SU1272004A1

SU1272004A1 - Double-entry centrifugal pump

Info

Publication number: SU1272004A1
Application number: SU853919303A
Authority: SU
Inventors: Артур Михайлович Кац; Леон Ильич Файнберг; Павел Родионович Хлопенков; Николай Степанович Яловой
Original assignee: Предприятие П/Я М-5356
Priority date: 1985-04-24
Filing date: 1985-04-24
Publication date: 1986-11-23

Abstract

Изобретение относитс к области насосостроени и может быть использвано в центробежных насосах двустороннего входа . Цель изобретени - повышение ресурса работы путем разгрузки подшипников (П) от действи остаточных неуравновешенных осевых сил, вызванных неточностью изготовлени . В отводе 2, на его внутренней поверхности, установлена перегородка 8, дел ща его на две равные части. Перего-; родка 8 размещена с зазорами The invention relates to the field of pump construction and can be used in centrifugal pumps of double inlet. The purpose of the invention is to increase the service life by unloading bearings (P) from the effect of residual unbalanced axial forces caused by inaccuracy of manufacture. In tap 2, on its inner surface, a partition 8 is installed, dividing it into two equal parts. Negotiation; rod 8 is placed with gaps

Description

Изобретение относится к иасосостроениюThe invention relates to iasosostroenie

И может быть йспользойано в центробеж-;And it can be used in a centrifugal;

Пых насосах двустороннего входа, в которых требуется полная разгрузка подшипников ротора от действующих на них осевых сил.Fifth double-entry pumps, in which complete unloading of the rotor bearings from the axial forces acting on them is required.

Цель изобретения — повышение ресурса ⁵работы путем разгрузки подшипников от действия остаточных неуравновешенных осевых сил, вызванных неточностью изготовления.The purpose of the invention is to increase the service life ⁵ by unloading bearings from the action of residual unbalanced axial forces caused by manufacturing inaccuracies.

На чертеже изображен центробежный на- ю сос двустороннего входа, продольный разрез.The drawing shows a centrifugal pump with a bilateral entrance, a longitudinal section.

Насос содержит корпус 1 с отводом 2 и подводами 3 и установленный в нем ротор 4, опирающийся на подшипники 5 и включающий рабочие колеса 6, обращенные друг к другу ведущими дисками 7. В отводе 2 '5 установлена перегородка 8, делящая его на две равные части, закрепленная на внутренней поверхности отвода 2 и размещенная с зазорами δι и δ₂ относительно ведущих дисков 7 колес 6. При этом поверхностями колес 6 и перегородки 8 образована камера 9, сообщенная с подводами 3 и посредством зазоров 61 и δ₂ с отводом 2. В роторе 4 выполнены каналы 10, сообщающие подшипники 5 с камерой 9. Последняя сообщена с подводами 3 каналами 10 и II. 25The pump comprises a housing 1 with a branch 2 and inlets 3 and a rotor 4 mounted therein, resting on bearings 5 and including impellers 6 facing each other by the driving discs 7. A partition 8 is installed in the branch 2 '5, dividing it into two equal parts mounted on the inner surface of the outlet 2 and placed with gaps δι and δ ₂ relative to the driving disks 7 of the wheels 6. At the same time, the surfaces of the wheels 6 and the partition 8 form a chamber 9 connected with the inlets 3 and through the gaps 61 and δ ₂ with the outlet 2. B rotor 4 made channels 10, communicating bearings Iki 5 with camera 9. The latter is communicated with inlets 3 channels 10 and II. 25

Центробежный насос работает следующим образом.Centrifugal pump operates as follows.

Перекачиваемая среда, переходя через подводы 3 и рабочие колеса 6, выбрасывается в отвод, разделенный перегородкой 8 на две равные части. При этом часть 30 перекачиваемой среды через зазоры δι и δ₂, образованные ведущими дисками 7 колес 6 и перегородкой 8, проходит через кольцевую камеру 9 и каналы 10 в роторе 4 к подшипникам 5, обеспечивая тем самым их нормальную работу, и через каналы 11 в 35 подводы 3. При наличии остаточной неуравновешенности осевых сил ротор 4 с колесами 6 смещается, и величины зазо ров δι и 6₂ изменяются. При этом гидрав· лическое сопротивление и потери в мень? шем зазоре увеличиваются, а в большем зазоре уменьшаются. Это приводит к тому, что скорость течения жидкости в меньшем зазоре уменьшается, а давление увеличивается по сравнению с большим зазором. Такое распределение давлений вызывает возникновение результирующей осевой силы, направленной в сторону меньшего зазора. Зазоры δι и бу₂ при этом выравниваются. Следовательно, ротор 4 насоса постоянно находится в состоянии динамического равновесия, т.е. остаточная неуравновешенность осевых сил ввиду технологических неточностей изготовления насоса в предлагаемой конструкции отсутствует, а следовательно, уменьшается износ подшипников и увеличивается ресурс работы насоса.The pumped medium, passing through the inlets 3 and the impellers 6, is thrown into the outlet, divided by a partition 8 into two equal parts. Moreover, part 30 of the pumped medium through the gaps δι and δ ₂ formed by the driving discs 7 of the wheels 6 and the baffle 8 passes through the annular chamber 9 and the channels 10 in the rotor 4 to the bearings 5, thereby ensuring their normal operation, and through the channels 11 35 inlets 3. In the presence of residual imbalance of axial forces, the rotor 4 with wheels 6 is displaced, and the clearances δι and 6 ₂ change. In this case, hydraulic resistance and losses in less? then the gap increases, while in the larger gap they decrease. This leads to the fact that the flow rate of the liquid in the smaller gap decreases, and the pressure increases compared to the large gap. Such a distribution of pressures causes the appearance of a resulting axial force directed towards a smaller clearance. The gaps δι and boo ₂ are aligned. Therefore, the rotor 4 of the pump is constantly in a state of dynamic equilibrium, i.e. the residual imbalance of axial forces due to technological inaccuracies in the manufacture of the pump in the proposed design is absent, and therefore, the wear of the bearings decreases and the service life of the pump increases.

Claims

The invention relates to pump engineering. I can be used in centrifugal-; Puff double-entry pumps, which require complete unloading of the rotor bearings from the axial forces acting on them. The purpose of the invention is to increase the service life by unloading bearings from the effect of residual unbalanced axial forces caused by inaccuracy in the manufacture. The drawing shows a centrifugal pump of double-sided inlet, longitudinal section. The pump comprises a housing 1 with a branch 2 and supply lines 3 and a rotor 4 mounted therein, resting on bearings 5 and including impellers 6 facing each other by drive disks 7. In branch 2 a partition 8 is installed, dividing it into two equal parts, fixed on the inner surface of the outlet 2 and placed with the gaps 6i and 62 relative to the driving discs 7 of the wheels 6. In this case, the surfaces of the wheels 6 and the partition 8 are formed by a chamber 9 communicated with the inlets 3 and by means of the gaps 6 and 62 with the outlet 2. In the rotor 4 channels 10 are made, informing the bearing 5 with the cam 9. The latter communicates with the inlets 10 and channels 3 II. The centrifugal pump operates as follows. The pumped medium, the passage through the inlets 3 and the impellers 6, is thrown into the outlet divided by the partition 8 into two equal parts. In this part of the pumped medium through the gaps 6i and 62, formed by drive disks 7 wheels 6 and a partition 8, passes through the annular chamber 9 and the channels 10 in the rotor 4 to the bearings 5, thereby ensuring their normal operation, and through the channels 11 in the inlets 3 In the presence of residual unbalance of axial forces, the rotor 4 with the wheels 6 is displaced, and the magnitudes of the gaps 6 | and H2 are changed. At the same time, the hydraulic resistance and losses in the smaller gap increase, and in the larger gap decrease. This leads to the fact that the flow rate of the fluid in the smaller gap decreases and the pressure increases as compared with the larger gap. This distribution of pressures causes the resultant axial force to be directed towards a smaller gap. The gaps 6i and 6yi are equalized. Therefore, the rotor 4 of the pump is constantly in a state of dynamic equilibrium, i.e. The residual imbalance of the axial forces due to technological inaccuracies in the manufacture of the pump in the proposed design is absent, and consequently, the wear of the bearings decreases and the service life of the pump increases. Claims 1. A centrifugal two-way inlet pump comprising a housing with an outlet and outlets and a rotor mounted therein, supported by bearings and including impellers facing one another with driving disks, characterized in that. in order to increase the service life by unloading the bearings from the effect of residual unbalanced axial forces caused by inaccuracy of manufacture, a baffle is installed in the elbow, dividing it into two equal parts, fixed on the inner surface of the elbow and accommodated with gaps A wheel is formed between the wheels and the partition, communicating with the leads and by means of gaps with taps.

2. A pump according to claim 1, characterized in that channels are made in the rotor, which communicate bearings with the chamber.