CN106870911B - The design method and device of lubricating oil system for air blower and compressor subsidiary engine - Google Patents
The design method and device of lubricating oil system for air blower and compressor subsidiary engine Download PDFInfo
- Publication number
- CN106870911B CN106870911B CN201610785397.9A CN201610785397A CN106870911B CN 106870911 B CN106870911 B CN 106870911B CN 201610785397 A CN201610785397 A CN 201610785397A CN 106870911 B CN106870911 B CN 106870911B
- Authority
- CN
- China
- Prior art keywords
- design
- lubricating oil
- oil
- pressure
- pump
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16N—LUBRICATING
- F16N7/00—Arrangements for supplying oil or unspecified lubricant from a stationary reservoir or the equivalent in or on the machine or member to be lubricated
- F16N7/38—Arrangements for supplying oil or unspecified lubricant from a stationary reservoir or the equivalent in or on the machine or member to be lubricated with a separate pump; Central lubrication systems
- F16N7/385—Central lubrication systems
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Control Of Positive-Displacement Pumps (AREA)
Abstract
The present invention provides a kind of design method of lubricating oil system for air blower and compressor subsidiary engine, including step 10, determines the design driver of lubricating oil system；The design driver includes project information, industry design standard, drum pressure fan lubricating utensil list, lubricating oil physical property, flow of lubrication pressure, lubricating oil charge oil pressure, the placement location of accumulator, compressor coasting time, the building block of lubricating oil system and engineering utility condition；Step 20 carries out air blower, the design of compressor subsidiary engine lubricating oil system according to the design driver；The present invention be able to achieve large blower, compressor subsidiary engine lubricating oil system design work simplification, intelligence.
Description
Technical field
The present invention relates to mechanical design fields, and in particular to a kind of lubricating oil system for air blower and compressor subsidiary engine
Design method and device.
Background technique
The prior art lacks a kind of technology of integrated lubricating oil system for realizing air blower and compressor subsidiary engine, needs out
Hair.
Summary of the invention
An object of the present invention is to be able to achieve the side of the lubricating oil system of integrated design air blower and compressor subsidiary engine
Method and its device.
According to an aspect of the present invention, a kind of design of lubricating oil system for air blower and compressor subsidiary engine is provided
Method, comprising:
Step 10, the design driver for determining lubricating oil system；The design driver includes project information, industry
Design standard, the drum list of pressure fan lubricating utensil, lubricating oil physical property, flow of lubrication pressure, lubricating oil charge oil pressure, accumulator
Placement location, compressor coasting time, the building block of lubricating oil system and engineering utility condition；The lubricating oil system is used
In air blower and compressor subsidiary engine；The project information includes user's name, item address, project name, project number and dress
Set title；
The industry design standard includes for standard ordered by the API614 fourth edition of lubricating oil system and the 5th edition, right
In the GB and API standard of lubricating oil system components；The lubricating oil system components
The bulging pressure fan lubricating utensil list includes compressor thrust bearing, compressor rolling bearing, gear-box and increasing
Press；
The lubricating oil physical property includes viscosity, specific heat and density；Flow of lubrication pressure needed for described includes lubricating oil
Flow and pressure；
The lubricating oil system building block selection is that the component of determining lubricating oil system is constituted；The engineering utility condition
Refer to the Complete sets of a project design basis conditions such as cooling water, source nitrogen, low tension；
Step 20 carries out air blower, the design of compressor subsidiary engine lubricating oil system according to the design driver；The drum
Blower, the design of compressor subsidiary engine lubricating oil system include determining caliber by flow relocity calculation, determining that oil pump is defeated by pressure drop calculating
Pressure, oil pump design, the design of pipe design pressure, oil strainer, top petrol tank design, accumulator designs, thermodynamic computing, oil out
Case design, heater design, safety valve calculate design.
According to another aspect of the present invention, a kind of setting for lubricating oil system for air blower and compressor subsidiary engine is also provided
Counter device comprising:
Design parameter determining module determines the design driver of lubricating oil system；The design driver includes item
Mesh information, industry design standard, the drum list of pressure fan lubricating utensil, lubricating oil physical property, flow of lubrication pressure, lubricating oil fuel feeding
Pressure, the placement location of accumulator, compressor coasting time, the building block of lubricating oil system and engineering utility condition；It is described
Lubricating oil system is used for air blower and compressor subsidiary engine；The project information include user's name, item address, project name,
Project number and device name；
The industry design standard includes for standard ordered by the API614 fourth edition of lubricating oil system and the 5th edition, right
In the GB and API standard of lubricating oil system components；The lubricating oil system components
The bulging pressure fan lubricating utensil list includes compressor thrust bearing, compressor rolling bearing, gear-box and increasing
Press；
The lubricating oil physical property includes viscosity, specific heat and density；Flow of lubrication pressure needed for described includes lubricating oil
Flow and pressure；
The lubricating oil system building block selection is that the component of determining lubricating oil system is constituted；The engineering utility condition
Refer to the Complete sets of a project design basis conditions such as cooling water, source nitrogen, low tension；
Module is designed, air blower is carried out according to the design driver, compressor subsidiary engine lubricating oil system designs；It is described
Air blower, the design of compressor subsidiary engine lubricating oil system include determining caliber by flow relocity calculation, calculating determining oil pump by pressure drop
Output pressure, oil pump design, the design of pipe design pressure, oil strainer, top petrol tank design, accumulator designs, thermodynamic computing,
Tank design, heater design, safety valve calculate design.
The method and device thereof of the lubricating oil system of air blower and compressor subsidiary engine provided by the invention, are able to achieve air blower
And the integrated design of the lubricating oil system of compressor subsidiary engine, avoid the duplication of labour, input a basic data, can repeatedly into
Row data referencing and output.In addition, critical data, calculating process write into software backstage, fundamentally also prevent leakage of data.
Figure of description
Fig. 1 is the flow chart of the method for the lubricating oil system of air blower provided in an embodiment of the present invention and compressor subsidiary engine；
Fig. 2 is the apparatus structure block diagram of the lubricating oil system of air blower provided in an embodiment of the present invention and compressor subsidiary engine.
Specific embodiment
Referring to Fig. 1, the design side of the lubricating oil system provided in an embodiment of the present invention for air blower and compressor subsidiary engine
Method, comprising:
Step 10, the design driver for determining lubricating oil system；The design driver includes project information, industry
Design standard, the drum list of pressure fan lubricating utensil, lubricating oil physical property, flow of lubrication pressure, lubricating oil charge oil pressure, accumulator
Placement location, compressor coasting time, the building block of lubricating oil system and engineering utility condition；The lubricating oil system is used
In air blower and compressor subsidiary engine.
Wherein, project information includes user's name, item address, project name, project number, contract number, quotation volume
Number, device name, version information, design, check and correction, audit: output is in outsourcing piece agreement, instrument control connection is single, consumption table, device
Table, API614 tables of data, the relevant user information of petrol station valuation list, petrol station specification；
Industry design standard includes for standard ordered by the API614 fourth edition of lubricating oil system and the 5th edition, for profit
The GB and API standard of oil system components, GB/T 151, GB/T 28574, GB/T10886, GB/T5171, API6144TH,
API614 5TH, API676, API610, API526 etc..
Drum pressure fan lubricating utensil list includes compressor thrust bearing, compressor rolling bearing, gear-box and supercharger.
Lubricating oil physical property includes viscosity, specific heat and density；Flow of lubrication pressure needed for described includes the flow of lubricating oil
And pressure.
The selection of lubricating oil system building block is that the component of determining lubricating oil system is constituted；The engineering utility condition refers to cold
But the Complete sets of a project such as water, source nitrogen, low tension design basis condition, for example, cooling water intake pressure, temperature, pressure of return water, temperature
Degree, nitrogen temperature pressure, low pressure piezoelectric voltage, frequency, the number of phases, steam pressure, temperature etc..
Step 20 carries out air blower, the design of compressor subsidiary engine lubricating oil system according to the design driver；The drum
Blower, the design of compressor subsidiary engine lubricating oil system include determining caliber by flow relocity calculation, determining that oil pump is defeated by pressure drop calculating
Pressure, oil pump design, the design of pipe design pressure, oil strainer, top petrol tank design, accumulator designs, thermodynamic computing, oil out
Case design, heater design, safety valve calculate design.
Wherein, determine that caliber includes: by flow relocity calculation in step 20
It is first 10 industry design standard (the i.e. API614 4 according to stepTHOr API6145TH) as defined in flow velocity model
It encloses and calculates caliber with lubricants capacity, calculation formula is as follows:
Wherein, d is caliber, and q is lubricants capacity, and v is lubrication oil flow rate；
Then the pipeline drift diameter adjacent with above formula d specification is adjusted, checking computations are iterated to flow velocity, are adjusted to industry design mark
In flow rates as defined in standard.
Wherein, it is calculated in step 20 by pressure drop and determines that fuel pump output pressure includes:
The component for generating pressure drop has been determined；The component for generating pressure drop includes pipeline, valve, oil cooler tube side, oil
Filter cartridge and thermostat valve；
It will determine that the design maximum pressure drop that the component for generating pressure drop generates in the process of running carries out algebraical sum operation, as
Fuel pump outlet to lubricating oil oil-feed port overall presure drop Δ P；
By in step 10 lubricating oil charge oil pressure and overall presure drop Δ P ask algebraical sum to obtain oil pump minimum output pressure；
Determine the pressure for being greater than the oil pump minimum output pressure as fuel pump output pressure Pnorm.
Wherein, the design of oil pump described in step 20 includes the design of grease pump and emergency bearing oil pump；
The grease pump designs
The grease pump designs
In the fuel pump output pressure Pnorm, at 65 ± 5 DEG C, coefficient is carried out to the total oil mass of lubricating oil according to API614 regulation
Adjustment, so that it is determined that oil pump minimum output flow is Q0；
It determines and is greater than and closest to Q0Oil pump model as selected grease pump, according to the fuel pump output pressure
PnormDetermine the output flow Q at 65 ± 5 DEG C1；
Calculate safety valve open state pressure PPSV, PPSV=max [(Pnorm+0.17), 1.1 × Pnorm], and according to institute
State PPSVDetermine the output flow Q under lubricating oil system minimum temperature2；
Calculate the pressure P of 100% full-gearPSV standard-sized sheet, PPSV standard-sized sheet=1.1 × PPSV, and according to the PPSV standard-sized sheetDetermine lubrication
Output flow Q under oil system minimum temperature3；
According to PnormNumerical value is maximized after numerical value and PPSV standard-sized sheet coefficient adjustment after coefficient adjustment, determines that grease pump drives
The power P M of dynamic motor,
PM=max [Pnorm × N, PPSV standard-sized sheet × N], wherein the value of N coefficient depends on Pnorm and PPSV standard-sized sheet.Example
Such as, when Pnorm is less than 5KW, N 1.25；When Pnorm is greater than 5KW less than 10KW, N 1.2；Pnorm is greater than 10KW and is less than 50KW
When, N 1.15；When Pnorm is greater than 50KW, N 1.1.
Have in oil pump product sample pressure flow Q tables of data and each discrete point fitting curve graph, the value of Q0 be in order to
Q1 is chosen, and the value of Q1, Q2, Q3 can pass through tables of data or curve graph Pnorm, PPSV、PPSV standard-sized sheetTo obtain.
The emergency bearing oil pump designs
According to the effect of emergency bearing oil pump, pressure P ' and oil mass needed for determining its accident condition；The effect of the emergency bearing oil pump
It is used including accident fuel feeding, cleaning turbine rotor is used and the cooling use of jiggering；
At the P ', 65 ± 5 DEG C, coefficient adjustment is carried out to accident oil mass according to API614 regulation, so that it is determined that oil pump
Minimum output flow is Q ' 0；
It determines and is greater than and closest to the oil pump model of Q ' 0 as selected emergency bearing oil pump, exported and pressed according to the oil pump
Power P ' determines the output flow Q ' 1 at 65 ± 5 DEG C；
It calculates safety valve open state and presses P 'PSV=max [(P '+0.17), 1.1 × P '], and according to the P 'PSVDetermine profit
Output flow Q ' under oil system minimum temperature2；
Calculate the pressure P ' of 100% full-gearPSV standard-sized sheet=1.1 × P 'PSV, and according to the P 'PSV standard-sized sheetDetermine lubricating oil system
Output flow Q ' under minimum temperature of uniting3；
It is maximized according to numerical value after numerical value after P ' coefficient adjustment and P ' PSV coefficient adjustment, determines grease pump driving electricity
The power P M ' of machine；
PM=max [P ' × N, P ' PSV standard-sized sheet × N], wherein the value of N coefficient depends on P ' and P ' PSV.
Have in oil pump product sample pressure flow Q tables of data and each discrete point fitting curve graph, the value of Q ' 0 be in order to
Q ' 1 is chosen, and the value of Q ' 1, Q ' 2, Q ' 3 can pass through tables of data or curve graph P ' norm, P 'PSV、P’PSV standard-sized sheetTo obtain.
Wherein, pipe design pressure described in step 20 includes
According to the building block of the lubricating oil system in step 10, determine oil pump be screw pump, gear pump or from
Heart pump；
When for screw pump or gear pump, pipe design pressure Pd=Pnorm+max (Pnorm × 0.2,0.3)；
When for centrifugal pump, pipe design pressure Pd=Pnorm+0.1.
Wherein, the design of oil strainer described in step 20 includes lubricating oil filter, control oil strainer and accident oil mistake
The design of filter；
The lubricating oil filter design is the filter core quantity of determining lubricating oil filter, the filter of the lubricating oil filter
Core quantity nLThe upward rounding of=(a × QL/Qf), a are load, the QfIt is filter insert under maximum differential pressure state
Circulation, the QLFor the total oil mass of lubricating oil in flow of lubrication pressure in the step 10；
The control oil strainer design includes determining the filter core quantity of control oil strainer, the control oil strainer
Filter core quantity nCThe upward rounding of=(a × Q control/Qf), a are load, the QfIt is filter insert under maximum differential pressure state
Circulation, the QControlFor the total oil mass of control oil in flow of lubrication pressure in the step 10；
The accident oil strainer includes the filter core quantity of determining accident oil strainer, the filter core of the accident oil strainer
Quantity nE=(a × QE/Qf) upward rounding, a are load, and the Qf is stream of the filter insert under maximum differential pressure state
Flux, the QEFor the total oil mass of control oil in the step 10 in accident oil stream amount pressure.
Wherein, top petrol tank described in step 20, which designs, includes:
Determine accident volume V1, the accident volume V1=T1×0.5×QL；When the T1 is the compressor running down of input
Between or project information require accident supply time, the QLFor the total oil mass of lubricating oil；
Determine that the volume of top petrol tank, the volume of the top petrol tank are greater than V1.
Wherein, accumulator designs described in step 20 include:
Determine cold oil minimum volume V needed for accumulatormin, the Vmin=Δ V × (P1/P0) ^ (1/g)/1- (P1/P2) ^
(1/g)；
Determine cold oil maximum volume V needed for accumulatormax, the Vmax=Vmin × Tmax/Tmin；
Determine oil volume Δ V, the Δ V=4 × QL；
The P1For lubricating oil system system minimum pressure, the P2Accumulator inlet pressure when for spare pump startup, it is described
P0For effective the blowing pressure, the g is gas adiabatic coefficent, the TminFor accumulator precharge of gas minimum temperature, the Tmax
Medium maximum temperature when being run for lubricating oil system；The QLFor the total oil mass of lubricating oil；
According to VmaxThe upward rounding of numerical value selects accumulator engineering volume.It is accurate in order to guarantee, utilize selected accumulator
Engineering volume is iterated operation to its practical oil drain quantity to verify.
Wherein, thermodynamic computing is to utilize Capture window handle, com component handle technology in step 20, can be by software base
Plinth data (for example, the medium and medium of shell side and tube side into go out temperature and pressure, respectively design maximum pressure drop, school
The structured datas such as baffle plate number, cutting rate in kernel normal form) it exports to development HTRI, utilize HTRI to carry out heating power meter
It calculates, and captures the calculated result of HTRI, to obtain water consumption, cooling water water speed, area margin.
Wherein, in step 20 tank design according to " design standard " in " top petrol tank design " and " design input " into
Row data point reuse carries out volume primary Calculation according to top petrol tank volume and design standard first.If primary Calculation includes: choosing
The petrol station of API614 standard is selected, then primary Calculation volume of fuel tank Q '=(T1 × 0.5+8+1) × QL, the T1 is top petrol tank thing
Therefore supply time, the QLFor lubricating oil total amount.If selecting the petrol station of non-API614 standard, Q '=A × QL, A therein can
To be manually entered.
Secondly, when the result in " check of API614 volume " does not meet as defined in API614, " fuel tank free area should be positive
When every liter lower 60 square centimeters per minute of normal flow " (the non-selected API614 of design standard then ignores this step), by lubricating lubricating pad
Oil mass is adjusted, and when result has passed through " check of API614 volume " and the control of space rate 5%~10%, current design is
Rationally, it otherwise needs to change tank design volume and pad oil mass to carry out interative computation again.
Wherein, the design of heater described in step 20 includes electric heater design or steam heater design；Design includes
Determine heat Qa required for heating oil, side plate and the extraneous heat Qb exchanged, heat temperature difference T, electric heater minimum power,
Logarithmic mean temperature Δ Tm, unit time heat exchange amount Qc and heat exchange area S1；
Qa=V4 × the γ × Cp × Δ T,
Qb=S × the Ks × T × Δ T,
The Δ T=T2-T1, wherein Cp is lubricating oil specific heat, and γ is lubrication oil density, and T is industry design standard regulation
Heating time, T1For environment minimum temperature, T2For minimum driving temperature, Δ T is the heating temperature difference, and Ks is fuel tank side board and the external world
Heat exchange coefficient, S is fuel tank side surface area and V4 is tank filling amount；
The electric heater minimum power Nheater=1.15 × (Qa+Qb)/T/1000 × γ；
The logarithmic mean temperature Δ Tm is calculated by the following formula acquisition:
Δ T1=T3-T1,
Δ T2=T3-T2,
Δ Tm=(Δ T1- Δ T2)/ln (Δ T1/ Δ T2),
Unit time heat exchange amount Qc=(the Qa+Qb)/T,
The heat exchange area S1=Qc/ (Δ Tm × K),
Steam heater steam consumption quantity Qs=1.25 × Qc/K1,
Wherein, Qc is unit time heat exchange amount, and S1 heat exchange area, T3 is saturated vapor temperature, and K1 is saturated vapor vapour
Change heat, K is the heater coefficient of heat transfer.
Wherein, it includes that lubricating oil relief valve design and accident oil safety valve are set that safety valve described in step 20, which calculates design,
Meter；Wherein, lubricating oil relief valve design includes flow area and Methods of Safety Valve Discharge Capacity needed for determining safety valve；
Flow area needed for the safety valve
The Methods of Safety Valve Discharge CapacityThe γ is
Oil density is lubricated, q is that Pdr is specified discharge pressure, and Pb is back pressure, and the Kd is that Kw is that Kc is that Kv is.
Step 30 will design output determined by step 20.Furthermore it is also possible to export outsourcing piece agreement, instrument control connection it is single,
Consume table/device table, API614 tables of data, petrol station valuation list and petrol station specification.
Referring to fig. 2, the embodiment of the present invention provides a kind of design of lubricating oil system for air blower and compressor subsidiary engine
Device comprising design parameter determining module 10 ', design module 20 ' and design output module 30 '.
Wherein, design parameter determining module 10 ' determines the design driver of lubricating oil system；The design input ginseng
Number includes project information, industry design standard, drum pressure fan lubricating utensil list, lubricating oil physical property, flow of lubrication pressure, profit
Lubricating oil charge oil pressure, the placement location of accumulator, compressor coasting time, the building block of lubricating oil system and the public item of engineering
Part；The lubricating oil system is used for air blower and compressor subsidiary engine；The project information includes user's name, item address, item
Mesh title, project number and device name；
The industry design standard includes for standard ordered by the API614 fourth edition of lubricating oil system and the 5th edition, right
In the GB and API standard of lubricating oil system components；The lubricating oil system components
The bulging pressure fan lubricating utensil list includes compressor thrust bearing, compressor rolling bearing, gear-box and increasing
Press；
The lubricating oil physical property includes viscosity, specific heat and density；Flow of lubrication pressure needed for described includes lubricating oil
Flow and pressure；
The lubricating oil system building block selection is that the component of determining lubricating oil system is constituted；The engineering utility condition
Refer to the Complete sets of a project design basis conditions such as cooling water, source nitrogen, low tension；
Module 20 ' is designed, air blower is carried out according to the design driver, compressor subsidiary engine lubricating oil system designs；
The air blower, the design of compressor subsidiary engine lubricating oil system include determining caliber by flow relocity calculation, calculating determination by pressure drop
Fuel pump output pressure, oil pump design, the design of pipe design pressure, oil strainer, top petrol tank design, accumulator designs, heating power
Calculating, tank design, heater design, safety valve calculate design.
The design that the output design module 20 of output module 30 ' generates is designed, and outsourcing piece agreement, instrument control connection can also be exported
System's list, consumption table/device table, API614 tables of data, petrol station valuation list and petrol station specification.
Provided by the present invention for the design method and device of the lubricating oil system of air blower and compressor subsidiary engine, realize big
Type air blower, compressor subsidiary engine lubricating oil system design work simplification, intelligence；Input scheme of foundation design data it
Afterwards, calculating, type selecting, data check, the output of design abstract, outsourcing piece technology association of each components of lubricating oil system can be automatically performed
Discuss generation, the single output of API614 tables of data Auto-writing, instrument control connection, the output of lubricating oil system water, electricity and gas consumption list, profit
Oil system price list (technology quotation), lubricating oil system specification etc. are a series of to need what is carried out to answer in product design process
General labourer makees, and the work such as complicated data calculating, Scheme Choice, document output is thoroughly simplified, it is possible to reduce designer
Design pressure, while reducing error probability, substantially increase design efficiency, reduce design cost.The present invention is suitable for
The design of the lubricating oil system of API614 standard and non-API614 standard.
Claims (10)
1. a kind of design method of the lubricating oil system for air blower and compressor subsidiary engine characterized by comprising
Step 10, the design driver for determining lubricating oil system；The design driver includes project information, industry design
Standard, drum pressure fan lubricating utensil list, lubricating oil physical property, flow of lubrication pressure, lubricating oil charge oil pressure, accumulator are put
Seated position, compressor coasting time, the building block of lubricating oil system and engineering utility condition；The lubricating oil system is for rousing
Blower and compressor subsidiary engine；The project information includes user's name, item address, project name, project number and device name
Claim；
The industry design standard includes for standard ordered by the API614 fourth edition of lubricating oil system and the 5th edition, for profit
The GB and API standard of oil system components；
The bulging pressure fan lubricating utensil list includes compressor thrust bearing, compressor rolling bearing, gear-box and supercharger；
The lubricating oil physical property includes viscosity, specific heat and density；Required flow of lubrication pressure includes the flow and pressure of lubricating oil
Power；
The lubricating oil system building block selection is that the component of determining lubricating oil system is constituted；The engineering utility condition refers to cold
But water, source nitrogen, low tension Complete sets of a project design basis condition；
Step 20 carries out air blower, the design of compressor subsidiary engine lubricating oil system according to the design driver；The air blast
Machine, the design of compressor subsidiary engine lubricating oil system include determining caliber by flow relocity calculation, calculating determining oil pump output by pressure drop
Pressure, oil pump design, the design of pipe design pressure, oil strainer, top petrol tank design, accumulator designs, thermodynamic computing, fuel tank
Design, heater design, safety valve calculate design.
2. the method according to claim 1, wherein described determine that caliber includes: by flow relocity calculation
First according to step be 10 industry design standards as defined in flow rates and lubricants capacity calculate caliber, calculation formula
It is as follows:
Wherein, d is caliber, and q is lubricants capacity, and v is lubrication oil flow rate；
Then the pipeline drift diameter adjacent with above formula d specification is adjusted, checking computations are iterated to flow velocity, adjusts to industry design standard and advises
In fixed flow rates.
3. the method according to claim 1, wherein described calculated by pressure drop determines fuel pump output pressure packet
It includes:
The component for generating pressure drop has been determined；The component for generating pressure drop includes pipeline, valve, oil cooler tube side, oil filtering
Device fuse and thermostat valve；
It will determine that the design maximum pressure drop that the component for generating pressure drop generates in the process of running carries out algebraical sum operation, as oil pump
It is exported to the overall presure drop Δ P of lubricating oil oil-feed port；
By in step 10 lubricating oil charge oil pressure and overall presure drop Δ P ask algebraical sum to obtain oil pump minimum output pressure；
Determine the pressure for being greater than the oil pump minimum output pressure as fuel pump output pressure Pnorm。
4. according to the method described in claim 3, it is characterized in that, oil pump design includes grease pump and emergency bearing oil pump
Design；
The grease pump designs
In the fuel pump output pressure Pnorm, at 65 ± 5 DEG C, coefficient adjustment is carried out to the total oil mass of lubricating oil according to API614 regulation,
So that it is determined that oil pump minimum output flow is Q0；
It determines and is greater than and closest to Q0Oil pump model as selected grease pump, according to the fuel pump output pressure Pnorm
Determine the output flow Q at 65 ± 5 DEG C1；
Calculate safety valve open state pressure PPSV, PPSV=max [(Pnorm+ 0.17), 1.1 × Pnorm], and according to the PPSVReally
Determine the output flow Q under lubricating oil system minimum temperature2；
Calculate the pressure P of 100% full-gearPSV standard-sized sheet, PPSV standard-sized sheet=1.1 × PPSV, and according to the PPSV standard-sized sheetDetermine lubricating oil system
Output flow Q under minimum temperature of uniting3；
According to PnormNumerical value and P after coefficient adjustmentPSV standard-sized sheetNumerical value is maximized after coefficient adjustment, determines grease pump driving motor
Power P M,
PM=max [Pnorm× N, PPSV standard-sized sheet× N], wherein the value of N coefficient depends on PnormAnd PPSV standard-sized sheet；
Emergency bearing oil pump designs
According to the effect of emergency bearing oil pump, pressure P ' and oil mass needed for determining its accident condition；The effect of the emergency bearing oil pump includes
Accident fuel feeding, which is used, cleaning turbine rotor is used and jiggering is cooling uses；
At the P ', 65 ± 5 DEG C, coefficient adjustment is carried out to accident oil mass according to API614 regulation, so that it is determined that oil pump is minimum
Output flow is Q ' 0；
Determination is greater than and closest to the oil pump model of Q ' 0 as selected emergency bearing oil pump, is determined at 65 ± 5 DEG C according to the P '
Output flow Q ' 1；
It calculates safety valve open state and presses P 'PSV=max [(P '+0.17), 1.1 × P '], and according to the P 'PSVDetermine lubricating oil
Output flow Q ' under system minimum temperature2；
Calculate the pressure P ' of 100% full-gearPSV standard-sized sheet=1.1 × P 'PSV, and according to the P 'PSV standard-sized sheetDetermine lubricating oil system most
Output flow Q ' under low temperature3；
According to numerical value and P ' after P ' coefficient adjustmentPSVNumerical value is maximized after coefficient adjustment, determines the function of grease pump driving motor
Rate PM '；
PM=max [P ' × N, P 'PSV standard-sized sheet× N], wherein the value of N coefficient depends on P ' and P 'PSV standard-sized sheet。
5. the method according to claim 1, wherein the pipe design pressure includes
According to the building block of the lubricating oil system in step 10, determine that oil pump is screw pump, gear pump or centrifugal pump；
When for screw pump or gear pump, pipe design pressure Pd=Pnorm+ max (Pnorm × 0.2,0.3)；
When for centrifugal pump, pipe design pressure Pd=Pnorm+0.1。
6. the method according to claim 1, wherein oil strainer design includes lubricating oil filter, control
The design of liquefaction filter and accident oil strainer；
The lubricating oil filter design is the filter core quantity of determining lubricating oil filter, the filter core number of the lubricating oil filter
Measure nL=(a × QL/Qf) upward rounding, a is load, the QfFor circulation of the filter insert under maximum differential pressure state
Amount, the QLFor the total oil mass of lubricating oil in flow of lubrication pressure in the step 10；
The control oil strainer design includes determining the filter core quantity of control oil strainer, the filter core of the control oil strainer
Quantity nC=(a × QControl/Qf) upward rounding, a is load, the QfFor stream of the filter insert under maximum differential pressure state
Flux, the QControlFor the total oil mass of control oil in flow of lubrication pressure in the step 10；
The accident oil strainer includes the filter core quantity of determining accident oil strainer, the filter core quantity of the accident oil strainer
nE=(a × QE/Qf) upward rounding, a is load, the QfFor circulation of the filter insert under maximum differential pressure state,
The QEFor the total oil mass of control oil in the step 10 in accident oil stream amount pressure.
7. the method according to claim 1, wherein top petrol tank design includes:
Determine accident volume V1, the accident volume V1=T1×0.5×QL；The T1For the compressor coasting time of input or item
The accident supply time of mesh information requirements, the QLFor the total oil mass of lubricating oil；
Determine that the volume of top petrol tank, the volume of the top petrol tank are greater than V1。
8. the method according to claim 1, wherein the accumulator designs include:
Determine cold oil minimum volume V needed for accumulatormin, the Vmin=Δ V × (P1/P0)^(1/g)/1-(P1/P2)^(1/g)；
Determine cold oil maximum volume V needed for accumulatormax, the Vmax=Vmin×Tmax/Tmin；
Determine oil volume Δ V, the Δ V=4 × QL；
The P1For lubricating oil system system minimum pressure, the P2Accumulator inlet pressure when for spare pump startup, the P0For
Effective the blowing pressure, the g are gas adiabatic coefficent, the TminFor accumulator precharge of gas minimum temperature, the TmaxFor profit
Medium maximum temperature when oil system is run；The QLFor the total oil mass of lubricating oil；
According to VmaxThe upward rounding of numerical value selects accumulator engineering volume.
9. the method according to claim 1, wherein heater design includes that electric heater designs；It is described
Electric heater design include heat Qa, side plate required for determining heating oil with the extraneous heat Qb exchanged, heat temperature difference T,
Electric heater minimum power, logarithmic mean temperature Δ Tm, unit time heat exchange amount Qc and heat exchange area S1；
Qa=V4 × the γ × Cp × Δ T,
Qb=S × the Ks × T × Δ T,
The Δ T=T2-T1, wherein Cp is lubricating oil specific heat, and γ is lubrication oil density, and T is to add as defined in industry design standard
Hot time, T1For environment minimum temperature, T2For minimum driving temperature, Δ T is the heating temperature difference, and Ks is that fuel tank side board and extraneous heat are handed over
Coefficient is changed, S is fuel tank side surface area and V4 is tank filling amount；
The electric heater minimum power Nheater=1.15 × (Qa+Qb)/T/1000 × γ；
The logarithmic mean temperature Δ Tm is calculated by the following formula acquisition:
Δ T1=T3-T1,
Δ T2=T3-T2,
Δ Tm=(Δ T1- Δ T2)/ln (Δ T1/ Δ T2),
Unit time heat exchange amount Qc=(the Qa+Qb)/T,
The heat exchange area S1=Qc/ (Δ Tm × K),
Steam heater steam consumption quantity Qs=1.25 × Qc/K1,
Wherein, Qc is unit time heat exchange amount, and S1 heat exchange area, T3 is saturated vapor temperature, and K1 is saturated vapor heat of vaporization,
K is the heater coefficient of heat transfer.
10. a kind of design device of the lubricating oil system for air blower and compressor subsidiary engine characterized by comprising
First design module, determines the design driver of lubricating oil system；The design driver includes project information, row
Industry design standard, the drum list of pressure fan lubricating utensil, lubricating oil physical property, flow of lubrication pressure, lubricating oil charge oil pressure, accumulation of energy
Placement location, compressor coasting time, the building block of lubricating oil system and the engineering utility condition of device；The lubricating oil system
For air blower and compressor subsidiary engine；The project information include user's name, item address, project name, project number and
Device name；
The industry design standard includes for standard ordered by the API614 fourth edition of lubricating oil system and the 5th edition, for profit
The GB and API standard of oil system components；The lubricating oil system components
The bulging pressure fan lubricating utensil list includes compressor thrust bearing, compressor rolling bearing, gear-box and supercharger；
The lubricating oil physical property includes viscosity, specific heat and density；Required flow of lubrication pressure includes the flow and pressure of lubricating oil
Power；
The lubricating oil system building block selection is that the component of determining lubricating oil system is constituted；The engineering utility condition refers to cold
But water, source nitrogen, low tension Complete sets of a project design basis condition；
Second design module carries out air blower according to the design driver, compressor subsidiary engine lubricating oil system designs；It is described
Air blower, the design of compressor subsidiary engine lubricating oil system include determining caliber by flow relocity calculation, calculating determining oil pump by pressure drop
Output pressure, oil pump design, the design of pipe design pressure, oil strainer, top petrol tank design, accumulator designs, thermodynamic computing,
Tank design, heater design, safety valve calculate design.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610785397.9A CN106870911B (en) | 2016-08-31 | 2016-08-31 | The design method and device of lubricating oil system for air blower and compressor subsidiary engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610785397.9A CN106870911B (en) | 2016-08-31 | 2016-08-31 | The design method and device of lubricating oil system for air blower and compressor subsidiary engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN106870911A CN106870911A (en) | 2017-06-20 |
| CN106870911B true CN106870911B (en) | 2019-09-17 |
Family
ID=59238803
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610785397.9A Active CN106870911B (en) | 2016-08-31 | 2016-08-31 | The design method and device of lubricating oil system for air blower and compressor subsidiary engine |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN106870911B (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107063685B (en) * | 2017-06-30 | 2023-12-22 | 中国船舶重工集团公司第七�三研究所 | Gear minimum lubricating oil mass measuring device |
Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201057131Y (en) * | 2007-06-27 | 2008-05-07 | 中国石油天然气股份有限公司 | Improved design of drip-injection type lubricating system of compressor |
| CN101205910A (en) * | 2006-12-20 | 2008-06-25 | 乐金电子(天津)电器有限公司 | Scroll compressor having function of reducing lubricating oil resistance |
| AU2008343245A1 (en) * | 2007-12-20 | 2009-07-09 | Chevron U.S.A. Inc. | Base oil properties expert system |
| CN102029442A (en) * | 2010-11-03 | 2011-04-27 | 北京航空航天大学 | Method for improving lubrication performance of spiral taper gear |
| CN103366078A (en) * | 2012-04-05 | 2013-10-23 | 中国航空工业集团公司沈阳发动机设计研究所 | Bearing cavity ventilation design method of aero-engine |
| CN103593537A (en) * | 2013-11-27 | 2014-02-19 | 哈尔滨理工大学 | Method for building lubricating oil film model after thermal coupling deformation of static pressure center frame |
| CN104598666A (en) * | 2014-12-01 | 2015-05-06 | 哈尔滨理工大学 | Large-scale hydrostatic support critical load parameter acquiring method |
| CN105041579A (en) * | 2014-04-28 | 2015-11-11 | 中船重工(重庆)海装风电设备有限公司 | Lubricating grease adding method and lubricating system for pitch bearing of wind turbine generator system |
| CN105135197A (en) * | 2015-09-02 | 2015-12-09 | 哈尔滨理工大学 | Lubricating property forecasting method of double-rectangular-cavity hydrostatic thrust bearing |
-
2016
- 2016-08-31 CN CN201610785397.9A patent/CN106870911B/en active Active
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101205910A (en) * | 2006-12-20 | 2008-06-25 | 乐金电子(天津)电器有限公司 | Scroll compressor having function of reducing lubricating oil resistance |
| CN201057131Y (en) * | 2007-06-27 | 2008-05-07 | 中国石油天然气股份有限公司 | Improved design of drip-injection type lubricating system of compressor |
| AU2008343245A1 (en) * | 2007-12-20 | 2009-07-09 | Chevron U.S.A. Inc. | Base oil properties expert system |
| CN102029442A (en) * | 2010-11-03 | 2011-04-27 | 北京航空航天大学 | Method for improving lubrication performance of spiral taper gear |
| CN103366078A (en) * | 2012-04-05 | 2013-10-23 | 中国航空工业集团公司沈阳发动机设计研究所 | Bearing cavity ventilation design method of aero-engine |
| CN103593537A (en) * | 2013-11-27 | 2014-02-19 | 哈尔滨理工大学 | Method for building lubricating oil film model after thermal coupling deformation of static pressure center frame |
| CN105041579A (en) * | 2014-04-28 | 2015-11-11 | 中船重工(重庆)海装风电设备有限公司 | Lubricating grease adding method and lubricating system for pitch bearing of wind turbine generator system |
| CN104598666A (en) * | 2014-12-01 | 2015-05-06 | 哈尔滨理工大学 | Large-scale hydrostatic support critical load parameter acquiring method |
| CN105135197A (en) * | 2015-09-02 | 2015-12-09 | 哈尔滨理工大学 | Lubricating property forecasting method of double-rectangular-cavity hydrostatic thrust bearing |
Also Published As
| Publication number | Publication date |
|---|---|
| CN106870911A (en) | 2017-06-20 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| Mazloum et al. | Dynamic modeling and simulation of an isobaric adiabatic compressed air energy storage (IA-CAES) system | |
| Malinowski et al. | Analytical model-based energy and exergy analysis of a gas microturbine at part-load operation | |
| Joudi et al. | Development of design charts for solar cooling systems. Part I: computer simulation for a solar cooling system and development of solar cooling design charts | |
| CN110163411A (en) | A kind of regional complex energy system operation optimization method | |
| CN109063255B (en) | Energy-saving control method, electronic equipment, storage medium, device and system | |
| CN109858129B (en) | Gas turbine dynamic simulation method for triple co-generation system | |
| Balli et al. | Various thermoeconomic assessments of a heat and power system with a micro gas turbine engine used for industry | |
| CN112165122A (en) | Operation method and system of comprehensive energy system | |
| Liu et al. | Thermal economy analysis and multi-objective optimization of a small CO2 transcritical pumped thermal electricity storage system | |
| Sonawat et al. | Positive displacement turbine-A novel solution to the pressure differential control valve failure problem and energy utilization | |
| CN103063354A (en) | Confirming method for turbine standard backpressure in thermal power generating unit energy consumption assessment and coal consumption check test | |
| Lu et al. | Dynamic modeling and numerical investigation of novel pumped thermal electricity storage system during startup process | |
| CN116384088A (en) | A Design Method of Residual Energy Utilization System Considering Equipment Variable Efficiency Model | |
| Campanari et al. | Microturbines and trigeneration: optimization strategies and multiple engine configuration effects | |
| CN106870911B (en) | The design method and device of lubricating oil system for air blower and compressor subsidiary engine | |
| Gurgenci | Performance of power plants with organic Rankine cycles under part-load and off-design conditions | |
| He et al. | Thermodynamic investigation of variable‐speed compression unit in near‐isothermal compressed air energy storage | |
| Guo et al. | Optimization strategy using corresponding-point methodology (CPM) concerning finite time and heat conduction rate for CAES systems | |
| Cheng et al. | CAES-SC hybrid energy storage: Dynamic characteristics and control via discharge process | |
| Misenheimer et al. | Modeling hybrid nuclear systems with chilled-water storage | |
| CN108197412B (en) | Multi-energy coupling energy management system and optimization method | |
| CN110553308A (en) | An energy cooperative operation control system | |
| Zhang et al. | Quantification of model uncertainty of water source heat pump and impacts on energy performance | |
| Sun et al. | Experimental study on the influence of pump frequencies and oil flow rates on the performance of organic rankine cycle systems | |
| CN116881758A (en) | Method for establishing basic unit model of comprehensive energy system based on statistical synthesis method |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20220706 Address after: 110027 No. 16 A-17, Kaifa Road, Shenyang Economic and Technological Development Zone, Liaoning Province Patentee after: Shenyang general equipment branch of Shenyang Blower Group Co.,Ltd. Address before: 110869 No. 16 A Development Road, Shenyang Economic and Technological Development Zone, Liaoning Province Patentee before: SHENYANG BLOWER WORKS GROUP PRESSURE VESSEL Co.,Ltd. |
|
| TR01 | Transfer of patent right |