JPS63219954A - Friction type continuously variable transmission - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

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]

In general, this type of friction-type continuously variable transmission does not have the function of a clutch, so power from the friction-type continuously variable transmission can be switched on and off by separately connecting a clutch on the output side. ing.

[Problem that the invention seeks to solve]

However, in such a structure in which the clutch is connected separately, the device tends to become larger because the space required 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 problem is that the structure is complicated.

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 friction type continuously variable transmission.

[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). A multi-disc clutch (8) is provided between the output shaft (6) and a cylindrical clutch body (8) that is loosely fitted to the output shaft (6).
) The engagement groove (11a) provided on the inner circumferential surface of the output rotating body (11) is inserted outward into the engagement groove (13) for supporting the friction plate, which is formed so as to pass through the outer circumference of the output rotating body (11). The functions and effects are as follows.

[For production]

According to the above configuration, the tapered surface of the taper cone presses against the output rotating body, so that the rotational force of the taper cone transmitted from the drive rotating body is transmitted to the output rotating body,
The output rotating body rotates. When the output rotating body rotates, the engagement protrusion provided on its inner circumferential 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-disc 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 idle 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 rotating body is engaged with the engagement groove from the outside, the engagement amount of the engagement protrusion and the retention amount of the friction plate are determined relative to 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/notch by utilizing the narrow space located inside the output rotating body, it is possible to make the overall size smaller compared to the conventional method in which the clutch is provided separately. became.

Furthermore, since a part of the engagement groove for supporting the friction plate is used to engage the retaining convex part of the output rotating body with the crucanochipode, it is easy to manufacture and saves processing time. Became.

〔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) that is supported through the transmission case (M), and a plurality of taper cones are arranged around the carrier (2). (3), a drive gear (4) as a drive rotary body is fixedly arranged on the transmission upper side of the input shaft (1), and a driven gear (5) provided on the small diameter side of the taper cone (3). It is interlocked.

In addition, a first transmission member (7) is spline-fitted to the upper transmission end of the cylindrical output shaft (6) loosely fitted to the input shaft (1), and a double cylindrical member is spline-fitted to the lower end of the cylindrical output shaft (6). The clutch body (8) and the second transmission member (9) are loosely fitted. A hydraulic first multi-plate clutch (8) is disposed on the upper transmission side of the clutch body (8), and a second multi-disc clutch (B) is disposed on the lower transmission side of the clutch body (8).
), and a driven disk (11) serving as an output rotating body is fitted on the outside so as to be able to shift and transmit torque, and the outer circumferential portion of the driven disk (11) is in contact with the tapered surface (3a) of the taper cone (3). That's how it is.

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 tapered surface (3a) and the driven disk (11)
The contact position with the outer peripheral portion shifts, and the rotation ratio of the taper cone (3) and the driven disk (11) changes. In other words, the rotational power of the input shaft (1) is shifted to the driven disk (11).
It will be transmitted to In addition, a pressure regulating device (12) is provided on the large diameter side of the taper cone (3) to move the taper cone (3) to the small diameter side along the rotation axis.
The tapered surface (3a) is pressed against the outer peripheral surface of the driven disk to generate a strong frictional force.

The first multi-plate clutch (A) will be explained.

A large number of transmission fitting grooves (13) are provided on the transmission upper side of the outer cylinder (8a) of the clutch body (8) along the axis (P) direction.
is formed to penetrate inside and outside, and a retaining convex portion (11a) provided on the inner circumferential surface for guiding the driven disk (11).
) from the outside to about half the depth, while a plurality of drive plates (14) are fitted from the inside to about half the depth.

Further, a plurality of driven plates 1- (15) are fitted into the first transmission member (7) in an alternating manner with the drive plates (14).

Furthermore, a first hydraulic piston (16) is provided adjacent to the partition wall (8b) of the clutch body (8), and the partition wall (8b) and the first
A hydraulic chamber (S+) formed between the hydraulic piston (16)
) by drilling an oil passage (17) across the clutch body (8), output shaft (6), and input shaft (1), and supplying pressure oil from the outside to the hydraulic chamber (S). 1. The hydraulic piston (16) is moved to the upper side of the transmission.

When the first hydraulic piston (16) moves, the drive plate (14) and the driven plate (15) come into pressure contact, and the clutch body (8) and the first transmission member (7) are integrally connected, and the clutch body (8) First transmission member (7
), that is, the clutch is engaged.

Note that (18) in FIG. 1 is a seal that prevents oil leakage, and (19) is a spring that pushes back the first hydraulic piston (16) when the pressure is reduced. Further, a bearing (20) is provided between the free end portion of the clutch body (8) located on the transmission upper side and the first transmission member (7).
is interposed therebetween, and is sufficiently reinforced to resist the pressing force applied from the tapered surface (3a).

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 along the axis (P) direction on the transmission lower side of the outer cylinder (8a) of the clutch body (8), and the inner side thereof. At the same time, the drive plate (22) is fitted to the second transmission member (
9), the driven plates (23) are externally fitted in a state alternating 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
An oil passage (25) communicating with the hydraulic chamber (S2) formed between the By supplying pressure oil to the chamber (S2), the second hydraulic piston (24) is moved toward the lower side of the transmission. When the second hydraulic piston (24) moves, the drive plate (22) and the driven plate (23) come into pressure contact, the clutch body (8) and the second transmission member (9) are integrally connected, and 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 provided 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). (28) and the second transmission member (9) to the idle gear (3
0), and a large diameter transmission gear (2
9) and an output gear (31) provided on the output shaft (6) are engaged with each other. Therefore, when the first multi-disc clutch (^) is engaged, the rotational power of the output shaft (6) is reversed and significantly decelerated, and transferred to the transmission output shaft (27) and the second multi-disc clutch (B). ) is turned on, the rotational power of the second 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 (R) is engaged, forward power is obtained.

In this way, in the friction type continuously variable transmission to which the present invention is applied,
Despite having two anti-clutches (Δ”) and (B) internally, it is small in size, and has only one driven disc (1).
The groove for securing the convex portion (11a) of 1) and the transmission engagement groove (13) of the trouble plate (14) are shared, etc.
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 drawings]

The drawings show an embodiment of the friction type continuously variable transmission according to the present invention, with FIG. 1 being a longitudinal side view and FIG. 2 being an exploded perspective view of a multi-plate clutch. (1)...Human power axis, (3)...Taper cone, (3a)...Taber surface, (4)...
... Drive rotating body, (6) ... Output shaft, (7)
......Transmission member, (8)...Clutch body, (11)...Output rotating body, (11a)
......Engagement protrusion, (13)...Engagement groove, (8)...Multi-plate clutch 7chi.

Claims (1)

[Claims] The axis (P) of the drive rotor (4) connected to the input shaft (1)
) is provided with a taper cone (3) that rotates on its own axis in conjunction with the drive rotor (4), and an output rotor (
11) is provided to be shiftable in the direction of the axis (P), the friction type continuously variable transmission is provided such that the output rotating body (11)
) is arranged on the axis of the output shaft (6), and this output shaft (6)
A multi-disc clutch (A) is connected between the transmission member (7) provided for the
In addition, an engagement groove (13) for supporting the friction plate is provided, which is formed to extend through the outer periphery of the clutch body (8).
), the friction type continuously variable transmission is engaged from the outside with an engaging protrusion (11a) provided on the inner circumferential surface of the output rotating body (11).