JPH0527773B2 - - Google Patents

Description

[Detailed Description of the Invention] [Industrial Application Field] The present invention provides a tapered cone that rotates on its own axis in conjunction with the drive rotor around the axis of the drive rotor connected to the input shaft. The present invention relates to a friction type continuously variable transmission device in which an output rotating body that contacts the tapered surface of the tapered cone is provided so as to be shiftable in the axial direction.

[Conventional technology]

Generally, this type of friction type continuously variable transmission does not have the function of a clutch, so it is possible to connect a clutch separately on the output side to connect and disconnect the power from the friction type continuously variable transmission. It's getting old.

[Problem that the invention seeks to solve]

However, such a structure in which the clutches are connected separately tends to increase the size of the device because the space necessary for the connection must be secured separately.

For example, if the clutch is directly connected to the extension of the output shaft of the device, it will be bulky in the axial direction, and if it is installed parallel to the output shaft, it will not only be bulky in the radial direction but also require a new transmission shaft. The disadvantage is that the structure becomes complicated because of the need for this.

The present invention has focused on such a situation and aims to reduce the size of the entire friction type continuously variable transmission by rationally incorporating a clutch into the device.

[Means for solving problems]

The characteristic configuration of the present invention for achieving the above object is that an output shaft 6 is arranged on the axis of the output rotating body 11, and a transmission member 7 provided on the output shaft 6 and a
A multi-plate clutch A is provided between a cylindrical clutch body 8 which is loosely fitted into the clutch body 8, and an engagement groove 13 for supporting a friction plate formed in an inner and outer penetrating state of the outer circumferential portion of the clutch body 8 is provided with a multi-plate clutch A for supporting the output. The engaging protrusion 11a provided on the inner circumferential surface of the rotating body 11 is engaged from the outside, and its functions and effects are as follows.

[Effect]

According to the above configuration, the tapered surface of the taper cone presses against the output rotary body, so that the rotational force of the taper cone transmitted from the drive rotary body is transmitted to the output rotary body, and the output rotary body rotates. When the output rotating body rotates, the engagement protrusion provided on its inner peripheral surface and the engagement groove for supporting the friction plate are engaged, so that the cylindrical clutch body rotates for output. Rotates with the body. In this state, when the multi-plate clutch is operated to engage, the transmission member integrated with the output shaft and the clutch body are connected, and the rotational force of the clutch body is transmitted to the output shaft via the transmission member. Further, by operating the multi-disc clutch to disengage, the connection between the transmission member and the clutch body is released, the clutch body returns to its original free rotation state, and power transmission to the output shaft via the transmission member is cut off. In this case, since the engagement protrusion of the output rotor is engaged with the engagement groove from the outside, the engagement amount of the engagement protrusion and the engagement amount of the friction plate are determined by the depth of the groove. By setting it rationally, contact between the engagement convex portion and the friction plate can be avoided even when the output rotating body is shifted for a speed change operation.

〔Effect of the invention〕

As explained above, by incorporating a multi-plate clutch using the narrow space located inside the output rotating body, it has become possible to make the overall size smaller compared to the conventional method in which the clutch is provided separately. .

Moreover, since a part of the engagement groove for supporting the friction plate is used to engage the engagement protrusion of the output rotating body with the clutch body, it is easy to manufacture and saves processing time. Summer.

〔Example〕

Hereinafter, a friction type continuously variable transmission to which the present invention is applied will be explained based on the drawings.

As shown in FIG. 1, a carrier 2 is externally fitted via a bearing onto an input shaft 1 which is supported through a transmission case M, and a plurality of taper cones 3 are arranged around the carrier 2. A driving gear 4 as a driving rotary body is fixedly disposed on the transmission upper side of the shaft 1, and is engaged with a driven gear 5 provided on the small diameter side of the taper cone 3.

Further, a first transmission member 7 is spline-fitted to the upper transmission end of the cylindrical output shaft 6 which is loosely fitted to the input shaft 1, and a double cylindrical clutch body 8 and a second transmission member are fitted on the lower side thereof. A transmission member 9 is loosely fitted into each member. A hydraulic first multi-plate clutch A is installed on the upper side of the clutch body 8, and a second multi-plate clutch B is installed on the lower side of the clutch body 8, and a driven disk serving as an output rotating body is installed on the outside of the clutch body 8. 11 is fitted onto the outside so as to be able to shift and transmit torque, and the outer periphery thereof is in contact with the tapered surface 3a of the taper cone 3.

Therefore, the rotational power of the input shaft 1 is transferred to the drive gear 4.
The rotational force is transmitted to the tapered cone 3 via the driven gear 5, and then is transmitted as rotational force to the driven disk 11 due to frictional rotational resistance. In this case, when the driven disk 11 is shifted along its axial direction, the contact position between the tapered surface 3a and the outer peripheral portion of the driven disk 11 shifts, and the rotation ratio between the taper cone 3 and the driven disk 11 changes.
In other words, the rotational power of the input shaft 1 is transmitted to the driven disk 11 after being changed in speed. In addition, on the large diameter side of the taper cone 3, there is a pressure regulating device 1 for moving the taper cone 3 toward the small diameter side along the automatic axis.
2 is provided, and the tapered surface 3a is pressed against the outer peripheral surface of the driven disk to generate a strong frictional force.

The first multi-disc clutch A will be explained.

A large number of transmission fitting grooves 13 are formed on the transmission upper side of the outer cylinder 8a of the clutch body 8 along the axis P direction so as to penetrate inside and outside, and are provided on the inner circumferential surface for guiding the driven disk 11. Convex portion 1 for engagement
1a from the outside to about half the depth,
A plurality of drive plates 14 are fitted from the inside at about half the depth. Further, a plurality of driven plates 15 are fitted to the first transmission member 7 in a state where they alternate with the drive plates 14.

Further, a first hydraulic piston 16 is provided adjacent to the partition wall 8b of the clutch body 8, and an oil passage 17 communicating with the hydraulic chamber _S1 formed between the partition wall 8b and the first hydraulic piston 16 is connected to the clutch body 8, output shaft 6,
The first hydraulic piston 16 is moved to the upper side of the transmission by being bored across the input shaft 1 and supplying pressure oil from the outside to the hydraulic chamber _S1 . When the first hydraulic piston 16 moves, the drive plate 14
The driven plate 15 is brought into pressure contact, and the clutch body 8 and the first transmission member 7 are integrally connected.
The state is such that power can be transmitted from the clutch body 8 to the first transmission member 7, that is, the clutch is engaged. In addition, 18 in FIG. 1 is a seal that prevents oil leakage, and 19 is a spring that pushes back the first hydraulic piston 16 in a state where the pressure is reduced. A bearing 20 is interposed between the free end of the clutch body 8 located on the transmission upper side and the first transmission member 7, and is sufficiently reinforced to resist the pressure applied from the tapered surface 3a. is being done.

Next, the second multi-plate clutch B will be explained.

As shown in FIG. 2, a large number of transmission fitting grooves 21 are formed on the lower transmission side of the outer cylinder 8a of the clutch body 8 along the axis P direction, and a drive plate 22 is fitted inside the grooves 21. At the same time, driven plates 23 are fitted onto the second transmission member 9 so as to alternate with the drive plates 22. Further, a second hydraulic piston 24 is provided adjacent to the partition wall 8b of the clutch body 8, and the partition wall 8b and the second hydraulic piston 2
Oil passage 2 communicating with hydraulic chamber S ₂ formed between S 2 and S 4
5 is bored across the clutch body 8, the output shaft 6, and the input shaft 1, and by supplying pressure oil from the outside to the hydraulic chamber _S2 , the second hydraulic piston 24 is moved toward the lower side of the transmission. be. Second hydraulic piston 24
When the clutch body 8 moves, the drive plate 22 and the driven plate 23 come into pressure contact, and the clutch body 8
The clutch body 8 and the second transmission member 9 are integrally connected, and the clutch is in a state where power can be transmitted from the clutch body 8 to the second transmission member 9, that is, the clutch is engaged.

Note that 26 in FIG. 1 is a spring for pushing back the second hydraulic piston 24 in a state where the pressure is reduced.

A transmission output shaft 27 is arranged parallel to the output shaft 6, and a small diameter transmission gear 28 and a large diameter transmission gear 29 are provided on the shaft 27, and the small diameter transmission gear 28 and the second transmission member 9 are set to idle. Gears are interlocked via a gear 30, and a large diameter transmission gear 29
and the output gear 31 provided on the output shaft 6 are engaged with each other. Therefore, when the first multi-disc clutch A is engaged, the rotational power of the output shaft 6 is reversed and significantly decelerated to the transmission output shaft 27, and when the second multi-disc clutch B is engaged, the rotational power of the output shaft 6 is transferred to the transmission output shaft 27. The rotational power of the transmission member 9 is transmitted to the transmission output shaft 27 in a normal rotation state. That is, when the first multi-plate clutch A is engaged, reverse power is obtained, and when the second multi-disc clutch B is engaged, forward power is obtained.

In this way, the friction-type continuously variable transmission to which the present invention is applied is small in size despite having two multi-plate clutches A and B internally, and moreover, it engages the convex portion 11a of the driven disk 11. For example, the transmission groove 13 of the trouble plate 14 is shared with the groove for the trouble plate 14.
Appropriate consideration has also been given to the manufacturing aspect.

Incidentally, although reference numerals are written in the claims section for convenient comparison with the drawings, the present invention is not limited to the structure shown in the accompanying drawings.

[Brief explanation of the drawing]

The drawings show an embodiment of the friction type continuously variable transmission according to the present invention, with FIG. 1 being a longitudinal sectional side view and FIG. 2 being an exploded perspective view of a multi-plate clutch. 1...Input shaft, 3...Taper cone, 3a...
Tapered surface, 4... Drive rotating body, 6... Output shaft, 7
...Transmission member, 8...Clutch body, 11...
Output rotating body, 11a... Engagement convex portion, 13...
Engagement groove, A...Multi-plate clutch.

Claims (1)

[Claims] 1 Axial center P of the drive rotor 4 connected to the input shaft 1
A tapered cone 3 that rotates on its own axis in conjunction with the driving rotary body 4 is arranged around the output rotary body 1 that comes into contact with the tapered surface 3a of the taper cone 3.
1 is provided so as to be shiftable in the direction of the axis P, the output rotating body 1
An output shaft 6 is disposed on the axis of the output shaft 6, and a multi-plate clutch A is provided between a transmission member 7 provided on the output shaft 6 and a cylindrical clutch body 8 loosely fitted on the output shaft 6. An engagement groove 13 for supporting a friction plate is formed to penetrate inside and outside the outer circumference of the clutch body 8.
In the friction type continuously variable transmission device, an engaging convex portion 11a provided on the inner circumferential surface of the output rotating body 11 is engaged from the outside.