JPS58128557A - Transmission mechanism for converting equal input rotary motion into unequal output rotary motion - 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 a transmission mechanism for converting uniform input rotational motion into non-uniform output rotation.

A type of transmission mechanism with which various cam movement programs can be realized is a so-called star roller transmission mechanism. Not only is this suitable for such a transmission mechanism, but it also enables a locking operation, ie, a rest period. However, star roller transmissions are relatively expensive. Because this star-shaped roller transmission.

This is because the mechanism requires various high requirements with respect to precision, especially in terms of manufacturing. It is impossible to achieve extremely small step movements with such a transmission mechanism.

The problem underlying the present invention is to make it possible to realize various cam movement mechanisms, at least similar to the star roller drive, and which, unlike the star roller drive, have fewer requirements for a-building accuracy and manufacturing quality. The goal is to create a power transmission mechanism that can be used.

The above-mentioned problem forming the basis of the present invention comprises a carrier rotatable about an axis and driven with a uniform rotational movement,
An interlocking part is rotatably supported concentrically on this carrier, and this interlocking part is guided on the one hand via rollers along the cam closing path of the control cam, and on the other hand can be circuited around the above-mentioned axis. The control cam is mounted concentrically on the driven member, in which case the control cam is likewise rotatable about the axis and kinematically coupled to the carrier. .

The various cam movement mechanisms are such that the carrier and the control cam can be driven in opposite directions on the one hand and in the same direction on the other hand.
Therefore, it is possible to reach The transmission mechanism according to the invention determines how much delay and acceleration or locking, i.e., rest time, or backstepping that is not possible with the star roller transmission mechanism occurs when the driven shaft rotates. This depends not only on the shape of the control cam, but also on the rotational speed ratio of the control cam to the carrier. If the control cams are moving in the same direction of rotation but at a slower speed than the carrier, the driven shaft undergoes the nth rotation of the drive shaft (where n Id is any number greater than 1). Perform one exercise program each time. If the control cams are driven in opposite directions relative to the carrier, the movement program of the driven shaft is
(again, n represents any number greater than 1).

(Of course, the number n has a technically significant upper limit.) It is advantageous to provide that the carrier and the control cam are driven by a common drive. This is because, with this configuration, it is possible to maintain a predetermined exercise program without using additional monitoring and control mechanisms. It is proposed to form the carrier and the control cam as gear wheels or to connect them rotationally rigidly to a gear wheel.

This transmission mechanism can be constructed with little outlay by configuring the carrier and the control cam so that they are driven by a shaft parallel to the above-mentioned shaft and equipped with gear wheels.

The control cam is formed as a groove formed in the gear wheel, in which groove the roller of the interlock is guided. Such a control cam can be manufactured relatively easily in terms of manufacturing technology, and does not cause any problems in assembly.

In an advantageous embodiment, the linkage is designed as a toothed segment, which meshes with a toothed segment of the driven shaft. However, this interlocking part is formed as a two-armed lever rotatably supported on a carrier, and one end of this lever supports a roller, and the other end is supported concentrically, for example, on a lever of a driven shaft. It is also possible to combine with a connected rondo. The most compact design is achieved by rotatably mounting the carrier and the control cam on a driven shaft.

The invention will be explained in more detail below with reference to embodiments illustrated in the accompanying drawings.

Inside the casing 1, a drive shaft 2 driven by a drive motor S and nine driven shafts 4 provided parallel to the drive shaft are rotatably supported within a ball bearing 6. The driven shaft 4 is an axle due to the shaft 9 having a carrier 8 formed as a gearwheel 7 and a control cam 11 formed as a groove in the nine end face 12 facing the gearwheel 7 . The gear 7, the carrier 8 and the gear 9 are supported on the driven shaft 4 via a ball bearing 15, a ball bearing 14 and a needle bearing 16. The linkage in the form of a toothed segment 17 has an attached pivot lever 18, which is pivotably mounted concentrically in the carrier 8 via a needle bearing 19. Toothed segment 17 engages with toothed segment 21 of driven shaft 4 .

The bearing bolt 22 provided on the toothed segment 17 includes
Two rows (23) guided in the control cam 11 are rotatably mounted.The control cam 11 has a maximum distance in the M direction and a minimum distance in the M direction with respect to the driven shaft 4. That is, when the gears 7 and 9 make a relative movement of 360° with respect to each other, the toothed segment 17 performs a reciprocating rotational movement.As a result, the toothed segments 17 and 12 mesh with each other, so that the driven shaft 4 A corresponding resonant rotational movement for gear 7 is induced.

Two gears 24 and 26 are rotatably and firmly fixed on the drive shaft 2. Of these gears, the gear 24 meshes with the gear 7, and the gear 26 meshes with the gear 9 via an intermediate gear 27.

The intermediate gear 27 induces a reciprocal rotational movement relative to the gear 90 and the gear 7.

However, gears 26 and 9 are KH due to other exercise programs.
By varying their diameters, they can be configured to mesh directly with each other. In this case, gear 9 always has a different pitch diameter than gear 7. In such a case, gears 7 and 9 rotate in the same direction with different angular velocities.

The transmission mechanism according to FIGS. 1 and 2 is as follows.

The drive motor 5 uniformly drives the drive shaft 2 in the direction of the arrow 28 . The carrier 8 is rotated in the direction of the arrow 29 via the gear 24 and the gear 7. Gear 26 rotates gear 27 in the direction of arrow 51 so that gear 27 rotates in control cam 11.
At the same time, the gear 9 is rotated in the direction of the arrow 62, that is, in the opposite direction to the direction of rotation of the gear 7 and the carrier 8. The toothed segment 17 performs a pivoting movement along the carrier 8 in accordance with the course of the cam 11. The magnitude of this turning movement is determined by the maximum pressure #LMA of the control cam 11 and the minimum distance M. The gear segment 17 runs along the driven shaft 4 via the toothed segment 21 in the direction of the arrow 53.

That is, if the toothed segment 17 returns to the carrier 8 and does not perform a pivoting movement, the driven shaft 4 is rotated at the same angular velocity as the carrier 8. The rotational movement of the toothed segment 17, which is transmitted from the toothed segment 17 to the toothed segment 21 of the driven shaft 40, is superimposed on this rotational movement. That is, the driven shaft 4 is subjected to acceleration and retardation effects that depend on the shape of the control cam 11 and on the direction of rotation and relative angular velocity of this control cam with respect to the support 8 of this control cam.

Depending on the shape of the control cam 11 relative to the carrier 8, its direction of rotation and its speed of rotation, the driven shaft 4 carries out one or more acceleration and retardation movements when the drive shaft 2 rotates. Alternatively, any one of these acceleration motions and delay motions is performed only each time the drive shaft 2 performs the n-th rotational motion. With a suitable design of the control cam 11, it is also possible to achieve a temporary standstill of the driven shaft 4. Even a backstep movement, which means a temporal reversal of the driven shaft 4, is possible.

[Brief explanation of drawings]

FIG. 1 is a schematic diagram of the structure of the transmission mechanism, and FIG. 2 is a sectional view of the structure of the transmission mechanism along the line layer-to-rail according to FIG. Symbol 4 in the figure...Double drive shaft 8...Carrier 11...Control cam 21...Driven member 25...-Roller

Claims (1)

[Claims] t In a transmission mechanism for converting a uniform input rotational motion into a non-uniform output rotational motion, the transmission mechanism is rotatable around the wax 4) and is driven with a uniform rotational motion. carrier (
8), on which an interlocking part (17) is rotatably supported concentrically, and on the one hand, this interlocking part moves along the cam closing path of the control cam (11) via a roller (25). On the other hand, the control cam (11) is attached to the driven part # (21) which is rotatable concentrically about the O axis (4), and in this case the control cam (11) is guided by the O axis (4).
The above-mentioned transmission mechanism is rotatable around 4) and is dynamically connected to the carrier (8). 2. Transmission mechanism according to claim 1, in which the carrier (8) and the control cam (11) can be driven at different rotational speeds. (5) Claims 1 or 2, wherein the carrier (8) and the control cam (11) can be driven in opposite directions.
Transmission mechanism described in section. 4. Transmission mechanism according to claim 1 or 2, in which the carrier (8) and the control cam (11) are driveable in the same direction. & The carrier (8) and the control cam (11) share a common drive unit (
3), the transmission mechanism according to any one of claims 1 to 4. 4. The carrier (8) and the control cam (11) are designed as teeth (7, 9) and are rotationally rigidly connected to these wheels. The transmission mechanism described in any one of the above. l The carrier (8) and the control cam (11) are attached to the above shaft (4)
7. Transmission mechanism according to any one of claims 1 to 6, which is driveable by a shaft (2) parallel to and provided with gear wheels (24, 216). & The control cam (11) is formed as a groove machined into the gear (9), and the interlocking part (17) is inserted into this groove.
Transmission mechanism according to any one of claims 1 to 8, in which a roller (23) is guided. 9. The interlocking part is the toothed segment (21) of the driven shaft (4).
) is formed as a toothed segment (17) meshing with the claim #! The transmission mechanism according to any one of items 1 to 8. 1cL Transmission mechanism according to claim 9, wherein the carrier (8) and the control cam (11) are rotatably mounted on the driven shaft (4).