Stream motor

Application filed April 11, 1928.

This invention relates to stream motors operative with wind, water, steam, or the like as motive power.

One object of this invention is to provide 5 an improved stream motor which operates in an efficient manner regardless of the direction of flow of the motivating stream, as long as the direction is at an angle to the axis of the motor.

Another object of this invention is to provide an improved stream rotor in which the vanes move with their trailing edges foremost.

Another object of the invention is the pro15 vision of a device of the character described, wherein the rotor comprises a plurality of vanes equally spaced and symmetrically arranged about the rotor axis, which vanes are stationary throughout the cycle of the motor, 20 and are related in proximity to one another at a particular angle so that a suction may be created upon the exterior face of a vane and a pressure upon the interior face of an adjacent vane, for which purpose the spaces be25 tween the vanes freely communicate within the rotor.

A further object of the invention is to produce an improved device of the type specified, in which the vanes are of uniform surface 30 formation and relation to one another for stream line action.

Still another object of the invention is to furnish a device of the nature set forth in which the rotor vanes are angularly disposed 35 to the axis of the rotor for reducing the impact and loss of energy of the motivating stream in its action on the rotor.

Still a further object of the invention is to create an improved device of the species men⁴⁰ tioned, which is adapted to operate as a steam turbine.

Other objects will in part be evident and in part pointed out hereinafter.

Generally described, the invention pro⁴⁵ vides a stream rotor which includes a plurality of vanes arranged in stationary relation and in proximity to one another, the spaces between the vanes communicating freely, and the vanes forming such an angle of approach ⁵⁰ with one another and the motivating stream

1,740,596 tion. The said motor includes a rotor 11 that is mounted upon a vertical axial shaft 12. The latter is journaled at its lower free end in a bearing 13 of an anchor plate 14, ₄ from which extends upwardly a bracket 15 forming another bearing 16 for the said shaft. Between the said bearings is a bevel gear 17 on the shaft 12, and meshing with the teeth thereof is another bevel gear 18 on a horizontal ₁₀ drive shaft 19 that is journaled in bearing 20 in the bracket 15. A ball bearing support to carry the weight of the rotor 11 is provided at 21 at the bearing 16.

While the rotor shaft 12 is supported at _ie only one end thereof, steadiness in a high degree is obtained, since as the speed of the rotor 11 increases, so does the stability thereof, according to the principle of the gyroscope.

The rotor includes a plurality of vanes 22 that are in proximity to one another. Each vane has an outer or leading edge 23 and an inner or trailing edge 24. Both the leading and trailing edges of each vane are free so ₂₅ that clear spaces 25 are provided between adjacent vanes. These spaces communicate with the air chamber C within the rotor 11.

Each vane 22 forms an angle A with a radial line from the axis of the rotor, which 30 angle is hereinafter designated as the angle of approach of the stream to the vane nearest thereto in the direction of flow. This angle may be approximately thirty degrees. It will be noted that the inside and outside sur35 faces of each vane are in parallelism. Now, as the motivating stream strikes the rotor 11, a suction or region of reduced pressure is created on the outside of certain vanes and a region of increased pressure or velocity act40 ing against the corresponding vanes is created on the inside thereof. This causes the rotor to turn, and the direction of rotation of the same is dependent solely on the direction of the vanes. More specifically, as shown in 45 Fig. 3, vanes 22 and 26 are shown in diagrammatic relation to each other. In each case the direction of the wind is the same, being indicated by arrow a, yet vane 22 will move clockwise, while vane 26 will move ₅₀ counterclockwise. The action of the currents is as follows: The current, after striking vane 22 is deflected as shown by arrow 5, creating a suction on the vane in a clockwise direction. Other current entering space 25, or being de55 fleeted thereinto from a next adjoining vane 22, strikes the inner side of said vane as indicated by arrows c producing a clockwise force that is additive to that indicated at δ. At vane 26 these forces are in opposite direc60 tion.

The vanes 22 form angles B of approximately forty five degrees with the rotor axis, measuring from the edges of the vanes. Thus the tendency toward a stream line effect 65 is accentuated, and eddying considerably re duced, so that the operating efficiency of the device is high.

Preferably a main base is provided at 27 which is formed with a plurality of equally spaced, symmetrical points, 28, each of which ₇₀forms an angle of sixty degrees, as may be readily understood. This base is located centrally between the upper and lower ends of the rotor, and is at right angles to the shaft 12. The vanes 22 are fastened to similar sides ₇₅of the points 28, and if the rotor is to turn in opposite direction, the vanes are fastened to the opposite sides of said points. The base 27 is solid and acts beneficially in the rotor chamber C as a stream guide. Other bases, _g0or partitions parallel to 27 may be provided.

Each vane 22 tapers towards its end at the end of the rotor 11. This taper decreases the working face of the vane nearest the rotor axis, where the stream is least effective. An _8geasy attachment of the vanes is thereby insured, this occurring in any suitable manner, by means of hollow spiders at the rotor ends, or being directly bracketed to the shaft 12.

It has been found to be most advantageous :_gothat the number of vanes employed be. six or multiples of six. The adj acent vanes must be in comparative proximity to one another. If the upper and lower vanes be regarded as separate, then the unit number of vanes ₉₅might be properly designated as six pairs.

While the vanes are here shown as beingrigid, they may be pivoted for movement so that the direction of rotation may be reversed or the speed of the rotor reduced for a given - _10(fvelocity of the motivating stream. Other constructions for speed and direction control are hereinafter described.

The vanes 22 may be made of any suitable material, as, for example, sheet metal which ₁₀₅has the desired weather proof qualities, and its mode of fastening may be any that is well known in the art.

In Fig. 4 is shown a modification of the invention, wherein my improved rotor is uti- _Πο lized in a spherical casing 29 so as to provide a steam turbine. The said casing has bearings 30 for the horizontal shaft 31 of the rotor 11. A pair of diametrically opposite openings 32 and 33, whose axes lie in the central trans- -i₁₅verse plane of the rotor, are provided. The opening 32 constitutes an intake nozzle, while 33 is an exhaust outlet. The relation in size of these openings may of course be such as to permit of proper expansion of the steam. 120

In Fig. 5 is shown a further modification of the invention in which a plurality of turbine units are employed, more particularly three in number. Of these the end turbine units 34 have rotors for turning in one direc- 125 tion, while the intermediate unit 35 has its rotors ll^a reversed. Similarly, the direction of flow of steam through unit 35 is opposite to that in units 34. The several rotors are all mounted on one continuous shaft 31% and 130

1,740,596 the casings may be interconnected at the bearings 30^a. In operation, units 34 alone are operated, unless it be desired to slow down the shaft 31^a, in which case unit 35 is operated to create a counterforce. To reverse the direction of rotation of the said shaft, units 34 may be idle, and unit 35 operated alone. This arrangement provides a simplified speed and direction control of a high degree of simplicity.

By the arrangement shown in Fig. 6, a plurality of intermediate units 35 are provided, so that the force of units 34 may be balanced and the shaft brought to a stop. Further, the shaft may rotate with equal power in either direction, according as the intermediate or end units are operated. A more sensitive speed control is thus ensured.

It will be noted that the speed of any one unit can be directly regulated, as, for example, by throttling the steam supply. Where a plurality of units are employed, automatic control can be provided, so that in the event that the speed of the shaft becomes excessive, steam may be supplied to the intermediate units in a regulated quantity to reduce the shaft speed to a desired number of rotations per minute.