WO2017156933A1 - Système de rinçage résistant aux hautes pressions doté de plusieurs joints d'étanchéité mécaniques - Google Patents

Système de rinçage résistant aux hautes pressions doté de plusieurs joints d'étanchéité mécaniques Download PDF

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Publication number
WO2017156933A1
WO2017156933A1 PCT/CN2016/089301 CN2016089301W WO2017156933A1 WO 2017156933 A1 WO2017156933 A1 WO 2017156933A1 CN 2016089301 W CN2016089301 W CN 2016089301W WO 2017156933 A1 WO2017156933 A1 WO 2017156933A1
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Prior art keywords
pressure
pump
high pressure
pump casing
mechanical seals
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PCT/CN2016/089301
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English (en)
Chinese (zh)
Inventor
邢宇
邢天宜
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邢宇
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Publication of WO2017156933A1 publication Critical patent/WO2017156933A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/70—Suction grids; Strainers; Dust separation; Cleaning
    • F04D29/708—Suction grids; Strainers; Dust separation; Cleaning specially for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/086—Sealings especially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/426—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/70—Suction grids; Strainers; Dust separation; Cleaning

Definitions

  • the invention relates to a shaft seal flushing system for a centrifugal pump.
  • it relates to a multi-stage and multi-set mechanically dense series connection to form a step-by-step pressure reduction high pressure flushing system with multiple sets of mechanical seals.
  • FIG. 1 and 2 are schematic diagrams of a prior art 2CW-CW buffered double-contact wet seal, which is a schematic diagram of a buffer flushing system without pressure (communicating with the atmosphere) and capable of circulating (Fig. 1) And the internal structure details ( Figure 2), its role is mainly to the media end mechanical seal friction pair cooling.
  • Figure 2 its role is mainly to the media end mechanical seal friction pair cooling.
  • Option 52 or Arrangement 2 is a non-pressurized double-sealing system for conditions that do not allow leakage to the atmosphere side.
  • the scheme 52 system consists of a double seal injected into the buffer fluid therein. A buffer fluid is placed in the sealed tank, and the outlet of the sealed tank communicates with the exhaust to maintain the pressure of the buffer fluid close to atmospheric pressure. As a result of the inside seal leakage, the medium leaks into the buffer. In fact, there will always be a certain leak.
  • Scheme 52 works best when used in non-polymeric clean media with a vapor pressure above the buffer fluid pressure. This type of medium flashes in the sealed tank and the steam escapes to the exhaust. If the vapor pressure of the medium is lower than the buffer fluid or the sealed tank pressure, the leaked fluid will remain liquid and will contaminate the buffer fluid.
  • Option 52 is not suitable for use in dirty or easily polymerizable media. In this case, option 53 should be considered.
  • Figure 3 and Figure 4 are the 3CW-FB configuration of the 53 flushing scheme.
  • the principle of the back-facing double-contact wet seal flushing system with the barrier fluid between the two mechanical seals and the circulating fluid can be circulated.
  • Schematic diagram (Fig. 3) and internal structural details (Fig. 4) the system has two functions, one is to cool the mechanical seal friction pair on the media end, and the other is to leak the direction of the mechanical seal once the media end leaks. It must be that the barrier liquid leaks into the material of the pump chamber, and it will never leak the material into the barrier liquid and then leak into the atmosphere outside the atmospheric mechanical seal to pollute the environment.
  • Option 53 or Arrangement 3 pressurized double seal system for conditions that do not allow leakage to the atmosphere side.
  • the protocol 53a system consists of a double seal and a blocking fluid injected therein.
  • the blocking fluid is in a sealed tank having a pressure that is about 1.5 bar (23 psi) above the pressure of the pump seal chamber.
  • the differential seal regulator can be used to reduce the outer seal pressure by 20-25 psi greater than the pump seal chamber pressure.
  • Scheme 53b is also a pressurized double seal, which differs from option 53a in that the pressure generated by the bladder-type accumulator is used to maintain the density. Sealed cycle.
  • Scheme 53c is also a pressurized double seal which is above the seal chamber pressure that maintains the pressure using a piston accumulator.
  • Scheme 53 is more commonly used in dirty, abrasive or polymerizable media. In such an environment, if option 52 is selected, it may damage the sealing end face or cause problems to the buffer fluid system.
  • the two shortcomings of Option 53 must be considered: First, there is always a certain amount of blocking fluid leaking into the medium during actual use. Typically, this leak is small and the amount of leakage can be monitored by observing the sealed tank level. Therefore, the medium must be able to allow the blocking fluid to produce a small amount of contamination. Second, the scheme 53 system relies on the proper pressure of the sealed can. If the canister pressure drops, the system will begin to work similar to option 52 or a non-pressurized double seal, and a complete seal cannot be achieved. In particular, over time, the direction of leakage of the inner seal will reverse, the clogging fluid will be contaminated by the process fluid, and problems will occur, including possible seal failures.
  • the technical problem to be solved by the present invention is to provide a high pressure flushing system with multiple sets of mechanical seals capable of greatly increasing the capacity of the centrifugal pump to withstand pressure.
  • a high pressure flushing system with multiple sets of mechanical seals comprising a centrifugal pump composed of a pump casing, an impeller disposed in the pump casing, and a pump shaft connected to the impeller at one end,
  • the other end of the pump shaft is mechanically sealed from the pump casing through a high-pressure end provided on the shaft hole of the pump casing, and the end is connected to a motor for driving the rotation of the impeller through a coupling, the pump shaft connecting the coupling
  • the end of the pump shaft is positioned by a bearing disposed on the bearing housing, and the outer sleeve of the pump shaft is sleeved with a sleeve, and the sleeve is fixedly connected to the pump shaft through a sleeve sealing ring, and the sleeve is located at
  • the outer portion between the pump casing and the bearing is formed with first to Nth buffer cavities through a first to Nth sealing gland end and end seal, and each of the sealing gland
  • the pressure in the N buffer chambers is sequentially increased from the Nth buffer chamber having the lowest pressure adjacent to the bearing to the first buffer chamber having the highest pressure adjacent to the pump casing.
  • the pressure difference between each adjacent two buffer chambers in the N buffer chambers is:
  • P adjacent the pressure difference between two adjacent accumulators, and the pressure difference between each set of mechanical seals.
  • the static ring and the moving ring in the mechanical seal of the high pressure side of each of the sealing glands constitute a pair of friction pairs, wherein the static ring is fixedly connected with the corresponding sealing gland, and the moving ring and the moving ring The sleeve is fixedly connected.
  • the medium pressure in the pump casing is less than the pressure of the buffer in the first buffer chamber adjacent to the pump casing.
  • the medium pressure in the pump casing is greater than the pressure of the buffer in the first buffer chamber adjacent to the pump casing.
  • the N is an integer greater than 2.
  • the high pressure flushing system with multiple sets of mechanical seals of the invention can greatly improve the ability of the current centrifugal pump to withstand high pressure. Has the following effects:
  • the accumulators and other components in the 52 and 53 flushing schemes of API682 are the basic configuration of the international standard, so there is no need to change any prior art equipment. Only the pressure of the accumulator can be adjusted according to the invention to make the existing centrifugal pump. The pressure bearing capacity is doubled.
  • the bearing box can be used as a sealed cavity ( Figure 5), not only makes the bearing box a dual-purpose cavity, but also effectively shorten the distance between the support point and the force point.
  • the accumulator used is a standard part, so it is easy to implement.
  • the structure is simple, the occupied space is small, the operation is convenient, and the production cost is low.
  • the flushing system of the shaft seal has a function of reducing the pressure difference that has never been seen before.
  • Application of the invention can improve the high pressure resistance of the centrifugal pump and prolong the service life of the mechanical seal, as long as the change is made at the medium end of the high pressure material to achieve the purpose of arrangement 2 and arrangement 3 in the API682 standard.
  • Each position in the API682 standard can be achieved by changing the medium end of the high pressure material.
  • FIG. 1 is a schematic structural view of a prior art 52 standard flushing scheme
  • Figure 2 is an internal structure of a prior art 52 standard flushing scheme
  • FIG. 3 is a schematic structural view of a prior art 53 standard flushing scheme
  • FIG. 4 is a schematic diagram showing the internal structure of a standard rinsing scheme of the prior art 53;
  • Figure 5 is a schematic structural view of the high pressure resistant flushing scheme of the present invention.
  • Figure 6 is a schematic view showing the internal structure of the high pressure resistant flushing scheme of the present invention.
  • A Pressure position at the end of the high pressure material
  • B Pressure position at the low pressure end of the atmosphere
  • the high pressure flushing system with multiple sets of mechanical seals of the present invention comprises a pump casing 7, an impeller 6 disposed in the pump casing 7, and a pump shaft 1 connected to the impeller 6 at one end.
  • a centrifugal pump is constructed, the other end of the pump shaft 1 is extended out of the pump casing 7 through a high-pressure end mechanical seal 4 disposed on the shaft hole of the pump casing 7, and the end is connected through the coupling 9 for driving the impeller 6
  • Rotating motor 10 the end of the pump shaft 1 connecting the coupling 9 is positioned by a bearing 11 disposed on the bearing housing 8, and the outer portion of the pump shaft 1 is sleeved with a sleeve 2, and the sleeve 2 passes
  • the sleeve sealing ring 3 is fixedly connected to the pump shaft 1, and the sleeve 2 passes through the first to Nth sealing glands 31, 32 at the outer circumference between the pump casing 7 and the bearing 11.
  • the first and the Nth buffer chambers 121, 122, . . . 12N are formed by the end seals of the 3N, and the N is an integer greater than 2.
  • a mechanical seal 5 sealingly connected to the sleeve 2 is disposed at a shaft hole of each of the high pressure sides of the sealing gland, and a liquid inlet of each sealing gland is connected to an internal fitting through a liquid inlet pipe 14
  • the liquid outlet of the accumulator 15 having a buffer, the outlet of each of the sealing glands is connected to the inlet of the accumulator 15 through an outlet line 13, and the sealing pressure of the pump casing 7 is close to
  • the bottom of the cover 31 is sealingly connected to the pump casing 7.
  • the pressure in the N buffer chambers 121, 122, ... 12N is sequentially from the Nth buffer chamber 12N having the lowest pressure adjacent to the bearing 11 to the first buffer chamber 121 having the highest pressure adjacent to the pump casing 7 in order. increase.
  • P adjacent the pressure difference between two adjacent accumulators, and the pressure difference between each set of mechanical seals.
  • the static ring and the moving ring in the mechanical seal 5 on the high pressure side of each of the sealing glands constitute a pair of friction pairs, wherein the static ring is fixedly connected with the corresponding sealing gland, and the moving ring and the moving ring The sleeve 2 is fixedly connected.
  • the medium pressure in the pump casing 7 is less than the pressure of the buffer in the first buffer chamber 121 adjacent to the pump casing 7, at which time the buffer becomes a barrier fluid.
  • the medium pressure in the pump casing 7 is greater than the first buffer adjacent to the pump casing 7 The pressure of the buffer in the liquid chamber 121.
  • the high pressure flushing system of the present invention having multiple sets of mechanical seals enables the fluid between the two sets of facing mechanical seals located in the pump casing and adjacent to the bearing to be different from the pressureless 52 of the API682 standard.
  • the flushing 53 scheme has a pressure greater than the material. Rather, there are multiple sets of mechanical seals facing the back configuration between the two sets of facing-facing mechanical seals to form a plurality of closed cavities, and the pressure between the sets of facing-back mechanical seals is adjusted to be between The average value, if the double-face mechanical seal is installed, the two friction pairs of the mechanical seal each bear half the pressure of the total pressure, so that the two friction pairs of the mechanical seal share the total pressure difference, thereby reducing the mechanical seal load. the goal of.
  • each of the buffer chambers 121-N is provided with an accumulator 15 for each independent buffer chamber along the direction of the high pressure material end toward the low pressure atmosphere end.
  • the pressure of the buffer fluid in the body 121-N is successively decreased, so that each set of mechanical seals 5 can bear their respective pressure drops. It is possible to decompose the total pressure drop of the centrifugal pump into several partial pressure drops, that is to say the sum of these partial pressure drops is the total pressure drop of the centrifugal pump.
  • N the number of mechanical seals
  • P material pressure Mpa
  • 10 the limit pressure Mpa that each mechanical seal should withstand
  • the above formula can be used to calculate the number of mechanical seals that should be installed so that the necessary installation space can be reserved.
  • P out the outlet pressure (Mpa) of the centrifugal pump.
  • Substance P centrifugal pump transported material sealed chamber (Mpa).
  • the material pressure of the sealed chamber can be estimated by the above formula. Otherwise, it is necessary to install a pressure gauge to actually measure the pressure value of the mechanical seal chamber. This method is more reliable.
  • K insurance factor, value range: 0.5 ⁇ k ⁇ 1, generally 0.7
  • N The number of mechanical seals should be configured to take a positive integer greater than the calculated value.
  • the calculated value is either 3 or 2.9.
  • m The number of accumulators that should be configured, also the number of buffer circulation systems and the number of mechanical seal glands.
  • P adjacent the pressure difference between two adjacent accumulators; also the pressure difference (Mpa) of each set of mechanical seals.
  • P xi The pressure (Mpa) that the accumulator with the serial number i should set.
  • the accumulator should be set to a pressure (ignoring atmospheric pressure):
  • P X2 The pressure (Mpa) that the accumulator should set; it is also the pressure difference (Mpa) that each of the two sets of mechanical seals is subjected to.
  • the pressure of the accumulator closest to the material side can be adjusted to be greater than the pressure of the sealing chamber material, and the fluid inside the accumulator becomes a barrier liquid,
  • the leakage direction can only be leaked into the material, and the purpose of the layout 3 in the API682 standard can be completed.
  • the pressure of other accumulators is still set according to the method of the present invention, and the pressure difference can be gradually reduced, thereby reducing the pressure load of each stage of the mechanical seal, that is, the service life of the mechanical seal can be effectively extended, and the API 682 can be completed.
  • the task of arranging 3 in the standard is described.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

L'invention concerne un système de rinçage résistant aux hautes pressions doté de plusieurs joints d'étanchéité mécaniques, le système comprenant une pompe centrifuge formée par un carter de pompe (7), un rotor (6) et un arbre de pompe (1). Une extrémité de l'arbre de pompe (1) est reliée au rotor (6), et l'autre extrémité s'étend hors du carter de pompe (7) à travers un joint d'étanchéité mécanique d'extrémité haute pression (4) disposé au niveau d'un trou d'arbre du carter de pompe (7). Une partie extérieure d'une douille (2), située entre le carter de pompe (7) et un palier (11), est pourvue de première à n ième chambres tampons (121, 122, …, 12N) formées en reliant les premier à n ième joints d'étanchéité de presse-étoupe (31, 32, …, 3N) bout à bout d'une manière étanche. Un trou d'arbre au niveau d'un côté haute pression de chaque joint d'étanchéité de presse-étoupe est pourvu d'un joint d'étanchéité mécanique (5) relié à la douille de manière étanche. Une entrée de liquide de chaque joint d'étanchéité de presse-étoupe est reliée de manière correspondante, par une conduite d'entrée de liquide (14), à une sortie de liquide d'un accumulateur (15) rempli d'un liquide tampon. Une sortie de liquide de chaque joint d'étanchéité de presse-étoupe est reliée de manière correspondante, par une conduite de sortie de liquide (13), à une entrée de liquide de l'accumulateur (15). Le fond du joint d'étanchéité de presse-étoupe (31) du carter de pompe (7) est relié de manière étanche au carter de pompe (7). La résistance aux températures élevées de la pompe centrifuge du système de rinçage résistant aux hautes pressions est ainsi améliorée.
PCT/CN2016/089301 2016-03-16 2016-07-08 Système de rinçage résistant aux hautes pressions doté de plusieurs joints d'étanchéité mécaniques WO2017156933A1 (fr)

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CN201610149434.7A CN105673579B (zh) 2016-03-16 2016-03-16 具有多套机械密封的耐高压冲洗系统

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CN107701730A (zh) * 2017-10-18 2018-02-16 江苏飞跃机泵集团有限公司 一种用于密封强腐蚀强挥发性有毒液体的机械密封装置
CN109163097A (zh) * 2018-10-31 2019-01-08 东莞市华汇精密机械有限公司 一种超细微粒球磨机的机械密封装置
CN113441084A (zh) * 2021-06-30 2021-09-28 高道密封科技(苏州)有限公司 一种超高压反应釜机械密封和具有该密封的反应釜及方法

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CN106655589B (zh) * 2016-11-29 2023-06-06 邢天宜 抵抗深海高水压具有电机旋转轴装备的轴封系统
CN110906003A (zh) * 2019-12-11 2020-03-24 天津长瑞大通流体控制系统有限公司 具有收集装置的用于密封装置的免于泄漏检测系统及方法
CN110894910A (zh) * 2019-12-11 2020-03-20 天津长瑞大通流体控制系统有限公司 一种用于具有报警的密封装置的免于泄漏检测系统及方法
CN112682347B (zh) * 2020-12-01 2022-08-16 安徽工程大学 一种非接触物料化工泵密封件
CN113417866B (zh) * 2021-08-10 2022-09-06 合肥恒大江海泵业股份有限公司 一种高温高压泵

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CN204553314U (zh) * 2014-10-15 2015-08-12 邢宇 使双端面机械密封摩擦副冷却的轴套及其离心泵冷却系统
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FR2308032B1 (fr) * 1976-04-14 1979-01-05 Sigma Vyzkumny Ustav Cerpacich
DE10012663B4 (de) * 2000-03-15 2012-08-02 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Merbelsrod Kühlmittelpumpe mit elektronisch kommutiertem Eletromotor
CN104895825A (zh) * 2014-10-15 2015-09-09 邢宇 使双端面机械密封摩擦副冷却的轴套及其离心泵冷却系统
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CN205388050U (zh) * 2016-03-16 2016-07-20 邢宇 具有多套机械密封的耐高压冲洗系统

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107701730A (zh) * 2017-10-18 2018-02-16 江苏飞跃机泵集团有限公司 一种用于密封强腐蚀强挥发性有毒液体的机械密封装置
CN109163097A (zh) * 2018-10-31 2019-01-08 东莞市华汇精密机械有限公司 一种超细微粒球磨机的机械密封装置
CN109163097B (zh) * 2018-10-31 2024-05-14 广东华汇智能装备股份有限公司 一种超细微粒球磨机的机械密封装置
CN113441084A (zh) * 2021-06-30 2021-09-28 高道密封科技(苏州)有限公司 一种超高压反应釜机械密封和具有该密封的反应釜及方法

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