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Compressor design
- Thread starter AnhsirkT
- Start date
so overall temp will reduce but not less than suction temp (it will in b/w both of them ) so no chance of liquid droplets
You seem to be comparing at equal pressure level. The reality is that pressure at discharge is higher than suction which means dew point may increase and it may increase significantly or not depending on your liquid-vapor phase envelope. It may work but we do not have all the details.
But certainly, relying on suction temperature as criterion means you are ignoring the above.
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You seem to be comparing at equal pressure level. The reality is that pressure at discharge is higher than suction which means dew point may increase and it may increase significantly or not depending on your liquid-vapor phase envelope. It may work but we do not have all the details.
But certainly, relying on suction temperature as criterion means you are ignoring the above.
If you plan an escape, you must succeed as if you fail, you will be punished for trying. Never say or write down your plan. Heart is the only place where secrecy is granted.
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- #22
For dew point analysis @ main feed it is : pressures @ 1st stage suction and 2nd stage suction.
See attached a generic example to illustrate the concept (applies generally).
Obviously considerations are to be taken into account, for example if side stream and main feed stream have identical gas composition.
If you have superheated pure Ethylene, then what is the knock out drum purpose?
See attached a generic example to illustrate the concept (applies generally).
Obviously considerations are to be taken into account, for example if side stream and main feed stream have identical gas composition.
If you have superheated pure Ethylene, then what is the knock out drum purpose?
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- #24
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- #25
Actually KO drum just for safety if any liquid appear then drain out (dry drum).
Ethylene in theses drums at superheated condition (10C more than dew point)
So final combination also at superheated condition there is never any condition at which ethylene get condesed.
Let's say 2S stage suction at dew point (7 bar -62C) than 1 S dicharge will definitely superheated after compression (7.2bar 20or 25C) and mixture will be will give temperature more than -61C so superheated
Ethylene in theses drums at superheated condition (10C more than dew point)
So final combination also at superheated condition there is never any condition at which ethylene get condesed.
Let's say 2S stage suction at dew point (7 bar -62C) than 1 S dicharge will definitely superheated after compression (7.2bar 20or 25C) and mixture will be will give temperature more than -61C so superheated
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- #27
If side stream not superheated than also some things mixing with this is superheated (same ethylene )than mixture will be superheated
'' Let's say 2S stage suction at dew point (7 bar -62C) than 1 S dicharge will definitely superheated after compression (7.2bar 20or 25C) and mixture will be will give temperature more than -61C so superheated''
'' Let's say 2S stage suction at dew point (7 bar -62C) than 1 S dicharge will definitely superheated after compression (7.2bar 20or 25C) and mixture will be will give temperature more than -61C so superheated''
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- #28
By the way, can you give the pressures, expected temperatures and flow capacity from first suction to final discharge?
If you plan an escape, you must succeed as if you fail, you will be punished for trying. Never say or write down your plan. Heart is the only place where secrecy is granted.
If you plan an escape, you must succeed as if you fail, you will be punished for trying. Never say or write down your plan. Heart is the only place where secrecy is granted.
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- #30
You did not provide the capacities? Despite this missing information, here are some thoughts:
Are looking at the most effective design? see explanation below (referring to multistage centrifugal compressor design; CAUTION: the below preliminary analysis is depending on the flow capacities involved which you did not provide):
1 S 1.4BAR D 8.2BAR -> compression ratio requires 4 impellers @ max peripheral speed < 290 m/s
2 S 8 BAR 10.5BAR -> compression ratio requires 1 impeller @ max peripheral speed < 200 m/s
3 S 10.3 BAR 17BAR -> compression ratio requires 1 impeller @ max peripheral speed < 290 m/s
Mobilizing a dedicated compressor casing for a single impeller does not look very economical with reference to stage 2 and 3.
The selection should fit a single horizontally-split casing of six impellers 4+1+1 (3 sections) and with two injections (side streams).
This way you do not have to worry about design 1 vs. 2, basically the mixing occurs inside the compressor (stage diffuser / return channel).
The flow capacities involved, will dictate if the flows are realistic for centrifugal type design and whether you need 3D type of impellers which would add some stringency to the rotor-dynamics, should it be all 2D's type this does not appear as a difficult machine to build.
If you plan an escape, you must succeed as if you fail, you will be punished for trying. Never say or write down your plan. Heart is the only place where secrecy is granted.
Are looking at the most effective design? see explanation below (referring to multistage centrifugal compressor design; CAUTION: the below preliminary analysis is depending on the flow capacities involved which you did not provide):
1 S 1.4BAR D 8.2BAR -> compression ratio requires 4 impellers @ max peripheral speed < 290 m/s
2 S 8 BAR 10.5BAR -> compression ratio requires 1 impeller @ max peripheral speed < 200 m/s
3 S 10.3 BAR 17BAR -> compression ratio requires 1 impeller @ max peripheral speed < 290 m/s
Mobilizing a dedicated compressor casing for a single impeller does not look very economical with reference to stage 2 and 3.
The selection should fit a single horizontally-split casing of six impellers 4+1+1 (3 sections) and with two injections (side streams).
This way you do not have to worry about design 1 vs. 2, basically the mixing occurs inside the compressor (stage diffuser / return channel).
The flow capacities involved, will dictate if the flows are realistic for centrifugal type design and whether you need 3D type of impellers which would add some stringency to the rotor-dynamics, should it be all 2D's type this does not appear as a difficult machine to build.
If you plan an escape, you must succeed as if you fail, you will be punished for trying. Never say or write down your plan. Heart is the only place where secrecy is granted.
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- #32
Yes I am planning to make 2 casing
First with 1 section
Second casing with two sections(2&3)
Flow is 200tonnes/hr.
But design 2 required only 4MOV moter ooerted valve to isolate casing and no chance of condensate so is it good?
Your singal casing idea is good.
but if two casing provide then first casing discharge should go to second casing via KO drum or directly in line ?
First with 1 section
Second casing with two sections(2&3)
Flow is 200tonnes/hr.
But design 2 required only 4MOV moter ooerted valve to isolate casing and no chance of condensate so is it good?
Your singal casing idea is good.
but if two casing provide then first casing discharge should go to second casing via KO drum or directly in line ?
200 t/h is the inlet rated capacity? it is also needed to know side streams to have the complete pictures.
Anyway, this would require a single casing, 6 stage horizontally-split compressor (roughly: 4 x 900 mm + 1 x 650 mm + 1 x 900 mm), with two injections. The 1st two impellers of the 1st section should be 3D type and for 2nd section a 2D type impeller should be possible. Rated speed ~ 5500 rpm.
I would be preferable to balance the load / inter-stage pressure between 1st and 2nd stage so to have 3 stage on 1st section, if process allows for this adjustment.
Edit: a more than one casing - solution could cost between 1 to 1.5 Million USD extra in terms of capital equipment cost. Other potential impacts:
-Increased installed costs;
-Additional process and utility piping and instruments;
-Substantially increased footprint and equipment weight;
-Increased utility consumption;
-Additional dry gas seal panels, bigger lube oil system size.
What driver type are you considering.
Anyway, this would require a single casing, 6 stage horizontally-split compressor (roughly: 4 x 900 mm + 1 x 650 mm + 1 x 900 mm), with two injections. The 1st two impellers of the 1st section should be 3D type and for 2nd section a 2D type impeller should be possible. Rated speed ~ 5500 rpm.
I would be preferable to balance the load / inter-stage pressure between 1st and 2nd stage so to have 3 stage on 1st section, if process allows for this adjustment.
Edit: a more than one casing - solution could cost between 1 to 1.5 Million USD extra in terms of capital equipment cost. Other potential impacts:
-Increased installed costs;
-Additional process and utility piping and instruments;
-Substantially increased footprint and equipment weight;
-Increased utility consumption;
-Additional dry gas seal panels, bigger lube oil system size.
What driver type are you considering.
- Thread starter
- #34
It is needed the capacity through each stage the machine not just the total at outlet; so you have
1st stage = 80 kg/h through stage
2nd stage = 80 + 80 (injection) = 160 kg/h through stage
3rd stage = 160 + 40 (injection) = 200 kg/h through stage
is this correct?
If you plan an escape, you must succeed as if you fail, you will be punished for trying. Never say or write down your plan. Heart is the only place where secrecy is granted.
1st stage = 80 kg/h through stage
2nd stage = 80 + 80 (injection) = 160 kg/h through stage
3rd stage = 160 + 40 (injection) = 200 kg/h through stage
is this correct?
If you plan an escape, you must succeed as if you fail, you will be punished for trying. Never say or write down your plan. Heart is the only place where secrecy is granted.
- Thread starter
- #36
right it is t/h.
Ok, something like this:
4 x 900 mm + 1 x 630 mm + 1 x 900 mm
Absorbed power ~ 6.8 MW (total)
Rated speed ~ 5500 rpm.
1st impeller 3D high Mach followed by conventional 3D or a 2D. The rest are all 2D impellers.
At first sight, does not seem to be any problematic rotor-dynamically.
I do not see any reason for a two casing solution let alone a three casing.
On the injection lines, you may need to put a knock out drum on each line, but not even sure of this, ask process engineering. Ask them also if there is room to adjust the load between 1st and 2nd stage (inter-stage pressure) - but it is not a must.
If you plan an escape, you must succeed as if you fail, you will be punished for trying. Never say or write down your plan. Heart is the only place where secrecy is granted.
Ok, something like this:
4 x 900 mm + 1 x 630 mm + 1 x 900 mm
Absorbed power ~ 6.8 MW (total)
Rated speed ~ 5500 rpm.
1st impeller 3D high Mach followed by conventional 3D or a 2D. The rest are all 2D impellers.
At first sight, does not seem to be any problematic rotor-dynamically.
I do not see any reason for a two casing solution let alone a three casing.
On the injection lines, you may need to put a knock out drum on each line, but not even sure of this, ask process engineering. Ask them also if there is room to adjust the load between 1st and 2nd stage (inter-stage pressure) - but it is not a must.
If you plan an escape, you must succeed as if you fail, you will be punished for trying. Never say or write down your plan. Heart is the only place where secrecy is granted.
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