UA18363U - Two-side inlet pump - Google Patents

Abstract

Two-side inlet pump has stator and rotor sections, at that the stator section has a body with hydraulic cavity, inlet and pressure branch pipes, and covers, and the rotor section has a shaft with working wheel with two-side inlet, this is connected to the stator section with slide bearings and end gasket, at that at both sides of the working wheel and the stator section radial gap is formed. The pump has two same units for axial force relief, those are placed at two sides of the working wheel and are two rings one of which is installed at the outer side of the inlet to working wheel, and the other ring is placed in front of the first one on stator section, with formation of end throttle slot between those, and slide bearings placed in the covers of the body, circular cavity of those is connected by channels with pressure section of hydraulic cavity of the pump. The end gasket is installed at the side of torque transfer.

Description

Description of the invention

The declared technical solution, a two-way inlet pump, belongs to the field of mechanical engineering and can be used in pumps with a semi-spiral feeder and a spiral diverter with a two-turn spiral, for example: in second lift condensate, low-pressure emergency pumps, two-way inlet pumps, as well as in lace pumps.

A well-known pump with two-way inlet type D |1), which has a casing with a hydraulic cavity, inlet and pressure nozzles and a cover installed on the casing. The body and cover have a common horizontal connector with a 70 gasket between the flanges. End seals are built into the body on both sides. The rotor part has a shaft with a two-way input impeller, and it is connected to the stator part by bearings installed in the remote part (outside the housing) on both sides of it.

Such a case has a number of structural flaws that negatively affect the technical result. Thus, the horizontal connector is eroded during the operation of the pump, in addition, when pumping liquid with a high 12 temperature, the connector is subject to internal forces arising both in the case and in the cover.

The above reasons lead to a violation of the tightness of the connection and, as a result; leakage of pumped liquid appears. The use of ball bearings ensures a short service life and they are used in pumps with low power. Installing bearings outside the housing increases the distance between the supports, which leads to shaft deflection, vibration and wear of the end seals. This also leads to depressurization of the pump.

A series of pumps |2, 3, 4, 5) is also known, in which there is a horizontal connector between the housing and the cover, the end seals are located in the housing, and the external sliding bearings are installed with radial thrust bearings.

Such pumps are designed for higher loads than the previously described pump. But all the shortcomings described above also belong to this series of pumps. In addition, the use of sliding bearings and radial thrust bearing increases and complicates the design of the unit and does not eliminate the disadvantages of reducing the distance between the supports. Along with the disadvantages, the specified pumps have an important advantage - a hydraulic cavity with a well-calculated and designed semi-spiral feeder and a spiral diverter with a two-turn spiral in the pump body

Taking into account the positive qualities and to eliminate the listed shortcomings, the task was set to design and manufacture a pump of an improved design by reducing the distance between the supports of the sliding bearings and without a horizontal connector between the body and the cover, without disturbing the existing and practically tested geometry pump housing.

To solve the problem, a two-way inlet pump is proposed, which has a stator and a rotor part, while the stator part contains a housing with a hydraulic cavity, inlet and pressure nozzles, and a cover, and the rotor part includes a shaft with a two-way inlet impeller and is connected to the stator part with sliding bearings and an end seal, while a radial gap is formed on both sides of the impeller and the stator part.

The proposed technical solution differs from the known ones in that the pump has two identical nodes for unloading the axial force, located on both sides of the impeller, and are two rings, "one of which is installed on the outside of the entrance to the impeller, and the other ring is located opposite of the first, Z 740 on the stator part, forming an end throttling gap between them, in addition, the sliding bearings, c are placed in the housing covers, the annular cavity of which is connected by a channel with the pressure part of the hydraulic c" cavity of the pump, in addition, the end seal is installed with side of the torque transmission.

Distinctive features of the two-way inlet pump have a number of positive qualities that affect the technical result, namely: - the pump has two identical axial force unloading nodes. The presence of two identical nodes - unloading of the axial force, allows you to compensate for the axial force caused by the operation of the pump, both from one and from

Ge | on the other hand, in relation to the impeller. The reason for the appearance of the axial force can be the heterogeneity of the pumped liquid, mechanical impurities in it and the imperfection of the geometry of the flow part of both the body and the impeller; b 20 - unloading nodes are located on both sides of the impeller. Thus, the axial force generated on the wheel is compensated directly near the wheel. This means that the resulting axial force c» acts on the shaft only in the area of the wheel. This force does not act on the other part of the shaft; - unloading nodes are two rings, one of which is installed on the outside of the entrance to the impeller, and the other ring is located opposite the first one, on the stator part. This design is the most simple and technologically implemented. Nodes work like a thrust bearing; c - installed rings form an end throttling gap between themselves. The specified gap is a gap of such a size that is necessary for the movement of the rotor part when compensating the axial force.

Therefore, the presence of a throttling gap between the rings and a radial gap between the stator part and the wheel allowed the thrust bearing to be aligned with the unloading device for the axial movement of the shaft 60 (hydro heel); - sliding bearings placed in the housing covers. This allows you to reduce the distance between the axes of the supports, which increases the rigidity of the shaft and eliminates or reduces its deflection. Positively affects the vibration and noise characteristics of the entire pump; - the annular cavity of which is connected by a channel to the pressure part of the hydraulic cavity. Since the pressure in the bo hydraulic cavity of the discharge part is greater than in any part of the hydraulic cavity,

a certain amount of pumped liquid flows through the annular cavity of the slide bearing.

Thus, both bearings are lubricated and cooled; - the end seal is installed on the side of the torque transmission. This made it possible to simplify the design of the pump, reduce its dimensions and weight, since one end of the shaft has an end seal, and the other end of the shaft is shortened and closed with a cover.

The distinguishing features listed above are necessary and sufficient to solve the problem. All distinguishing features are in a cause-and-effect relationship with the obtained result and allow at a high technical level to create a construction of a two-way inlet pump, in which thrust bearings are structurally placed with a hydraulic heel, the action of which is aimed at balancing axial forces. In addition, sliding bearings are built directly into the housing covers. This arrangement gives the shaft rigidity. Compared to known pumps, the claimed pump is reduced in size and weight.

The essence of the technical solution is explained by the drawings:

Figure 1 shows a two-way inlet pump (section view).

In Fig. 2 - footnote I.

In Fig. 3 - footnote II.

In Fig. 4 - footnote II.

The two-way inlet pump has a stator and a rotor part. The stator part has a body 1 with a hydraulic cavity, with inlet 2 and pressure nozzles (the pressure nozzle is not shown in Fig.) and covers 3, 4. The rotor part 2o contains a shaft 5 with an impeller 6 of two-way input. Shaft 5 is connected to the stator part by sliding bearings 7, 8 and an end seal 9. The pump is equipped with two identical axial force unloading units. Nodes are two rings 10, 11 and 12, 13 of the thrust bearing. Rings 10, 12 are stationary, fixed in the body, and rings 11, 13 are mobile, relatively stationary 10, 12, mounted on the wheel. Rings 10, 11 and rings 12, 13 were formed between each other along the throttling gap 14, 15, and a radial gap 16, 17 was formed on both sides of the impeller b and the stator part. Annular cavities 18, 19, sliding bearings 7, 8, zv' connected by channels (not shown in Fig.) with the pressure part of the hydraulic cavity t of the pump. An end seal 9 is installed on the open side of the shaft.

The two-way inlet pump works as follows.

The pumped liquid enters the inlet pipe 2, then the impeller 6 of the two-way inlet moves clockwise along the semi-spiral feeder. When rotating, the wheel 6 under the action of centrifugal force gives the pumped liquid additional energy, and the liquid is directed to the pressure nozzle through the spiral diverter with a double-turn spiral. At the same time, part of the working fluid that came out of the impeller 6 passes through the throttling slits 14, 15 at the end through the radial gaps 16, 17. Thus, the movable and fixed rings 11, 13 and 10, 12, which formed the throttling slits 14, 15 , are thrust bearings that absorb the axial force acting on the rear part. Together, the throttling slits 14, 15 and the radial gaps 16, 17 act as a hydraulic heel, which in "- automatic mode self-sets the working wheel b in the optimal position. Thus, when the axial force acts on the rotor from right to left, the impeller shifts along the axis of rotation to the left - the end throttling gap 15 decreases. As a result, in the cavity between the end throttling gap 15 and the radial gap 17, the fluid pressure increases, which opposes the axial force. In an emergency situation, when the hydraulic pump does not have time to react and counteract the axial force, the ring 13, installed on the working wheel 6, abuts against the ring 12, located on the stator part. Thus, rings 12, 13 work as a thrust bearing, and rings 10, 11, . on the right side, formed an enlarged throttling gap 14. Therefore, on the right, in the cavity between the throttling gap and? 14 and the radial gap 16, the liquid is under reduced pressure and contributes to the movement of the rotor to the right.

When moving the rotor to the right, the right part works, i.e. rings 10, 11, throttling gap 14 and radial gap 16. At the same time, the left part is unloaded and thereby contributes to the mitigation of the force - moving the rotor.

In this way, self-regulation of the position of the impeller in the pump is ensured. because At the same time, the working fluid from 2) the pressure part of the hydraulic cavity is supplied to the annular cavity 18, 19 of the sliding bearings 7, 8 through the channels. This happens due to the difference in pressure in the pressure part of the 5or sub-hydraulic cavity and the part of the hydraulic cavity with lower pressure. Therefore, the pumped liquid

Me. provides lubrication and cooling of sliding bearings built into the housing covers. 4) On the side of the output of the shaft 5 from the pump, the end seal 9 prevents the flow of liquid along the shaft.

Thus, the proposed two-way inlet pump is made with a new design solution, namely: sliding bearings are built into the housing covers, thrust bearings are placed directly close to the impeller, while they are combined with the hydraulic heel.

Compared to pumps of the same type, the claimed pump is more technological in manufacturing, easier to assemble, adjust and more reliable in operation.

Sources of information: 1. Marcinkovsky V.A., Vorona P.N. "Pumps of nuclear power stations", M, "Znergoatomizdat" 1987, p. 75, because fig. 2.39. 2. Mykhaylov A.N., Malyushenko V.V. "Pump the vane!" M., "Mashinostroenie", 1977, p. 225, fig. 130.

Z. Marcinkovsky V.A., Vorona P.N. "Pumps of nuclear power stations", M, "Znergoatomizdat" 1987, p. 49, fig. 2.13. 4. Marcinkovsky V.A., Vorona P.N. "Pumps of nuclear power stations", M, "Znergoatomizdat" 1987, p. Fig. 70, 65 2.34. 5. Marcinkovsky V.A., Vorona P.N. "Pumps of nuclear power stations", M, "Znergoatomizdat" 1987, p. 78,

Fig. 2.42 - prototype.

Claims (1)

The formula of the invention A two-way inlet pump containing a stator and a rotor part, and the stator part includes a body with a hydraulic cavity, inlet and pressure nozzles, and covers, and the rotor part includes a shaft with a two-way inlet impeller, connected to the stator part by sliding bearings and end seal 70, while a radial gap is formed on both sides of the impeller and the stator part, which is distinguished by the fact that the pump contains two identical axial force unloading units located on both sides of the impeller, and are two rings, one of which is installed on on the outside of the entrance to the impeller, and the other ring is placed opposite the first one, on the stator part, forming an end throttling gap between them, and the sliding bearings are placed in the housing covers, the ring cavity of which is connected by a channel to the pressure part of the hydraulic cavity of the pump, before the end seal is installed on the side of the torque transmission. that 2 (ze) (Se) (ze) (ee) yo - and? - (ee) (95) (o) syu" 60 b5