JPS5857555A - Automatic non-stage 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 The present invention relates to an automatic continuously variable transmission in a drive device having a prime mover and a driven shaft, and the role of the automatic IJJ transmission is to transfer torque supplied by the prime mover to the driven shaft. It is a stepless adjustment to the required torque on the shaft.

To this end, the automatic continuously variable transmission according to the invention includes a speed-dependent clutch and a speed-dependent clutch for controlling the transmission ratio between the input shaft and the output shaft in a stepless manner in cooperation with said clutch. section, the section having a central shaft carrying at least one radially extending shaft, the shaft having a conical diameter rotatable about its axis, and the conical body having a central shaft carrying at least one radially extending shaft; an outer circumferential surface having an axially concave curvature, the conical body being longitudinally movable on the radial shaft and adapted to be rotationally driven about the shaft; The shaped body is dependent on the desired torque-speed ratio via an axial pressure induced by the speed-dependent clutch and is capable of cooperating with a spring-loaded annular body rotatable about the axis of the central shaft. , wherein the spring-loaded annular body has a section having a conical inner circumferential surface having an axially convex curvature; ! It has an i-section mechanism.

This continuously variable speed action is realized by a cone movable on a radial shaft and with different diameters cooperating with the conical inner circumferential surface of the annular body and its different diameter sections. In addition, according to the features proposed according to the invention, an automatic continuously variable transmission is provided with a relatively short and compact construction, in which the cross-sectional dimensions are smaller than those normally required in such transmission gears. Therefore, the automatic transmission as a whole is relatively light and, because of its weight and size, can be integrated into a vehicle that is normally provided with a manual transmission.

Displacement of the cone is preferably effected by a axial thrust, speed-dependent control mechanism derived from a speed-dependent clutch. Such action is possible if the conical body is axially movable at its narrow end and the beveled end of an axially movable control ring rotationally mounted on the latch plate. This can be advantageously achieved by providing a radius 7 flange with a corresponding beveled circumferential edge that can cooperate with the edge. Here the clutch plate is actuated by a centrifugal weight consisting of a row 2 housed in a control cage which can be rotated in a circumferential path around the central shaft via an input shaft.

These features ensure that the conical body and/or the transmission cannot be activated unless a predetermined speed is exceeded, making the transmission particularly suitable for use in motor vehicles.

lc[, the input shaft of the automatic transmission has a beveled edge corresponding to the beveled edge of the control ring on the drum connected to the central shaft, and located at the same radial distance from the central shaft as the control ring. If an edge is provided, it is possible to connect directly to the output shaft. In this case, when the control ring is pushed out of the conical body to its substantially outer position, the control ring and the drum edge contact each other, so as to directly connect the input and output shafts without intervening control sections. This structure is preferable from the viewpoint of energy loss and wear and tear, since the parts that perform the transmission action perform their functions and remain stationary.

pins distributed on the circumferential edge of the drum for directly connecting an input shaft and an output shaft to rapidly increase the speed of the output shaft, for example to rapidly accelerate a car incorporating the automatic transmission; By providing
It is possible to obtain a so-called "kickdown" effect. The axis of the Srs bottle is parallel to the central shaft, such that the pin can be driven to move longitudinally within the drum, and the control ring resists centrifugal connecting forces. It is mounted so that it can be displaced in the axial direction.

The effect of making efficient use of the available volume space and obtaining an optimum velocity and force distribution could be achieved if the central shaft carried six radial shafts uniformly distributed in its circumferential direction. and in such a construction internal induced forces are absorbed in a simple and effective manner if the radial shaft extends between the central shaft and the drum connected to the shaft. I can do it.

The requirement that the direction of rotation of the output shaft can be reversed is essential in this type of device, and this condition can be achieved in a simple manner in the automatic continuously variable transmission according to the present invention. be. This is because the adjustment mechanism for changing the drive direction is operable to move the conical body or the annular body to the output shaft, respectively, depending on whether the annular body is stationary or rotates around a central shaft. This is because it is possible to continue.

If, according to another embodiment of the invention, the transmission action is started as a static operating position and after passing through various speed ratios, a direct connection between the input shaft and the output shaft is realized without the intervention of control components. power loss and wear and tear within the automatic transmission are minimized. One embodiment of the invention will now be described more specifically, by way of example, with reference to the accompanying drawings, in which: FIG.

In the embodiment shown in the accompanying drawings, some structural details that are fundamental to the good operation of the structure have been omitted, as they are not necessary for a concise explanation of the invention. These omitted parts include divine fitting and locking parts, while some other parts are shown as one piece, but are actually multiple parts from an assembly point of view. It is more structured and assembled. Furthermore, the suspension system of the entire transmission has been left out of consideration, as well as some fixed transmissions, for example for speed-adapting an automatic transmission to the prime mover to which it is connected. .

Referring to the accompanying drawings, the illustrated embodiment has a housing 1, with a main shaft 2 extending centrally within the housing, on which a primary drive member 3 is mounted for rotation therewith. There is. This primary drive member has a first radial end flange 5 provided with a ring gear 6 as well as a sleeve 4 with a second end flange 7.
have. The ring gear 6 can be driven, for example, by a flywheel of a prime mover (not shown).

The outer circumferential part of the end flange T is designed as a clutch housing 8 fitted with a plurality of centrifugal rollers 9, for example six, which rolls radially outwards as a result of centrifugal force during rotation of the primary drive member. be forcibly moved. However, the clutch housing is formed so that the primary drive member moves not only in the radial direction but also in the axial direction. During this σ displacement, the row 29 comes into contact with the clutch 10. The clutch 1o is connected to the primary drive member in such a way that it can only be moved in the axial direction. When such a movement is performed, the clutch plate 10 is moved by the thrust ring 11 carrying the control ring 12.
come into contact with. The ring 12 is rotatable with respect to the thrust ring 11 via the balls 13 about the central axis of the main shaft 2 . The IJ ring 11 does not rotate, but is axially slidably supported by a ball 14 running in a guide track via a secondary drive member 15 having a sleeve 16 with radial flanges 17 and 18. ing. The radial flange 17 terminates 17 in an axial flange 19, which flange forms a support surface for the thrust ring 11. A ring gear 20 is provided on the radial flange 18, which gear 21 forms part of a drive shaft 22.
We are collaborating with A conical body 24 is mounted on the shaft 22 via a plurality of balls 23 housed in a guide track, and the body has a shape near its top that allows it to cooperate with the control ring 12. It has seven radial flange 25 with a circumferential edge. The drive shaft 22 is hollow and the auxiliary shaft 26
is mounted on top. The shaft 26 is mounted at one end in a drum 27 attached to the main shaft 2, and at the other end in a drum 29 via a larger diameter dowel 28.

The conical body 24 is provided with a concave rounded circumferential surface 30'lk, which can cooperate with a similarly curved inner circumferential surface 31 of the annular body 32. Here, the body 32 is forced into contact with the conical body via a plurality of disc springs 33, which springs 33 are placed at one end and are attached to the axial flange 34 of the annular body 32.
The other end is in mesh with the 7 axial flange 35 of the knob member 36.

Hub member 36 has a sleeve 37, a radially extending end flange 38 terminating in ring gear 39, and a radial end flange 40 located opposite end flange 38. and axial flange 41
It ended within (・ru.

The flange 41 terminates in a radial flange 42, which terminates in an axial flange 35 for supporting the spring 33.

The annular body 32 has a second axial flange 43 which is provided with a guide track for a ball 44 which has previously been formed in the axial flange 41 of the hub member 36. It is housed within the guide track. Thus, the annular body 32 is attached to the hub member 36 such that it cannot rotate but is movable in the axial direction.

The drum 29 is mounted on the sleeve 4 at one end and on the hub section 36 at the other end. r ram 2
9 is provided at both ends with axial flanges on which ball bearings 45, 46 are respectively arranged. The outer rings of the pole bearings 45 and 46 are located at the two ends of the hub part of the housing 1. The housing 1 is further equipped with a free rotation clutch 47, that is, a clutch that allows rotation in only one direction.

A ring gear 48 is provided radially inside the clutch 4γ, which ring gear can cooperate with an outer ring gear 49 on the slide member 50. The slide member 5o can slide on a shaft 52 constituting the output shaft of the automatic transmission via a ball 51 running in a guide track.

The connection between the main shaft 2 and the output shaft 520 is made by a bearing 53 so that the main shaft can rotate freely relative to the output shaft 52.

The slide member 50 has two inner ring gears 54 and 5.
5 is further provided. The ring gear 54 is the hub member 3
It is designed to cooperate with the ring gear 39 of 6.

The ring gear 55 can cooperate with a gear 56 mounted on the shaft 2 so that it does not rotate relative to the shaft. The sliding member 50 has two concentric parts 57 and 58
The parts are mounted by balls 59 in the guide tracks so that they can rotate with respect to each other but cannot slide axially relative to each other. Slide member 50
In this case, the ring gears 59, 54 and 55 are connected to the ring ear 60.
61 and 62 or is mounted on shaft 52 for movement in a manner that cooperates with housing 1, drum 29 and hub member 36. The slide member 5o can be moved and stopped via an operating lever (not shown).

The supporting piece 6 is attached to the drum 29 within the same cross-sectional area in which the end piece of the auxiliary shaft 26 is located.
3 is provided, and a pin 64 is mounted within the piece. One end of the pin 64 is a thrust bearing 65
The other end of the tube 64 carries a segment 66. Segment 66 has a substantially radially oriented peripheral surface that is identical in shape to the opposing control 120 surface.

Although only one conical body is shown in the figures, it is preferred to provide three such conical bodies uniformly distributed in the circumferential direction. Support piece 63, pin 64 and segment 66 are then arranged in the intermediate region. 1 in the upper part of the attached figure for clarity.
Two conical bodies 24 are shown and one support piece 63 is shown in the lower part.

The operation of the device described above takes place as follows.

When the primary drive member 3 is driven, the rows 29 come into contact with the clutch plates 10 due to the centrifugal force generated, bringing these plates into contact with the thrust string 11. As a result, the ring 11 starts rotating and the secondary drive member 1
5 is rotated. The rotational movement is transmitted via the ear 20, the gear 21 and the conical body 24, which is connected in a non-rotatable manner to the gear 21. The conical body 24 attempts to rotate the annular body 32.

However, the annular body 32 is spring-loaded so as not to rotate relative to the hub member 36 via the disk spring 33, and the hub member 36 is not only connected to its ring gear 39 and the ring gears 54 and 49 of the slide member part 57, but also to the ring gear 36. 48 to a free-rotating clutch, rotation is prevented. The annular body 32 thus remains stationary, so that the conical body 24 displaces on the annular body 32 and thus the entire drum and main shaft 2 rotate. Here, the direction of rotation is the same as the rotation direction of the prime mover. The main shaft 2 rotates the slide member part 58 and thus the output shaft 52 via a gear 56 mounted thereon as well as a ring gear 55.

If the input rotational speed of the primary drive member now increases, the centrifugal roller 9 moves the clutch plate 10 and the thrust ring 11 in the axial direction toward the conical body 24. The control rings 12 thus moved simultaneously press the conical body 24 radially outward.

Due to the radial displacement of the conical body 24, the annular body 32 is subjected to an axial displacement, so that the diameter at which the two grooves 24 and 32 mesh changes, and thus the speed ratio also changes. do. This process is performed by the primary drive member 3.
continues until a substantially one-to-one speed ratio is reached even as the input speed increases further. The conical body 24 is then in its radially outermost position and the control ring 12 is in contact with the segment 66, so that a direct connection between the input and output shafts is obtained.

In this position, the conical body 24 gradually stops, the drum 29 rotates at the same speed as the prime mover with its parts inside, and the transmission losses are reduced by the ball bearings 45 and 4.
6 only.

If rapid acceleration is required, it is preferable to break the aforementioned direct connection between the input and output shafts, i.e., with a 1:1 speed ratio.

In the present construction this can be achieved by pushing the bins 64 and the segments 66 connected to these via the thrust bearing 65 towards the primary drive member. At this time, by displacing the control ring 12 in the axial direction, the conical body 24
radially inwardly displaced as a result of axial pressure from 3;
The speed ratio is reduced and thus an increase in the output shaft 520 rotational speed is obtained.

The accompanying figures illustrate the device in a position where the direction of rotation of the output shaft 520 is equal to that of the drive motor. If the direction of rotation of the output shaft 520 is opposite to that of the drive motor, the slide member 50 will be rotated by the ring gears 49, 54 and 55, respectively.
1 and 62 until it begins to cooperate with shaft 52.

When the primary drive member 3 is driven, initially the same effects as described above occur, but this time the difference is that the annular member 32 is no longer prevented from rotating, while - the ram 29 is driven by the ring gears 61, 54, 49 and 6. It is connected to the housing 1 by ゜.

The annular body 32 therefore begins to rotate and move along the hub member 36. Via the ring gears 62 and 55, the hub part 36 is connected to the slide part 58 and thus to the output shaft 52, so that the latter has a direction of rotation opposite to that of the drive motor.

In this case too, different speed ratios can be obtained steplessly, so that the output shaft 52 can be driven within a wide control range in both directions.

[Brief explanation of the drawing]

The accompanying drawing is a schematic longitudinal sectional view of the automatic continuously variable transmission according to the present invention. 3: Primary drive member 9: Roller 10: Clutch plate 11 Nissura ring 15: Secondary drive member 20, 21: Ring gear 24: Conical body 32: Annular gear 33: Disc spring 36: Hub member 39, 54, 49: Ring gear 57: Slide member 4γ: Free rotation clutch 2: Main shaft 56: aP gear 55 Nirindia 52: Output shaft 26 Two radial shaft agents: Yurimura, 4 people

Claims (1)

[Scope of Claims] (1) A speed-dependent clutch; and a section for steplessly controlling the transmission ratio between the input shaft and the output shaft in cooperation with the clutch, the section comprising: a central shaft carrying at least one radially extending shaft;
The shaft has a conical body rotatable about its axis, the conical body having an outer circumferential surface having an axially concave curvature, and the conical sub-sections extending over the radial shaft. is longitudinally movable and driven in rotation around the shaft, the conical body being adapted to achieve the desired torque-speed ratio via axial pressure induced by the speed-dependent clutch. dependent and capable of cooperating with a spring-loaded annular body capable of rotating about the axis of the central shaft, said spring-loaded annular body having a conical shape with an axially convex curvature. An automatic continuously variable transmission comprising: a section having an inner circumferential surface; and an adjustment mechanism capable of determining the direction of rotation of an output shaft relative to the input shaft. (2. In the automatic continuously variable transmission according to claim 1, the conical body is provided with a radial flange having a beveled circumferential edge at its narrow end, and An automatic continuously variable transmission characterized in that the edges are capable of cooperating with corresponding beveled end edges of an axially movable control ring. (3) The automatic transmission according to claim 2. An automatic continuously variable transmission characterized in that the control ring is rotatably supported on a clutch plate of the speed dependent clutch, and the clutch plate is actuated by a centrifugal weight. (4) ) The automatic continuously variable transmission according to claim 5, wherein the centrifugal weight is formed from a roller housed in a control cage that can be rotated in a circumferential path around the central shaft by the input shaft. (5) In the automatic continuously variable transmission according to any one of claims 1 to 4, the automatic continuously variable transmission is characterized in that: The ram is provided with a beveled edge corresponding to the beveled edge of the control ring and located at the same radial distance from the central shaft as the control ring, the control ring being connected to the conical body. characterized in that when pressed to its substantially outermost position, said control ring and drum edge contact each other to directly connect said input shaft and output shaft without the intervention of said control section. Automatic continuously variable transmission. (6) In the automatic continuously variable transmission according to any one of Items 2 to 5, the automatic continuously variable transmission is provided with binka beads distributed on the peripheral edge of the drum. and the axis of the pin is parallel to the central shaft so that the pin can be driven longitudinally and also axially moves the control ring against the centrifugal connecting force. An automatic continuously variable transmission, characterized in that it is installed in the drum so as to be able to displace the drum.
In the automatic continuously variable transmission described in Section 1, the central shaft is uniformly distributed in its circumferential direction at 6°C.
An automatic continuously variable transmission characterized in that it carries two radial shafts, each shaft optionally having a conical body. (8) In the automatic continuously variable transmission according to claim 7, the radial shaft is connected to the central shaft;
An automatic continuously variable transmission, characterized in that the transmission extends between the central shaft and a connected drum. (9) Percentage tolerance range 1st to 8th terms (・Drag force・
In the automatic continuously variable transmission according to one clause, the adjustment mechanism for changing the drive direction is adapted to adjust the direction of the drive direction depending on whether the annular body is stationary or rotating about a central shaft. An automatic continuously variable transmission characterized in that a conical body or an annular body can be connected to an output shaft. a [In the automatic continuously variable transmission according to any one of claims 1 to 9, after starting operation in a static operating position and passing through various transmission ratios, the input shaft and the output An automatic continuously variable transmission characterized in that a direct connection is achieved between the shafts without intervening the control part.