Twin channel reduction drive with electric motor

The present invention applies to mixer units oriented large and powerful and aerators and broadly oriented reduction units with a plurality of reduction steps, wherein the shaft of an electric motor is offset from the axis of the consumer power and arranged at right angles to said axis. The single-engine unit is divided into two channels of energy applied to a common final drive gear in two diametrically opposed. Means are provided to equalize the loads in both places, at all loads. Therefore a torque is exerted in lieu of driving load on one side. Torque balances the direct energy consumption and less deviations. Also dramatically reduces the size and weight of the unit.

An object of the present invention is to drastically reduce the size and weight of such a unit. An additional objective is to use smaller gears that can be produced with the most efficient methods. Another object is to provide a design which in many cases can be used alone aa drive shaft end in place of a separate sleeve and independently journalled for mounting the drive gear and a shaft journalled independently coaxial therewith, which carries the work items. A further object is the ability to easily convert use modified equipment that requires a different gear ratio, by changing a pair of coaxial drive sprockets and the distance cylindrical center. An additional objective is to drive a shift from the drive shaft end and arranged at right angles to the same electric motor. Another object is to provide a more compact design by mounting the electric motor between the pair of cylindrical drive sprockets. Other objects will appear in the course of the specification and in the preamble to the appended claims.The invention is described with reference to the drawings, which relate to a large mixer unit, and where. Figure 1 is a cross section taken at right angles to the axis of the power consumer, here the axis of the mixer shaft.. Figure 2 is a front elevational view thereof, and a section taken along lines 2 - 2 of FIG. 1.. Figure 3 is a reduced scale view looking along the axis of the mixer shaft power consumer, showing a plurality of working parts equally spaced around said axis.. Figure 4 is a sectional view similar to FIG. 1 showing a drive motor positioned differently.. Figure 5 is a sectional view taken along and lines 5-5 of FIG. 6, illustrating a modification.. Figure 6 is a side view and partly a section of it, looking in the direction 6-6 of Fig. May.Referring now to FIGS. 1 and 2, the electric motor 10 drives a pair of coaxial cylindrical pinions 11, 12 are integrally formed together. Helical teeth contain equal and opposite hand lead, and are mounted for axial self-adjusting roller bearings 13, 14. Actuation of the motor 10 allows small axial movements with minimal frictional resistance, so that their teeth are equal loads. The unit specifically is shown via one or more thin steel discs 15. These are fixed on the outer periphery towards the motor shaft, and on the inside to the sprocket member 11, 12 by means of a fixed coupling side.According to the invention, torques applied to the equality of the two pinions 11, 12 are transmitted to a common final drive gear through separate channels to exert a torque thereon essentially pure.The helical pinions 11, 12 mesh with helical gears 16, 17, respectively, whose axes are parallel to the axis of pinions 11, 12 and intersect the axis 18 of the final drive gear 20 at right angles. Gear 20 is a cylindrical gear, either with straight or helical teeth. Is attached to a sleeve 21 hinged in practice known in a pair of axially spaced bearings (not shown). This is rotated by a pair 22, 23 of cylindrical coupling pinions placed in diametrically opposite sides of gear 20. Their axes are parallel to axis 18. 22 receives the movement pinion gear 16 through a pair bevelgear 24, 25, while sprocket 23 is rotated by gear 17 through a pair bevelgear 26, 27.Sleeve 21 is connected to and encloses the main shaft 30 which extends vertically in the middle to be acted upon. . Figure 3 is a reduced-scale schematic view of the shaft 30 and the workpieces 31. They are equally spaced around the axis 18. In the known design mentioned shaft 30 is mounted in spaced bearings independently. The various parts 31 exert equal near a pure torque on the shaft 30. This pair is balanced by something like a pure driving torque exerted on the final drive gear 20 diametrically opposed pinions 22, 23.The absence of a load driving minimizes sided carrying loads and much reduces shaft deflections. In many cases it is feasible to do away with the sleeve 21 and to use only a main shaft 30. This simplifies the design and reduces the cost.

The use of paired helical gears in the first reduction stage enables the engine placed in a position suitable support. It also allows the team to be changed to a different speed, changing the coaxial gear pair 11, 12 while leaving your gears 16, 17 only, and the configuration of the drive shaft in a parallel position. An increase or decrease in the center distance decreases or increases the reduction ratio respectively.The embodiment illustrated in FIG. Figure 4 shows the electric motor 10a coaxial positioned between sprockets 11a, 12a. These sprockets are secured on opposite sides of the motor housing in the common motor shaft which is mounted on the engine frame of ball bearings 13a, 14a. These are made with a slight axial play. Cylindrical roller bearings could also be used instead.In a slight modification, not illustrated, the motor shaft is a sleeve with internal grooves extending in axial direction. Pinion shaft extends into the interior thereof and has corresponding external grooves. Balls in said grooves connecting the sleeve and the shaft and provide the necessary axial freedom.A totally different embodiment will now be described with Figs. 5 and 6. Here loads equal in the two arms of the unit are achieved by using a motor having counter-rotating elements. While the conventional engine has a stator and a rotor, the motor used here have two opposite rotational rotors. What was the stator before now becomes the opposite direction of the original rotor. Such counter-rotating engines are known techniques.A opposite rotational speeds, for example 1800 rpm the electrical effect is the same as if a conventional engine were in turn to 3600 rpm This engine is much smaller than a conventional motor rotating at 1800 rpm Moreover, if the engine is the size of a conventional motor rotating at 1800 rpm, its two elements, only spin at 900 rpm, and save a 1:02 reduction step on the train.The torque transmitted to each of the counter-rotating members is exactly opposite and equal. Does not require opposite hand helical gears to accomplish this.The engine 40 comprises counter-rotating coaxial parts 40a, 40b made of any suitable known manner. Part 40a of the rotor is shown embracing the inner rotor 40b. Pinions rotating parts 11b, 12b equally in opposite directions. They show very schematically in FIGS. 5 and 6 and are rotatably mounted on a slide 45. The spur gears 11b, 12b are fixed to the ends of shafts 46, 47. Setting the slide 45 to change the sprocket size and thus the relationship.The sprockets 11b, 12b mesh spur gears coaxial with 16b, 17b whose axis intersects the axis 50 of the final drive gear 51 at right angles and parallel to the axis of the sprockets 11b, 12b. Rigidly connected to the gears 16b, 17b are spiral bevel gears 52, 53, respectively. They fit in with the same transmission rate end 51, here spiral bevel gear.Only a double reduction is used in this case illustrated. But triple reduction could also be used if desired.While the invention has been described in connection with several embodiments thereof, it should be understood that it is capable of much more modification. For the definition of its scope was based in the appended claims.


Post a Comment