JPH0538443U - Belt type continuously variable transmission - Google Patents

Abstract

(57) [Abstract] [Purpose] The cam of the transmission pulley is such that the movable flange side and the fixed flange side are connected by a cam, and the spring that presses the movable flange toward the fixed flange side is placed across this cam. Therefore, it is an object of the present invention to provide a belt type continuously variable transmission that does not cause a change in gear ratio, has a quick gear change response, and has a long belt life. According to the belt type continuously variable transmission of the present invention, a fixed flange fixed to the rotary shaft side, a movable flange having a belt mounted between the fixed flange, the movable flange side and the rotary shaft side. To press the movable flange toward the fixed flange side by receiving torque, a spring that is mounted across this cam to urge the movable flange toward the fixed flange side, and a sliding resistance due to the urging force of the spring from the cam. It is characterized in that it is provided with a speed change pulley having a sliding member for blocking.

Description

[Detailed description of the device]

[0001]

[Industrial applications]

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

[0002]

[Prior Art]

 The "Auxiliary machine drive device" is described in the published Utility Model No. 1-65971. This is a belt-type continuously variable transmission that transmits the driving force of the vehicle engine to auxiliary equipment such as an oil pump.

There are various types of speed change pulleys depending on the speed change method of a belt type continuously variable transmission, and FIG. 6 shows an example thereof. The speed change pulley 201 includes a fixed flange 205 on the rotary shaft 203 side and a movable flange 209 that forms a mounting groove for the belt 207 between the fixed flange 205, and the hub 211 on the movable flange 209 side and the rotary shaft 203. The cam 215 is provided between the hub 213 and the hub 213, and the disc spring 217 is mounted between the hub 211 and the hub 213.

The disc spring 217 applies tension to the belt 207 by pressing the movable flange 209 to the fixed flange 205 side, and prevents slippage between the belt 207 and the flanges 205 and 209. Further, the cam 215 operates by receiving the transmission torque, and prevents the movable flange 209 from moving due to the belt 207 biting into the mounting groove having a wedge-shaped cross section to suppress the change of the gear ratio.

[0005]

[Problems to be solved by the device]

 However, since the disc spring 217 is arranged between the hub 211 and the hub 213 straddling the cam 215, the sliding resistance due to the urging force causes a loss in the torque for operating the cam 215, which causes the cam 215 to function. become worse.

Therefore, when a large torque is applied to the belt 207, the movable flange 209 moves to change the gear ratio, and at the time of gear shifting, the relative rotation of the movable flange 209 with respect to the rotating shaft 203 side and the axial movement thereof occur. This hinders the gear shifting response.

Further, since the relative rotation of the movable flange 209 is hindered, slippage easily occurs between the movable flange 209 and the belt 207, and the life of the belt 207 is shortened due to abrasion. In addition to this, since the set load is reduced due to the abrasion of the disc spring 217 at the sliding portions with the hubs 211 and 213, the belt 207 easily slips due to insufficient belt tension. Therefore, the set load of the disc spring 217 must be increased in advance in anticipation of such a decrease in the load, and as a result, the belt 207 is given an excessive load and its durability deteriorates.

Therefore, the present invention uses a speed change pulley having a cam connecting the movable flange and the rotary shaft side, and a spring arranged across the cam and pressing the movable flange toward the fixed flange. It is an object of the present invention to provide a belt-type continuously variable transmission that does not cause deterioration of the cam function or shift response due to sliding resistance of the.

[0009]

[Means for Solving the Problems]

 The belt type continuously variable transmission according to the present invention has a fixed flange fixed to the rotary shaft side, a movable flange having a belt mounted between the fixed flange, and the movable flange side and the rotary shaft side. The cam that receives the torque to press the movable flange toward the fixed flange side, the spring that is installed across this cam and urges the movable flange toward the fixed flange side, and the sliding resistance due to the spring urging force is cut off from the cam. It is characterized in that it is provided with a speed change pulley having a sliding member for sliding.

[0010]

[Action]

 A sliding member is arranged between the spring and one or both of the movable flange side and the rotating member side, which are its mounting members, to block the sliding resistance. Rotation and axial movement are not hindered, and gear change response and belt durability are improved. Further, since it is not necessary to increase the set load in consideration of wear of the spring, the durability of the belt is improved also in this aspect.

[0011]

【Example】

 The first embodiment will be described with reference to FIGS. This embodiment is used to drive an auxiliary machine of a vehicle. Hereinafter, the left and right directions are the left and right directions in FIGS. 1 to 3, and members and the like without reference numerals are not shown.

The input shaft 3 (rotary shaft) of the drive pulley 1 (engine-side speed change pulley) is supported by a casing 9 by bearings 5 and 7, and a lock nut 11 of a bearing 7 is screwed to the right end thereof. ing. A pulley is attached to the left end of the input shaft 3, and this pulley is connected to the accessory pulley via a V-belt. In this way, the input shaft 3 is rotationally driven by the driving force of the engine.

A fixed flange 13 is welded to the input shaft 3. Hollow cam members 15 and 17 are fitted to the outer periphery of the input shaft 3 on the right side thereof. The right cam member 17 (mounting member) is spline-connected to the input shaft 3 and has its right end brought into contact with the inner ring of the bearing 7. As shown in FIG. 2, cams 19 are formed at the facing portions of the cam members 15 and 17, respectively.

As described above, the left cam member 15 is capable of relative rotation and axial movement with respect to the input shaft 3 side while the cam 19 is engaged. A movable flange 21 is welded to the cam member 15. A belt 25 is mounted in a belt mounting groove 23 formed between the movable flange 21 and the fixed flange 13.

As shown in an enlarged manner in FIG. 3, a bearing 27 (sliding member) is arranged on the outer periphery of the right cam member 17. The outer ring 29 of the bearing 27 is in contact with a stopper portion 31 provided on the cam member 17. (In this case, as shown by the chain double-dashed line in FIG. 3, a bearing housing portion 33 may be provided in the stopper portion 31 to press-fit the outer ring 29. Further, the inner ring 35 of the bearing 27 and the outer periphery of the cam member 17 are The space provided between them allows them to rotate freely.

As shown in FIG. 1, six disc springs 39 (springs) are mounted between the retainer portion 37 of the left cam member 15 and the inner ring 35 of the bearing 27 to fix the movable flange 21. It is pressed against the flange 13 side.

The drive pulley 1 is thus constructed.

The drive pulley 1 is connected to a driven pulley (shift pulley on the driven side) via a belt 25 to form a belt type continuously variable transmission.

The driven pulley is connected to a vehicle accessory such as an oil pump or a supercharger via a belt transmission device including a pair of pulleys and a V-belt connecting the pulleys. The driven pulley is provided with a gear shift operation means using a hydraulic actuator. Like the drive pulley 1, the driven pulley has a cam that connects the movable flange side and the rotating shaft side, and a disc spring that presses the movable flange toward the fixed flange and the sliding resistance of the disc spring are blocked from the cam. And a sliding member are provided.

The disc spring 39 of the drive pulley 1 has a larger biasing force than the disc spring of the driven pulley. Therefore, when no other force is applied, the belt pitch diameter R of the drive pulley 1 becomes maximum (the state shown in FIG. 1) due to the biasing force of the disc spring 39, and the tension of the belt 25 causes the belt pitch diameter of the driven pulley to be increased. Is minimized and the gear ratio of the belt type continuously variable transmission is minimized.

Here, when the flange spacing of the driven pulley is narrowed by the hydraulic actuator, the belt pitch diameter of the driven pulley becomes large, the belt pitch diameter R of the drive pulley 1 becomes small, and the gear ratio increases. Thus, the shift operation is performed.

As described above, in the drive pulley 1, the sliding resistance of the disc spring 39 is blocked by the bearing 27 so that the relative rotation of the movable flange 21 is not hindered and the operation of the cam 19 is not hindered.

As described above, even if a large transmission force is applied to the belt 25 because the cam 19 operates normally, the movable flange 21 is pushed back to the left by the thrust force 41 of the cam 19 shown in FIG. It is possible to prevent an inconvenient change in the gear ratio due to the movable flange 21 moving to the right. Further, since the relative rotation of the movable flange 21 is not hindered, the axial movement of the movable flange 21 during the gear shifting operation is smoothed, the reduction of the gear shift response is prevented, and the belt 25 and the movable flange 21 are prevented. The slippage between them is reduced, the wear of the belt 25 is reduced, and the life is extended. Furthermore, since there is no sliding point on the disc spring 39 and the set load does not change due to wear, it is not necessary to increase the set load in anticipation of this change. Therefore, the durability of the belt 25 does not deteriorate due to the application of an excessive load.

Next, a second embodiment and a third embodiment will be described with reference to FIGS. 4 and 5, respectively. Hereinafter, the differences from the first embodiment will be described with reference to the members having the same functions as those in the first embodiment with the same reference numerals.

As shown in FIG. 4, in the second embodiment, the needle bear ring 45 is used as the sliding member of the speed change pulley 43. The needle bearing 45 is arranged between the stopper portion 49 of the right cam member 47 (mounting member) and the disc spring 39. The needle bearing 45 can receive a large load as compared with the one in which the axial load is applied to the radial bearing (bearing 27) as in the speed change pulley in the first embodiment, and the outer ring 29 is press-fitted. Is unnecessary.

As shown in FIG. 5, in the third embodiment, the sliding bearing 53 is used as the sliding member of the speed change pulley 51. The slide bearing 53 is made of washer-shaped porous sintered metal impregnated with oil, and is inexpensive as compared with the first and second embodiments.

In each of the second and third embodiments, the effect of blocking the sliding resistance of the disc spring 39 is the same as that of the first embodiment, and therefore the description is omitted.

In the present invention, the sliding member may be arranged on both sides of the spring or between the spring and the spring.

[0029]

[Effect of the device]

 This invention relates to a belt type continuously variable transmission using a speed change pulley in which a movable flange side and a fixed flange side are connected by a cam and a spring for pressing the movable flange toward the fixed flange side is arranged across the cam. By blocking the sliding resistance of the spring with a sliding member, the function of the cam and the relative rotation of the movable flange were not obstructed. Therefore, the cam operates normally to suppress fluctuations in the gear ratio, prevent deterioration of gear shift response, avoid belt slippage and excessive load, and prolong belt life.

[Brief description of drawings]

FIG. 1 is a sectional view of a transmission pulley used in a first embodiment.

FIG. 2 is a development view of a cam provided on the speed change pulley of FIG.

FIG. 3 is an enlarged view of a main part of FIG.

FIG. 4 is a sectional view showing a main part of a speed pulley used in a second embodiment.

FIG. 5 is a sectional view showing a main part of a speed change pulley used in a third embodiment.

FIG. 6 is a sectional view of a conventional example.

[Explanation of symbols]

 1,43,51 Speed change pulley 3 Input shaft (rotary shaft) 13 Fixed flange 17,47 Cam member (mounting member) 19 Cam 21 Movable flange 25 Belt 27 Bearing (sliding member) 39 Disc spring (spring) 45 Needle bearing (sliding) 53) Sliding bearing (sliding member)

Claims (1)

[Scope of utility model registration request] 1. A fixing flange fixed to the rotating shaft side,
A movable flange in which a belt is mounted between the fixed flange, a cam that connects the movable flange side and the rotary shaft side and presses the movable flange toward the fixed flange side, and a cam that is mounted across the cam. A belt-type continuously variable transmission including a speed change pulley having a spring for urging the movable flange toward the fixed flange and a sliding member for blocking sliding resistance caused by the urging force of the spring from the cam.