The document discusses compressor surge in centrifugal compressors. It defines surge as a condition where the flow of gas reverses direction in the compressor due to an imbalance between the compressor's delivery pressure and the downstream system pressure. This causes surging of gas flow at frequencies of 0.3 to 3 seconds per cycle. The document outlines factors that can lead to surge, provides a theoretical compressor characteristics curve to illustrate stable and unstable operating regions, describes the surge cycle in detail, and explains that the purpose of an antisurge control system is to prevent the operating point from reaching the surge limit line through controlled opening of an antisurge valve.
In the hydrocarbon processing and production industry, gas is compressed for transportation to consuming markets and for use in processing operations. This presentation is about the construction and operation of compressors.
In this presentation you will learn about the construction and operation of centrifugal compressors.
This compressor works on the principle of centrifugal action. It finds wide variety of applications in engineering field. It is available in market from low to high capacities.
Centrifugal Compressors
SECTION ONE - ANTI-SURGE PROTECTION AND THROUGHPUT REGULATION
0 INTRODUCTION
1 SCOPE
2 MACHINE CHARACTERISTICS
2.1 Characteristics of a Single Compressor Stage
2.2 Characteristic of a Multiple Stage Having More
Than One Impeller
2.3 Use of Compressor Characteristics in Throughput
Regulation Schemes
3 MECHANISM AND EFFECTS OF SURGE
3.1 Basic Flow Instabilities
3.2 Occurrence of Surge
3.3 Intensity of Surge
3.4 Effects of Surge
3.5 Avoidance of Surge
3.6 Recovery from Surge
4 CONTROL SCHEMES INCLUDING SURGE PROTECTION
4.1 Output Control
4.2 Surge Protection
4.3 Surge Detection and Recovery
5 DYNAMIC CONSIDERATIONS
5.1 Interaction
5.2 Speed of Response of Antisurge Control System
6 SYSTEM EQUIPMENT SPECIFICATIONS
6.1 The Antisurge Control Valve
6.2 Non-return Valve
6.3 Pressure and flow measurement
6.4 Signal transmission
6.5 Controllers
7 TESTING
7.1 Determination of the Surge Line
7.2 Records
8 INLET GUIDE VANE UNITS
8.1 Application
8.2 Effect on Power Consumption of the Compressor
8.3 Effect of Gas Conditions, Properties and Contaminants
8.4 Aerodynamic Considerations
8.5 Control System Linearity
8.6 Actuator Specification
8.7 Avoidance of Surge
8.8 Features of Link Mechanisms
8.9 Limit Stops and Shear Links
APPENDICES
A LIST OF SYMBOLS AND PREFERRED UNITS
B WORKED EXAMPLE 1 COMPRESSOR WITH VARIABLE INLET PRESSURE AND VARIABLE GAS COMPOSITION
C WORKED EXAMPLE 2 A CONSTANT SPEED ~ STAGE COMPRESSOR WITH INTER-COOLING
D WORKED EXAMPLE 3 DYNAMIC RESPONSE OF THE ANTISURGE PROTECTION SYSTEM FOR A SERVICE AIR COMPRESSOR RUNNING AT CONSTANT SPEED
E EXAMPLE OF INLET GUIDE VANE REGULATION
FIGURES
2.1 TYPICAL COMPRESSOR STAGE CHARACTERISTIC PLOTTED WITH FLOW AT DISCHARGE CONDITIONS
2.2 TYPICAL COMPRESSOR STAGE CHARACTERISTIC PLOTTED WITH FLOW AT INLET CONDITIONS
2.3 PERFORMANCE CHARACTERISTICS OF A COMPRESSOR STAGE AT VARYING SPEEDS
2.4 SYSTEM WORKING POINT DEFINED BY INTERSECTION OF PROCESS AND COMPRESSOR CHARACTERISTICS
2.5 DISCHARGE THROTTLE REGULATION
2.6 BYPASS REGULATION
2.7 INLET THROTTLE REGULATION
2.8 INLET GUIDE VANE REGULATION
2.9 VARIABLE SPEED REGULATION
3.1 GAS PULSATION LEVELS FOR A CENTRIFUGAL COMPRESSOR
3.2 REPRESENTATION OF CYCLIC FLOW DURING SURGE OF LONG PERIOD
3.3 TYPICAL WAVEFORM OF DISCHARGE PRESSURE DURING SURGE
3.4 MULTIPLE SURGE LINE FOR A MULTISTAGE CENTRIFUGAL COMPRESSOR
3.5 TYPICAL MULTIPLE SURGE LINES FOR SINGLE STAGE AXIAL-FLOW COMPRESSOR
4.1 GENERAL SCHEMATIC FOR COMPRESSORS OPERATING IN PARALLEL TO FEED MULTIPLE USER PLANTS
4.2 ILLUSTRATION OF SAFETY MARGIN BETWEEN SURGE POINT AND SURGE PROTECTION POINT AT WHICH ANTISURGE SYSTEM IS ACTIVATED
4.3 ANTISURGE SYSTEM FOR COMPRESSOR WITH FLAT PERFO ..........
In the hydrocarbon processing and production industry, gas is compressed for transportation to consuming markets and for use in processing operations. This presentation is about the construction and operation of compressors.
In this presentation you will learn about the construction and operation of centrifugal compressors.
This compressor works on the principle of centrifugal action. It finds wide variety of applications in engineering field. It is available in market from low to high capacities.
Centrifugal Compressors
SECTION ONE - ANTI-SURGE PROTECTION AND THROUGHPUT REGULATION
0 INTRODUCTION
1 SCOPE
2 MACHINE CHARACTERISTICS
2.1 Characteristics of a Single Compressor Stage
2.2 Characteristic of a Multiple Stage Having More
Than One Impeller
2.3 Use of Compressor Characteristics in Throughput
Regulation Schemes
3 MECHANISM AND EFFECTS OF SURGE
3.1 Basic Flow Instabilities
3.2 Occurrence of Surge
3.3 Intensity of Surge
3.4 Effects of Surge
3.5 Avoidance of Surge
3.6 Recovery from Surge
4 CONTROL SCHEMES INCLUDING SURGE PROTECTION
4.1 Output Control
4.2 Surge Protection
4.3 Surge Detection and Recovery
5 DYNAMIC CONSIDERATIONS
5.1 Interaction
5.2 Speed of Response of Antisurge Control System
6 SYSTEM EQUIPMENT SPECIFICATIONS
6.1 The Antisurge Control Valve
6.2 Non-return Valve
6.3 Pressure and flow measurement
6.4 Signal transmission
6.5 Controllers
7 TESTING
7.1 Determination of the Surge Line
7.2 Records
8 INLET GUIDE VANE UNITS
8.1 Application
8.2 Effect on Power Consumption of the Compressor
8.3 Effect of Gas Conditions, Properties and Contaminants
8.4 Aerodynamic Considerations
8.5 Control System Linearity
8.6 Actuator Specification
8.7 Avoidance of Surge
8.8 Features of Link Mechanisms
8.9 Limit Stops and Shear Links
APPENDICES
A LIST OF SYMBOLS AND PREFERRED UNITS
B WORKED EXAMPLE 1 COMPRESSOR WITH VARIABLE INLET PRESSURE AND VARIABLE GAS COMPOSITION
C WORKED EXAMPLE 2 A CONSTANT SPEED ~ STAGE COMPRESSOR WITH INTER-COOLING
D WORKED EXAMPLE 3 DYNAMIC RESPONSE OF THE ANTISURGE PROTECTION SYSTEM FOR A SERVICE AIR COMPRESSOR RUNNING AT CONSTANT SPEED
E EXAMPLE OF INLET GUIDE VANE REGULATION
FIGURES
2.1 TYPICAL COMPRESSOR STAGE CHARACTERISTIC PLOTTED WITH FLOW AT DISCHARGE CONDITIONS
2.2 TYPICAL COMPRESSOR STAGE CHARACTERISTIC PLOTTED WITH FLOW AT INLET CONDITIONS
2.3 PERFORMANCE CHARACTERISTICS OF A COMPRESSOR STAGE AT VARYING SPEEDS
2.4 SYSTEM WORKING POINT DEFINED BY INTERSECTION OF PROCESS AND COMPRESSOR CHARACTERISTICS
2.5 DISCHARGE THROTTLE REGULATION
2.6 BYPASS REGULATION
2.7 INLET THROTTLE REGULATION
2.8 INLET GUIDE VANE REGULATION
2.9 VARIABLE SPEED REGULATION
3.1 GAS PULSATION LEVELS FOR A CENTRIFUGAL COMPRESSOR
3.2 REPRESENTATION OF CYCLIC FLOW DURING SURGE OF LONG PERIOD
3.3 TYPICAL WAVEFORM OF DISCHARGE PRESSURE DURING SURGE
3.4 MULTIPLE SURGE LINE FOR A MULTISTAGE CENTRIFUGAL COMPRESSOR
3.5 TYPICAL MULTIPLE SURGE LINES FOR SINGLE STAGE AXIAL-FLOW COMPRESSOR
4.1 GENERAL SCHEMATIC FOR COMPRESSORS OPERATING IN PARALLEL TO FEED MULTIPLE USER PLANTS
4.2 ILLUSTRATION OF SAFETY MARGIN BETWEEN SURGE POINT AND SURGE PROTECTION POINT AT WHICH ANTISURGE SYSTEM IS ACTIVATED
4.3 ANTISURGE SYSTEM FOR COMPRESSOR WITH FLAT PERFO ..........
Centrifugal compressor anti-surge control system modellingIJECEIAES
From the middle of XX century, natural gas is an important mineral, widely used in the energy sector. Transportation of natural gas is carried out via gas pipeline networks and compression stations. One of the key features which need to be implemented for any centrifugal gas compressor is a surge protection. This article describes the method and develops software application intended for simulation and study of surge protection system of a centrifugal compressor used in modern gas compression stations. Within the article research method, modelling environment’s block diagram, proposed algorithms and results are described. For surge cases control and prediction, Anti-surge control block implemented which based on practical experience and centrifugal compressor theory. To avoid complicated energy balancing differential equations the volumetric flow calculation algorithm proposed which is used in combination with Redlich-Kwong equation of state. Developed software’s adequacy test performed through modeling of onestage gas compression scheme at rated speed with comparison of parameters with reference commercial software and verification of the anti-surge control system.
A steam turbine is a prime mover in which the potential energy of the steam is transformed into kinetic energy and later in its turn is transformed into the mechanical energy of rotation of the turbine shaft
Surging is associated with sudden drop in delivery pressure & with violent aerodynamic pulsation which is transmitted throughout the machine
the position is reached where no further increase in mass flow can be obtained no matter how wide open the control valve is ‐ CHOKING
Centrifugal compressor anti-surge control system modellingIJECEIAES
From the middle of XX century, natural gas is an important mineral, widely used in the energy sector. Transportation of natural gas is carried out via gas pipeline networks and compression stations. One of the key features which need to be implemented for any centrifugal gas compressor is a surge protection. This article describes the method and develops software application intended for simulation and study of surge protection system of a centrifugal compressor used in modern gas compression stations. Within the article research method, modelling environment’s block diagram, proposed algorithms and results are described. For surge cases control and prediction, Anti-surge control block implemented which based on practical experience and centrifugal compressor theory. To avoid complicated energy balancing differential equations the volumetric flow calculation algorithm proposed which is used in combination with Redlich-Kwong equation of state. Developed software’s adequacy test performed through modeling of onestage gas compression scheme at rated speed with comparison of parameters with reference commercial software and verification of the anti-surge control system.
A steam turbine is a prime mover in which the potential energy of the steam is transformed into kinetic energy and later in its turn is transformed into the mechanical energy of rotation of the turbine shaft
Surging is associated with sudden drop in delivery pressure & with violent aerodynamic pulsation which is transmitted throughout the machine
the position is reached where no further increase in mass flow can be obtained no matter how wide open the control valve is ‐ CHOKING
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SAIF ALDIN ALI MADIN
سيف الدين علي ماضي
S96aif@gmail.com
Presentation
on
Axial Flow Compressor
Introduction
Construction
Working
Design
Main Parts
Stalling
Surging
Stage Losses
Advantages - Disadvantages & Applications
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Explore the heart of refrigeration systems with this insightful presentation on refrigerant compressors. Learn about different types of compressors, their working principles, and gain practical insights through numerical examples. Whether you're a student or a professional in the field, this slide deck provides valuable knowledge in the realm of HVAC and refrigeration technology
This document was produced as part of my final year project of training to obtain a petroleum engineering diploma.
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2. INDEX:
• Effects of Compressor Surge.
• Factors Leading to Onset of Surge.
• Theoretical characteristic curve of compressor.
• Surge Description.
• Developing Surge Cycle on Performance curves.
• Purpose of Antisurge control system.
3. EFFECTS OF COMPRESSOR SURGE:
• Flow reverses in 20 to 50 milliseconds
• Surge cycles at a rate of 0.3 s to 3 s per cycle
• Compressor vibrates.
• Temperature rises.
• “Whooshing” noise.
• Trips may occur.
• Conventional instruments and human operators may fail to recognize
surge.
4. FACTORS LEADING TO ONSET OF SURGE:
• Startup
• Shutdown
• Operation at reduced throughput
• Operation at heavy throughput with:
• Trips Power loss
• Operator errors Process upsets
• Load changes Gas composition changes
• Cooler problems Filter or strainer problems
• Driver problems
• Surge is not limited to times of reduced throughput. Surge can occur at
full operation
5. THEORETICAL CHARACTERISTICS CURVE XYZ:
Theoretical characteristics curve XYZ for a constant speed:
22-Jun-19 5
Mass flow
PressureRatio
0
1
X
Y
Z
S
O
X-Y: Unstable
Y-O; Stable
Y Maximum
Efficiency and
Pressure Ratio
X, Pressure head produced by the action of the
impeller on the gas trapped between the vanes
Onset of
Surge
Stonewall point
Maximum flow
6. THEORETICAL CHARACTERISTICS CURVE XYZ:
CONTINUED
Point X:
The centrifugal pressure head produced by the action of the impeller on the gas
trapped between the vanes. As flow is increased diffuser begins to influence the
pressure rise, for which the pressure ratio increases upto point B.
Point Y:
Efficiency approaches its maximum and the pressure ratio also reaches its
maximum. Further increase of mass flow will result in a fall of pressure ratio.
Point Z:
For mass flows greatly in excess of that corresponding to the design mass flow,
the gas angles will be widely different from the vane angles and breakaway of
the gas will occur. In this hypothetical case, the pressure ratio drops to unity
at ‘Z' and all the power is absorbed in overcoming internal frictional resistances.
7. SURGE DESCRIPTION:
• If we suppose that the compressor is operating at a point ‘S' on the part
of characteristics curve having a positive slope, then a decrease in mass
flow will be accompanied by a fall in pressure at diffuser outlet.
• If the pressure of the gas downstream of the compressor does not fall
quickly enough, the gas will tend to reverse its direction and will flow
back in the direction of the resulting pressure gradient.
• When this occurs, the pressure ratio drops rapidly causing a further drop
in mass flow until the point ‘X' is reached, where the mass flow is zero.
• When the pressure downstream of the compressor has reduced
sufficiently due to reduced mass flow rate, the positive flow becomes
established again and the compressor picks up to repeat the cycle of
events which occurs at high frequency.
8. • This surging of gas may not happen immediately when the operating
point moves to the left of ‘Y' because the pressure downstream of the
compressor may at first fall at a greater rate than the delivery pressure.
• As the mass flow is reduced further, the flow reversal may occur and the
conditions are unstable between ‘X' and ‘Y'.
• As long as the operating point is on the part of the characteristics having
a negative slope (Y to Z), however, decrease in mass flow is
accompanied by a rise in delivery pressure and the operation is stable.
9. Developing the surge cycle on the compressor curve
Qs, vol
Pv / Pd
Machine shutdown
no flow, no pressure
Flow rate decreased then,
• Pressure builds
• Resistance goes up
• Compressor “rides” the curve
A
• Compressor reaches surge point A
• Compressor looses its ability to make
pressure
• Suddenly Pd drops and thus Pv > Pd
• Plane goes to stall - Compressor surges
Pd
To Vent
Surge Cycle diagram
Pv
Diffuser outlet pressure = Pd
Discharge header pressure = Pv
10. A-B-C (Pv ) and A-C-B-C (Pd )
Qs, vol
Pv / Pd
A
B
• Because Pv > Pd the flow reverses
• Compressor operating point goes to point B
C
D
Pd
To Vent
Surge Cycle diagram
Pv
Diffuser outlet pressure = Pd
Discharge header pressure = Pv
• Diffuser outlet pressure decreases with flow rate as it
follows theoretical characteristic curve
• Due to pressure difference reverse flow occurs.
• Diffuser outlet pressure increases due to reverse flow until both are equal.
• At this presssure compressor is not able to develop forward flow.
• Further Pd follows Pv to reach point C.
11. C-D-A
Qs, vol
Pv / Pd
A
B
C
C:
• Discharge header pressure (Pv)= Diffuser outlet pressure (Pd ) due to reduce in
input and flow reversal.
• At this pressure compressor is able to pick forward flow
• Pressure goes down => less negative flow
D
D
• Compressor “jumps” back to
performance curve and goes to point D
• Forward flow is re-established
Pd
To Vent
A
• Compressor starts to build pressure
• Compressor “rides” curve towards surge
• Point A is reached
• The surge cycle is complete
• From A to B 20 - 50 ms Drop into surge
• From C to D 20 - 120 ms Jump out of surge
• A-B-C-D-A 0.3 - 3 seconds Surge cycle
Surge Cycle diagram
Pv
Diffuser outlet pressure = Pd
Discharge header pressure = Pv
12.
13. PURPOSE OF ANTISURGE CONTROL SYSTEM:
• The purpose of the “ANTISURGE CONTROL SYSTEM” is to avoid the
operating point “A” reaches the “Surge Limit Line”.
• To achieve this objective, it’s defined, on the right of the “SLL”, a
protection line where the control system will operate opening the
antisurge valve.
• This line is called “SURGE CONTROL LINE” (“SCL”). Usually 10 % of
flow margin.
• The opening of the antisurge valve increases the suction flow moving the
operating point along the speed characteristic curve, from the critical
condition to the stable operating area.