JP2007107612A - Belt type continuously variable transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a belt type continuously variable transmission capable of accurately carrying out circumferential positioning of a movable sheave, and capable of carrying out cost reduction and miniaturization. <P>SOLUTION: The belt type continuously variable transmission is provided with variable pulleys 35, 36 comprising stationary sheaves 37, 41 unmovable in the axial and circumferential directions, and movable sheaves 38, 42 capable of moving in the axial direction on rotary shafts SP, SS. Circumferential positioning means for the movable sheaves 38, 42 with respect to the rotary shafts SP, SS are provided on outer circumference parts of the movable sheaves 38, 42. It is also suitable that the circumferential positioning means are provided with movable sheave external teeth 38G, 42G formed on the outer circumference parts of the movable sheaves 38, 42, stationary sheave external teeth 37G, 41G formed on outer circumference parts of the stationary sheaves 37, 41, and rotating members 70, 80 rotatably supported by stationary members, and formed with external teeth concurrently meshing with the movable sheave external teeth and the stationary sheave external teeth. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention comprises a variable pulley comprising a fixed sheave that is not movable in the axial direction on a rotating shaft and a movable sheave that is movable in the axial direction on the primary side and the secondary side, and a belt winding radius around those variable pulleys The present invention relates to a belt-type continuously variable transmission that can obtain a desired gear ratio by changing the speed.

  Conventionally, a belt type continuously variable transmission is known as a transmission for a vehicle. This type of belt-type continuously variable transmission is mounted on a primary shaft (drive side rotating shaft) and a secondary shaft (driven side rotating shaft) arranged in parallel to each other, a primary pulley mounted on the primary shaft, and a secondary shaft. Secondary pulley. Each of the primary pulley and the secondary pulley includes a fixed sheave fixed to or integrally formed with the rotating shaft, and a movable sheave movable in the axial direction with respect to the fixed sheave. For the primary pulley and the secondary pulley, a hydraulic chamber is provided for moving each movable sheave closer to and away from the corresponding fixed sheave. The hydraulic pressure in each hydraulic chamber is controlled separately, whereby the groove width of the pulley is changed to change the belt winding radius, the transmission ratio is set to a desired value, and the belt tension is adjusted. .

  By the way, each movable sheave is movable in the axial direction with respect to the fixed sheave as described above, but must be immovable in the circumferential direction. As a structure for this purpose, for example, in Patent Document 1, ball grooves (ball splines) are respectively formed on the inner peripheral side of the movable sheave and the outer peripheral side of the rotating shaft, and a plurality of balls are arranged in these grooves. I have to. Thus, the movable sheave is movable in the axial direction and immovable in the circumferential direction with respect to the corresponding rotation shaft via the ball and the ball groove (ball spline).

  Further, in Patent Document 2 or Patent Document 3, a pin protrudes from the back intermediate portion of the movable sheave in a form penetrating a fixed piston formed in a hydraulic chamber and fixed to a rotating shaft. Thus, a structure is disclosed in which the movable sheave is movable in the axial direction and immovable in the circumferential direction with respect to the corresponding rotating shaft.

JP 2001-323978 A JP 2000-170885 A Japanese Patent Publication No.7-117131

  By the way, as described in the above-mentioned Patent Document 1, ball grooves are formed on the inner peripheral side of the movable sheave and the outer peripheral side of the rotary shaft, respectively, and the corresponding rotary shaft is utilized by utilizing the ball spline coupling by the ball and the ball groove. On the other hand, the structure in which the movable sheave can be moved in the axial direction but cannot move in the circumferential direction requires high-precision machining of the ball groove, and has a problem that it is expensive. In other words, the ball grooves formed on the inner peripheral side of the movable sheave and the outer peripheral side of the rotary shaft are arranged in the circumferential direction in order to secure the assemblability, the circumferential backlash, and the smooth mobility in the axial direction. This is because it has to be processed with high precision. Although the movable sheave collapses due to the force applied to the movable sheave from the belt, this acts as a force that crushes the ball, so there is a concern that the durability of the ball itself may deteriorate, such as when the transmission torque is increased. Is done.

  Further, as described in Patent Document 2 or 3, a pin having a form penetrating a fixed piston that forms a hydraulic chamber is protruded from a rear intermediate portion of the movable sheave, and the movable sheave corresponds to the pin and the fixed piston. The structure that can move in the axial direction and cannot move in the circumferential direction with respect to the rotating shaft includes a problem that there is a concern about insufficient belt clamping pressure. That is, a hydraulic pressure for generating a belt clamping pressure acts on the fixed piston forming the hydraulic chamber. As a result, the fixed piston falls down, and as a result, the hole of the fixed piston penetrating portion by the pin expands and the hydraulic oil leaks. Because there is a fear.

  SUMMARY OF THE INVENTION Accordingly, an object of the present invention is to provide a belt type continuously variable transmission capable of solving the conventional problems, positioning the movable sheave in the circumferential direction with high accuracy, and reducing the cost and size. It is to provide.

  A belt-type continuously variable transmission according to an aspect of the present invention includes a belt-type continuously variable transmission including a variable pulley including a fixed sheave that cannot move in the axial direction and the circumferential direction on a rotating shaft and a movable sheave that can move in the axial direction. A circumferential positioning means for the movable sheave with respect to the rotating shaft is provided on an outer peripheral portion of the movable sheave.

  According to this aspect, since the circumferential positioning of the movable sheave with respect to the rotation shaft is performed at the outer peripheral portion of the movable sheave, it is possible to avoid complication of processing as compared with the conventional one formed on the inner peripheral portion, The positioning accuracy can be increased, the cost can be reduced, and the size can be reduced.

  Here, the circumferential positioning means is rotatably supported on the movable sheave outer teeth formed on the outer periphery of the movable sheave, the fixed sheave outer teeth formed on the outer periphery of the fixed sheave, and the fixed member. And a rotating member formed with external teeth that mesh with the movable sheave external teeth and the fixed sheave external teeth at the same time.

  According to this embodiment, the rotating member formed with the external teeth simultaneously meshing with the movable sheave external teeth and the fixed sheave external teeth is rotatably supported by the fixed member in the circumferential direction with respect to the rotating shaft of the movable sheave. Positioning is possible.

  Moreover, it is preferable that the said rotation member is provided in the position corresponding to the bulge bending direction of the said rotating shaft.

  According to this aspect, the rotating member formed with the external teeth that simultaneously mesh with the movable sheave external teeth and the fixed sheave external teeth in the bulging and bending direction of the rotating shaft corresponding to the direction of the force applied from the belt to the movable sheave and the fixed sheave. Due to this reaction force, bending deformation of the movable sheave and the fixed sheave is suppressed and stress is reduced, so that the durability of the variable pulley and the torque transmission efficiency by the belt can be improved.

  Further, at least one of the rotating members may be provided at a position corresponding to the bulging and bending direction of the rotating shaft when the speed ratio is at the maximum deceleration.

  According to this embodiment, at the time of the most reduction of the transmission ratio, both the variable pulley and the belt are in the state where the stress is the greatest, and the effect of improving the durability by the above-described stress reduction action is most effectively obtained. .

  Note that at least one of the rotating members may be provided at a position corresponding to the bulging and bending direction of the rotating shaft when the speed ratio is at the maximum speed.

  According to this aspect, the highest speed increase region of the gear ratio is the gear ratio region that is most frequently used while the vehicle is running. In particular, the effect of improving the torque transmission efficiency by the belt described above is most effective in reducing the fuel consumption. It is done.

  Here, the rotating member has a position corresponding to the bulging and bending direction of the primary-side rotating shaft when the gear ratio is at the maximum speed, and the position corresponding to the bulging and bending direction of the secondary-side rotating shaft when the gear ratio is the most decelerated. At least one may be provided at each position.

  According to this aspect, the variable pulley has a large deformation on the primary side when the gear ratio is at the maximum speed and a large amount on the secondary side at the time of the minimum speed reduction. Since it is suppressed by the reaction force, the durability of the variable pulley and the torque transmission efficiency by the belt can be improved over a wide range of gear ratios.

  Further, the rotating member may be configured as a power transmission gear that transmits power from the input shaft or to the output shaft.

  According to this embodiment, since the torsion does not occur on the rotating shaft of the variable pulley, the stress generated by the movable sheave and the fixed sheave can be reduced, and the structure can be simplified, reduced in size, and reduced in cost.

  In addition, the circumferential positioning means in the secondary variable pulley is fixed to a movable sheave driven gear that meshes with the secondary movable sheave outer teeth formed on the outer periphery of the secondary movable sheave, and to the secondary fixed sheave or rotating shaft. A fixed sheave drive gear provided, a sun gear to which the movable sheave driven gear is connected, a ring gear driven by the fixed sheave drive gear, and a planetary gear mechanism including a pinion carrier connected to an output shaft. Good.

  According to this aspect, the movable sheave driven gear coupled to the sun gear meshes with the secondary movable sheave outer teeth formed on the outer peripheral portion of the secondary movable sheave, and is fixed to the secondary fixed sheave or the rotating shaft. Since the fixed sheave drive gear drives the ring gear of the planetary gear mechanism including the pinion carrier connected to the output shaft, the secondary side movable sheave and the fixed sheave are positioned in the circumferential direction, and the planetary gear mechanism ring gear and sun gear Since the power transmission ratio from each of the movable sheave and the fixed sheave can be changed by changing the gear ratio, the degree of freedom in design increases.

  Further, the circumferential positioning means in the secondary variable pulley is fixed to the movable sheave driven gear that meshes with the secondary movable sheave outer teeth formed on the outer peripheral portion of the secondary movable sheave and the secondary fixed sheave or rotating shaft. A fixed sheave drive gear provided, a double pinion carrier to which the movable sheave driven gear is connected, a planetary gear mechanism including a ring gear and a sun gear driven by the fixed sheave drive gear, and the sun gear is connected And a differential gear mechanism arranged coaxially with the movable sheave driven gear.

  According to this configuration, the movable sheave driven gear connected to the double pinion carrier meshes with the secondary movable sheave outer teeth formed on the outer peripheral portion of the secondary movable sheave, and is fixed to the secondary fixed sheave or the rotating shaft. The fixed sheave drive gear thus driven drives the ring gear of the planetary gear mechanism including the sun gear coupled to the differential gear mechanism that is arranged coaxially with the movable sheave driven gear. Since the direction positioning is performed and the space for arranging the left and right drive shafts and the differential gear mechanism is reduced, the size and cost can be reduced.

  Hereinafter, preferred embodiments of a belt type continuously variable transmission according to the present invention will be described in detail with reference to the drawings.

[First Embodiment]
FIG. 1 is a schematic configuration diagram showing a part of a vehicle to which a belt type continuously variable transmission according to the present invention is applied. A vehicle 1 shown in FIG. 1 is configured as a so-called FF vehicle (front engine front drive: front wheel drive vehicle in front of the engine), and includes an engine 2 as a drive source. As the engine 2, a gasoline engine, a diesel engine, an LPG engine, a hydrogen engine, a bi-fuel engine, or the like can be adopted. Here, a description will be given assuming that a gasoline engine is used as the engine 2.

  As shown in FIG. 1, the vehicle 1 has a transaxle 3 that is disposed on the side of a horizontally placed engine 2 and connected to a crankshaft SC of the engine 2. The transaxle 3 includes a transaxle housing 4, a transaxle case 5, and a transaxle rear cover 6. The transaxle housing 4 is disposed on the side of the engine 2, and the transaxle case 5 is fixed to the opening end of the transaxle housing 4 on the side opposite to the engine 2. The transaxle rear cover 6 is fixed to the opening end of the transaxle case 5 opposite to the transaxle housing 4. A torque converter 7 is disposed inside the transaxle housing 4. Inside the transaxle case 5 and the transaxle rear cover 6, a forward / reverse switching mechanism 8, a belt-type continuously variable transmission mechanism 9, and a final deceleration. A machine (differential device) 10 is arranged.

  The torque converter 7 includes a drive plate 11 and a front cover 12 fixed to the crankshaft SC of the engine 2 via the drive plate 11. As shown in FIG. 1, a pump impeller 14 is connected to the front cover 12. The torque converter 7 includes a turbine runner 15 that can rotate while facing the pump impeller 14.

  The turbine runner 15 is fixed to an input shaft SI that extends substantially coaxially with the crankshaft SC. Further, a stator 16 is disposed inside the pump impeller 14 and the turbine runner 15. The stator 16 is supported by a hollow shaft 18 extending from the transaxle case 5 via a one-way clutch 17, and the rotation direction of the stator 16 is set to be rotatable only in one direction by the one-way clutch 17. The above-described input shaft SI is inserted into the hollow shaft 18, and a lock-up clutch 20 is attached to the end of the input shaft SI on the front cover 12 side via a damper mechanism 19.

  The pump impeller 14, the turbine runner 15, and the stator 16 described above define a hydraulic fluid chamber, and this hydraulic fluid chamber is operated from an oil pump 21 disposed between the torque converter 7 and the forward / reverse switching mechanism 8. Liquid is supplied. Then, when the engine 2 is operated and the front cover 12 and the pump impeller 14 are rotated, the turbine runner 15 starts to be dragged by the flow of the hydraulic fluid. Further, the stator 16 converts the flow of the hydraulic fluid into a direction that assists the rotation of the pump impeller 14 when the rotational speed difference between the pump impeller 14 and the turbine runner 15 is large.

  Thus, the torque converter 7 operates as a torque amplifier when the rotational speed difference between the pump impeller 14 and the turbine runner 15 is large, and operates as a fluid coupling when the rotational speed difference between the two becomes small. When the vehicle speed reaches a predetermined speed after the vehicle 1 starts, the lockup clutch 20 is operated so that the power transmitted from the engine 2 to the front cover 12 is mechanically and directly transmitted to the input shaft SI. Become. Further, the fluctuation of the torque transmitted from the front cover 12 to the input shaft SI is absorbed by the damper mechanism 19.

  The oil pump 21 between the torque converter 7 and the forward / reverse switching mechanism 8 has a rotor 22, and the rotor 22 is connected to the pump impeller 14 via a hub 23. The hub 23 is spline-fitted to the rotor 22, and the main body 24 of the oil pump 21 is fixed to the transaxle case 5 side. Accordingly, the power of the engine 2 is transmitted to the rotor 22 via the pump impeller 14, thereby driving the oil pump 21.

  The forward / reverse switching mechanism 8 has a planetary gear mechanism 25 of a double pinion type. The planetary gear mechanism 25 includes a sun gear 26 attached to an end of the input shaft SI on the continuously variable transmission mechanism 9 side, a ring gear 27 disposed concentrically on the outer peripheral side of the sun gear 26, and a plurality of pinion gears that mesh with the sun gear 26. 28, a plurality of pinion gears 29 that mesh with both the ring gear 27 and the pinion gear 28, and a carrier 30 that holds each pinion gear 28 so as to be capable of rotating, and holds the pinion gear 28 in an integrally revolving state around the sun gear 26. Including.

  The carrier 30 of the forward / reverse switching mechanism 8 is fixed to the primary shaft SP included in the belt-type continuously variable transmission mechanism 9, and the power transmission path between the carrier 30 and the input shaft SI is connected using the forward clutch CL. Blocked. The forward / reverse switching mechanism 8 has a reverse brake BR that controls the rotation and fixation of the ring gear 27.

  On the other hand, the belt-type continuously variable transmission mechanism 9 includes the above-described primary shaft (driving side rotating shaft) SP extending substantially coaxially with the input shaft SI, and a secondary shaft (driven side rotating) arranged in parallel with the primary shaft SP. Axis) SS. The primary shaft SP is rotatably supported by the bearings 31 and 32, and the secondary shaft SS is rotatably supported by the bearings 33 and 34. The primary shaft SP is equipped with a primary pulley 35, and the secondary shaft SS is equipped with a secondary pulley 36.

  The primary pulley 35 is configured as a variable pulley by a fixed sheave 37 integrally formed on the outer periphery of the primary shaft SP and a movable sheave 38 slidably mounted on the outer periphery of the primary shaft SP. The fixed sheave 37 and the movable sheave 38 face each other, and a substantially V-shaped pulley groove 39 is formed between them. The movable sheave 38 is movable in the axial direction of the primary shaft SP with respect to the fixed sheave 37, and the continuously variable transmission mechanism 9 moves the movable sheave 38 in the axial direction of the primary shaft SP to A hydraulic actuator 40 is provided to approach and separate the fixed sheave 37.

  Similarly, the secondary pulley 36 is also configured as a variable pulley by a fixed sheave 41 integrally formed on the outer periphery of the secondary shaft SS and a movable sheave 42 slidably mounted on the outer periphery of the secondary shaft SS. The fixed sheave 41 and the movable sheave 42 face each other, and a substantially V-shaped pulley groove 44 is formed between them. The movable sheave 42 is also movable in the axial direction of the secondary shaft SS with respect to the fixed sheave 41, and the continuously variable transmission mechanism 9 moves the movable sheave 42 in the axial direction of the secondary shaft SS to A hydraulic actuator 45 that moves the fixed sheave 41 toward and away from the fixed sheave 41 is provided.

  Around the pulley groove 39 of the primary pulley 35 and the pulley groove 44 of the secondary pulley 36, a belt B composed of a number of metal pieces and a plurality of steel rings is wound. Then, the hydraulic pressures by the hydraulic actuators 40 and 45 are separately controlled, whereby the groove widths of the primary pulley 35 and the secondary pulley 36 are changed, and the winding radius of the belt B is changed. As a result, the transmission ratio by the continuously variable transmission mechanism 9 is set to a desired value, and the tension of the belt B is adjusted. The bearing 34 that supports the secondary shaft SS is fixed to the transaxle rear cover 6, and a parking gear PG is provided between the bearing 34 and the secondary pulley 36.

  Further, as shown in FIG. 1, a shaft 48 supported by bearings 46 and 47 is connected to the secondary shaft SS of the belt type continuously variable transmission mechanism 9. A drive gear 49 is fixed to the shaft 48, and power is transmitted from the belt-type continuously variable transmission mechanism 9 to the final reduction gear 10 via the drive gear 49. The final reduction gear 10 includes an intermediate shaft 50 that is arranged in parallel with the secondary shaft SS. The intermediate shaft 50 is supported by bearings 51 and 52, and a counter driven gear 53 that meshes with the drive gear 49 of the secondary shaft SS and a final drive gear 54 are fixed to the shaft 50.

  Further, the final reduction gear 10 has a hollow differential case 55 that incorporates a differential gear mechanism. The differential case 55 is rotatably supported by bearings 56 and 57, and a ring gear 58 is formed on the outer periphery thereof. The ring gear 58 meshes with the final drive gear 54 of the intermediate shaft 50. Further, the differential case 55 supports a pinion shaft 59 therein, and two pinion gears 60 are fixed to the pinion shaft 59. Each of the pinion gears 60 is engaged with two side gears 61. The left and right front drive shafts 62R and 62L are separately connected to the side gears 61, and the front drive shafts 62R and 62L have wheels ( Front wheel FW is fixed.

  In the first embodiment, the circumferential positioning means for the fixed sheave and the movable sheave in the primary pulley 35 and the secondary pulley 36 will be described in detail later. A side rotation member 80 is provided. The primary side rotating member 70 is rotatably supported by the bearings 71 and 72, and the secondary side rotating member 80 is rotatably supported by the bearings 81 and 82 with respect to the transaxle case 5 and the transaxle rear cover 6 as fixed members. . The primary side rotating member 70 is formed with external teeth 70G that simultaneously mesh with movable sheave external teeth 38G formed on the outer peripheral portion of the movable sheave 38 and fixed sheave external teeth 37G formed on the outer peripheral portion of the fixed sheave 37. ing. On the other hand, the secondary-side rotating member 80 has external teeth 80G that simultaneously mesh with movable sheave external teeth 42G formed on the outer peripheral portion of the movable sheave 42 and fixed sheave external teeth 41G formed on the outer peripheral portion of the fixed sheave 41. Is formed.

  FIG. 2 is an enlarged cross-sectional view showing the main part of the belt-type continuously variable transmission mechanism 9 according to the first embodiment of the present invention, which is related to the primary pulley 35 of the continuously variable transmission mechanism 9. The structure to be shown is shown. The primary shaft SP is rotatable about the axis, and oil paths SPA and SPB are formed in the primary shaft SP in the axial direction. These oil passages SPA and SPB communicate with a hydraulic circuit of a hydraulic control device (not shown). Further, the primary shaft SP is provided with oil passages SPC and SPD that extend in the radial direction toward the outer peripheral surface thereof and communicate with the oil passage SPA. The oil passage SPC and the oil passage SPD are provided at different positions in the axial direction. Specifically, the oil passage SPC is disposed closer to the end of the primary shaft SP than the oil passage SPD. Yes. An oil passage SPE that is opened between the movable sheave 38 and the fixed sheave 37 and supplies oil that lubricates the contact portion of the belt B is also communicated with the oil passage SPB toward the outer peripheral surface of the primary shaft SP. It is stretched in the radial direction.

  On the other hand, the movable sheave 38 is continuous from the inner cylindrical portion 38A that slides along the outer peripheral surface of the primary shaft SP as the rotation axis, and the end portion on the fixed sheave 37 side of the inner cylindrical portion 38A toward the outer peripheral side. It has a radial direction part 38B and an outer cylinder part 38C which is continuous in the vicinity of the outer peripheral side of the radial direction part 38B and extends in the axial direction toward the bearing 32 side. The aforementioned movable sheave outer teeth 38G are formed at the outer peripheral end of the radial direction portion 38B. Further, an oil passage 38D penetrating from the inner peripheral surface to the outer peripheral surface is formed in the inner cylindrical portion 38A. The oil passage 38D and the oil passage SPD communicate with each other via an annular notch formed on the outer peripheral surface of the primary shaft SP.

  Further, the belt type continuously variable transmission mechanism 9 includes a first cylinder member 91, a second cylinder member 92, and a piston member 93 that are annular partition members. As can be seen from FIG. 2, the first cylinder member 91 has a radial portion 91A extending in the radial direction of the primary shaft SP and a cylindrical portion 91B extending from the radial portion 91A substantially in parallel with the axis of the primary shaft SP. is doing. Similarly, the second cylinder member 92 includes a first radial portion 92A extending in the radial direction of the primary shaft SP, a cylindrical portion 92B extending substantially parallel to the axis of the primary shaft SP from the radial portion 91A, and a cylindrical portion. A second radial portion 92C extending in the radial direction of the primary shaft SP along the back surface of the movable sheave 38 from 92B. The piston member 93 is positioned between the cylindrical portion 91B and the cylindrical portion 92B of each of the first cylinder member 91 and the second cylinder member 92, and is disposed at the outer peripheral end and the inner peripheral end of the piston member 93. Are provided with seal members 93A and 93B, respectively. The seal member 93A at the outer peripheral end of the piston member 93 is in sliding contact with the inner peripheral surface of the cylindrical portion 91B of the first cylinder member 91, and the seal member 93B at the inner peripheral end is the outer peripheral surface of the cylindrical portion 92B of the second cylinder member 92. Slid in contact.

  In addition, the small diameter part of the front-end | tip of primary shaft SP is press-fitted in the center hole part formed in radial direction part 91A and 1st radial direction part 92A of the 1st cylinder member 91 and the 2nd cylinder member 92, and 1st The cylinder member 91 and the second cylinder member 92 are fixed between the bearing 32 fixed to the transaxle rear cover 6 and the step portion of the primary shaft SP using a lock nut 100.

  A seal member 92D is also provided at the outer peripheral end of the second radial direction portion 92C of the second cylinder member 92, and the seal member 92D is disposed so as to be in sliding contact with the inner peripheral surface of the outer cylindrical portion 38C of the movable sheave 38. Yes. Thus, the first hydraulic chamber 40 </ b> A that constitutes a part of the hydraulic actuator 40 described above is defined between the second cylinder member 92 and the movable sheave 38. Further, a second hydraulic chamber 40B that similarly constitutes a part of the hydraulic actuator 40 is defined between the first cylinder member 91 and the piston member 93. The first hydraulic chamber 40A is connected to the first hydraulic chamber 40A via an oil passage 92E formed at the boundary between the first radial direction portion 92A and the cylindrical portion 92B of the second cylinder member 92 and the first hydraulic chamber 40A. The hydraulic pressure is supplied. Therefore, by controlling the hydraulic pressure in the first hydraulic chamber 40A and the second hydraulic chamber 40B, the movable sheave 38 is moved with respect to the fixed sheave 37, and the winding radius of the belt B is changed. A gear ratio can be obtained.

  Further, as shown in detail in FIG. 2, the primary-side rotating member 70 in the first embodiment described above is fixed to the bearing 71 and the transaxle rear cover 6 fixed at both ends to the transaxle case 5. The shaft body 70A is rotatably supported by the bearings 72, and the cylindrical gear portion 70B is formed integrally with the shaft body 70A or is provided separately from the relative rotation of the shaft body 70A. The cylindrical gear portion 70B has external teeth 70G that simultaneously mesh with both movable sheave outer teeth 38G formed on the outer peripheral portion of the movable sheave 38 and fixed sheave outer teeth 37G formed on the outer peripheral portion of the fixed sheave 37. Is formed as described above. Although the secondary side rotation member 80 is not described in detail, it can be configured in the same manner as the primary side rotation member 70.

  Thus, when the movable sheave 38 moves in the axial direction, the movable sheave outer teeth 38G move along the outer teeth 70G in the cylindrical gear portion 70B of the primary-side rotating member 70, so the primary shaft SP and the movable sheave 38 are moved. Can be moved relatively smoothly in the axial direction. However, the primary shaft SP and the movable sheave 38 cannot move relative to each other in the circumferential direction because the movable sheave outer teeth 38G and the fixed sheave outer teeth 37G mesh with the outer teeth 70G in the cylindrical gear portion 70B. It is.

  According to the first embodiment, the circumferential positioning of the movable sheave 38 with respect to the primary shaft SP, which is the rotating shaft, is performed by the movable sheave outer teeth 38G on the outer peripheral portion of the movable sheave 38, so that it is formed on the inner peripheral portion. Compared to the conventional one, it is possible to avoid complication of processing, and in particular, it is possible to achieve higher precision, lower cost and smaller size in the circumferential positioning. Further, the rotation shaft of the movable sheave 38 has a simple configuration in which the primary side rotation member 70 formed with the external teeth 70G simultaneously meshing with the movable sheave outer teeth 38G and the fixed sheave outer teeth 37G is rotatably supported by the fixed member. The circumferential positioning with respect to the primary shaft SP can be performed. Although the above description has been made based on the configuration of FIG. 2 related to the primary pulley 35 of the continuously variable transmission mechanism 9, as shown in FIG. 1, the secondary pulley 36 also uses the secondary side rotation member 80. Can be configured similarly.

  Here, with reference to FIG. 3 to FIG. 5, preferred arrangements of the primary side rotation member 70 and the secondary side rotation member 80 described above with respect to the rotation center axis of the primary shaft SP and the secondary shaft SS that are the respective rotation axes will be described. explain.

  FIG. 3 is a schematic side view of the primary pulley 35 and the secondary pulley 36 as viewed from the extending direction of the rotation center axis of the primary shaft SP and the secondary shaft SS. The rotation center axis of the primary shaft SP is SPC and the secondary shaft SS. Is shown as SSC. The state of the belt B wound around the primary pulley 35 and the secondary pulley 36 is indicated as Bγmax when the gear ratio is at the maximum deceleration, and Bγmin when the gear ratio is at the maximum speed. Further, the primary-side rotating member 70 and the secondary-side rotating member 80 each have different angles α and β from the center line connecting the rotation center axis SPC of the primary shaft SP and the rotation center axis SSC of the secondary shaft SS. It is shown.

  As long as the primary side rotating member 70 and the secondary side rotating member 80 exert a circumferential positioning action on the primary shaft SP and the secondary shaft SS, which are the respective rotating shafts of the movable sheaves 38 and 42, as shown in FIG. A plurality of each may be provided, but from the viewpoint of cost performance, the primary-side rotating member 70 and the secondary-side rotating member 80 correspond to the bulging and bending directions of the primary shaft SP and the secondary shaft SS that are the respective rotating shafts. It is preferable that they are provided at different positions.

  In this way, the movable sheave external teeth in the bulging and bending directions of the primary shaft SP and the secondary shaft SS, which are rotation axes corresponding to the direction of the force applied from the belt B to the movable sheaves 38 and 42 and the fixed sheaves 37 and 41, respectively. The movable sheaves 38 and 42 and the fixed sheaves 37 and 41 are caused by the reaction force of the primary side rotating member 70 and the secondary side rotating member 80 formed with the external teeth 70G and 80G simultaneously meshing with the 38G and 42G and the fixed sheave outer teeth 37G and 41G. This is because the bending deformation of the first pulley 35 and the secondary pulley 36, which are variable pulleys, and the torque transmission efficiency by the belt B can be improved.

Then, the suitable arrangement position of the primary side rotation member 70 and the secondary side rotation member 80 is further demonstrated with reference also to FIG. Generally, the maximum bulge bending of the primary shaft SP and the secondary shaft SS (indicated by a thick solid line on the left side of FIGS. 4A to 4C) is indicated by an arrow in FIG. As shown, the angles α = α ₁ and β = β ₁ are generated. On the other hand, when the speed change ratio is at the maximum speed, as shown by the arrows in FIG. 4B, they occur in the directions of the aforementioned angles α = α ₂ and β = β ₂ . Here, an _{α 1 <α 2 = β 2} <β 1.

Therefore, when both the primary pulley 35 and the secondary pulley 36, which are variable pulleys, and the belt B are intended to improve durability by reducing the stress at the time of the maximum reduction of the gear ratio, the primary side rotation The position at which the member 70 and the secondary side rotation member 80 are made to correspond to the maximum bulge and bending direction of the primary pulley 35 and the secondary pulley 36 when the speed ratio is the most reduced, that is, the angle α = α shown in FIG. _It is sufficient to provide at least one each at a position corresponding to the direction of ₁ and β = β ₁ .

On the other hand, when it is desired to obtain the most effective fuel consumption reduction effect by improving the torque transmission efficiency by the belt B in the maximum speed increase region of the gear ratio, which is the most frequently used gear ratio region during travel of the vehicle, the primary side The position at which the rotary member 70 and the secondary side rotary member 80 are made to correspond to the maximum bulge and bending direction of the primary pulley 35 and the secondary pulley 36 when the gear ratio is at the maximum speed, that is, the angle α shown in FIG. = alpha ₂ ° and beta = beta may be provided at least one on position corresponding to the ₂ directions.

As shown in FIG. 4C, the position where the primary-side rotating member 70 is made to correspond to the maximum bulge and bending direction of the primary shaft SP which is the primary-side rotating shaft when the speed ratio is the highest speed, that is, the angle α = The position corresponding to the direction of α ₂ , and the position corresponding to the maximum bulging and bending direction of the secondary shaft SS that is the secondary side rotation shaft when the speed change ratio of the secondary side rotation member 80 is the maximum deceleration, that is, the angle β = At least one may be provided at a position corresponding to the direction of β ₁ .

  In this way, the primary pulley 35 is greatly deformed when the gear ratio is at the highest speed and the secondary pulley 36 is greatly deformed at the time of the slowest speed reduction. This is because the durability of the variable pulley and the torque transmission efficiency by the belt can be improved correspondingly over a wide range of gear ratios, because the secondary side rotation member 80 is restrained by the reaction force.

[Second Embodiment]
Hereinafter, a belt-type continuously variable transmission according to a second embodiment of the present invention will be described with reference to FIG. The same elements as those described in relation to the first embodiment described above are denoted by the same reference numerals, and redundant description is omitted.

  The belt type continuously variable transmission partially shown in FIG. 5 is characterized in that the secondary side rotation member 80 used in the first embodiment is configured as a power transmission gear that transmits power to the output shaft. Thus, when the secondary side rotation member 80 is a power transmission gear that transmits power to the output shaft, the shaft 48 connected to the secondary shaft SS shown in FIG. , And the drive gear 49 may be omitted. Instead, the secondary rotating member 80 is coupled to transmit power to the intermediate shaft 50 as an output shaft from which the counter driven gear 53 is omitted. Thus, the power transmitted from the primary pulley 35 via the belt B to the secondary pulley 36 is transferred to the shaft 50 supported by the bearings 51 and 52 via the secondary rotating member 80 without passing through the secondary shaft SS. Then, the final drive gear 54 is driven.

  According to the second embodiment, since the torsion does not occur in the secondary shaft SS that is the rotation shaft of the secondary pulley 36, the stress generated by the movable sheave 42 and the fixed sheave 41 can be reduced, and the structure is simple. Can be achieved. Further, since the shaft 48, the bearings 46 and 47 that support the shaft 48, and the drive gear 49 can be omitted, the entire transaxle 3 (belt type continuously variable transmission) can be reduced in size and cost.

  In addition, although illustration description is abbreviate | omitted, you may comprise not only the above-mentioned secondary side rotation member 80 but the primary side rotation member 70 as a power transmission gear which transmits the motive power from an input shaft.

[Third Embodiment]
Next, a belt type continuously variable transmission according to a third embodiment of the present invention will be described with reference to FIG. This third embodiment is mainly different from the first and second embodiments described above in that the configuration of the circumferential positioning means in the secondary variable pulley is rotatably supported by a fixed member, and is outside the movable sheave. The movable sheave driven gear that meshes with the movable sheave outer teeth and the secondary-side rotating shaft are fixedly installed instead of the secondary-side rotating member 80 that is a rotating member formed with external teeth that mesh with the teeth and the fixed sheave outer teeth simultaneously. It is a point using a planetary gear mechanism including a sun gear to which a fixed sheave driving gear and a movable sheave driven gear are connected, a ring gear that is driven to the fixed sheave driving gear, and a pinion carrier that is connected to an output shaft, and other configurations Are the same, the same elements as those described in relation to the first and second embodiments described above are denoted by the same reference numerals, and the overlapping description will be omitted. Abbreviated.

  In FIG. 6, reference numeral 83 denotes a movable sheave driven gear that meshes with the movable sheave outer teeth 42 </ b> G, and is connected to a sun gear 85 </ b> S of a planetary gear mechanism 85 described later by a connecting shaft 87. The movable sheave driven gear 83 only needs to have a length that meshes with the movable sheave outer teeth 42 </ b> G in the movable range of the movable sheave 42. On the other hand, 84 is a fixed sheave drive gear fixed to the secondary shaft SS which is the secondary side rotation shaft, and meshes with a fixed sheave driven gear 86 connected to the ring gear 85R of the planetary gear mechanism 85. A single pinion carrier 85C that rotatably supports a single pinion that meshes with the sun gear 85S and the ring gear 85R of the planetary gear mechanism 85 is connected to a shaft 50 as an output shaft. The shaft 50 corresponds to the intermediate shaft 50 supported by the bearings 51 and 52 in the previous embodiment shown in FIG. 1, and a final drive gear 54 is fixed.

  Thus, when the movable sheave 42 moves in the axial direction, the movable sheave outer teeth 42G move along the movable sheave driven gear 83, so that the secondary shaft SS and the movable sheave 42 move smoothly relative to each other in the axial direction. Is possible.

  By the way, in this embodiment, the movable sheave driven gear 83 is connected to the sun gear 85S of the planetary gear mechanism 85, and the fixed sheave drive gear 84 fixed to the secondary shaft SS is connected to the ring gear 85R of the planetary gear mechanism 85. The fixed sheave driven gear 86 is engaged with the sun gear 5S and the ring gear 85R so that the pinion gear acts as an idle gear, and the movable sheave driven gear 83 and the fixed sheave driving gear 84 rotate in synchronization. As a result, the movable sheave 42 and the secondary shaft SS, and hence the fixed sheave 41, cannot be moved relative to each other in the circumferential direction.

  In the above description, the example in which the fixed sheave drive gear 84 is fixed to the secondary shaft SS has been described. However, the fixed sheave drive gear 84 may be integrally formed on the back surface of the fixed sheave 41. The diameter of the fixed sheave drive gear 84 is preferably set larger than the diameter of the movable sheave driven gear 83. In this way, the dead space in the vicinity of the secondary pulley 36 can be used effectively, and the transaxle 3 (belt type continuously variable transmission) as a whole can be reduced in size and cost.

  Further, the fixed sheave drive gear 84 and the fixed sheave driven gear 86 may be constituted by spur gears, but are preferably constituted by helical gears in consideration of the rotational directions of both. For example, in FIG. 6, when the secondary shaft SS and the fixed sheave drive gear 84 rotate clockwise as viewed from the right side, the fixed sheave drive gear 84 is a right-handed helical gear. In this way, along with the transmission of power from the fixed sheave drive gear 84 to the fixed sheave driven gear 86, the fixed sheave drive gear 84, and then the secondary shaft SS on which it is fixed, is moved to the left in FIG. Thrust is generated, which acts as a force for pressing the fixed sheave 41 toward the movable sheave 42 side. Thus, the force for clamping the belt B is increased and the lateral deflection of the belt B is reduced, so that the durability of the belt is improved. Note that the axial movement of the secondary shaft SS due to the thrust described above is restricted by a thrust washer 65 as an axial movement restricting part fixed to the transaxle rear cover 6.

Further, in the present embodiment, the transmission ratio between the power passing through the fixed sheave 41 and the power passing through the movable sheave 42 is set by appropriately changing the diameters of the sun gear 85S and the ring gear 85R of the planetary gear mechanism 85. Can be changed. More specifically, now, the diameter of the sun gear 85S is Ns, the diameter of the ring gear 85R is Nr, and the torque as power transmitted via the fixed sheave 41 is transmitted via TQs and the movable sheave 42. When the torque as power is TQm, the following equation (1) is established.
(1) TQm = TQs × Ns / Nr

  Therefore, the transmission ratio can be changed by changing and setting the diameter Ns of the sun gear 85S and the diameter Nr of the ring gear 85R.

Furthermore, in the present embodiment, it is possible to suppress a decrease in transmission torque capacity due to slippage between the variable pulley and the belt B. That is, the friction coefficient between the fixed sheave 41 and the belt B is μs, the friction coefficient between the movable sheave 42 and the belt B is μm, and the gear ratio between the fixed sheave driving gear 84 and the fixed sheave driven gear 86 is ks. When the transmission ratio between the sheave outer teeth 42G and the movable sheave driven gear 83 is km, and the ratio (Ns / Nr) between the diameter Ns of the sun gear 85S and the diameter Nr of the ring gear 85R is ρ, the following expression (2) is established. .
(2) (km × μm) / (ks × μs) = ρ

  Here, the transmission torque capacity from each of the fixed sheave 41 and the movable sheave 42 is proportional to the product of the pressing force to the belt B and the friction coefficient. That is, when the pressing force to the belt B is now P, the transmission torque capacity from the fixed sheave 41 is P × μs, and the transmission torque capacity from the movable sheave 42 is P × μm. Therefore, if the friction coefficient of the fixed sheave 41 and the friction coefficient of the movable sheave 42 are different, in the example in which power is transmitted only through the secondary shaft SS as in the prior art, torque that can be transmitted by the sheave having the smaller friction coefficient. Is the total transmittable torque (for example, the total transmittable torque when μs> μm is 2 μm × P). On the other hand, in the present embodiment, the total transmittable torque is (μm + μs) × P larger than 2 μm × P, and a decrease in the transmission torque capacity can be suppressed.

[Fourth Embodiment]
Next, a belt type continuously variable transmission according to a fourth embodiment of the present invention will be described with reference to FIG. This fourth embodiment is mainly different from the above-described third embodiment in that the movable sheave driven gear is connected to the double pinion carrier instead of connecting the movable sheave driven gear to the sun gear. The gear mechanism is used, and its sun gear is connected to a differential gear mechanism that is arranged coaxially with the movable sheave driven gear, and the other configurations are the same. The same elements as those described in connection with the embodiment are denoted by the same reference numerals, and redundant description is omitted. In the fourth embodiment, since a planetary gear type is used as the differential gear mechanism, the second gear element in the differential gear mechanism is referred to as the second gear mechanism in the preceding planetary gear mechanism. It will be distinguished from gear elements.

  In FIG. 7, reference numeral 100 denotes a planetary gear mechanism. A movable sheave driven gear 83 that meshes with the movable sheave outer teeth 42 </ b> G is connected to a double pinion carrier 100 </ b> C of the planetary gear mechanism 100 by a hollow connecting shaft 102. On the other hand, the fixed sheave drive gear 84 fixed to the secondary shaft SS that is the secondary rotation shaft is fixed to the fixed sheave driven gear 86 that is connected to the ring gear 100R of the planetary gear mechanism 100, as in the third embodiment. Is engaged. A sun gear 100S of the planetary gear mechanism 100 is coupled to a second ring gear 110R of a differential gear mechanism 110 described later disposed coaxially with the movable sheave driven gear 83. In the differential gear mechanism 110, the second sun gear 110S is connected to the drive shaft 62L of the left wheel FW disposed inside the hollow connecting shaft 102, and the second double pinion carrier 110C is driven to the drive shaft 62R of the right wheel FW. Respectively.

Also in the fourth embodiment, it is possible to obtain the same circumferential positioning function, power transmission ratio changing function, and transmission torque capacity decrease suppressing function as those in the third embodiment. That is, the friction coefficient between the fixed sheave 41 and the belt B is μs, the friction coefficient between the movable sheave 42 and the belt B is μm, and the gear ratio between the fixed sheave driving gear 84 and the fixed sheave driven gear 86 is ks. When the transmission ratio between the sheave outer teeth 42G and the movable sheave driven gear 83 is km, and the ratio (Ns / Nr) between the diameter Ns of the sun gear 100S and the diameter Nr of the ring gear 100R is ρ, the following expression (3) is established. .
(3) μm / μs = (1−ρ) × ks / km

  In addition to the above function, the rotation direction of the sun gear 100S and the rotation direction of the second ring gear 110R are matched to form the outer periphery of the differential case 55 used in the conventional device or the first to third embodiments, and the final The ring gear 58 meshing with the drive gear 54 can be omitted. As a result, it is possible to reduce the distance between the secondary shaft SS and the left and right drive shafts 62L, 62R, and further reduce the size and cost of the entire transaxle 3 (belt type continuously variable transmission). It becomes.

1 is a schematic configuration diagram showing a part of a vehicle to which a first embodiment of a continuously variable transmission according to the present invention is applied. It is a principal part expanded sectional view which shows a part of 1st Embodiment of the continuously variable transmission by this invention. It is a partial schematic side view for demonstrating arrangement | positioning of the rotation member in 1st Embodiment of the continuously variable transmission by this invention. It is the schematic front view and schematic side view for demonstrating suitable arrangement | positioning of the rotation member in 1st Embodiment of the continuously variable transmission by this invention, (A) is the largest swelling of each pulley at the time of the gear ratio being the most deceleration. The position corresponding to the bending direction, (B) is the position corresponding to the maximum bulging and bending direction of each primary pulley 35 and secondary pulley 36 when the gear ratio is at the maximum speed, and (C) is the maximum increasing for the primary pulley. At the time of speed, the secondary pulley indicates a position corresponding to the maximum bulge and bending direction at the time of slowdown. This is the fourth embodiment. It is a schematic front view which shows a part of 2nd Embodiment of the continuously variable transmission by this invention. It is a schematic block diagram which shows a part of vehicle to which 3rd Embodiment of the continuously variable transmission which concerns on this invention was applied. It is a schematic block diagram which shows a part of vehicle to which 4th Embodiment of the continuously variable transmission which concerns on this invention was applied.

Explanation of symbols

9 Belt type continuously variable transmission mechanism 35 Primary pulley 36 Secondary pulley 37 Primary side fixed sheave 37G Primary side fixed sheave external teeth 38 Primary side movable sheave 38G Primary side movable sheave external teeth 41 Secondary side fixed sheave 41G Secondary side fixed sheave external teeth 42 Secondary side movable sheave 42G Secondary side movable sheave outer teeth
70 Primary side rotating member 80 Secondary side rotating member SP Primary shaft SS Secondary shaft

Claims (9)

A belt-type continuously variable transmission comprising a variable pulley comprising a fixed sheave that cannot move axially and circumferentially on a rotating shaft and a movable sheave that can move axially,
A belt type continuously variable transmission characterized in that circumferential positioning means for the movable sheave with respect to the rotating shaft is provided on an outer peripheral portion of the movable sheave.   The circumferential positioning means is rotatably supported by a movable sheave external tooth formed on the outer peripheral portion of the movable sheave, a fixed sheave external tooth formed on the outer peripheral portion of the fixed sheave, and a fixed member, The belt-type continuously variable transmission according to claim 1, further comprising a movable sheave external tooth and a rotating member formed with external teeth that simultaneously mesh with the fixed sheave external tooth.   The belt-type continuously variable transmission according to claim 2, wherein the rotating member is provided at a position corresponding to a bulging and bending direction of the rotating shaft.   4. The belt-type continuously variable transmission according to claim 3, wherein at least one of the rotating members is provided at a position corresponding to a bulging and bending direction of the rotating shaft when the speed ratio is at a minimum speed.   4. The belt-type continuously variable transmission according to claim 3, wherein at least one of the rotating members is provided at a position corresponding to a bulging and bending direction of the rotating shaft when the speed ratio is at the maximum speed. .   The rotating member is at least at a position corresponding to the bulging and bending direction of the primary-side rotating shaft when the gear ratio is at the maximum speed, and at a position corresponding to the bulging and bending direction of the secondary-side rotating shaft when the speed ratio is the most decelerated. 4. The belt type continuously variable transmission according to claim 3, wherein the belt type continuously variable transmission is provided one by one.   The belt-type continuously variable transmission according to any one of claims 2 to 6, wherein the rotating member is configured as a power transmission gear that transmits power from an input shaft to an output shaft.   The circumferential positioning means in the secondary-side variable pulley is fixed to a movable sheave driven gear that meshes with the secondary-side movable sheave outer teeth formed on the outer periphery of the secondary-side movable sheave, and a secondary-side fixed sheave or rotating shaft. A fixed sheave drive gear, a sun gear to which the movable sheave driven gear is connected, a ring gear driven by the fixed sheave drive gear, and a planetary gear mechanism including a pinion carrier connected to an output shaft. The belt-type continuously variable transmission according to claim 1. The circumferential positioning means in the secondary variable pulley is fixed to the movable sheave driven gear that meshes with the secondary movable sheave outer teeth formed on the outer periphery of the secondary movable sheave, and the secondary fixed sheave or rotating shaft. A fixed sheave drive gear, a double pinion carrier to which the movable sheave driven gear is connected, a planetary gear mechanism including a ring gear and a sun gear driven by the fixed sheave drive gear, and the sun gear is connected. The belt-type continuously variable transmission according to claim 1, further comprising a differential gear mechanism disposed coaxially with the movable sheave driven gear.

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