I see that you changed the pic to show my condenser/separator idea. Thanks, Chilly. You do nice work. :D
http://www.blairwing.com/images/Autocascade14.jpg
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I see that you changed the pic to show my condenser/separator idea. Thanks, Chilly. You do nice work. :D
http://www.blairwing.com/images/Autocascade14.jpg
We discussed this condenser idea before I still don't know how to size them I have a call in to my supplier for a quote when and if they get back to me I'll send you what I have.. I am looking for enthlpy charts and other data to better calculate the sizing on these systems, still a lot to learn so I'll keep looking...
Chilly1, if you download and install the coolpack refrigeration utillities you will be able to get a P-h chart for R290. I've linked to it below.
http://www.et.dtu.dk/Coolpack/Files/RefUtil.exe 2.69MB
The cap tubes are:
96" R23
82" R290
I will cut another 12" off the R290 tube and that will bring us closer to the 65% ratio.
I thought the physical properties of the refrigerants would also have an effect on the mass flow rate through the cap tube, so just sizing them by comparing the densities does not make sense to me.
I have nothing to recover the gas to, so its fresh charge from scratch every time I recharge.
If there were shutoff valves in both liquid lines, you could pump down the system to make adjustments (cut cap tubes, change driers, etc.) without losing any of the charge, although you would need to watch the static pressures very closely as they may rise to dangerous levels.
Yup, all this would be great if I had easy access to refrigeration components. Unfortunatly as I am not in the trade or any trade (being a student at the moment) it makes it rather more interesting when trying to obtain parts for my system. As it stands I have to buy all the tools and parts to do anything as my previous tool inventory consisted of a spanner, hammer and some screwdrivers. This makes things somewhat more costly in the short term. :( All this aside it still alot of fun :D
Cap tube has been cut, this time i took it off the other end at the evaporator. Im in the process of recharging the system. Im going to try a new thermal compound between the cpu and evap. Its rated to -150ºC compared to the previous -40ºC.
These are the numbers for the cpu on idle (1.89v@2700MHz approx. 120Watts) with the shorter R290 cap tube
Idle
R23
Evap Exit: -51.0ºC
SST: -59ºC (2.2 barg)
SCT: -5ºC (21 barg)
R290
Evap Exit: 16.5ºC
SST: -12ºC (2.2 barg)
SCT: 62ºC (21 barg)
Air in: 19.3ºC
Air out: 25.1C
CPU: -11ºC
Gary, how much more should I cut off. I've currently got the cap tubes at:
95" R23
70" R290
The R290 tube is getting close to the 5 foot mark. I chopped an inch off the R23 tube when I was redoing the R290, long story but it had to be done.
Aren't you going to post the current full load numbers, too?
Ok, I changed the charge a little to see what I could get, here are the numbers from running full load.
R23
Evap Exit: -42.2ºC
SST: -58ºC (2.4 barg)
SCT: -3ºC (22.1 barg)
R290
Evap Exit: 17.8ºC
SST: -10ºC (2.4 barg)
SCT: 65ºC (22.1 barg)
Air in: 20.4ºC
Air out: 27.1C
CPU: 3ºC
Russel thanks for the chart I am doing the calcs now it will be a few days as I have to pull my old textbooks out there are a few principles I need to brush up on..
Note that the condenser delta-T, under full load, has been progressively increasing as we shorten the cap tube. Assuming the condenser airflow has not changed, we are pumping progressively more heat. This is a good sign. We are getting there.
Keep on chopping. :D
Less than 5 feet is getting into the unstable range, but let's cross that bridge when we get to it. Cut it to 5 feet and see if that does it.
Air flow hasn't changed. How much will I take off this time, 6inches?
Sorry, I have a bad habit of editing. Seems I was editing while you were posting. Cut it to 5 feet and let's see what that does.
R290 and R23 when you Factor in the P/T and Enthalpy The closet we can get is 55% and we are there with the current cap tub length. The amount of heat the refrigerant is capable of carrying (enthalpy) needs to be at the ratio of 65% so we are out of balance by 10% when you started trimming the cap tube you were out 18% What we need to do is test using the exact same load and charge every time and change only one variable. Otherwise the system becomes harder to predict. As a guess I would say that we need to increase the pressure in the r23 evaporator and decrease the pressure in the R290 evap. We need to have an epr valve set at .8 bar between the evaporators This is still preliminary I need to factor in the HOC and the heat added by the motor.
An EPR cannot bring the pressure down to .8 bar. It can only bring the pressure up to .8 bar, IF the pressure drops below that point.
Aint autocascades fun :D
Im having some beers and watching films so work is off for the moment. Im 23 tomorrow, lets hope some birthday luck will kick in when I trim the cap down to 5 feet. I can see the temperatures are getting better with each cut of the tube, so lets hope the next one will do it. Talk later guys, let me know if you think of something ingenious that will help this system. I know you love the autocascade :D
Happy Birthday, Russell. :D
(Trying to remember 23... late 60's... after nam... before college... nope, can't remember a thing... must have been the drugs... LOL)
Sorry, Gary I meant a .8 bar delta across the valve making the suctionpressure on the R290 .8 bar less than the R23 evaporator. This would balance the system and give us an adjustment for tuning it.Quote:
Originally posted by Gary Lloyd
An EPR cannot bring the pressure down to .8 bar. It can only bring the pressure up to .8 bar, IF the pressure drops below that point.
I've done the last chop on the cap tube, from charging and watching temps, I feel this last chop has had a detrimental effect on the system. Could this be possible? Im just pulling down the system at the moment then im going to run full load at 2700MHz@1.89v and give you some numbers. Im thinking a chop on the R23 tube might help, though I could be wrong.
One more thing. Im trying to find out the rpm of my compressor, as I know the displacement I could then calculate the voulmetric flowrate if i know the rpm. I've looked at the manufacturers website and have been unable to find a number. Got any ideas?
Here are the numbers after running full load for 20 minutes:
R23
Evap Exit: -38.7ºC
SST: -58ºC (2.4 barg)
SCT: -3ºC (22.1 barg)
R290
Evap Exit: 20.1ºC
SST: -10ºC (2.4 barg)
SCT: 65ºC (22.1 barg)
Air in: 22.4ºC
Air out: 28.4C
CPU: 6ºC
It looks like you are using a tiny bit less R23 this time. Last time your evap exit was -42C.
I'm assuming the sight glass is clear, right?
I would keep chopping. Even though this takes us into the unstable range, when we see what size works, we can figure out what size to substitute.
The R23 cap tube is just right. I would leave it alone.
The tech sheet says it consumes 698 Watts and has a COP of 1.69 if thats any help.
The sight glass is about 85% full with a stream of bubbles comming up from the bottom.
I have studied the tech sheet, and am still puzzled. The inability to flood the R290 evaporator is the puzzle, but at some point it must push through. How could it not?
Add R290. The sight glass must be clear.
Maybe its just sucking the R23 and leaving the R290 to just sit there? The Suction line near the compressor, and after the R23/R290 junction is definatly sub zero.
The whole purpose of shortening the cap tube is to push the R290 through the evap. If there isn't solid liquid at the cap tube entrance, then this is far less likely to happen. We need that sightglass to be clear. Add More R290 until it is clear.
The R23 is doing exactly what it is supposed to do. it is flooding its evap, absorbing the heat load, and is superheated at the exit, meaning it is entirely vapor at that point.
If only the R290 evap were working that well. But we are not going to flood that evaporator with liquid by feeding it vapor. The sight glass must be clear.
Hoping you are keeping up with my chronic editing... LOL
Another point on clearing the sight glass. If the sight glass shows 85% liquid and 15% vapor, I would assume that the 15% is R23, which robs the R23 evap of part of its refrigerant, while starving the R290 evap.
R290 cannot condense at this point, therefore if the sight glass is clear, we know that the separation is complete.
Im adding more R290 but its hurting my cpu temperatures as the R23 SCT is rising due to LP rising. I'm still adding the R290. Do i keep going till there are absolutely no bubbles. I normally have a stream of bubbles rushing from the inlet pipe to the outlet pipe when I look in the sightglass, even when the sightglass appears full. The flow enters from the bottom of the sight glass if that makes any difference.
Is the exit temperature dropping?
The less bubbles, the more complete the separation of the refrigerants.
The more we get into this, the better I like the parallel condenser/separator (C/S) idea, and the suction line heat exchanger Chilly has added I think will greatly enhance this. There should be a sightglass at the C/S exit, and preferable a TXV. I am still undecided on the value of the EPR.
http://www.blairwing.com/images/Autocascade14.jpg
BTW, I am thoroughly enjoying the learning opportunity here. Thanks, Russell. :toast:
The captube is suitable in this application, although a pev at the inlet to the R290 and a captube on the block with a epr on the outlet of the block would let us play with the balance. I am checking my sources for the condenser today and when I find something I'll post it.
As you can probably tell I like using controls to balance a system..
I'm thinking an EPR on the outlet of the R290 evap would make more sense.
Strictly from an experimental point of view, I would like to start with a stripped down version, just the bare essentials, i.e. compressor, C/S, evaps, and (adjustable) metering devices.
Then control the variables, and add gadgets.
The R290 evap exit temp is increasing.
What are all the numbers?
The reason I think an epr on the R23 evap is that the evaporating P/T that has the same enthalpy as R290 is higher by about .8 bar. I suguessted this to balance the heat gains within the system. I'm interested enough to build a system, been incapacitated for a week and a half with a resperatory infection so I still gotta wait....
I left it running for a good 25minutes on full load, these are the numbers.
R23
Evap Exit: -39.1ºC
SST: -53ºC (3.2 barg)
SCT: -2ºC (22.4 barg)
R290
Evap Exit: 25.6ºC
SST: -4ºC (3.2 barg)
SCT: 65ºC (22.4 barg)
Air in: 21.9ºC
Air out: 30.8C
CPU: 5ºC
Your delta is increasing, it's removing more heat, how hot did the compressor get on this run?
Not only has the condenser delta-T increased, but the difference between the R290 SST and the R23 SCT has dropped. This indicates much better heat transfer in the heat exchanger. I think we are getting close. I like it. :D
The compressor top is hot, but I can leave my hand on it. The bottom is mild/cool. So i'd say its not overheating.
Whats the next step?
The next step is to chop another foot off the R290 cap tube.
Once we get the R290 gushing through, as you put it, am I going to see lower R23 evap temperatures? Or will my suction pressure get too high? One more thing, if we get the cap tubes balanced will a bigger compressor then bring down the the suction pressure also will the cap tubes need to be rebalanced with a larger compressor?
Note that despite the large increase in R23 SST, there was little increase in CPU temp. Once the R290 cap tube is right, I am thinking we could decrease the R23 evap temp by lengthening the R23 cap tube, or possibly just by increasing the amount of R23.
But let's cross that bridge when we come to it.
And yes, once we have the cap tubes right, a bigger compressor would contribute directly to the bottom line.
Took another 12 inches off the R290 cap tube. Left it running on full load, here are the results.
R23
Evap Exit: -37.4ºC
SST: -52ºC (3.4 barg)
SCT: -2ºC (22.5 barg)
R290
Evap Exit: 26.5ºC
SST: -2ºC (3.4 barg)
SCT: 65ºC (22.5 barg)
Air in: 22.8ºC
Air out: 30.5C
CPU: 6ºC
Hmmmmm... we have now totally eliminated the difference between R290 SST and R23 SCT, and it still isn't enough. I would guestimate that we are flowing enough R290 to handle almost 300 watts of load. What would you estimate the CPU load to be?
The sight glass is clear, right?
Is the bottom of the compressor cold yet?
Please tell me to butt out if this is the wrong time to step in here;) I wont be offended:cool:
I teach 11 to 16 year old's maths and I find that I really understand high end maths, much more, after I have reduced a difficult topic into something the kids will understand. And I also see things there that I had missed before.
Now whilst I understand classic cascades quite well, this autocascades has me really confused. There seems to be at least 3 variables here:
1. cap tube length for r23.
2. cap tube length for r290.
3. charge of r23 and r290.
Is the ratio of the r23 and r290 important, shouldnt the ratio be the same and only the quantity altered i.e. shouldnt you calculate an efficient ratio first lets say its 2 to 1 than increase the charge in that ratio?
If you can explain this in very basic terms to me you may be able to see something that you are missing. Sorry if this isnt appropriate at this time, but if it isnt just ignore the post as I said at the beginning.
regards
John.
I dont think I have ever seen the sightglass clear, there are bubbles rushing up the center if it and its about 95% full.
The bottom of the compressor is cool and the side is cold where the suction line enters. The top is hot but not too hot, I can hold my hand there for aslong as I want.
The load should be around 120 Watts
Feel free to jump in. We are stumbling around in the dark also. :D
At the location of the sight glass, the temperature/pressure is such that the R23 cannot possibly condense into liquid. Thus a clear sight glass tells us that there is complete separation of the two refrigerants.
Each evaporator must flow enough refrigerant through to handle its heat load. We know this is happening if its exit temperature is very cold, just slight above its evaporating temperature (SST).
This is not happening in the R290 evaporator.
This is happening too easily in the R23 evaporator, thus we can lengthen it, which will reduce its temperature while still handling its heat load.
At this point, it looks like the R23 cap tube is too short, and the R290 cap tube is too long.
I have no idea what the proportions of anything should be at this point. Autocascades are the new kid on the block, proportions are proprietary and super secret. On commercial autocascade systems, you evacuate the system, and the manufacturer sends you a premixed refrigerant charge for the system, for a mere $1000 or so.
The way I see it. You need enough R23 to remove the heat input at the evaporator and enough R290 to condense the R23. If you have too little R290 then you condense less R23 thus evaporator temperatures rise until the specific heat of the R23 is enough to cope with the load on the evaporator.
We might try increasing the airflow through the condenser to both reduce high side pressure and improve separation. I would assume that any bubbles in the sightglass are a result of incomplete separation, and are making this more difficult. I believe this is R23 vapor going through the R290 evaporator.
If the separator is very warm, a fan might help there also.
Got a deskfan blowing over compressor, separator and discharge line. Condensor air out temps are slowly dropping. The separator is warm to the touch but only slightly. The R290 has got to be more than 30ºC subcooled. Just one more thing, the R23 evap exit temp is taken just 2inches from the evap exit and the delta-T is around 15ºC from SST. Just wanted to run that by.
Keep in mind that the mixed refrigerants in the condenser completely distorts the pressure temperature relationship. The actual R290 SCT is probably a couple degrees above condenser air out temp, thus the R290 subcooling is far less than you might think.
If the r290 is exiting its evaporator at a few degrees above ambient, dosnt that mean it isnt evaporating enough inside its evaporator i.e. there is too much charge of r290?
Regards
John.
More specifically, not enough refrigerant flowing through the evaporator, which could mean insufficient R290 at the entrance to the cap tube, and/or cap tube too restrictive. Insufficient R290 at the cap tube entrance could indeed be R290 undercharge, not overcharge.Quote:
If the r290 is exiting its evaporator at a few degrees above ambient, dosnt that mean it isnt evaporating enough inside its evaporator i.e. there is too much charge of r290?
Given the suction pressure, if R290 refrigerant were flooding completely through the evaporator in liquid form, the bottom of the compressor would be a ball of ice.
Gary, shall I try and get rid of all the bubbles. I will continue to add R290, but the more I add the higher my LP is getting. Is there a value for one of the system parameters i should not pass when adding the R290 or can I keep adding till the bubbles go?
But I dont understand sir:D
Could you take me round Russels system a component at a time?
We start with a charge of r23 and r290 in the compressor, both gasses at ambient switch on the compressor and both gasses are compressed and the heat is increased too. And then?
Regards
John.
Lets see,
Once the compressor is turned on, the R290 starts to condense in the air cooled condensor. The R23 stays as a gas. This fluid flows to the phase separator where the gas is taken off the top and the liquid R290 is taken off the bottom.
The R290 is then metered to the heat exchanger via the cap tube. The R290 evaporates in the heat exchanger and this condenses the R23. Note the refrigerants are separated by the heat exchanger walls. The liquid R23 is now metered to the evaporator where it removes the heat load from the cpu. The R23 gas is now returned to the compressor. Before it gets there it meets and mixes with the R290 gas from the heat exchanger and then enters the compressor.
Thus the cycle begins again.
Just a thought: Russell, are you absolutely certain that you are measuring the R290 exit and not the R23 entrance?
Good question Gary :D
I've doubled checked this many times, checked that the sensor is still in place and even felt the pipes with my hand. They are warm, as the pipe gets closer to the R23 junction the pipe gets colder as expected.
One other thing. If the R290 is evaporating at -2ºC and the compressor inlet is colder than that, will I be getting liquid slugging? I dont know how to tell.
Thanks Russel
So if there was too much liquid r290 flowing threw its evap than it wouldnt be able to evaporate and this would have the same effect as too little r290? And if this is the case how do you know which is the correct determination?
Regards
John.
By measuring the evaporator exit temperature and comparing it to the saturated temperature we get an idication of what is going on.
Im my system the exit temperature is 28ºC above the evaporating temperature for the system pressure. Thus if there was any liquid at that point in the system, there would be enough heat to boil it. If there was too much liquid then the exit temperature would be alot closer to the saturated temperature.
Okay,
So you have been increasing the r290 charge and shortening the r290 cap tube, and this will increase the flow rate of the r290 through the evaporator?
Each time you increase the flow rate of the r290 the cpu temp increases, so that means the r23 isnt being cooled as much as it was with a slower r290 flow. How could that be?
Regards
John.
I am not sure we can trust the R290 SST with a stream of R23 bubbles mixed in. We need a clear sightglass.
Somehow I get the feeling that we are missing something here. Possibly with complete separation, we would not have needed to shorten the cap tube? Can it be that the stream of bubbles is what is throwing the whole thing off?
Have you tried increasing the condenser airflow?
The condensor fan is at maximum speed. Will putting a desk fan infront of the condesor help? Is that the best place for it?
The fan is setup infront of it. I can open a window and bring air temps down. Its around 0ºC outside.
Just noticed the air temp in is around 24ºC and out temp is 30ºC. Ive opened the window and im bringing the temperatures down. Im gonna nail this beast if its the last thing i do. :mad:
How does the phase seperator work? I assume that the liquid r290 settles to the bottom under gravity and is thus filtered off the bottom with the r23 gas filtered off at the top.
If the correct ratio of r23 to r290 isnt charged wouldnt the r290 be saturated with r23 vapour and then eventually form large bubbles of r23 vapour some where down the line?
Regards
John.
Its just a pipe where the mix enters and there are 2 exits, one at the top and one at the bottom. Gravity does its job and the 2 phases separate.
Ive been adding more R290 Gary and im still seeing bubbles. The bottom of the compressor is starting to get cold now. With the extra fan on the condensor the HP is dropping.
Also the r290 evap(heat exchanger?) works by dropping the pressure f the r290 allowing it to evaporate and hence remove heat from the r23? If there are large bubbles of r23 expanding in the heat exchanger wouldnt that force out the r290 before it had done its work?
Sorry for all the questions guys:(
Regards
John.
Somehow I keep thinking that if we add enough R290, the bubbles must disappear, but I'm not entirely sure of this.
Stop right there. Shut off the machine. Our problem is separation.Quote:
The bottom of the compressor is starting to get cold now.
Thats good enough for me, I need to goto bed now. Have to work out a better way for separation. What about larger diameter pipes on the condensor exit? Redesign the phase separator? I will let you think about that ones. One more thing, I need the machine to run my pc. If i let some charge out so the compressor is warm, then we will be ok. yeah?
Is this your phase seperator?
http://www.russellpetrie.plus.com/im...ade/autoc4.jpg
I would think the closer the r290 exit tube is to the bottom the better chance the r23 gas in there has a chance to escape.
Regards
John
The R290 exit is about 1 inch from the bottom. So it is quite close. I imagined the separator to be flooded so the R290 level was above the exit pipe, but this does not appear to be the case. There might be too much turbulance caused by the stream entering the phase separator that the liquid cant settle and as a result the R23 and R290 are getting sucked out the bottom.
John, The following links should enable us to build a mathetical model of this system. I get as far as figuering the enthalpy and mass ratios but the capillary tube calculations are a little beyond where I am comfortable yet. Wanna give it a shot...
Use the charts log(p)-h and select the refrigerants from these you can calculate the enthalpy (kJ/kg) at the pressures in this system you will also need the mass for each refrigerants. R23 is 70.01 and r290 is 44.10. Article on capillary flow in a tube...
http://www.fys.uio.no/~eaker/thesis/node11.html
http://www.blairwing.com/images/Refrig_Data_Sum.pdf
http://www.et.dtu.dk/Coolpack/Files/RefUtil.exe
On the seperator we need to calculate the flow rates and turbulance of the refrigerants to get proper seperation, we may need to cool the seperator down to the condensing point of the r290 at that pressure. This alone may solve the liquid r290 issue..
YesQuote:
If i let some charge out so the compressor is warm, then we will be ok. yeah?
The condensing point of R290 is 62ºC at 22bara (this is the pressure at the top of the separator) the separator is around ambient temperature and no where near 62ºC. Unfortunatly this does not fix the separator problem. In the separator the inlet stream sprays downwards, you cant see this in any picture so I though I would point it out.
I cant see from that pic where the r23/r290 is entering the phase seperator. this could be a combination of r23 exiting at the r290 exit point and liquid r290 being sucked through the r23 exit line.
Is there anyway of knowing how far up the phase seperator the liquid r290 is?
Chilly1, 1am here in the UK so I will look at those figures tomorrow, getting very sleepy, but learning a great deal, thanks guys.
Regards
John.
maybe u could fill the phase seperator w/ steel wool to force the liquid to the bottom
The C/S idea is looking better all the time. Massive drop in velocity, with no problem settling and separating.
With the conventional condenser, we could very well have a buildup of R23 in the condenser, having difficulty pushing its way out the bottom along with the liquid R290. And if we don't have a liquid seal in the bottom of the condenser, then we may need to do some more condensing in the separator.
c/s?
Good God I should be in bed now:D
Regards
John.
That could add to the problem. It should spray straight to the opposite wall.Quote:
In the separator the inlet stream sprays downwards, you cant see this in any picture so I though I would point it out.
Parallel condenser/separator. The big thing on the right:Quote:
c/s?
http://www.blairwing.com/images/Autocascade14.jpg
Gary I think the addition of the subcooler and a mid condenser tap for the r23 with both the discharge of the condenser and the mid tap into a tube in a shell with the shell so we would have is a desuperheating phase seperator with two inlets and two outlets.
Never would have belived that refrigeration would lead to soil physics. Check out Darcy's equation ... Trying to find some useful description of the flow of refrigerants in a capillary tube.. For something so simple it gets very complicated,
Could you go clockwise from the compressor and explain the components starting with the orange rectangle. I havnt learned so much in such a short amount of time since I was at Uni:cool:
Regards
John.
High Pressure 19.8 bara 1980000 Pa
Low Pressure 2.8 bara 280000 Pa
Viscosity 0.000125 kg/ms
Radius 0.0155 inch 0.0003937 meters
Density 1.9558 dm3/kg 511.2997239 kg/m3
Length 48 inches 1.2192 meters
Velocity 216.1248958 m/s
Volumetric flow 0.534626006 m3/s
Mass Flow 273.354129 kg/s
I punched these numbers for propane into Darcy's Equation. Maybe I missed something obvious, but look at the mass flow of propane? That cant be right.
CompressorClock wise desuperheater,oilseperator,condenser,capillary tube,interstage heatexchanger,capillary tube,evaporator (the brass colored thing) Pressure expansion Valve, Suction line subcooler,compressor
The velocity is also greater than the sound velocity data for propane. Now if I remember my thermodynamics/fluid flow, then we can't have a fluid travelling faster than sound in an adiabatic process (in this case its the pressure drop across the capillary) pipe. Am I right?
I see your point. If we install a 1/4 line from a middle return bend in the condenser to the middle of the separator, this would provide another path to prevent buildup of R23 in the condenser.Quote:
Gary I think the addition of the subcooler and a mid condenser tap for the r23 with both the discharge of the condenser and the mid tap into a tube in a shell with the shell so we would have is a desuperheating phase seperator with two inlets and two outlets.
The middle tap would tend to favor R23 vapor, while the bottom connection would tend to favor R290 liquid.
I'll annotate it if that would help. I threw in the PEV so we could raise the pressure in the R23 evaporator while not effecting the suction pressure effectively changing the balance, Basically if I were to factor in the enthalpies and densities of both refrigerants and used this for the only midigating factor in the system balance and based it on current pressures I would need a delta across the epr of .8 bar. But I think there is more to this than only the heatcarrying capacity and the densities. I think the viscosity and misicibility of the refrigerants and the oil's density and flow rates also need to be considered, published research in this field is scarse and what there is is modeled on other fields of study. I am still looking .....
Exactly then Russell_hq would need only modify his current condenser by putting in a tap a ways down from the top of the condenser this would still allow a liquid seal in the condenser and would stop the liquid from being blown out. I am looking for that condenser. Theres a coil manafacturer in texas that may have it.Quote:
Originally posted by Gary Lloyd
I see your point. If we install a 1/4 line from a middle return bend in the condenser to the middle of the separator, this would provide another path to prevent buildup of R23 in the condenser.
The middle tap would tend to favor R23 vapor, while the bottom connection would tend to favor R290 liquid.
http://www.blairwing.com/images/Autocascade16.jpg
hey guys, why dont you stop talking about how easy it is to build and build one. You can do the calculations while your sleeping, and then build it in the living room so you can watch dawsons creek, while you build. Or maybe you can close your eyes while you build it, so its a bit more of a challenge.
I just couldnt help it:D
Also, if necessary, we could soft solder the common suction line along the side of the separator.
I have all the pieces to build one but why build when we have a guinie pig to watch...LOL!Quote:
Originally posted by captaincascade
hey guys, why dont you stop talking about how easy it is to build and build one. You can do the calculations while your sleeping, and then build it in the living room so you can watch dawsons creek, while you build. Or maybe you can close your eyes while you build it, so its a bit more of a challenge.
I just couldnt help it:D
I couldn't resist either..http://www.blairwing.com/images/PhaseFive.jpg
Future project.....