JPH0266358A - Continuously variable transmission - Google Patents

Abstract

PURPOSE:To improve a power transfer efficiency with a strong and simple structure by diagonally supporting and orthogonally moving an intermediate shaft on which the assembly of disks of equal major diameter is mounted and an engaging assembly of disks having major diameter is decreased stepwise on a plane including input and output shafts mounted to an oppositely reducing directions to each other. CONSTITUTION:The major diameter of a disk assembly consisting of a plurality of disks 2 and frame members 3 of equal diameter is slightly decreased stepwise and provided in an input shaft 1 together with a disk spring 18. A disk assembly 17 having an opposite direction of decreasing major diameter is mounted on an output shaft 14 together with a disk spring 19 and both the shafts are disposed in parallel. The disk assembly of the same major diameter is mounted on an intermediate shaft 8, diagonally supported on a plane including the input and the output shafts 1, 14 and disposed so as to be movable to an orthogonal direction. Disks 2, 15 have thin peripheral edge parts, form a space to the peripheral edge part of an adjacent disk and the disk assembly of the intermediate shaft 8 is formed in the space capable being inserted thereinto and having a slightly larger width. Accordingly, an excellent power transfer efficiency can be attained with a strong, simple and compact structure.

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a continuously variable transmission used in automobiles or various machines.

(Prior art) There have been various types of mechanical continuously variable transmissions, but in automobiles, which are typical machines that require frequent gear changes, variable transmissions are used by combining steel belts and segment pieces. 2. Description of the Related Art There have been provided a so-called Vandona type continuously variable transmission having a structure in which rotational force is transmitted between V-pulleys, and a Barbary type continuously variable transmission in which the continuously variable transmission is arranged in a bypass circuit of a differential gear device.

(Problems to be Solved by the Invention) Automobiles are often operated under harsh conditions such as sudden starts and sudden accelerations, which tends to shorten the life of the power transmission section. Steel belts tend to be short-lived. Furthermore, when considering the compactness of the structure, it is generally said that the maximum output of the Vandona type continuously variable transmission is limited to approximately 100 horsepower.

Furthermore, when using a conventional continuously variable transmission, it is difficult to obtain large horsepower.

In view of the above, it is an object of the present invention to provide a continuously variable transmission which has a strong structure, allows quick speed change operation, is simple and compact in structure, and has excellent power transmission efficiency.

(Means for Solving the Problems) In order to achieve the above object, a continuously variable transmission according to the present invention comprises an input shaft, an output shaft, and an intermediate shaft that transmits rotation from the input shaft to the output shaft. The input shaft and the output shaft are located parallel to each other, and the input shaft and the output shaft include a plurality of disc assemblies whose outer diameters change slightly in stages, and the direction in which the outer diameter increases or decreases. A plurality of disk assemblies having the same outer diameter are attached to the intermediate shaft, and
Each of the plurality of disc assemblies attached to the input shaft, the intermediate shaft, and the output shaft is composed of a disc body of equal diameter with a thin peripheral edge, and there is a gap between the peripheral edge of the adjacent disc body. is formed, and the peripheral edge of the disc body attached to the intermediate shaft is formed to be slightly larger than the width of the gap so that it can be inserted into the gap between the peripheral edge parts of the disc body attached to the input shaft and the output shaft, Disc springs are interposed at the ends of the input shaft and output shaft, and the intermediate shaft is supported obliquely with respect to the plane containing the input shaft and output shaft, and the input shaft remains at a constant angle. It is characterized by being movable in a direction perpendicular to a plane containing the output axis.

(Operation) The present invention configured as described above operates as follows.

An intermediate shaft supported diagonally with respect to a plane containing an input shaft and an output shaft (hereinafter referred to as input/output shaft) is moved in a direction perpendicular to the above plane while keeping this diagonal angle constant, and the input shaft and intermediate shaft are The periphery of a plurality of disc bodies constituting a disc assembly of a certain outer diameter mounted on one shaft is inserted into the gap. A disc spring is interposed at the end of the input shaft, and this disc spring induces pressure contact, so that the peripheral edge of the disc mounted on the input shaft and the disc mounted on the intermediate shaft are The peripheral edge portions are securely pressed against each other, and rotation is reliably transmitted from the input shaft to the intermediate shaft. At the same time, a disc assembly on the output shaft side having an outer diameter (large diameter or small diameter) different from the outer diameter of the disc assembly on the input shaft side is also connected to the disc assembly mounted on the intermediate shaft. There is a similar engagement relationship, and a disc spring is also interposed at the end of the output shaft, and this disc spring induces a pressing force, so the rotation transmitted from the input shaft to the intermediate shaft passes through the output shaft. The speed is increased or decelerated and taken out. In this case, since the change in the outer diameter of the multiple disk assembly attached to the input/output shaft is slight, heat generation and wear due to slipping are unlikely to occur (the intermediate shaft is perpendicular to the plane containing the input/output shaft). By moving in the direction of the input shaft and the intermediate shaft and between the intermediate shaft and the output shaft
A state in which either a pair of disc assemblies are in complete pressure contact or two adjacent sets of disc assemblies attached to the input/output shaft and the intermediate shaft are in a pressure contact state is continuously repeated. Therefore, a state close to continuously variable speed can be obtained.

(Example) Embodiments of the present invention will be described with reference to the drawings.

In FIG. 1, ■ is an input shaft, and this input shaft 1 has a plurality of disk assemblies consisting of a plurality of disk bodies 2 of equal diameter and two frames 3 that can sandwich the disk bodies 2. 4 is installed. In this embodiment, the outer diameters of the plurality of disc assemblies 4 gradually increase from left to right in the figure.

5.5' is a screw shaft that is rotatably installed, a chain sprocket nod 6.6' is mounted on the screw shaft 5.5', and a chain 7 is suspended around the chain sprocket 6.6'. As the chain 7 is rotated by a power transmission means (not shown), the threaded shaft 5.5' is rotated.

8 is an intermediate shaft, and this intermediate shaft 8 is connected to the threaded shaft 5.5' by a connecting member 9.9' to connect both connecting members 9.9' as shown in FIG. It is supported obliquely with respect to the connecting rod 10 so that the right end portion is located above.

The connecting part +A9.9' is provided with a threaded part 11.11' that can be screwed into the threaded shaft 5.5'.
' is rotated, so that the threaded part 11 of the connecting member 9.9' is rotated.
．． 11' moves up and down, the intermediate shaft 8 is supported obliquely to a plane containing the input shaft 1 and an output shaft (to be described later), and while this oblique angle remains constant, it is supported in a direction perpendicular to the plane containing the input and output axes. It is configured to be movable. The intermediate shaft 8 has a plurality of disk aggregates 13 each consisting of a plurality of disk bodies 12 of equal diameter.
is installed.

In FIG. 1, 14 is an output shaft installed parallel to the input shaft 1, and this output shaft 14 has a plurality of disk bodies 15 of equal diameter and two frames that can sandwich the disk bodies 15. A plurality of disc aggregates 17 consisting of a body 16 are attached. In this embodiment, the outer diameters of the plurality of disc assemblies 17 gradually decrease from left to right in the figure.

18 and 19 are disk springs interposed at one ends of the input shaft 1 and the output shaft 14.

In FIG. 3, 20 is a gap formed between the frame 3 and the thin peripheral edge 21 of the disc body 2 and between the thin peripheral edge 21 of the adjacent disc body 2.2. The outermost edge of the peripheral edge portion 21 is formed in the shape of an acute-angled protrusion. 22 is a gap formed between thin peripheral portions 23 of adjacent disk bodies 12.12. The outermost edge of the peripheral edge portion 23 is formed in the shape of an acute-angled protrusion. The thickness of the peripheral edge part 23 is slightly larger than the width of the gap so that the peripheral edge part 23 can be inserted into the gap 20.
1 is also formed to be slightly larger than the width of the gap 22 so that it can be inserted into the gap. The disc body 15 attached to the output shaft 14 is also attached to the input shaft 1. Like the disc body 2, the outermost end has a thin peripheral edge formed in the shape of an acute-angled protrusion. A gap is formed between it and the periphery of the body. The relationship between the peripheral edge of the disk body 15 attached to the output shaft 14 and the peripheral edge of the disk body 12 attached to the intermediate shaft 8 is also as follows.
Similar to the relationship between the circumferential edge of the disk body 2 and the circumferential edge of the disk body 12, the thickness of the circumferential edge of the disk body mounted on one shaft is the same as that of the disc body mounted on the other shaft. It is formed slightly larger than the width of the gap so that it can be inserted into the gap in the peripheral portion. The pressure contact force is transmitted by the thin peripheral edges of the discs attached to the input/output shaft and the intermediate shaft being in pressure contact with each other.

FIGS. 4(a), 4(b), and 4(c) are diagrams illustrating a state in which the peripheral edges of the disc bodies attached to the input shaft, intermediate shaft, and output shaft are engaged. FIG. 4(a) shows a disk assembly 4 attached to the input shaft 1 and a disk assembly 7 attached to the output shaft 14, and a disk of a certain outer diameter attached to the intermediate shaft 8. To assembly - The state in which the bodies 13 are completely pressed together is shown.

In the figure, the installation direction of the input shaft I and the output shaft load 4 is perpendicular to the plane of the paper, and the intermediate shaft 8 is supported obliquely with respect to the plane containing the input shaft and the output shaft, and this diagonal angle remains constant. It is movable in the direction of the arrow. (The actual movement of the intermediate axis is as follows: The right arrow corresponds to the downward movement in Figure 2 with respect to the plane containing the input/output axis, and the left arrow corresponds to the downward movement of the intermediate axis with respect to the plane containing the input/output axis. (This corresponds to the state of moving upward in the figure.) 13a is a disk assembly installed on the upper right side of the disk assembly 13 as shown in FIG. As shown in the figure, this is a disc assembly installed on the lower left side of the disc assembly 13. At this time, neither of the disc assemblies 13a and 13b is in pressure contact with the disc assembly mounted on the input/output shaft.

Now, as the intermediate shaft moves in the direction of the right arrow as shown in FIG. 4(b), the pressure contact state between the disc assembly 13 and the disc assemblies 4 and 17 is gradually relaxed. ,
The disc assembly 13a starts to be pressed against the disc assembly 4a, which has a slightly larger diameter than the disc assembly 4, and the disc assembly 17a, which has a slightly smaller diameter than the disc assembly 17. By further moving the intermediate shaft in the direction of the right arrow as shown in FIG. After being relaxed, the disc assembly 13a, the disc assembly 4a, and the disc assembly 17
The pressure contact area with a further expands.

FIG. 5 is a layout diagram in which a continuously variable transmission according to the present invention is combined with a differential gear device, and the rotation of the input shaft 24 is controlled by the ring gear 2.
5 and the planetary gear 2 is transmitted to the ring gear 25.
6 mesh with each other, and a sun gear 27 meshes with this planetary gear 26, and rotational torque is transmitted from the sun gear 27 to the output shaft 28. Further, the planetary gear 26 is connected to a carrier 29.
The structure is such that rotation is transmitted to the carrier 29 through a continuously variable transmission 30 that bypasses these differential gears, a pawl clutch 31 with a synchronizing mechanism, and a plurality of gears 32.

FIG. 6 is a diagram showing an example of the rotational speed of each part of the differential gear device shown in FIG. P, C, D, (pitch circle diameter) are proportional to the teeth, and in (goods) d.

and d2 are the sun gear 2, respectively, when the number of teeth of the sun gear 27 is 26 and the number of teeth of the ring gear 25 is 134.
7 and the ring gear 25, the ratios of P, C, and D are shown. The rotation speed is also proportional to the pitch circle diameter (number of teeth), and the rotation speed is proportional to the pitch circle diameter (number of teeth).
L2 and L□ are the rotation speed (RPM) of the input shaft, respectively.
, indicates the rotational speed (RPM) of the carrier and the rotational speed (RPM) of the output shaft. Now, the rotation speed of the input shaft is 600OR
PM, and the rotation speed at overdrive of the output shaft is 70.
0ORPM, the rotation speed at start/low speed is reduced by 174 (1
500PPM), the rotation speed in reverse is the same <174 deceleration (
1500I? PM), the corresponding rotational speed range of the carrier is linear, 7000 above and -15
00 and straight line I, each straight line connecting 6000 on 1 and straight line L2
Find the intersection with 4780 PPM and 6162 RPM. Also, 1500 on straight line L3 and 600 on straight line L1
5270PP by finding the intersection of the straight line connecting 0 and the straight line L2
M is obtained, and the carrier rotation speed range from start/low speed to overdrive is 5270 PPM to 61 PPM.
62r! Becomes PM.

During this time, the continuously variable transmission according to the present invention operates, thereby making it possible to perform continuously variable transmission over a wide shift width.

Also, when using a high-performance torque sensor (not shown) in combination, the torque is at its maximum when the brake is applied, so it is important to ensure that the transmission is quickly set to the stop position using the signal from the torque sensor. As a result, a clutch becomes unnecessary.

(Effects of the Invention) ■) The pressure contact area is an important element that determines the magnitude of the transmitted torque, and in the present invention, the rotational l/rook is transmitted by the thin peripheral portions of the plurality of disc bodies being pressed against each other. Since this is a method, the pressure contact area can be easily increased by increasing the number of disk bodies.

2) Since a disc spring is interposed between the input shaft and the output shaft, pressure contact force is induced by the disc spring, and rotational torque can be reliably transmitted with a simple structure.

3) Since the outer diameter of the disc assembly attached to the input and output shafts changes only slightly, heat generation and wear are less likely to occur at the press-welded parts, and the disc assembly is supported diagonally with respect to the plane containing the input and output shafts. With the intermediate shaft moving in a direction perpendicular to the plane, the pressure contact area between the input shaft and the disc body mounted on the intermediate shaft and between the disc body mounted on the intermediate shaft and the output shaft changes continuously. This allows rotational power to be transmitted, making it possible to smoothly shift continuously without the need for a clutch during gear shifting.

[Brief explanation of the drawing]

FIG. 1 is a side view of the continuously variable transmission according to the present invention, showing a partial cross section, FIG. 2 is a view taken along the line A-A in FIG. 1, and FIG. 3 is a two-dot chain line in FIG. Enlarged view of part B shown in Fig. 4 (a), (b)
) and (c) are diagrams explaining the state in which the pressure contact state of the disk assembly mounted on the input shaft, intermediate shaft, and output shaft changes, and FIG. 5 shows the differential gear device and the continuously variable transmission according to the present invention. FIG. 6 is a diagram showing an example of the rotational speed of each part of the differential gear device shown in FIG. 5. 1. Input shaft, 2. Disk body, 3. Frame body, 4°4a.
・Disk assembly, 5, 5' ・Screw shaft, 6゜6' ・・
Chain sprocket, 7...Chain, 8...Intermediate shaft, 9.9'...Connecting member, lO...Connecting rod, 11.1
1'...Screw part, 12...Disc body, 13.13a
13b - disc assembly, 14... output shaft, 15...
Disc body, 16...frame body, 17.17a...disc assembly,
18... Disc spring, 19... Disc spring, 20... Gap, 21
...periphery, 22...gap, 23...periphery, 24...
Input shaft, 25...Ring gear 26...Planetary gear, 27
...Sun gear, 28..Output shaft, 29..Carrier,
30... Continuously variable transmission, 31... Clutch with synchronizing mechanism, 32... Gear No. 5 Illustrated supplementary display of the Heisei case Name of the invention in 1986 Relationship with each case to correct the continuously variable transmission Correction order Date Heisei Application No. 219499

Claims (1)

[Claims] A continuously variable transmission having an input shaft, an output shaft, and an intermediate shaft that transmits rotation from the input shaft to the output shaft, the input shaft and the output shaft being located parallel to each other, and the input shaft and the output shaft having an outer shaft. A plurality of disk assemblies whose diameters slightly change step by step are mounted so that the increasing or decreasing directions of the outer diameters are opposite, and a plurality of disk assemblies having the same outer diameter are mounted on the intermediate shaft. ,
Each of the plurality of disc assemblies attached to the input shaft, the intermediate shaft, and the output shaft is composed of a disc body of equal diameter with a thin peripheral edge, and there is a gap between the peripheral edge of the adjacent disc body. is formed, and the peripheral edge of the disc body attached to the intermediate shaft is formed to be slightly larger than the width of the gap so that it can be inserted into the gap between the peripheral edge parts of the disc body attached to the input shaft and the output shaft, Disc springs are interposed at the ends of the input shaft and output shaft, and the intermediate shaft is supported obliquely with respect to the plane containing the input shaft and output shaft, and the input shaft remains at a constant angle. A continuously variable transmission characterized by being movable in a direction perpendicular to a plane containing the output shaft and the output shaft.