Centrifugal impact transmission

Abstract

A centrifugal impact transmission between a drive shaft (1) with one or more rotors (1) and one or more driven shafts (6) parallel to the drive shaft (1): each rotor (1) or rotor level (1) includes one or more arms (2) joined to the rotor (1) by a joint (4) and with a mass (3) at the free end thereof, which can be disconnected via a clutch. Each driven shaft (6) includes at least one lever (7), joined to the driven shaft (6) via a one-way clutch, and aligned with a rotor (1), the lever (7) having a return mechanism (8). In this way, each arm (2) has at least one lever (7) aligned with it, and the rotation of each rotor (1) produces the consecutive impact of the arms (2) thereof on each lever (7) aligned with the rotor (1).

Claims

1. A centrifugal impact transmission comprising: a drive shaft (5) having a plurality of rotors (1); a driven shaft (6) parallel to the drive shaft (5); wherein each one of the rotors (1) comprises a plurality of arms (2), each one of the arms has a first end joined to the corresponding rotor (1) by a joint (4), which rotates on the rotor; a mass located on a second end of each one of the arms, the masses on adjacent rotors are facing opposite directions; wherein the driven shaft (6) comprises a plurality of levers (7) connected to the driven shaft (6) by using a one-way clutch, wherein each one of the levers (7) corresponds to one of the rotors and is coplanar with the corresponding rotor (1), a return mechanism (8); wherein rotation of each one of the rotors (1) produces centrifugal forces that rotate each one of the arms producing the masses to impact the corresponding lever (7); and wherein the return mechanism (8) is a rocker (81) joined to two adjacent levers (7) so the impact of each mass on the corresponding lever (7) pushes forward the adjacent lever (7).

2. The transmission according to claim 1, wherein each one of the rotors (1) comprise a clutch.

3. The transmission according to claim 1, wherein each one of the masses (3) rotates freely on a shaft parallel to the drive shaft (5).

4. The transmission according to claim 1, wherein each one of the arms has a curved shape.

5. The transmission according to claim 1, wherein the levers (7) have a return movement between 10° and 30°.

6. The transmission according to claim 1, wherein the arms (2) of the rotors (1) are distributed on two or more levels.

7. The transmission according to claim 1, further comprising a flywheel on the driven shaft (6).

Description

DESCRIPTION OF THE DRAWINGS

(1) In order to ensure a better understanding of the invention, the following drawings are included.

(2) FIG. 1: Perspective view of an example embodiment of the invention.

(3) FIG. 2: Upper view of the example embodiment of FIG. 1.

(4) FIG. 3: Perspective view of a second example embodiment.

EMBODIMENTS OF THE INVENTION

(5) Hereinafter, a brief description of an embodiment of the invention is provided, for purely illustrative purposes and without limitation.

(6) The embodiment shown in the drawings comprises a drive shaft (5) having at least one rotor (1a, 1b) each rotor having with a plurality of arms (2) finished with a mass (3). The arms (2) are joined to the center of the rotor (1) by means of respective joints (4), which can rotate freely thereon. If desirable, the stroke of the arms (2) can be limited within a desired range by means of the corresponding stops (not shown in the drawings). Both rotors (1a, 1b) represented are located on the same drive shaft (5) and are connected to it. However, both rotors (1a, 1b) may comprise clutches that activate or deactivate the rotation of each rotor (1a, 1b) independently.

(7) The transmission in the drawings also comprises a driven shaft (6) that is parallel to the drive shaft (5), with a series of levers (7). The levers (7) are connected to the driven shaft (6) by means of a one-way clutch (not visible). That is, the rotation of the lever (7) is transmitted to the driven shaft (6) in only one direction. By contrast, the lever (7) rotates independently from the driven shaft (6) in the opposite direction. An example of this type of clutches, which are known in the art, is a ratchet mechanism or a unidirectional bearing.

(8) Each lever (7) comprises a return mechanism (8) that has been represented in FIGS. 1 and 2 as a coiled spring. However, they could also be torsion springs, sheet springs, or any other spring known in the art. The type of spring and the position where the other end thereof is fixed to can be relevant. For example, a torsion spring fixed to the driven shaft (6) is preferable over the spring represented.

(9) Additionally, FIG. 3 shows a new form of a return mechanism that can be used when the number of levers (7) on a driven shaft (7) is higher than two, since it requires coupling two levers (7) in pairs. Any odd lever (7) would have to use some type of spring.

(10) The return mechanism (8) of FIG. 3 comprises a rocker (81) joined by respective bushings (82) to the levers (7). The rocker (81) is articulated in the center thereof, so that the impact over one lever (7) transmits the movement to the rocker (81), which pushes forward the other lever (7) of the pair. This implies that the two levers cannot be impacted at the same time, requiring instead a certain minimum offset.

(11) The rotation of each rotor (1a, 1b) causes the centrifugal force to separate the masses (3) of the drive shaft (5) by rotating the arm (2) thereof on the joint (4). In one point of the journey thereof, the mass (3) hits the lever (7), which absorbs the energy by moving backwards, causing the driven shaft (6) to rotate. The movement of the lever (7) can be regulated, but preferably it should not be too excessive in order to give it enough time to return. 20° is a recommended value. The return of the lever (7) to the rest position thereof is not transmitted to the driven shaft (6) by the one-way clutch.

(12) Once the lever (7) returns to the rest position thereof, it can be hit by the following arm (2), while the previous arm (2) deploys by means of the centrifugal force.

(13) FIG. 2 shows the position of the two levers (7) on FIG. 1, one of them in the rest position and the other in the position after being impacted.

(14) The invention can be applied also to several driven shafts (6) and levers (7), in any combination thereof:

(15) A driven shaft (6) with as many levers (7) as rotors (1), with the shaft aligned with said rotors.

(16) Two or more driven shafts (6), each of them with as many levers (7) as rotors (1), with the shafts aligned with said rotors.

(17) Two or more driven shafts (6), each with a lever (7) aligned with a different rotor (1).

(18) Several driven shafts (6), each with a number of levers (7) aligned with all the rotors (1) or with some of them.

(19) Each of these combinations of driven shafts (6) and levers (7) provides different outputs on each driven shaft (6). For example, with a single lever (7) per driven shaft (6) aligned with a single-arm (2) rotor (1), the result is a single movement of the driven shaft (6) for each revolution of the rotor (1), so the output can be considered as “step by step”.

(20) It can also be a continuous output if there is a sufficient number of levers (7) and arms (2) for the sum of returns to equal 360°. For example, if the transmission comprises six arms (2) on each rotor (1) or level, and three rotors (1) or three levels of arms (2) are arranged, the driven shaft (6) receives 18 impacts per revolution. If the lever (7) goes back 20°, this equates to a revolution of the driven shaft (6) for each revolution of the drive shaft (5). A higher number of rotors (1) and levers (7) makes it possible to increase the output speed.

(21) Another way of modifying the output of the driven shaft (6) is to modify the length of the arms (2) or levers (7), the weight of the mass (3) and the return movement of the lever (7). In any case, it is recommended that the number of arms (2) per rotor does not exceed six arms, in order to give time for the lever (7) to return.

(22) If the number or arrangement of the arms (2) is not balanced, it may also be necessary to include a counterweight (not shown) in order to center the axis of inertia on the drive shaft (5).

(23) The mass (3) may include a bearing so that the impact on the lever (7) has no friction. Equally, it could be made of a low friction material, but with high resistance to impact and abrasion. The shape of the arm (2), which is curved in the figures, may also vary in order to control the angle of impact. Equally, it may be advantageous to include a guide (not shown) directing the deployment of the arms (2) after impact. This guide may, for example, keep the arm (2) folded until a moment before impact, for example, at 90° rotation of the rotor (1), achieving maximum centrifugal force by means of the accumulated potential energy thereof.

(24) In the represented figures, the arms (2) of the different rotors (1a, 1b) are offset, with the impacts perfectly distributed. However, the offset between the different arms (2) may be modified:

(25) If all the arms (2) impact on the levers (7) of the same driven shaft (6) at once, the rotation will be reduced but the pair will be elevated.

(26) If the impacts are distributed homogeneously, that is, if they are distributed so that the time between two consecutive impacts is the same, the drive shaft (5) is slowed down less.

(27) In any case, it is recommended to place flywheels 80 in any driven shaft (6) requiring one in order to stabilize the output and store kinetic energy.

(28) The power source of the drive shaft (5) and how every driven shaft (6) is used is not considered relevant for the invention, since the invention is particularly versatile.

(29) The shafts (5, 6) are generally arranged vertically, but other arrangements are possible. For example, if they are arranged horizontally, it is preferred that the impact on the levers (7) is made during the descending movement of the arm (2).