state of the torque cam device during no load and during driving. As shown in FIGS. 2-1 to 2-3, the torque cam device 70 of the belt-type continuously variable transmission 1 includes a first cam device 71, a second cam device 72, a cam roller 73 that is a rolling element, and a buffer. It comprises two elastic members 74 and 74 as means and a retainer (not shown) that holds the cam roller 73. The torque cam device 70 is disposed radially outside the secondary oil chamber 64. A plurality of torque cam devices 70 are arranged in the circumferential direction.

  The first cam device 71 includes an input side drive cam surface 71a and an output side drive cam surface 71b that are opposed drive cam surfaces, an input side auxiliary driven cam surface 71c that is an opposed auxiliary driven cam surface, and an output side auxiliary. And a driven cam surface 71d. The input side drive cam surface 71 a and the output side auxiliary driven cam surface 71 d are formed on one side surface 75 a of a ring-shaped input side first cam member 75 disposed around the secondary pulley shaft 61. On the other hand, the output side drive cam surface 71b and the input side auxiliary driven cam surface 71c are one side surface 76a (input side first cam) of a ring-shaped output side first cam member 76 disposed around the secondary pulley shaft 61. The side surface 75a of the member 75 is opposed to one side surface 75a.

  The input side drive cam surface 71a and the output side drive cam surface 71b are formed on the input side first cam member 75 and the output side first cam member 76, respectively, so that the cam angles α1 and α2 are the same. On the other hand, the input-side auxiliary driven cam surface 71c and the output-side auxiliary driven cam surface 71d have an output-side first cam member 76 and an input-side first cam member 75 so that the cam angles α3, α4 are the same. Is formed. Here, the cam angle is an angle with respect to the circumferential direction (hereinafter simply referred to as “circumferential direction”) of the input-side first cam member 75 and the output-side first cam member 76. The cam angles α1 and α2 and the cam angles α3 and α4 have different directions with respect to the circumferential direction. That is, in the input side driving cam surface 71a and the output side driving cam surface 71b, and the input side auxiliary driven cam surface 71c and the output side auxiliary driven cam surface 71d, the directions in which the inclination directions with respect to the circumferential direction intersect each other, that is, reverse Direction. The cam angles α1, α2 and cam angles α3, α4 may be the same or different in magnitude, that is, the absolute value of the inclination angle with respect to the circumferential direction.

  Here, the input side first cam member 75 is fixed to the secondary movable sheave 63 in the circumferential direction by spline fitting and in the axial direction by a snap ring or the like. Thereby, the input-side first cam member 75 is integrated with the secondary movable sheave 63 and the output torque input to the secondary movable sheave 63 is transmitted. The input-side first cam member 75 is formed with a storage space portion 75 c that stores a part of the elastic member 74. The storage space portion 75 c is open to the other side surface 75 b of the input side first cam member 75. When the input-side first cam member 75 is fixed to and integrated with the secondary movable sheave 63, the portion opened to 75 b on the other side surface of the storage space 75 c is the portion of the secondary movable sheave 63. It is blocked by the back surface 63a.

  The output first cam member 76 is fixed to the power transmission shaft 91 by a spline, a snap ring or the like. As a result, the output side first cam member 76 is integrated with the power transmission shaft 91, and the output torque input to the output side first cam member 75 via the cam roller 73 is input to the output side first cam member 76. It is transmitted to the shaft 91. The other side surface 76 b of the output side first cam member 76 is in contact with the power transmission shaft 91. The output-side first cam member 76 is formed with a storage space 76 c that stores a part of the elastic member 74. The storage space portion 76 c is opened on the other side surface 76 b of the output side first cam member 76. When the output-side first cam member 76 is fixed to and integrated with the power transmission shaft 91, the portion opened to the other side surface 76 b of the storage space 76 c is blocked by the power transmission shaft 91. Is done.

  As described above, the input-side first cam member 75 and the output-side first cam member 76 are fixed to different rotating members (secondary movable sheave 63, power transmission shaft 91). Therefore, since the input side first cam member 75 and the output side first cam member 76 can be rotated relative to each other, the input side drive cam surface 71a and the output side drive cam surface 71b can be rotated relative to each other. The driven cam surface 71c and the output side auxiliary driven cam surface 71d can be rotated relative to each other.

  The second cam device 72 includes an input side driven cam surface 72a and an output side driven cam surface 72b, which are opposed driven cam surfaces. The input side driven cam surface 72 a is formed on one side surface 77 a of the input side second cam member 77. On the other hand, the output side driven cam surface 72b is formed on one side surface 78a of the output side second cam member 78 (a side surface facing one side surface 77a of the input side second cam member 77).

  The input-side driven cam surface 72a and the output-side driven cam surface 72b are formed on the input-side second cam member 77 and the output-side second cam member 78, respectively, so that the cam angles α5, α6 are the same. Yes. Here, the cam angles α5 and α6 are preferably the same as the cam angles α3 and α4 of the input side auxiliary driven cam surface 71c and the output side auxiliary driven cam surface 71d. That is, the absolute value of the inclination angle with respect to the circumferential direction is the same between the input-side driven cam surface 72a and the output-side driven cam surface 72b, and the input-side auxiliary driven cam surface 71c and the output-side auxiliary driven cam surface 71d. In addition, it is preferable that the inclination directions with respect to the circumferential direction are the same direction.

  Here, the input-side second cam member 77 is disposed on the radially outer side of the output-side first cam member 76 and slides in the circumferential direction with respect to the output-side first cam member 76 and the power transmission shaft 91. Supported as possible. The other side surface 77b of the input-side second cam member 77 is in contact with the power transmission shaft 91, and movement to the power transmission shaft side in the axial direction is restricted. However, the present invention is not limited to this, and the input-side second cam member 77 may restrict movement of the input-side second cam member 77 toward the power transmission shaft in the axial direction. Further, the input-side second cam member 77 is formed with a storage space portion 77c that stores a part of the elastic member 74. The storage space 77 c is open on the other side surface 77 b of the input-side second cam member 77. When the input-side second cam member 77 is disposed outside the output-side first cam member 76, the portion opened to the other side surface 77b of the storage space 77c is caused by the power transmission shaft 91. Blocked.

  The output-side second cam member 78 is disposed on the radially outer side of the input-side first cam member 75 and can slide in the circumferential direction with respect to the input-side first cam member 75 and the secondary movable sheave 63. Supported by The other side surface 78b of the output-side second cam member 78 is in contact with the back surface 63a of the secondary movable sheave 63, and movement to the secondary movable sheave side in the axial direction is restricted. However, the present invention is not limited to this, and the output-side second cam member 78 may restrict movement of the output-side second cam member 78 in the axial direction toward the power transmission shaft. The output-side second cam member 78 is formed with a storage space portion 78c that stores a part of the elastic member 74. The storage space portion 78 c is open on the other side surface 78 b of the output-side second cam member 78. When the output-side second cam member 78 is disposed outside the input-side first cam member 75, the portion opened to the other side surface 78b of the storage space portion 78c is the secondary movable sheave 63. It is blocked by the back surface 63a.

  As described above, the input-side second cam member 77 and the output-side second cam member 78 can slide in the circumferential direction on different rotating members (the output-side first cam member 76 and the input-side first cam member 75). It is supported by. Therefore, since the input side second cam member 77 and the output side second cam member 78 can rotate relative to each other, the input side driven cam surface 72a and the output side driven cam surface 72b can rotate relative to each other. When a plurality of torque cam devices 70 are arranged in the circumferential direction, a plurality of input side second cam members 77 and output side second cam members 78 may be arranged in the circumferential direction for each torque cam device 70. However, it may be formed in a ring shape. When formed in a ring shape, the input-side driven cam surface 72a and the output-side driven cam surface 72b are respectively connected to the input-side second cam member 77 and the output-side second cam member 78 for each torque cam device 70. A plurality are formed in the circumferential direction.

  The cam roller 73 is a rolling element and is formed in a cylindrical shape. This cam roller 73 is arranged between the input side first cam member 75 and the output side second cam member 78 arranged on the secondary movable sheave side, and on the output side first cam member 76 and the input side arranged on the power transmission shaft side. It is arranged between the second cam member 77. That is, the cam roller 73 is disposed between the opposing driving cam surfaces of the first cam device 71 and between the opposing auxiliary driven cam surfaces and between the opposing driven cam surfaces of the second cam device 72. The cam roller 73 matches the radial thickness of the input-side first cam member 75 or the output-side first cam member 76 with the radial thickness of the input-side second cam member 77 or the output-side second cam member 78. The height is almost the same as the distance. Thereby, the cam roller 73 can contact the input side drive cam surface 71a and the output side drive cam surface 71b, and can contact the input side auxiliary driven cam surface 71c and the output side auxiliary driven cam surface 71d. And can contact the input driven cam surface 72a and the output driven cam surface 72b. In this embodiment, the cam roller 73 is used as the rolling element, but the present invention is not limited to this, and a ball may be used. In this case, the balls are arranged between the input side first cam member 75 and the output side first cam member 76 and between the input side second cam member 77 and the output side second cam member 78, respectively. .

  The elastic members 74 are accommodated between the storage space portion 75c and the storage space portion 78c, and between the storage space portion 76c and the storage space portion 77c, respectively. Specifically, the elastic members 74 and 74 are accommodated such that both end portions 74a and 74b are in contact with one end surfaces 75d, 76d, 77d, and 78d of the accommodation space portions 75c, 76c, 77c, and 78c, respectively. . Accordingly, the input-side first cam member 75 and the output-side second cam member 78 are arranged in a direction in which the end surface 75d and the end surface 78d are separated by the elastic member 74, that is, the input-side drive cam surface 71a and the output-side driven cam surface. Forces P1 in the direction in which 72b approaches (the direction in which the cam surface approaches when the other cam surface is viewed from one cam surface) are acting. On the other hand, the output-side first cam member 76 and the input-side second cam member 77 are similarly moved away from the end surface 76d and the end surface 77d by the elastic member 74, that is, the output-side drive cam surface 71b and the input-side cover. A force P2 in the direction in which the drive cam surface 72a approaches is acting.

  Here, the storage space portions 75c, 76c, 77c, 78c for accommodating the elastic members 74, 74 are the other side surface 75b of the input side first cam member 75, the other side surface 76b of the output side first cam member 76, and the input. The other side surface 77 b of the side second cam member 77 and the other side surface 78 b of the output side second cam member 78 are opened. Therefore, even when the output-side second cam member 78 is disposed on the radially outer side of the input-side first cam member 75 and the input-side second cam member 77 is disposed on the radially outer side of the output-side first cam member 76. The elastic members 74 and 74 can be stored in the storage spaces 75c, 76c, 77c, and 78c from the side surfaces 75b, 76b, 77b, and 78b.

  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 105 and 106. The intermediate shaft 92 is rotatably supported by bearings 107 and 108. 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 reduction gear 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 around 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 driving force transmitted to the torque cam device 70 is transmitted to the power transmission shaft 91 of the power transmission path 90. The driving force 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 to rotate the intermediate shaft 92. The driving force 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 meshed with the ring gear 46 also rotates in the same direction as the input shaft 38, and the sun gear 44 meshed with each pinion 45 becomes the input. It rotates in the opposite direction to the shaft 38. That is, the primary pulley shaft 51 connected to the sun gear 44 rotates in the direction opposite to the input shaft 38. 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 is transmitted to the torque cam device 70. The driving force 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.

  Further, the ECU (not shown) includes conditions such as the speed of the vehicle and the accelerator opening of the driver and a map (for example, an optimum 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 the hydraulic oil supplied from the hydraulic oil supply control device (not shown) to the primary oil chamber 54 that generates the 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 required when starting the vehicle, the primary movable sheave 53 is adjusted so that it is most distant 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. Here, since the width between the secondary fixed sheave 62 and the secondary movable sheave 63 is minimized, the width between the input-side first cam member 75 and the output-side first cam member 76 is maximized.

  On the other hand, 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, adjusted so that the width of the primary groove 100a is minimized. As a result, 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 gear ratio is minimized. Here, since the width between the secondary fixed sheave 62 and the secondary movable sheave 63 is maximized, the width between the input first cam member 75 and the output first cam member 76 is minimized.

  On the other hand, in the secondary pulley 60, the secondary movable sheave is controlled by a torque cam device 70, which will be described later, by controlling the hydraulic pressure of hydraulic oil supplied from a hydraulic oil supply control device (not shown) to the secondary oil chamber 64 which is a belt clamping pressure generating means. The belt clamping pressure for clamping the belt 100 generated between the secondary fixed sheave 62 and the secondary movable sheave 63 is adjusted by the axial thrust generated at 63. 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. FIG. 3 is a diagram illustrating a state of the torque cam device when the driven force during driving is less than a predetermined value. FIG. 4 is a diagram illustrating a state of the torque cam device when the driven force at the time of driving is a predetermined value or more. Here, the driving force F <b> 1 during driving refers to a unidirectional force transmitted from a member integrated with the input-side first cam member 75. When the torque cam device 70 is used in the belt-type continuously variable transmission 1, it means the output torque of the internal combustion engine 10 in the direction of moving the vehicle forward transmitted to the input side first cam member 75 of the torque cam device 70. On the other hand, the driven forces F2 and F3 when driven are integrated with the force in the other direction transmitted from the member integrated with the input first cam member 75 and the output first cam member 76. This means a force in the same direction as the driving force F1 transmitted from the member. When the torque cam device 70 is used in the belt type continuously variable transmission 1, the output torque of the internal combustion engine 10 in the direction to reverse the vehicle transmitted to the input side first cam member 75 of the torque cam device 70 and the engine brake are applied. The resistance torque transmitted to the output side first cam member 76 when used.

  Here, in the torque cam device 70, the cam member that comes into contact with the cam roller 73 differs depending on the forward and backward movement of the vehicle, the direction of the force (driving force F1, driven force F2, F3, etc.), and the cam surface that comes into contact. For example, in the torque cam device 70, when the vehicle is moving forward and the driving force F1 is transmitted, the input side first cam member 75 serves as an input member, and the output side first cam member 76 serves as an output member. Further, when the vehicle is moving forward, the torque cam device 70 transmits the driven F2 and the driven F2 can be absorbed by the compression of the elastic members 74, 74, the input side second cam member 77 is input. The output side second cam member 78 becomes an output member. Further, when the vehicle is moving forward and the torque cam device 70 transmits F2 when driven, and this F2 cannot be absorbed by the compression of the elastic members 74 and 74, the output first cam member 76 inputs. The input side first cam member 75 becomes an output member. The torque cam device 70 transmits the driven force F3 that is the driving force when the vehicle is moving backward, and when the driven F3 can be absorbed by the compression of the elastic members 74 and 74, the output side The second cam member 78 is an input member, and the input second cam member 77 is an output member. Further, the torque cam device 70 transmits the driven F3 when the vehicle is moving backward, and when the driven F3 cannot be absorbed by the compression of the elastic members 74, 74, the input side first cam member 75 receives the input. The output side first cam member 76 becomes an output member. Further, when the vehicle is moving backward and the torque cam device 70 transmits a driving force (not shown) in the same direction as the driving force F3 to the output first cam member 76, the output first cam member 76 is The input side first cam member 75 serves as an output member.

  First, the torque cam device 70 at the time of no load will be described. When no load is applied, neither driving force nor driven force is applied. In this case, as shown in FIG. 2A, the force acting on the torque cam device 70 is caused by the elastic member 74 between the input side first cam member 75 and the output side second cam member 78. A force P1 in a direction in which the surface 71a and the output-side driven cam surface 72b approach each other, and a force P2 in a direction in which the output-side driven cam surface 71b and the input-side driven cam surface 72a approach each other. Due to these forces P1 and P2, the cam roller 73 is sandwiched between the input-side drive cam surface 71a and the output-side driven cam surface 72b on the secondary pulley side, and the output-side drive cam surface 71b and the input side on the power transmission shaft side. It is sandwiched between the driven cam surface 72a. Therefore, in the no-load torque cam device 70, the input side drive cam surface 71a and the output side drive cam surface 71b always come into contact with the cam roller 73 regardless of the width between the secondary movable sheave 63 and the secondary fixed sheave 62. Then, the input side driven cam surface 72 a and the output side driven cam surface 72 b come into contact with the cam roller 73.

  Next, the torque cam device 70 when the driving state is switched from no load to driving will be described. Specifically, when the output torque of the internal combustion engine 10 in the direction to advance the vehicle transmitted to the secondary movable sheave 63 from no load is transferred to the input side first cam member 75 as the driving force F1 during the drive. The torque cam device 70 will be described. As shown in FIG. 2A, when the torque cam device 70 shifts from no load to driving, the output torque of the internal combustion engine 10 in the direction of advancing the vehicle transmitted to the secondary movable sheave 63 becomes the driving force F1 on the input side. 1 is transmitted to the cam member 75. Here, the contact of the input side drive cam surface 71a and the output side drive cam surface 71b with the cam roller 73 at no load is always maintained regardless of the width between the secondary movable sheave 63 and the secondary fixed sheave 62. Therefore, as described above, the driving force F1 is instantaneously transmitted from the input side driving cam surface 71a to the output side driving cam surface 71b via the cam roller 73. At this time, the input-side driven cam surface 72a and the output-side driven cam surface 72b approach the input-side driving cam surface 71a by the force P1 in the direction approaching the output-side driving cam surface 71b by the elastic member 74, respectively. Directional force P2 is acting. Therefore, the contact of the input side driven cam surface 72a and the output side driven cam surface 72b with the cam roller 73 at the time of no load is maintained even during driving. Accordingly, relative rotation does not occur between the input side drive cam surface 71a and the output side drive cam surface 71b, and the vehicle is interposed between the input side drive cam surface 71a and the output side drive cam surface 71b via the cam roller 73. The output torque of the internal combustion engine 10 in the direction to advance the engine is instantaneously transmitted.

  Further, the force in the direction in which the input side first cam member 75 and the output side first cam member 76 are separated by the driving force F1 transmitted from the input side driving cam surface 71a to the output side driving cam surface 71b via the cam roller 73. That is, axial thrust is generated. That is, the first cam device 71 can instantaneously transmit the driving force and can generate the axial thrust instantaneously when shifting from the no-load time to the driving time. The generated axial thrust acts on the secondary movable sheave 63 as a force in a direction in which the secondary movable sheave 63 is directed to the secondary fixed sheave 62, and sandwiches the belt 100 between the secondary movable sheave 63 and the secondary fixed sheave 62. A belt clamping pressure is generated.

  As described above, when the torque cam device 70 shifts from no load to driving, such as when the vehicle starts, the first cam mechanism 71 can instantaneously transmit the driving force without relative rotation, and the belt The clamping pressure can be generated instantaneously. Therefore, it is possible to suppress the slack at the start of the vehicle and the shortage of the belt clamping pressure borne by the torque cam device 70.

  Next, the torque cam device 70 when the driving state is switched from no load to driven is described. Specifically, the input-side first cam member 75 is driven as a driven force F3 in the direction opposite to the driving force F1 when the output torque of the internal combustion engine 10 in the direction in which the vehicle is transmitted to the secondary movable sheave 63 from the no-load time is moved backward. The torque cam device 70 at the time of shifting to the driven state transmitted to the motor will be described. The driven force F3 transmitted to the input side first cam member 75 is output side first via an elastic member 74 arranged between the input side first cam member 75 and the output side second cam member 78. The driven force F <b> 3 is transmitted to the two cam members 78 in the same direction as the direction acting on the input side first cam member 75. Here, since the input side second cam member 77 and the output side second cam member 78 are in contact with the cam roller 73 when there is no load, the input side driven cam surface 72a and the output side driven cam surface 72b The driven force F3 transmitted to the output-side second cam member 78 is instantaneously transmitted to the input-side second cam member 77 via the cam roller 73. The driven force F3 transmitted to the input side second cam member 77 is output side first via an elastic member 74 disposed between the output side first cam member 76 and the input side second cam member 77. This driven force F3 is transmitted to the cam member 76 in the same direction as the direction in which it acts on the input side first cam member 75.

  As described above, when the torque cam device 70 shifts from no load to driven when the vehicle is moving backward, the second cam mechanism 72 can transmit the driving force instantaneously without relative rotation, The belt clamping pressure can be generated instantaneously. Therefore, it is possible to suppress the slack at the time of reverse traveling of the vehicle and the shortage of the belt clamping pressure borne by the torque cam device 70.

  Next, the torque cam device 70 when the driving state is switched from driving to driven is described. Specifically, the resistance torque transmitted to the power transmission shaft 91 from the time when the driving force F1 is transmitted to the first input cam member 75 is output as the driven force F2 in the same direction as the driving force F1. The torque cam device 70 when shifting to the driven state transmitted to the first side cam member 76 will be described. The driving force F <b> 2 transmitted to the output side first cam member 76 is input to the second input side via an elastic member 74 disposed between the output side first cam member 76 and the input side second cam member 77. This driven force F <b> 2 is transmitted to the cam member 77 in the same direction as the direction in which it acts on the output side first cam member 76. Here, since the input side second cam member 77 and the output side second cam member 78 and the cam roller 73 are kept in contact with each other during driving, the driven force F2 transmitted to the input side second cam member 77 is maintained. Is instantaneously transmitted to the output-side second cam member 78 via the cam roller 73. The driven force F2 transmitted to the output-side second cam member 78 is the input-side first cam member 75 and the output-side second cam. This driven force F2 is transmitted to the input side first cam member 75 in the same direction as the direction acting on the output side first cam member 76 via the elastic member 74 disposed between the cam member 78 and the cam member 78.

  As described above, even if the torque cam device 70 shifts from driving to driven, relative rotation does not occur between the input driven cam surface 72a and the output driven cam surface 72b, and the input driven A driven force F2 is instantaneously transmitted via the cam roller 73 between the cam surface 72a and the output side driven cam surface 72b. The driven force F2 generates a force in a direction in which the input-side second cam member 77 and the output-side second cam member 78 are separated, that is, an axial thrust. In other words, the second cam device 72 can instantaneously transmit the driven force F2 when shifting from driving to driven, can maintain the generation of axial thrust, and the secondary movable sheave 63 and the secondary fixed The belt clamping pressure for clamping the belt 100 with the sheave 62 can be maintained. When the driving state of the torque cam device 70 is switched from driving to driven, the opposing driving cam surface and the opposing driven cam surface are not separated from the cam roller, so that the generation of impact torque can be suppressed. Further, it is possible to suppress a decrease in durability due to switching of the driving state. Further, since the transmission of the driving force F1 and the driven force F2 is switched quickly as compared with the conventional torque cam device, the responsiveness of the vehicle when using the engine brake is improved.

  Here, the torque cam device 70 when driven will be described. In the driven torque cam device 70, as described above, the driven forces F2 and F3 are the input side first cam member 75, the output side first cam member 76, the input side second cam member 77, and the output side second cam. It is transmitted to the member 78 in the direction in which the elastic members 74 are compressed. When the driven forces F2 and F3 cannot counter the elastic force of the elastic members 74 and 74 and the elastic members 74 and 74 cannot be compressed, the input side first cam member 75 and the output side first cam member are driven. No relative rotation occurs with 76. That is, unless the elastic members 74 are compressed by the driven forces F2 and F3, the input side first cam member 75 and the output side first cam member 76 are not separated from the cam roller 73. Therefore, when the driving state of the torque cam device 70 is switched from the driven state to the driven state, the opposed driven cam surface and the cam roller are not separated from each other, and the opposed driving cam surface and the cam roller are elastic members serving as buffering means. 74 and 74 make it difficult to separate, so that the generation of impact torque can be suppressed, and a decrease in durability due to switching of the driving state can be suppressed. Further, since the transmission of the driving force F1 and the driven force F2 is switched quickly compared to the conventional torque cam device, the responsiveness of the vehicle at the time of reacceleration is improved.

  On the other hand, when the driven forces F2 and F3 oppose the elastic force of the elastic members 74 and 74 and the elastic members 74 and 74 can be compressed, as shown in FIG. The direction in which the input side driving cam surface 71a and the output side driven cam surface 72b are separated from the second cam member 78, that is, the direction in which the output side driven cam surface 72b and the output side auxiliary driven cam surface 71d approach each other. Start moving to. Further, as shown in the figure, the output side first cam member 76 is in the direction in which the output side driving cam surface 71b and the input side driven cam surface 72a are separated from the input side second cam member 77, that is, the input side. The side driven cam surface 72a and the input side auxiliary driven cam surface 71c start to move in the approaching direction. Thereby, relative rotation occurs between the input-side first cam member 75 and the output-side first cam member 76 when driven. That is, when the elastic members 74, 74 are compressed by the driven forces F2, F3, the input side first cam member 75 and the output side first cam member 76 are separated from the cam roller 73.

  Here, the amount of compression of the elastic members 74, 74 varies depending on the magnitudes of the driven forces F2, F3. Accordingly, the amount of relative rotation between the input-side first cam member 75 and the output-side first cam member 76 during driving also varies depending on the magnitudes of the driven forces F2 and F3. Accordingly, the relative rotation between the input-side first cam member 75 and the output-side first cam member 76 increases during driving due to the excessive driven forces F2 and F3. That is, depending on the magnitude of the driven forces F2 and F3, the input side auxiliary driven cam surface 71c approaches the input side driven cam surface 72a, and the output side auxiliary driven cam surface 71d becomes the output side driven cam surface 72b. approach. Then, as shown in FIG. 4, when the driven forces F2 and F3 are equal to or greater than a predetermined value, the elastic members 74 and 74 are opposed to the elastic force, and the elastic members 74 and 74 are most compressed, so that the input side auxiliary receiving force is compressed. The driving cam surface 71c and the output side auxiliary driven cam surface 71d are brought into contact with the input side driven cam surface 72a and the cam roller 73 that has been in contact with the output side driven cam surface 72b. Thereby, the relative rotation between the input side first cam member 75 and the output side first cam member 76 during driving is restricted. Here, the predetermined values of the driven forces F2 and F3 are determined according to the elastic force of the elastic member, but if the driven forces F2 and F3 are transmitted only by the second cam device 72, the input side The excessive driven forces F2 and F3, which may damage the second cam member 77 and the output-side second cam member 78.

  As described above, the relative position of the second cam device with respect to the first cam device changes depending on the magnitudes of the driven forces F2 and F3 when driven, that is, the input-side first cam member 75 and the output-side first cam member. When the driven forces F2 and F3 at the time of driving become equal to or greater than a predetermined value, the cam roller that has been in contact with the opposing driven cam surface contacts the opposing auxiliary driven cam surface. To do. Accordingly, when the driven forces F2 and F3 at the time of driving become a predetermined value or more, the relative position of the second cam device 72 with respect to the first cam device 71 does not change. Therefore, since the change in the relative position of the second cam device 72 with respect to the first cam device 71 when the driven forces F2 and F3 during driving are changed is within a certain range, the change in the driven forces F2 and F3. It is possible to maintain the change in vehicle responsiveness within a certain range.

  The cam angles α5 and α6 between the input side driven cam surface 72a and the output side driven cam surface 72b are the same as the cam angles α3 and α4 of the input side auxiliary driven cam surface 71c and the output side auxiliary driven cam surface 71d. In this case, when the driven forces F2 and F3 in the driven state are equal to or greater than a predetermined value, the input side auxiliary driven cam surface 71c and the output side auxiliary driven cam surface 71d, the input side driven cam surface 72a and the output The cam roller 73 that has been in contact with the side driven cam surface 72b comes into contact. That is, the driven forces F2 and F3 when driven are transmitted by both the first cam device 71 and the second cam device 72. Therefore, even if excessive driven forces F2 and F3 are input to the torque cam device 70, the opposing auxiliary driven cam surface of the first cam device 71 transmits a part of the excessive driven forces F2 and F3. Therefore, the durability of the first cam device 71 and the second cam device 72 can be improved.

  Further, when the relative position of the second cam device 72 with respect to the first cam device 71 is changed by the driven forces F2 and F3 when driven, the input-side driven cam surface 72a and the input-side auxiliary driven cam surface 71c are The output side driven cam surface 72b and the output side auxiliary driven cam surface 71d do not sandwich the cam roller 73. Accordingly, it is possible to prevent the cam roller 73 from being bitten by the difference in cam angle between the opposed driven cam surface and the opposed auxiliary driven cam surface.

  Further, when the driven forces F2 and F3 when driven become equal to or greater than a predetermined value, the input side auxiliary driven cam surface 71c and the output side auxiliary driven cam surface 71d come into contact with the cam roller 73, so that the second cam device The change in the relative position of the first cam device 71 with respect to 72 is restricted. Accordingly, when the driven forces F2 and F3 at the time of driving become equal to or greater than a predetermined value, the compression of the elastic members 74 and 74 is restricted, so that the elastic members 74 and 74 can be prevented from being damaged, and the excessive driven force F2 , F3 can be prevented from lowering the durability of the elastic members 74, 74 when transmitted.

  In the above embodiment, one cam roller 73 contacts the opposing driving cam surface, the opposing driven cam surface, and the opposing auxiliary driven cam surface, but the present invention is not limited to this. 5A and 5B are diagrams illustrating another configuration example of the cam roller. As shown in FIGS. 5A and 5B, the cam roller 73 includes an input side driving cam surface 71a and an output side driving cam surface 71b, an input side auxiliary driven cam surface 71c, and an output side auxiliary driven cam surface 71d. May be divided into a first cam roller 73a that contacts the first cam roller 73a and a second cam roller 73b that contacts the input driven cam surface 72a and the output driven cam surface 72b.

  The rotation direction of the cam roller 73 is different between when the input side drive cam surface 71a and the output side drive cam surface 71b are in contact with each other and when the input side drive cam surface 72a and the output side driven cam surface 72b are in contact. Different. Therefore, when one cam roller 73 comes into contact with the opposed driving cam surface and the opposed driven cam surface, the cam roller 73 is twisted, and the friction between the one opposing cam surface and the cam roller is counteracted. Slip occurs. Thereby, there exists a possibility that the transmission efficiency of a driving force and a to-be-driven force may fall.

  Therefore, as shown in FIGS. 5A and 5B, the first cam roller 73a that is the first rolling element that contacts at least the driving cam surface that faces the cam roller 73 that is the rolling element, and the driven cam surface that faces the first cam roller 73a. Are divided into the second cam roller 73b that is the second rolling element in contact with each other, these cam rollers can be rotated separately, and the rotation directions of these two cam rollers can be made different. Thereby, since the increase in the resistance at the time of rotation of the cam roller 73 can be suppressed, the fall of the transmission efficiency of a driving force and a to-be-driven force can be suppressed.

  Further, by dividing the cam roller 73, the cam roller 73 is not twisted, the driving cam surface facing the first cam roller 73a is in uniform contact, and the driven cam surface facing the second cam roller 73b is uniform. Will come into contact. Accordingly, the surface pressure at the time of contact between the cam roller 73 and each cam surface can be reduced. Accordingly, it is not necessary to increase the rigidity of the torque cam device 70 to counter the twist, and the torque cam device 70 can be downsized.

  During driving and driven, for example, as shown in FIG. 3, only the second cam roller 73b of the cam roller 73 is in contact with the opposed driven cam surface, and the driving cam surface opposed to the first cam roller and the auxiliary driven driven opposed to each other. There may be no contact with any of the cam surfaces. In this case, the first cam roller 73a may move with respect to the second cam roller 73b. That is, when the cam roller 73 is divided during driving and driving, the first cam roller 73a and the second cam roller 73b may move relative to each other.

  Here, in the cam roller 73 shown in FIG. 5A, a first cam roller 73a and a second cam roller 73b are rotatably supported by a cam roller rotating shaft 73c. Accordingly, the first cam roller 73a and the second cam roller 73b are supported so as to be relatively rotatable by the cam roller rotation shaft 73c, and can be relatively rotated around the cam roller rotation shaft 73c. In the cam roller 73 shown in FIG. 5B, the cam roller rotation shaft 73f is fixed to the second cam roller 73b, and the cam roller rotation shaft 73g is rotatably supported by the cam roller rotation shaft 73f. Accordingly, the first cam roller 73a is rotatably supported by the cam roller rotation shafts 73f and 73g via the rotation member 73h. That is, the first cam roller 73a and the second cam roller 73b are supported by the cam roller rotation shafts 73f and 73g so as to be relatively rotatable, and can be relatively rotated around the cam roller rotation shafts 73f and 73g. Accordingly, it is possible to suppress the relative movement of the first cam roller 73a and the second cam roller 73b, and it is possible to suppress a decrease in durability of the cam roller 73.

  In the cam roller 73 shown in FIG. 5A, the surface of the first cam roller 73a facing the second cam roller 73b and the surface of the second cam roller 73b facing the first cam roller 73a are tapered surfaces 73d and 73e, respectively. preferable. Thereby, the resistance at the time of relative rotation of the 1st cam roller 73a and the 2nd cam roller 73b can be reduced, and the fall of the transmission efficiency of a driving force and a to-be-driven force can be suppressed.

  In the above embodiment, when the driven forces F2 and F3 at the time of driving can be sufficiently transmitted only by the second cam device 72, the first cam device 71 has an auxiliary driven cam surface facing it. It does not have to be. In this case, the input side first cam member 75 and the output side first cam member 76 only transmit the driving force F1, and the input side second cam member 77 and the output side second cam member 78 are driven by the driven forces F2 and F3. It can be used for transmission only. Therefore, the rigidity can be increased as compared with the case where each member transmits both the driving force F1 and the driven forces F2 and F3. Thereby, deformation of each cam surface can be suppressed, and the transmission efficiency of the driving force F1 and the driven forces F2 and F3 can be improved. When the first cam device 71 does not have an opposing auxiliary driven cam surface, the compression of the elastic members 74 and 74 is maximized when the excessive driven forces F2 and F3 are transmitted, and the elastic member There is a possibility that 74 and 74 may be damaged. Therefore, the relative rotation between the second cam device 72 and the first cam device 71, that is, the output-side second cam member 78 and the input-side first cam member 75 so that the compression of the elastic members 74, 74 is not maximized. It is preferable to provide a restricting means for restricting relative movement between the first cam member 76 and the second cam member 77 on the input side and the first cam member 76 on the output side. This restricting means is fixed to, for example, the input side first cam member 75 and the output side first cam member 76, respectively, and before the compression of the elastic members 74, 74 reaches the maximum, the input side second cam member 77 and the output side It is a regulating member that contacts the second cam member 78. Here, the restricting member is preferably formed of, for example, an elastic member that suppresses the generation of impact torque when the input-side second cam member 77 and the output-side second cam member 78 are in contact with each other.

  Moreover, in the said Example, although the elastic members 74 and 74 are used as a buffering means, it is not limited to this. For example, instead of housing the elastic members 74 and 74 between the storage space portion 75c and the storage space portion 78c, and between the storage space portion 76c and the storage space portion 77c, it is used as an oil chamber to supply hydraulic oil (not shown). Hydraulic oil may be supplied as a working fluid from the control device, and the hydraulic pressure of the hydraulic oil may be used instead of the elastic force of the elastic member.

  In the above embodiment, the secondary oil chamber 64 and the torque cam device 70 are used as the belt clamping pressure generating means on the secondary side, but the present invention is not limited to this, and the torque cam device 70 is used as the belt clamping pressure generating means on the secondary side. You may use only. Further, as the secondary side belt clamping pressure generating means, for example, an electric motor such as a motor may be used in combination with the torque cam device 70.

  Moreover, in the said Example, although the torque cam apparatus 70 is arrange | positioned in the circumferential direction on the outer side of the secondary oil chamber 64, it is not limited to this. For example, a plurality may be arranged in the circumferential direction inside the secondary oil chamber 64. That is, the torque cam device 70 may be disposed in the secondary oil chamber 64. In this case, the hydraulic oil in the secondary oil chamber 64 can always be supplied to the torque cam device 70. Therefore, it is not necessary to newly form an oil passage for supplying hydraulic oil necessary for lubricating the torque cam device 70.

  As described above, the torque cam device according to the present invention is useful for a belt-type continuously variable transmission, and particularly for suppressing a decrease in responsiveness and a decrease in durability when the driving state is switched. Is suitable.

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 (front view) of the torque cam apparatus concerning this invention. It is a figure which shows the structural example (AA sectional drawing of FIGS. 2-1) of the torque cam apparatus concerning this invention. It is a figure which shows the structural example (side view) of the torque cam apparatus concerning this invention. It is a figure which shows the state of a torque cam apparatus in case the driven force at the time of driven is less than predetermined value. It is a figure which shows the state of a torque cam apparatus when the driven force at the time of driven is more than predetermined value. It is a figure which shows the other structural example of a cam roller. It is a figure which shows the other structural example of a cam roller.

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 oil chamber 55 primary partition wall 60 secondary pulley 61 secondary pulley shaft 62 secondary fixed sheave 63 secondary movable sheave 64 secondary Oil chamber 65 Secondary partition wall 70 Torque cam device 71 First cam device 71a Input side driving cam surface 71b Output side driving cam surface 71c Input side auxiliary driven cam surface 71d Output side auxiliary driven cam surface 72 Second cam device 72a Input side driven cam surface Driving cam surface 72b Output-side driven cam surface 73 Cam roller 73a First cam roller 73b Second cam rollers 73c, 73f, 73g Cam roller rotating shaft 74 Elastic member (buffer means)
75 Input side first cam member 76 Output side first cam member 77 Input side second cam member 78 Output side second cam member 80 Final reduction gear 90 Power transmission path 100 Belt 110 Wheel

Claims (9)

A first cam device that has at least an opposing drive cam surface that is relatively rotatable in the circumferential direction, and that generates thrust in the axial direction by a driving force during driving;
A second cam device having opposed driven cam surfaces that can rotate relative to each other in the circumferential direction, and generating thrust in the axial direction by a driven force when driven;
A rolling element that is in contact with the opposing driving cam surface during the driving and that is in contact with the opposing driven cam surface during the driving;
Buffer means for applying a force to rotate the opposing driven cam surface in the direction of contacting the rolling element to the opposing driven cam surface during the driving;
A torque cam device comprising:   The buffer means is disposed between the first cam device and the second cam device, and exerts a force in a direction in which the opposed driven cam surface approaches the opposed driving cam surface. The torque cam device according to claim 1. The first cam device has opposing auxiliary driven cam surfaces that are relatively rotatable in the circumferential direction,
The said auxiliary | assistant driven cam surface and the said rolling element contact when the driven force input into the said 2nd cam apparatus becomes the predetermined value or more at the time of the said driven. 3. The torque cam device according to 1 or 2.   The torque cam device according to claim 3, wherein the driven cam surface and the auxiliary driven cam surface have the same cam angle.   The said rolling element is divided | segmented into the 1st rolling element which contacts the said drive cam surface which opposes, and the 2nd rolling element which contacts the said driven cam surface which opposes. 2. The torque cam device according to 2.   The rolling element is divided into a first rolling element that contacts the opposing driving cam surface and the opposing auxiliary driven cam surface, and a second rolling element that contacts the opposing driven cam surface. The torque cam device according to claim 3 or 4, wherein the torque cam device is provided. The rolling element further includes a rolling element rotating shaft,
The torque cam device according to claim 5 or 6, wherein the rolling element rotating shaft supports the first rolling element and the second rolling element so as to be relatively rotatable.   The torque cam device according to claim 1, wherein the rolling element is a cam roller. 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