JPH0545298U - Gearbox - Google Patents

Abstract

(57) [Summary] (Correction) [Purpose] To provide a transmission that improves the bearing life, reduces the number of parts, and obtains the function of adjusting the clutch coupling force. [Structure] Internal gear 61 and pinion carrier 7
2 and 5 of the sun gear 67 are the input shaft 2
A planetary gear mechanism 59, which is on the first side and the output shaft 47 side and can be braked by other rotating members, a moving member 87 having a clutch portion 89 and a piston portion 93, a clutch 91, and a cylinder provided in the casing 11. An actuator 101 that includes a portion 99 and the piston portion 93 and receives a pressure supply to fasten the clutch 91; a stopper 83 that receives the thrust force of the actuator 101 applied to the other rotating member on the casing 11; and a moving member 87. Casing 1
The cam 103 is provided between the cam 103 and 1 to move the moving member 87 in the axial direction by receiving a torque, and the one-way clutch 57 that allows rotation during gear shifting.

Description

[Detailed description of the device]

[0001]

[Industrial applications]

 This invention relates to a transmission used in a vehicle or the like.

[0002]

[Prior Art]

 Japanese Unexamined Patent Publication No. 62-215150 discloses a transmission using a planetary gear mechanism. This is because one of the rotating members of the planetary gear mechanism is connected to the casing side by the first cone clutch to brake the rotation, or is connected to the other rotating member by the second cone clutch to change the speed respectively. Alternatively, the rotational force is transmitted at a constant speed.

A moving member is connected to the braking-side rotating member so as to be movable in the axial direction, a first cone clutch is provided between the moving member and the casing, and a second cone clutch is connected to the moving member. It is provided between the other rotating members. The first cone clutch is fastened by a spring arranged between the moving member and the braking side rotating member, and the second cone clutch presses the moving member via the thrust bearing to release the first cone clutch. It is fastened by the thrust force of the actuator.

[0004]

[Problems to be solved by the device]

 Because of this structure, the thrust bearing force of the actuator and spring is applied to the bearing that supports the rotating member on the braking side and other rotating members, which reduces bearing life. Also, in order to prevent the rotation of the piston of the actuator, the piston and the moving member are separated and the thrust bearing is arranged between them, so there are many parts. Further, this configuration does not have a thrust force adjusting function such as, for example, an assist action of the thrust force or a leveling action of the thrust force with respect to torque fluctuation.

In view of this, the present invention is a transmission that connects a rotating member of a planetary gear mechanism to a casing side via an actuator-operated clutch to perform a speed change, and the life of a bearing that supports another rotating member is reduced. Therefore, it is an object of the present invention to provide a transmission having a small number of parts and having a function of adjusting the clutch fastening force.

[0006]

[Means for Solving the Problems]

 The transmission of the present invention includes a planetary gear mechanism in which two rotating members of an internal gear, a pinion carrier, and a sun gear are an input shaft side and an output shaft, respectively, and other rotating members can brake, and a casing for housing the planetary gear mechanism. A moving member having a clutch portion and a piston portion, a clutch provided between the clutch portion and the other rotating member, a cylinder portion provided in the casing, and the piston portion, and receiving pressure supply. The actuator that engages the clutch, the stopper that receives the thrust force of the actuator applied to the other rotating member on the casing, the torque that is provided between the moving member and the casing, and moves the moving member in the axial direction. And a one-way clutch that is placed between the input shaft side and the output shaft side and allows rotation during shifting. The features.

[0007]

[Action]

 When the moving member is moved by the thrust force of the actuator and the clutch is fastened, the braking side rotating member is brought into sliding contact with the stopper, and the braking side rotating member is connected to the stopper via the clutch, the moving member and the cam. The sliding friction causes rotational braking on the casing, and rotation from the input shaft is changed by the planetary gear mechanism to rotate the output shaft. In this way, a large braking force is obtained by adding the frictional force with the stopper to the engagement force of the clutch. The one-way clutch is oriented so as to allow rotation at this time. Further, when the clutch is released, the contact with the stopper is also released, and the rotational force of the input shaft is transmitted to the output shaft at a constant speed or cut off according to the rotational force transmission direction of the one-way clutch.

The thrust force of the actuator or the like is input to the casing from the clutch and the braking side rotation member via the stopper, and is canceled by the anti-thrust force input to the casing from the cylinder portion of the actuator. In this way, the bearing that supports the rotating member is released from thrust force and extends its life.

Further, unlike the conventional example, since the piston of the actuator and the moving member are integrated and the thrust bearing is unnecessary, the number of parts is reduced. In addition, torque is applied from the clutch to the cam via the moving member during shifting. At this time, if the cam surface is inclined so that the cam thrust force acts in the clutch engaging direction, the clutch connecting force and the stopper frictional force are amplified and the output of the actuator can be reduced. If the cam surface is arranged so that the cam thrust force acts in the clutch releasing direction, the clutch coupling force and the stopper friction force are alleviated even if the torque increases or decreases. Therefore, for example, at the time of increasing the speed, even if the input torque is shockedly increased, the output shaft side is decelerated to prevent the driven machine from being damaged.

[0010]

【Example】

 The first embodiment will be described with reference to FIGS. 1 and 2. This embodiment is used in an accessory-side belt wheel device (driven pulley) of a belt transmission mechanism that transmits a driving force of an engine to an accessory (alternator, compressor, etc.) in a vehicle. Hereinafter, the left and right directions are the left and right directions in FIG. 1 and FIG. 2, and members and the like not attached with symbols are not shown.

As shown in FIG. 1, the driven pulley 1 includes a pulley 3, an electromagnetic clutch 5 and a transmission 7 of this embodiment.

The pulley 3 has a U-shaped cross section, and its inner circumference is supported by the outer circumference of the left end boss portion 13 of the casing 11 via bearings 9, 9. The pulley 3 is connected to a belt pulley device (drive pulley) on the crankshaft side of the engine via a belt mounted on the outer periphery of the pulley 3 and is rotationally driven by the driving force of the engine. A spacer 15 is arranged between the bearings 9 1, 9 and retaining rings 17, 19 are attached to the pulley 3 and the casing 11 on the left side of the left bearing 9. The casing 11 is fixed to the casing of the auxiliary machine.

An input shaft 21 is supported inside the boss portion 13 via bearings 23, 23. A spacer 25 is arranged between the bearings 23. A hub 29 having a flange 27 is spline-connected to the left end of the input shaft 21 and is fixed by a bolt 33 via a washer 31. A seal 35 is arranged between the hub 29 and the boss portion 13 on the left side of the left bearing 23 to prevent oil leakage from the casing 11.

A ring-shaped armature 37 is coaxially arranged outside the flange 27, and these are connected by leaf springs 41 fixed to the armatures 37 by rivets 39, respectively. A ring-shaped electromagnet 43 is arranged in the hollow portion of the pulley 3 and is fixed to the casing 11. Further, a non-magnetic ring 45 is arranged and welded to the pulley 3 so as to divide the pulley 3 in order to prevent the magnetic flux of the electromagnet 43 from being short-circuited and to guide it to the armature 37. Thus, the electromagnetic clutch 5 is configured.

When a coil current is applied to the electromagnet 43, as shown in the lower half of FIG. 1, the leaf spring 41 is bent by the attractive force, the armature 37 is attracted to the pulley 3, and the electromagnetic clutch 5 is connected. The rotational driving force of the engine is transmitted to the input shaft 21 via the electromagnetic clutch 5. The thrust force that attracts the armature 37 and pushes the pulley 3 to the right is input to the casing 11 via the retaining ring 17, the left bearing 9, the spacer 15, and the right bearing 9. When the coil current is cut off, the armature 37 returns to the left by the urging force of the leaf spring 41, the electromagnetic clutch 5 is released, and the input shaft 21 is separated from the engine.

An output shaft 47 is coaxially arranged on the right side of the input shaft 21, its left end is supported by a hollow portion of the input shaft 21 via a bearing 49, and its right end portion is supported by a casing 51 via a bearing 51. Is supported by. A washer 53 is arranged between the input shaft 21 and the output shaft 47. The output shaft 47 is connected to the input shaft of the auxiliary machine by the coupling 55. A one-way clutch 57 is arranged between the input shaft 21 and the output shaft 47.

A planetary gear mechanism 59 is arranged to the right of the electromagnetic clutch 5. The planetary gear mechanism 59 has an internal gear 61 (an input side rotating member) meshed in order, outer and inner pinion gears 63 and 65, and a sun gear 67 (an output side rotating member). The null gear 61 is formed on the right end portion of the input shaft 21, and the sun gear 67 is formed on the output shaft 47. The pinion gears 63 and 65 are supported by the pinion shafts 71 and 73 via the bearing ring 69, and the pinion shafts 71 and 73 are mounted on the pinion carrier 75 (another rotating member or braking side rotating member) arranged on the right side. It is supported.

Washers 77, 77 are arranged on both sides of the pinion gears 63, 65, and a retaining ring 79 for preventing the pinion gears 63, 65 from coming off is attached to the pinion shafts 71, 73 via the left washer 77. There is. The inner circumference of the pinion carrier 75 is rotatably fitted to the outer circumference of the boss portion 81 of the casing 11. A stopper 83 is non-rotatably connected to the left side of the pinion carrier 75 and a retaining ring 85 is attached to the left side of the boss portion 81.

A moving member 87 is arranged on the right side of the planetary gear mechanism 59, and the moving member 87 is provided with a clutch portion 89 extended to the outer peripheral side of the pinion carrier 75. A cone clutch 91 (clutch) that is connected to the carrier 75 when the moving member 87 moves to the left is formed. Further, the moving member 87 is provided with a piston portion 93, which is fluid-tightly engaged with the cylinder portion 99 of the casing 11 via seal rings 95, 97 so as to be movable in the axial direction. Actuator).

As shown in FIG. 2, a cam 103 is formed between the moving member 87 and the casing 11, and also serves as a detent for the moving member 87. Further, a return spring 107 for returning the moving member 87 to the right is arranged between the retaining ring 105 mounted on the casing 11 and the moving member 87, and a stopper portion 109 of the return spring 107 is formed on the casing 11. ing.

A hydraulic pressure is applied to the hydraulic chamber 111 of the hydraulic actuator 101 from an oil pump through a control valve device, and the moving member 87 is moved while bending the return spring 107, as shown in the upper half of FIG. Thus, the cone clutch 91 is fastened. When the cone clutch 91 is engaged, the pinion carrier 75 receives the thrust force of the actuator 101 and is pressed against the stopper 83. The pinion carrier 75 and the stopper 83 form a friction clutch 115. In this way, the pinion carrier 75 is connected to the casing 11 via the cone clutch 91, the moving member 87, the cam 103, and the friction clutch 115. Next, when the hydraulic pressure is released from the hydraulic chamber 111 by the control valve device, the moving member 87 returns to the right by the urging force of the return spring 107, and as shown in the lower half of FIG. 1, the cone clutch 91 and the friction clutch 115 are moved. And are released.

When the cone clutch 91 and the friction clutch 115 are engaged, the pinion carrier 75 is connected to the casing 11 and rotationally braked, and the rotation of the engine input to the input shaft 21 (internal gear 61) is accelerated. It is transmitted to the output shaft 47 (sun gear 67) and drives the auxiliary equipment to rotate. The one-way clutch 57 is arranged in a direction that allows this rotation.

At this time, the torque of the pinion carrier 75 is input to the cam 103, and as shown by the arrow in FIG. 2, a leftward cam thrust force 117 is generated to increase the engagement force between the cone clutch 91 and the friction clutch 115. Due to the assisting action of the cam 103, a sufficient braking force for the pinion carrier 75 can be obtained only by giving a relatively weak hydraulic pressure to the hydraulic actuator 101. When the cone clutch 91 and the friction clutch 115 are released from each other, the rotation of the input shaft 21 is transmitted to the output shaft 47 at a constant speed via the one-way clutch 57.

Since the pinion carrier 75 is set to the braking side in this way, the pinion gears 63 and 65 rotate to transmit torque only when the pinion carrier 75 stops rotating. Therefore, only the couple acts on the pinion gears 63 and 65, and the radial force is not applied to the bearing 69, so that the life thereof is extended.

The thrust force of the hydraulic actuator 101 that engages the cone clutch 91 and the friction clutch 115 and the thrust force 117 of the cam 103 are input to the casing 11 from the stopper 83 and the anti-thrust force that is input to the casing 11 from the cylinder portion 99. Is offset by. In this way, the bearings 23 and 23 of the input shaft 21 (internal gear 61) and the bearings 49 and 51 of the output shaft 47 (sun gear 67) are released from the thrust force for operating the clutches 91 and 115, and the life is extended.

Further, unlike the conventional example, the piston portion 93 and the clutch portion 89 are integrally formed, and the thrust bearing arranged between them is unnecessary, so that the number of parts is reduced accordingly. .. Further, since the cone clutch 91 is used, the speed change device has a small diameter. Thus, the transmission device 7 is configured.

Next, a second embodiment will be described with reference to FIGS.

In the transmission 119 of this embodiment, the gradient of the cam between the moving member and the casing is opposite to that of the first embodiment. In FIGS. 3 and 4, members having the same functions as those in the first embodiment are designated by the same reference numerals. Hereinafter, differences from the first embodiment will be described. The left and right directions are the left and right directions in FIGS. 3 and 4.

As shown in FIGS. 3 and 4, a cam 121 is formed between the moving member 87 and the casing 11. When the cone clutch 91 and the friction clutch 115 are in the connected state, the cam 121 receives the torque of the moving member 87 and applies the right cam thrust force 123 to the moving member 87 as indicated by the arrow in FIG.

Therefore, when the torque becomes large, the engaging force of each clutch 91, 115 is alleviated, the slip of the pinion carrier 75 is allowed to that extent, and the speed increasing rate of the planetary gear mechanism 59 decreases, and when the torque becomes small, each clutch 91, 115. The fastening force is increased to increase the speedup rate. In this way, the fluctuation of the gear ratio due to the torque fluctuation is suppressed to a small level, and the rotation of the auxiliary machine is stabilized.

Therefore, when the input torque suddenly increases, the engagement forces of the clutches 91 and 115 are momentarily relaxed by the cam thrust 123, and the respective stick slips (rapid slips in the engaged state) and the noise thereof. Is prevented and the planetary gear mechanism 59 and the auxiliary machinery are protected from a large torque impact.

As described above, since the transmission 119 has the function of the torque limiter (rotational speed limiter), if the torque (T) exceeds a constant value ( _TL ) as shown in FIG. The graph 125 of (N) does not rise like the broken line graph 127, but the rise is suppressed like the solid line graph 129. In this way, the auxiliary machine can be used in a proper rotational speed range, and even if the hydraulic pressure cannot be released from the hydraulic actuator 101 due to the malfunction of the hydraulic system, for example, the excessive load of the auxiliary machine is not applied and the damage can be avoided. .

In this invention, the internal gear and the sun gear may be rotationally braked. Also, the clutch may be another type of clutch, such as a multiple disc clutch.

[0034]

[Effect of the device]

 The transmission of this invention is a transmission in which the braking-side rotating member of the planetary gear mechanism is connected to the casing side by an actuator-operated clutch for gear shifting, and the thrust force of the actuator is transmitted through the damping-side rotating member. A stopper for receiving is provided in the casing, a piston of the actuator and a clutch member are integrally formed on the moving member, and the moving member and the casing are connected by a cam. Therefore, the bearings supporting the other two rotary members on the input / output shaft side are released from the thrust force of the actuator, the life is lost, the number of parts is reduced, and the function of adjusting the clutch engaging force is obtained by the cam.

[Brief description of drawings]

FIG. 1 is a sectional view of a belt wheel device using a first embodiment.

FIG. 2 is a development view of a cam used in the first embodiment.

FIG. 3 is a cross section of a second embodiment.

FIG. 4 is a development view of a cam used in the second embodiment.

FIG. 5 is a graph showing characteristics of the second embodiment.

[Explanation of symbols]

 7,119 Transmission 11 Casing 21 Input shaft 23,23,49,51 Bearing 47 Output shaft 57 One-way clutch 59 Planetary gear mechanism 61 Internal gear 67 Sun gear 75 Pinion carrier 83 Stopper 87 Moving member 89 Clutch part 91 Cone clutch ( Clutch) 93 Piston part 99 Cylinder part 101 Hydraulic actuator (actuator) 103, 121 Cam

Claims (1)

[Scope of utility model registration request] 1. A planetary gear mechanism in which two rotating members of an internal gear, a pinion carrier, and a sun gear are on an input shaft side and an output shaft side, respectively, and other rotating members can be braked, and a casing for housing the planetary gear mechanism. A moving member having a clutch portion and a piston portion, a clutch provided between the clutch portion and the other rotating member, a cylinder portion provided in the casing, and the piston portion, and receiving pressure supply. An actuator for engaging the clutch, a stopper for receiving the thrust force of the actuator applied to the other rotating member on the casing, and a cam provided between the moving member and the casing for moving the moving member in the axial direction by receiving a torque. , A one-way clutch that is arranged between the input shaft side and the output shaft side and allows rotation during gear shifting. Speed equipment.