CN108119393A - Based on the seal isolation liquid internal circulating load computational methods under plan54 system configurations - Google Patents
Based on the seal isolation liquid internal circulating load computational methods under plan54 system configurations Download PDFInfo
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- CN108119393A CN108119393A CN201710824247.9A CN201710824247A CN108119393A CN 108119393 A CN108119393 A CN 108119393A CN 201710824247 A CN201710824247 A CN 201710824247A CN 108119393 A CN108119393 A CN 108119393A
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- Prior art keywords
- seal
- heat
- face
- insulating liquid
- pressure
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Classifications
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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
- 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
- F04D29/58—Cooling; Heating; Diminishing heat transfer
- F04D29/586—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps
Abstract
Based on the seal isolation liquid internal circulating load computational methods under plan54 system configurations, using heat balance method, seal cavity, interior outer side seal component, shaft, pump cover cooling water, outer flushing liquor and insulating liquid are considered as a system, it must meet heat balance during based on sealing steady running, seal isolation liquid internal circulating load is calculated.The method have the advantages that：1st, for from different pump cover structures, regardless of whether with water-cooling jacket, if configuration is outer to rinse, and for plan54 systems, the equation of heat balance in the present invention can flexibly be used according to actual conditions.
Description
Technical field
Present invention relates particularly to based on the seal isolation liquid internal circulating load computational methods under plan54 system configurations.
Background technology
At present, the present invention relates to mechanical seal field, emphasis is related to mechanical seal operating heat, medium heat transfer, heat and hands over
The calculating of liquid internal circulating load is changed and seals off, and for the plan54 system configurations of high temperature pump mechanical sealing, according to different sealings
Arrangement each provides the computational methods of seal isolation liquid internal circulating load.
In recent years because high temperature oil pump mechanical seal leakage causes Petrochemical Enterprises that a lot of firing accidents have occurred, to equipment safety
Production brings serious influence.It is simple by the friction pair for selecting high temperature resistant, thermal conductivity good for high temperature pump mechanical sealing
Material is often not achieved expected effect, whether sealing is reliable, is heavily dependent on seal operation environment, configures
Rational sealing auxiliary system is exactly the effective measures for improving seal operation environment, extending sealing life.Analysis is more several close
Auxiliary system is sealed, only plan54 systems are to provide insulating liquid by oil gathering station oil pump while to the multiple sealings of pump group, and insulating liquid follows
Ring is promoted by outer loop device, with insulating liquid internal circulating load is adjustable, circulating effect is good, stand-by pump insulating liquid can also be in and follow
The irreplaceable advantage of the other systems such as ring status, it is especially suitable in the device that pump is concentrated.And the design key of the system exists
Plan54 is not given in the internal circulating load for how determining single seal isolation liquid, current international and domestic and relevant industries standard
The computational methods of liquid internal circulating load are sealed off under system configuration, it is thus determined that insulating liquid internal circulating load is of great significance.
The content of the invention
The purpose of the present invention aiming at above-mentioned deficiency at present, and provide based on the sealing under plan54 system configurations every
Chaotropic internal circulating load computational methods.
The present invention is based on the seal isolation liquid internal circulating load computational methods under plan54 system configurations, it is characterised in that：
One, determines mechanical seal heat balance equation
It is theoretical according to heat balance, when mechanical seal runs well, need to meet：
QF+ QA+ QB+ Qhs=Q1+ Q2+ Q3+ Q4+ Q5
In formula, QF- dynamic and static ring end face frictional heat；
QAThe stirring heat of-rotate element in sealing medium；
QBThe heat that the vibration and friction of-auxiliary element generate；
Qhs- the pump housing and pumped fluid are passed to the heat of seal cavity；
Q1- outer flushing liquor absorption is hot；
Q2- insulating liquid cyclic absorption heat；
Q3Cooling water takes away the heat of annular seal space in-pump cover water-cooling jacket；
Q4The heat that-annular seal space outer surface is taken away with atmosphere convection heat transfer；
Q5- take the heat of system out of by shaft；
Above formula can be reduced to：
QF+ Qhs=Q1+ Q2+ Q3；
Two, frictional heats QFDetermine
The frictional heat of single seal face is calculated as follows：
QF=fpgVAf
pg- seal face is than pressure, N/cm2；
V-seal face is averaged peripheral speed, m/s；
Af- seal face area, cm2；
(2.1) inner seal face pressure calculates
（1）It is calculated in face of back structure inner seal face pressure：
pg=ps+（K1-λ1）p1+（K2-λ2）p2；
P in formulaS- sealing compensation element spring pressure, N/cm2；
K1- inner seal presses the loading coefficient that in-flow calculates, K1=(D2 2-DB 2)/(D2 2-D1 2) ；
K2- inner seal presses the loading coefficient that outer-flowing type calculates, K2=(D2 2-DB 2)/(D2 2-D1 2) ；
D1,D2- be respectively the inside and outside diameter in inner seal end face, m；
DBThe balance diameter of-inner seal, m；
λ1The Film Pressure Coefficient of-inner seal intracavitary medium；
λ2The Film Pressure Coefficient of-outer side seal intracavitary insulating liquid；
p1The pressure of-inner seal intracavitary medium, N/cm2；
p2The pressure of-outer side seal intracavitary insulating liquid, N/cm2；
（2）Face-to-face or back-to-back arrangement inner seal face pressure is calculated as follows;
pg=pS+（K1-λ2）p2+（K2-λ1）p1
(2.2) outer side seal face pressure calculates
pg=pS+（K-λ）p
P in formulaS- sealing compensation element spring pressure, N/cm2
K-outer side seal presses the loading coefficient that in-flow calculates, K=(D2 2-DB 2)/(D2 2-D1 2)
D1,D2- be respectively the inside and outside diameter in outer side seal end face, m；
DBThe balance diameter of-outer side seal, m；
The Film Pressure Coefficient of λ-outer side seal intracavitary insulating liquid；
The pressure of p-outer side seal intracavitary insulating liquid, N/cm2；
The three, pump housings and pumped fluid are passed to the heat Q of seal cavityhsCalculating：
Qhs=U×A×DB×ΔT
In formula：U- material property coefficients；
A- heat transfer areas；
DBThe balance diameter of-sealing, unit mm；
The difference of Δ T- pump temperatures and annular seal space desired temperature, unit K;
The outer flushing liquors of four, absorb hot Q1, insulating liquid absorb hot Q2The heat Q of annular seal space is taken away with recirculated water in pump cover water-cooling jacket3
It is calculated as by following general public affairs：
Q=qρCpΔt/60
In formula：The flow of q-outer flushing liquor or insulating liquid, L/min;
The density of ρ-outer flushing liquor or insulating liquid, kg/L;
CpThe specific heat of-outer flushing liquor or insulating liquid, KJ/（Kg·K）;
The Wen Sheng, K of Δ t-outer flushing liquor or insulating liquid.
The method have the advantages that：1st, for from different pump cover structures, regardless of whether with water-cooling jacket, if configuration is outer to rinse, for
For plan54 systems, the equation of heat balance in the present invention can flexibly be used according to actual conditions.
2nd, by single calculating for covering seal isolation liquid internal circulating load, it may be determined that the global cycle amount needed for plan54 systems,
And provide reliable calculation basis for system tankage, piping oil reserve, insulating liquid supplement cycle and circulating ratio.
3rd, in the case where ensureing system worked well, using the computational methods, outer punching is even cancelled being greatly lowered
On the premise of washing lotion still ensures that sealing and system stable operation, the internal circulating load of insulating liquid can be calculated, possesses good economy
Effect.
4th, according to actual needs, it may be determined that a scope of insulating liquid internal circulating load, convenient for being flowed to seal isolation liquid
The parameters such as amount, pressure and temperature are rationally adjusted.
Specific embodiment
The present invention is first, according to the theoretical definite heat balance formula of heat balance；Second, according to double seals difference cloth
Structure is put, determines the calculation formula of frictional heat；Third, determine the scope of annular seal space boundary temperature.It is specific as follows：1. determine machinery
Seal heat balance equation
It is theoretical according to heat balance, when mechanical seal runs well, need to meet：
QF+ QA+ QB+ Qhs=Q1+ Q2+ Q3+ Q4+ Q5
In formula, QF- dynamic and static ring end face frictional heat
QAThe stirring heat of-rotate element in sealing medium
QBThe heat that the vibration and friction of-auxiliary element generate
Qhs- the pump housing and pumped fluid are passed to the heat of seal cavity
Q1- outer flushing liquor absorption is hot
Q2- insulating liquid cyclic absorption heat
Q3Cooling water takes away the heat of annular seal space in-pump cover water-cooling jacket
Q4The heat that-annular seal space outer surface is taken away with atmosphere convection heat transfer
Q5- take the heat of system out of by shaft
The heat that mechanical seal operating generates mainly has end face frictional heat QFWith the hot Q of stirring of rotate elementA, but due to stirring heat
It is not easy to determine, and is worth less compared with the frictional heat of end face, by end face frictional heat, suitable coefficient of friction is considered to determine, by QA
Calculating consider in end face frictional heat QFIt is interior, vibration and the frictional heat of auxiliary element can be ignored under normal operating conditions, it is right
In liquid end face seal, since the heat transfer coefficient of air is low, heat dissipation capacity Q4And Q5It is smaller, therefore can be ignored, then above formula can letter
It turns to：
QF+ Qhs=Q1+ Q2+ Q3
2. frictional heat QFDetermine
What it is due to plan54 system configurations is double mechanical seal, therefore frictional heat is the sum of medial and lateral seal face frictional heat,
The frictional heat of single seal face is calculated as follows：
QF=fpgVAf
F-seal face coefficient of friction in formula considers the security of sealing operation, takes f=0.2~0.3
pg- seal face is than pressure, N/cm2
V-seal face is averaged peripheral speed, m/s
Af- seal face area, cm2
For double mechanical seal, according to sealing structure layout feature, it is divided into face of the back of the body, face-to-face and 3 kinds back-to-back
Structure.The inside and outside circular surfaces of inner seal end face are by the pressure of liquid, during operating is sealed, the liquid of inside and outside circle
Liquid film propulsive thrust can be generated, this propulsive thrust attempts to push open sealing surface, but due to the difference of arrangement, inside and outside round table
The liquid of face effect is also different, therefore inner seal face pressure should take different calculating sides according to different arrangements
Method；For outer side seal, either which kind of arrangement, what the inside and outside circular surfaces of end face were respectively subjected to always is air
The pressure of pressure and insulating liquid, therefore face pressure computational methods are identical.
2.1 inner seal face pressures calculate
（1）It is calculated in face of back structure inner seal face pressure：
pg=ps+（K1-λ1）p1+（K2-λ2）p2
P in formulaS- sealing compensation element spring pressure, N/cm2
K1- inner seal presses the loading coefficient that in-flow calculates, K1=(D2 2-DB 2)/(D2 2-D1 2)
K2- inner seal presses the loading coefficient that outer-flowing type calculates, K2=(D2 2-DB 2)/(D2 2-D1 2)
D1,D2- be respectively the inside and outside diameter in inner seal end face, m；
DBThe balance diameter of-inner seal, m；
λ1The Film Pressure Coefficient of-inner seal intracavitary medium
λ2The Film Pressure Coefficient of-outer side seal intracavitary insulating liquid
p1The pressure of-inner seal intracavitary medium, N/cm2
p2The pressure of-outer side seal intracavitary insulating liquid, N/cm2
（2）Face-to-face or back-to-back arrangement inner seal face pressure is calculated as follows;
pg=pS+（K1-λ2）p2+（K2-λ1）p1
2.2 outer side seal face pressures calculate
pg=pS+（K-λ）p
P in formulaS- sealing compensation element spring pressure, N/cm2
K-outer side seal presses the loading coefficient that in-flow calculates, K=(D2 2-DB 2)/(D2 2-D1 2)
D1,D2- be respectively the inside and outside diameter in outer side seal end face, m；
DBThe balance diameter of-outer side seal, m；
The Film Pressure Coefficient of λ-outer side seal intracavitary insulating liquid；
The pressure of p-outer side seal intracavitary insulating liquid, N/cm2
3. the pump housing and pumped fluid are passed to the heat Q of seal cavityhsCalculating：
Qhs=U×A×DB×ΔT
In formula：U- material property coefficients；
A- heat transfer areas；
DBThe balance diameter of-sealing, unit mm；
The difference of Δ T- pump temperatures and annular seal space desired temperature, unit K.
Consider the security of heat transfer result of calculation, take（U×A）=0.00025, according to insulating liquid flash temperature and metal
It is lost below 200 DEG C of bellows and plays phenomenon unobvious characteristic, annular seal space boundary temperature is preferably at 160 DEG C~180 DEG C.For high-temperature pump.
4. outer flushing liquor absorbs hot Q1Hot Q is absorbed with insulating liquid2It is calculated as by following general public affairs：
Q=qρCpΔt/60
In formula：The flow of q-outer flushing liquor or insulating liquid, L/min
The density of ρ-outer flushing liquor or insulating liquid, kg/L
CpThe specific heat of-outer flushing liquor or insulating liquid, KJ/（Kg·K）
The Wen Sheng, K of Δ t-outer flushing liquor or insulating liquid
Temperature rises and generally takes 10 DEG C~25 DEG C.
5. recirculated water takes away the heat Q of annular seal space in pump cover water-cooling jacket3Computational methods be：
By general formula Q=q ρ CpΔ t/60 is calculated, but requires to consider two factors：First, the shadow of recirculated water later stage fouling resistance
It rings, cyclical level samming is taken to be upgraded to 5 DEG C；Second, pump cover water-cooling jacket structure, cooling water takes away the heat of annular seal space by total amount of heat
0.2-0.3 times convert.
Seal off liquid internal circulating load calculation process：
1st, according to pump configuration form, row mechanical seal heat balance equation.
2nd, according to sealing arrangement design feature, the corresponding secondary heat Q of sealing surface friction is arranged by arrangementFCalculating formula.
3rd, flow, the Wen Sheng of outer fliud flushing are determined, determines the temperature on inner seal chamber border, determines the Wen Sheng of insulating liquid, meter
Calculate insulating liquid not equality of temperature rise under, it is single seal isolation liquid flow.
4th, the total internal circulating load of whole system insulating liquid is determined according to number of seals, determines therefrom that the detailed configuration of plan54.
Claims (1)
1. based on the seal isolation liquid internal circulating load computational methods under plan54 system configurations, it is characterised in that：
One, determines mechanical seal heat balance equation
It is theoretical according to heat balance, when mechanical seal runs well, need to meet：
QF+ QA+ QB+ Qhs=Q1+ Q2+ Q3+ Q4+ Q5
In formula, QF- dynamic and static ring end face frictional heat；
QAThe stirring heat of-rotate element in sealing medium；
QBThe heat that the vibration and friction of-auxiliary element generate；
Qhs- the pump housing and pumped fluid are passed to the heat of seal cavity；
Q1- outer flushing liquor absorption is hot；
Q2- insulating liquid cyclic absorption heat；
Q3Cooling water takes away the heat of annular seal space in-pump cover water-cooling jacket；
Q4The heat that-annular seal space outer surface is taken away with atmosphere convection heat transfer；
Q5- take the heat of system out of by shaft；
Above formula can be reduced to：
QF+ Qhs=Q1+ Q2+ Q3；
Two, frictional heats QFDetermine
The frictional heat of single seal face is calculated as follows：
QF=fpgVAf
pg- seal face is than pressure, N/cm2；
V-seal face is averaged peripheral speed, m/s；
Af- seal face area, cm2；
(2.1) inner seal face pressure calculates
（1）It is calculated in face of back structure inner seal face pressure：
pg=ps+（K1-λ1）p1+（K2-λ2）p2；
P in formulaS- sealing compensation element spring pressure, N/cm2；
K1- inner seal presses the loading coefficient that in-flow calculates, K1=(D2 2-DB 2)/(D2 2-D1 2) ；
K2- inner seal presses the loading coefficient that outer-flowing type calculates, K2=(D2 2-DB 2)/(D2 2-D1 2) ；
D1,D2- be respectively the inside and outside diameter in inner seal end face, m；
DBThe balance diameter of-inner seal, m；
λ1The Film Pressure Coefficient of-inner seal intracavitary medium；
λ2The Film Pressure Coefficient of-outer side seal intracavitary insulating liquid；
p1The pressure of-inner seal intracavitary medium, N/cm2；
p2The pressure of-outer side seal intracavitary insulating liquid, N/cm2；
（2）Face-to-face or back-to-back arrangement inner seal face pressure is calculated as follows;
pg=pS+（K1-λ2）p2+（K2-λ1）p1
(2.2) outer side seal face pressure calculates
pg=pS+（K-λ）p
P in formulaS- sealing compensation element spring pressure, N/cm2
K-outer side seal presses the loading coefficient that in-flow calculates, K=(D2 2-DB 2)/(D2 2-D1 2)
D1,D2- be respectively the inside and outside diameter in outer side seal end face, m；
DBThe balance diameter of-outer side seal, m；
The Film Pressure Coefficient of λ-outer side seal intracavitary insulating liquid；
The pressure of p-outer side seal intracavitary insulating liquid, N/cm2；
The three, pump housings and pumped fluid are passed to the heat Q of seal cavityhsCalculating：
Qhs=U×A×DB×ΔT
In formula：U- material property coefficients；
A- heat transfer areas；
DBThe balance diameter of-sealing, unit mm；
The difference of Δ T- pump temperatures and annular seal space desired temperature, unit K;
The outer flushing liquors of four, absorb hot Q1, insulating liquid absorb hot Q2The heat Q of annular seal space is taken away with recirculated water in pump cover water-cooling jacket3
It is calculated as by following general public affairs：
Q=qρCpΔt/60
In formula：The flow of q-outer flushing liquor or insulating liquid, L/min;
The density of ρ-outer flushing liquor or insulating liquid, kg/L;
CpThe specific heat of-outer flushing liquor or insulating liquid, KJ/（Kg·K）;
The Wen Sheng, K of Δ t-outer flushing liquor or insulating liquid.
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| CN201710824247.9A CN108119393B (en) | 2017-09-13 | 2017-09-13 | Sealing spacer fluid circulation amount calculation method based on plan54 system configuration |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201710824247.9A CN108119393B (en) | 2017-09-13 | 2017-09-13 | Sealing spacer fluid circulation amount calculation method based on plan54 system configuration |
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| CN108119393A true CN108119393A (en) | 2018-06-05 |
| CN108119393B CN108119393B (en) | 2020-06-05 |
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Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5755394A (en) * | 1980-09-17 | 1982-04-02 | Sekisui Chem Co Ltd | Portable heating or cooling device |
| JP2004003493A (en) * | 2002-05-30 | 2004-01-08 | Mitsubishi Heavy Ind Ltd | Axial flow compressor and its bleeding method for its thrust balance disk |
| CN101325863A (en) * | 2008-08-06 | 2008-12-17 | 王志勇 | Radiator for cooling automatic cycle liquid |
| CN103470772A (en) * | 2013-09-26 | 2013-12-25 | 四川日机密封件股份有限公司 | High-speed high-pressure mechanical seal device |
| CN103713010A (en) * | 2014-01-08 | 2014-04-09 | 天津大学 | Quick-release testing device and method for measuring heat transfer process under condition of high heat flux density |
-
2017
- 2017-09-13 CN CN201710824247.9A patent/CN108119393B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5755394A (en) * | 1980-09-17 | 1982-04-02 | Sekisui Chem Co Ltd | Portable heating or cooling device |
| JP2004003493A (en) * | 2002-05-30 | 2004-01-08 | Mitsubishi Heavy Ind Ltd | Axial flow compressor and its bleeding method for its thrust balance disk |
| CN101325863A (en) * | 2008-08-06 | 2008-12-17 | 王志勇 | Radiator for cooling automatic cycle liquid |
| CN103470772A (en) * | 2013-09-26 | 2013-12-25 | 四川日机密封件股份有限公司 | High-speed high-pressure mechanical seal device |
| CN103713010A (en) * | 2014-01-08 | 2014-04-09 | 天津大学 | Quick-release testing device and method for measuring heat transfer process under condition of high heat flux density |
Non-Patent Citations (1)
| Title |
|---|
| 高章发: "泵内机械密封自冲洗孔尺寸及冲洗量的计算", 《FLUID MACHINERY》 * |
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