SU1268825A1 - Blade pump - Google Patents

Description

that the TC coincides with the openings 14 and the liquid from the high-pressure region is injected through the TC into the zone of the root section of the CC 7, which informs the main flow velocity in the direction of rotation of the CC 7 and leads to a decrease in the relative velocity of the main flow. By varying the flow rate and speed of the injected fluid, it is possible to achieve such a distribution of the preliminary spin along the radius of the ballast chamber 7, so that the pump will work practically without reverse currents at the inlet. 2 or ..

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The invention relates to pumpostronium.

The aim of the invention is to increase the intake capacity and efficiency for pony costs by decreasing the inrush currents at the input.

Figure 1 shows the blade pump, a longitudinal section; in Fig.2 a section aa in Fig.1.

The vane pump comprises a housing 1 and a front support 2 arranged therein, made in the form of a cowl 3 and shell 4 with a bearing 5, which form a cavity 6 in communication with the high pressure region of the pump. In case I, there is also installed a screw wheel 7 with a sleeve 8 having a shank 9 installed in: bearing 5. The front bearing 2 is provided with a spring-loaded ring 10 with blades 11 of a symmetrical profile and tangential channels 12 directed in the direction of rotation of the screw wheel 7, and the ring 10 is installed on the side 4 with the possibility of rotation. The shank 9 has longitudinal grooves 13, and in the shell 4, under the ring 10, there are radial holes 14, which communicate the cavity 6 of the support 2 with tangential channels 12. The support 2 is fixed on the pylons 15..

The vane pump works as follows.

On operating modes without reverse currents at the input, when the expenditure parameter q о, 5 {, is the angle

tp.p

blades and angle of attack, respectively), the blades 11 are located strictly behind the pylons 15, almost without increasing the hydraulic resistance at the entrance to the auger wheel.

- this ring 10 under the action of the spring occupies an extreme position, blocking the radial holes 14, with the result that the cavity 6 and the tangential 5 channels 12 are separated.

At lower costs (under-load conditions), when the consumption parameter, 5, on the periphery of the housing I, in front of the screw wheel 7, reverse currents appear, directed against the main flow and twisted in the direction of rotation of the screw wheel. As a result of the interaction of the reverse currents with the blades I1 on the last 15, a circumferential force occurs, under which the ring 10, overcoming the spring resistance, rotates so that the tangential channels 12 coincide with the radial holes 20 4 in the shell 4. Then the fluid from the region high pressure of the pump, for example, due to the impeller (not shown) through the axial channel in. the sleeve 8, the cavity 6, the bearing 5, 25, the longitudinal grooves 13 and the holes 14 are fed into the tangential channels (nozzles) 12, through which it is injected.; the radial 30 protrusions between the longitudinal grooves 13 form as if an additional safety wheel, which contributes to an increase in the pressure of the fluid in front of the radial orifices 14. 35 The tangential injection of the ejecting fluid in the direction of rotation of the auger wheel 7 indicates the speed (pre-twist) in the direction of rotation Radd scheni screw wheel, which reduces the angle of attack "and a decrease of the relative speed of the basic stream. In this case, the maximum

the twist of the main flow, and consequently, the greatest decrease in the angle of attack, takes place in the root sections of the screw wheel near the injection site of the ejecting fluid. As the bushing wheel moves away from the bushing to the periphery of the screw, the primary twist sharply drops to zero, so that in the middle and peripheral sections of the screw wheel the angles of attack practically do not change.

By varying the flow rate and speed of the injected fluid, it is possible to achieve such a distribution of the preliminary spin along the radius of the auger wheel, that in all its sections from the sleeve to the periphery the condition, 5, i.e. the pump operates with almost no reverse currents at the input. Since the latter are the main reason for the deterioration of the suction capacity and efficiency of the pump, as a result of their decrease, the suction capacity and efficiency of the pump are worse.

As the size and intensity of the reverse currents decrease, for example, as a result of increasing q (q 0.5), the circumferential force arising on the blades x 11 decreases and under the action of the spring the ring 10 rotates, partially blocking the flow section of the tangential channels 12. by reducing the flow rate of the injected fluid, the distribution of the preliminary spin of the main flow along the radius of the auger wheel remains close to optimal, i.e.

condition 5 is provided. one

When the flow through the pump increases, when the inlet currents disappear (q 0.5), the ring 10 under the action of the spring takes up its original position at which the radial holes 14 close and the injection of the ejecting fluid through the tangential channels 12 stops.

Claims (1)

Invention Formula Vane pump, comprising a housing and a front support housed therein, made in the form of a fairing and a shell with a bearing, forming A Q cavity in communication with the high pressure area of the pump and a screw wheel with a sleeve having a shank mounted in the bearing, characterized in that To increase the suction capacity and efficiency at lower costs by reducing the reverse currents at the inlet, the front support is equipped with a spring-loaded ring with symmetrical blades  profile and tangential channels directed in the direction of rotation of the auger wheel mounted on the sidewall can be rotated, while the longitudinal grooves are made on the shank, and the radial holes are in the shell under the ring, communicating the support cavity with tangential channels.