SU1727625A1 - Pneumatic centrifugal distributing apparatus - Google Patents

Abstract

Use: distribution of bulk materials in the pipelines for crops. SUMMARY OF THE INVENTION: The feeder 7 is made in the form of a curved tube, with the outlet 9 located from the axis of rotation of the feeder 7 at a distance that is not less than twice the diameter of the outlet 9 of the feeder 7, and the axis of the channel of the feeder 7 is in the same plane. Descent of the fat from the outlet 9 takes place in the zone of the horizontal diameter of the outlet 9, while the angular velocity of the disk 4 is greater than the angular velocity of the feeder 7. 4 Il.

Description

The invention relates to agricultural machinery, namely, devices for the distribution of bulk materials, and can be used in fat fertilizers.

w Draft area - an increase in the equilibrium distribution of the material along the discharge channels.

FIG. 1 shows a pneumatic-centrifugal distributor, transversal cut; in fig. 2 shows section A-A in FIG. one;

in Fig. $ feeder axonometry; in fig.

-pattel, longitudinal section.

The pneumatic-centrifugal distribution apparatus contains (Fig. 1, 2) a metering hopper 1, a housing 2 with discharge channels 3, a tapered centrifugal disk 4 with blades 5, a ring 6 fixed on the blades 5, a feeder 7 designed so that its inlet 8 (FIG. 4, 3) with diameter d is coaxial with the disk 4, and the outlet 9 is located at a distance R from the axis of rotation 10, moreover R 2d. The feeder 7 is made in the form of a curvilinearly narrowing tube, the bottom forming 11 which is otor curvilinear (Fig. 4). The heating pipe 12 connects the fan 13 to the housing 2. The vanes 5 are curved. The ring b is located in a plane perpendicular to the axis of rotation 10. The inner edges of the blades 5 are bent against the rotation of the disk 4, and the outer edges are bent in the direction of rotation. Feeder 7 has the ability to rotate at different speeds 0) 1 with respect to the angular velocity of the disk 4, and hell.

Fertilizer or other bulk material from the hopper 1 enters the inlet 8 of the rotary with the angular velocity of the feeder 7 and interacts with its inner surface. As the material particles enter the feeder 7 over the entire cross section of the inlet 8, part of the particles interacts with the inner surface of the feeder 7 in its upper part (point A), and other particles move down under gravity until it touches the inner surface of the feeder 7 (Fig. 3). The greatest distance from the inlet 8 will be particles that fall into point B located on the inner surface of the feeder 7. The bulk of the bulk particulate material interacts with the inner surface of the feeder 7 on the plane enclosed between the plane of the inlet 8, to the cross-section plane of the feeder 7, passing through point B, and the particles of the bulk material will interact both with the internal curve 11 and with other points of the internal surface of the rotating feeder 7.

Depending on the position of the particle

on the inner surface of the feeder 7 with respect to the transverse-vertical plane E passing through the axis 10 of rotation, the inertia forces acting on the particles will have a different direction.

At the point A, the angle between the vectors of the angular (portable) () l relative vr velocity is zero and, therefore, FK 0. On the inner surface of the feeder 7 from the plane of the inlet 8 to the plane E, the centrifugal force Rc and the projection onto the normal of the Coriolis force FK press the particle to the inner surface of the feeder 7. The shape of the feeder 7 is chosen in such a way

so that the force of gravity, its projection on the tangent to the inner surface in the longitudinal-vertical plane exceeds the force of friction from the action of the forces Rc, FK and the normal component of the force of gravity mg.

Due to the effect of gravity, the particles move downwards. In this case, the trajectories of the particles are shifted from the middle longitudinal-vertical plane towards the direction of the vector of the circumferential

speed v0 feeder 7.

Particles entering the inner surface of the feeder 7 at point C move along its surface under the action of the rolling force — the projection of the force of gravity on the tangent to curve 11 and the Coriolis force, since the force Rc is zero.

After the passage of the particles of the plane E, the centrifugal force of inertia Rc, for example, at point B tends to tear off

the particle from the inner surface of the feeder 7, and the Coriolis inertia force Pk and the force of gravity mg tend to press the particles against the inner surface of the feeder 7.

Coriolis inertia action

FK causes a displacement of particles from the middle longitudinal-vertical plane in the direction of the vector of peripheral velocity v0. Since the vectors Pk and v0 at the top

the feeder 7 coincide from the inlet 8 to the plane E, and in the lower part from the plane E to the outlet 9 is directed in different directions, the particles entering the inner surface

The feeder 7 at the top moves along complex curves, displaced to one side from the middle longitudinal-vertical plane. The point of exit of particles from the hole 9 depends on the ratio of the lengths of the sections and

the initial rate of entry of particles onto the inner surface of the feeder 7.

Particles entering the inner surface of the feeder 7 behind the plane E, due to the Coriolis force of inertia FK, will be displaced from the middle longitudinal-vertical plane in the direction opposite to the direction of the vector of peripheral velocity v0. The magnitude of the particle displacement from the median longitudinal-vertical plane depends on the curvature of the inner surface of the feeder 7, the feed rate of the particles to the feeder 7 and the angular velocity of rotation of the feeder 7.

Due to the continuous movement along the inner surface of the feeder 7 along spiral curves of different lengths, converging at one end of the horizontal diameter of the outlet hole 9 of the feeder 7, the particles exit from the hole 9 in a continuous flow.

With a distance R from the axis of rotation 10 to the hole 9 of at least 2d, the difference in absolute velocities of particles from the feeder 7 does not exceed 3%. This makes it possible to ensure a uniform circular flow of particles onto the blades 5 of the centrifugal disk 4, both at the horizontal and at the inclined (up to 10 °) position of the pneumo-centrifugal distributor.

At the exit of the feeder 7, particles acquiring radial and circumferential speeds fall on the inner edges of the blades 5 of the disk 4, which rotates in the opposite direction with angular velocity (tfi, and due to the fact that the inner edges of the blades 5 are bent against the rotation of the disk 4, their braking, i.e. smooth

reduction in peripheral speed. It also contributes to the further alignment of the distribution of the material around the circumference, as well as reducing the fragmentation of particles. Moving along the curvilinear surface of the blades 5, they change the direction of their circumferential speed, accelerate, move away from the outer crumb of the blades 5 and fall into the discharge channels 3 of the housing 2. Due to a decrease in the cross-section of the interscapular space towards the periphery of the disk 4, this is provided conical a disk and a ring 6 located on the blades 5 in a plane perpendicular to the axis of rotation 10, when the disk 4 is rotated, an air flow is created. This flow contributes to a uniform flow of material particles to the exhaust ducts 3 around the circumference and directs the flow of air from the injection nozzle 12 from the fan 13 to the exhaust ducts.

Claims (1)

Invention: Pneumatic-centrifugal switchgear, comprising a housing with discharge channels, a fan, the discharge pipe of which communicates with the housing cavity, a centrifugal disk with blades, over which a ring is installed, and a feeder, characterized in that, in order to increase the uniformity of distribution of the material along the outlet feed channels, the feeder is made in the form of a curvilinear tapered pipe, the axis of which is located in the same plane with its axis of rotation, and the distance from the axis of rotation of the feeder to the output STI is greater than or equal to twice the diameter of the inlet feeder.