Showing posts with label Mechine. Show all posts
Showing posts with label Mechine. Show all posts

5/26/2016

SLICKLINE

Slickline refers to a single strand wire which is used to run tools into wellbore for several purposes. It is used in the oil and gas industry, but also describes that niche of the industry that involves using a slickline truck or doing a slickline job.
Slickline looks like a long, smooth, unbraided wire, often shiny, silver/chrome in appearance. It comes in varying lengths, according to the depth of wells in the area it is used (it can be ordered to specification) up to 35,000 feet in length. It is used to lower and raise downhole tools used in oil and gas well maintenance to the appropriate depth of the drilled well. In use and appearance it is connected by the drum it is spooled off of in the back of the slickline truck to the wireline sheave a round wheel grooved and sized to accept a specified line and positioned to redirect the line to another sheave that will allow the slickline to enter the wellbore.[1] Slickline is used to lower downhole tools into an oil or gas well to perform a specified maintenance job downhole. Downhole refers to the area in the pipe below surface, the pipe being either the casing cemented in the hole by the drilling rig (which keeps the drilled hole from caving in and pressure from the various oil or gas zones downhole from feeding into one another) or the tubing, a smaller diameter pipe hung inside the casing.


Slickline is more commonly used in production tubing. The wireline operator monitors at surface the slickline tension via a weight indicator gauge and the depth via a depth counter 'zeroed' from surface, lowers the downhole tool to the proper depth, completes the job by manipulating the downhole tool mechanically, checks to make sure it worked if possible, and pulls the tool back out by winding the slickline back onto the drum it was spooled from. The slickline drum is controlled by a hydraulic pump, which in turn is controlled by the 'slickline operator'.

Slickline comes in different sizes and grades. The larger the size, and higher the grade, generally means the higher line tension can be pulled before the line snaps at the weakest spot and causes a costly 'fishing' job. Due to downhole tools getting stuck because of malfunctions or 'downhole conditions' including sand, scale, salt, asphaltenes, and other well byproducts settling or loosening off the pipe walls because of agitation either by the downhole tools or a change in downhole inflow, sometimes it is necessary to pull hard on the tools to bring them back uphole to surface. If the tools are stuck, and the operator pulls too hard, the line will snap or pull apart at the weakest spot, which is generally closer to surface as the further uphole the weak point in the line is, the more weight it has to support (the weight of the line).

Weak spots in the line can be caused by making the circle around the counter wheel, making a bend around a sheave, a kink in a line from normal use (when rigging up the equipment extra line must be pulled out from the truck to give enough slack when the pressure control lubricator is picked up - this leaves line coiled on the often rutted ground, and sometimes it snags and kinks the line).
When the slickline parts, this can create an expensive 'fishing' job. It is called fishing because you often have to try different 'fishing' tools until you get a 'bite', then you have to work the original tools downhole free, or cut off the slickline where they join the tools downhole so that you can pull the broken slickline back to surface and out of the way, in order to fish the stuck toolstring. Because of the downtime involved in 'fishing', meaning not being able to flow the oil/gas well, the client is losing money by lack of production and also the cost of the slickline unit to fish, and the cost of what is left in the hole if it is not fished out (in the oil/gas industry, if the cause of the fishing job was not the fault of the slickline company, the oil/gas company is usually responsible to pay for it, and it can be very expensive).

Slickline was originally called measuring line, because the line was flat like a tape measure, and marked with depth increments so the operators would know how deep in the hole they were. This probably changed because the flat measuring line wasn't as strong as the modern slickline, and separate depth counters were developed. It is advantageous to keep the diameter of the wire as small as possible for the following reasons:
  • It reduces the load of its own weight.
  • It can be run over smaller diameter sheaves, and wound on smaller diameter spools or reels without overstressing by bending (where the wire bends makes it weaker. Where it makes a complete circle, such as a counter wheel, makes it weaker yet).
  • It keeps the reel drum size to a minimum (which reduces the area needed in the back of the slickline unit to house the drum and hydraulic pump, reducing weight and leaving more room for the other specialized equipment needed for slickline operations).
  • It provides a small cross-section area for operation under pressure.
The disadvantage of a smaller diameter slickline is the lower strength. Depth and the nature of the job (a tool that must be pulled hard or might be stuck) will affect what slickline truck (different trucks specialize in different sizes of line) used.
The sizes of solid wireline in most common uses are: 0.092", 0.108", 0.125", 0.140", 0.150", and 0.160" in diameter, and are obtainable from the wire-drawing mills in one-piece standard lengths of 18,000, 20,000, 25,000 and 30,000 foot lengths. Other diameters and lengths are usually available on request from the suppliers, with the largest size currently available at 0.188".

Mechanical and Hydraulic Jars

Slickline tools operate with a mechanical action, controlled from surface in the wireline trucks operators compartment. Typically, this mechanical action is accomplished by the operation of jars. There are generally two types of jars; mechanical and hydraulic.
Mechanical jars look like a long, tubular piece of machined metal that slides longer or shorter approximately 75% to 90% of its total length. They give the effect of hammering on the downhole tools. The weight or hit of the 'hammer' depends on how much sinker bar is added above the jars. Generally, a slickline operator controls the downhole tools with taps and hits from the sinker bar via the mechanical jars, controlled at surface by lowering or raising the toolstring and monitoring weight, depth, and pressure. Mechanical jars for slickline can hit up or down the hole, making them a versatile form of jarring.
Hydraulic jars for slickline are generally meant to jar up only, because not enough sinker bar is able to feasibly be lubricated in to jar down on the downhole tools. Hydraulic jars work by the operator pulling up on the line, which puts an upward force on the top of the hydraulic jars. The bottom of the hydraulic jars is usually attached by threaded connection to the mechanical jars, which are attached to the downhole tools. Depending on how hard the operator pulls on the hydraulic jars will affect how fast they hit, and how hard they hit. When the top is pulled on, the inner mandrel begins to slide upwards. It has a restriction in it that hydraulic fluid has to bypass as it is pulled upwards, until it reaches an area of no restriction, allowing it to slide rapidly. The reason for the initial tighter restriction is to allow the operator to pull his line to the desired hitting range.
Generally once he hits that range on his weight indicator, he waits while the jars open to the less restricted point, whereupon the sinker bar travels upwards rapidly, providing an upwards hit on the downhole tools. The jars can then be 'reset' by lowering the line until the weight of the sinker bar closes, or pushes the inner mandrel of the hydraulic jars back to the starting position. Because the hydraulic jars are designed to provide a wait time to allow the operator to get up to the desired line tension, they can provide a very effective upwards hit.
Mechanical jar and hydraulic jar hitting power is affected by the length of the jars (the longer the length, they faster they can travel before they stop), the mass of the weight above them (the more the mass, the harder they will hit), and the tension of the line pulling on them.
Some completion components may be deployed and retrieved on slickline such as wireline retrievable safety valves, battery powered downhole gauges, perforating, placing explosively set bridge plugs, and placing or retrieving gas lift valves. Slickline can also be used for fishing, the process of trying to retrieve other equipment and wire, which has been dropped down the hole.

Applications

The most common applications for slickline are:
  • Tagging T.D. (Total Depth, which is the furthest depth possible down the wellbore)
  • Gauge Ring runs (which is running a special sized downhole tool called a gauge ring, which comes in various pre-machined diameters, designed to ensure the pipe is clear to a certain point)
  • Tubing Broach / Plunger Installations (a tubing broach looks like an aggressive, tubular file, available in different diameters, used for removing burrs and crimps in the inside of tubing and casing in oil and gas wells)

    Tubing Broach

  • Bailing sand and debris (removing formation sand/rock and other such debris left over from the drilling and completion of the well, using a specialized tool called a bailer. This tool uses either a Chinese water pump type stroke action or a hydrostatic vacuum action to suction up the downhole debris, allowing it to be conveyed back to surface via the wireline)
  • Shifting sleeves (formations downhole can be isolated behind sliding metal 'windows' called sliding sleeves. They are shifted open or closed by means of a specialized shifting tool locating the sleeve and it being jarred up or down, providing access or closing off that formation or section of casing)
  • Setting / Pulling plugs and chokes (specialized downhole tools which either lock into pre-machined restrictions in the tubing, or which lock into the tubing itself, sealing pressure from below or above the plug)
  • Setting / Pulling gas lift valves
  • Running tailpipes (tubing extensions where the tubing is not landed close enough to the formation perforations in the casing)
  • Bottom hole pressure and temperature surveys (specialized electronic and mechanical tools designed to measure the pressure and temperature at predetermined depths in the wellbore. This data can be used to determine reservoir life)
  • Spinner Surveys (to determine which formation perforations have the best inflow / which perforations make the most water / liquids)
  • Kinley perforator, sandline cutter, and caliper
  • Running production logging tools
  • Fishing operations (fishing usually refers to attempting to retrieve lost tools or wire, or other debris that was not intended to restrict the flow / disrupt the well operations. Fishing can be difficult, due the fish being downhole, and other affecting conditions such as high pressure, the fish being jammed in the tubing / casing)
  • Paraffin cutting (making a hole through and removing a wax buildup, which is a byproduct of oil cooling too much to reach surface)
  • Chipping ice / salt (restrictions and plugs which can be formed as by products of a flowing well)
  • Lubricating long assemblies in and out of the hole (lubricating is done via a larger than tool overall diameter pipe, joined at surface on top of the wellhead, which houses the valve that shuts the pressure in downhole. The lubricator should be long enough to be able to swallow the toolstring and downhole tools that are to be run or pulled)

Braided line

Braided line is generally used when the strength of slickline is insufficient for the task. Most commonly, this is for heavy fishing such as retrieving broken drill pipe. The most common use for braided line is fishing electric line tools.

Slickline Tools

Jar

This type of tool can be extended and closed rapidly to induce a mechanical shock to the tool string. This shock can induce certain components such as plugs to lock into place and then unlock for retrieving. Jars are commonly used to shear small brass or steel pins that are put in place to function certain down-hole tools at a certain moment. The operator can use the jars to shear the pins at a predetermined depth. Spang jars are manually operated by the wireline operator who either lifts or lowers wire rapidly, requiring a great deal of expertise. Power jars use springs or built-in hydraulics to give an upward jarring motion where greater force is required.

Stem

Stem essentially just serves to add weight to the toolstring. The weight may be necessary to overcome the pressure of the well. Some variations of stem, called roller stem, may have wheels built into the tool to allow the tool string to glide more easily down moderately deviated wells. Stem give the hammering action to the tool string which in turn allows the jars to transmit the force given by the movement of the stems bars. Depending on well conditions extra small OD stems are use or extra large. The range can be from .75" to 3.50" OD and the stems normally come in 2 ft, 3 ft or 5 ft lengths. The connection to the rope socket or other tools can be a threaded connection or a QLS system (quick connect).

Pulling tools

These are tools designed for fishing other wireline components which have been dropped down hole. All wireline tools are designed with 'fishing necks' on their top side, intended to be easily grabbed by pulling tools. Pulling tools are also used for retrieving seated components such as plugs.

Gauge Cutter (Gauge Ring)

A gauge cutter is a tool with a round, open-ended bottom which is milled to an accurate size. Large openings above the bottom of the tool allow for fluid bypass while running in the hole. Most often a gauge ring will be the first tool ran on a slickline operation. A gauge ring that is just undersized will allow the operator to ensure clear tubing down to the deepest projected working depth; for example 2 7/8" tubing containing 2.313" profiles would call for a gauge ring between 2.25" - 2.30". A gauge ring can also be used to remove light paraffin that may have built up in the tubing. Often a variety of different sized gauges and/or scratchers will be run to remove parafin little by little.Gauge cutter can be used for drift runs also.

Lead impression block

If an obstruction is found downhole, a lead impression block can be run to help determine its nature. The LIB has a malleable lead base in which the obstruction can leave an impression when they meet. The LIB is called Wireline Camera because of its function to mark any object downhole. They are also sometimes called "confusion" blocks because they only give a two-dimensional view of the down-hole object, making it hard for an inexperienced person to determine what three-dimensional object is in the hole

Downhole bailer

Bailers are downhole tools that are generally long and tubular shaped, and are used for both getting samples of downhole solids (sand, scale, asphaltines, rust, rubber and debris from well servicing operations) and for 'bailing' the unwanted downhole solids from the well. Bailers are attached either via threaded connection or releasable downhole tool to the wireline toolstring, and are manipulated from surface by the wireline operator. Bailers usually have an interchangeable bottom (the shoe) which also houses a check to keep the solids from falling or washing out of the bottom.

Sample bailer

A sample bailer is generally around a meter long, and has a hollow tube (the barrel) usually around 40 mm in diameter, with a 'ball check' on the bottom and an opening at the top. This tool is beat downwards into the as yet unknown obstruction using the mechanical jars and weight above of the wireline toolstring. Generally, after a predetermined amount of 'hits', hopefully allowing a usable sample of solids to fill the barrel. When the tool is pulled upwards, the solids usually (hopefully) settle the ball check onto its 'seat', which will keep the solids in the barrel during the return trip to surface, where the solids can be inspected to determine what the downhole obstruction was. This procedure can be 'hit and miss', the success depending on how readily the solid was accepted into the barrel, and if the ball check was properly seated on the return trip to surface. If the ball check is not seated (sometimes a large, hard piece of solid will sit in between the ball and seat) downhole fluids tend to 'wash' the sample out of the bottom of the sample bailer, leaving the inspectors at surface wondering if the tool actually collected a sample. Persistence is generally a good rule of thumb with this tool.

Stroke bailer

A stroke bailer functions like a 'Chinese water pump', and is used to collect unwanted solids from the wellbore. A stroke bailer is long and tubular looking, with a smaller rod that extends from the top, a hole in the bottom, and is generally around 7 meters long, but the length depends on how much barrel section is added to the bailer. The barrel 'free floats' on the stroke rod, which is attached to the wireline toolstring. The tool is usually 'spudded' into the downhole solid, then the wireline toolstring is pulled upwards, which in turn pulls the stroke up through the barrel. Ideally, this draws the downhole solid in through the bottom 'shoe' of the tool, past the check and into the barrel for collection. The tool is usually stroked either a predetermined number of times, or until it appears the tool is not stroking, which can mean either it is full, or stuck.

Hydrostatic bailer

A hydrostatic bailer functions like a 'vacuum', and is used to suck up unwanted solids from the wellbore. A hydrostatic bailer is generally around 2.5 meters long and is tubular looking, with two 10 mm holes on opposing sides at the top of the tool, and a hole in the bottom. A hydrostatic bailer uses a pinned plug with o-ring seals at the bottom, and a plug at the top to maintain the surface pressure that it was assembled at (nominally around 100 kPa) all the way to the bottom of the well, whereupon it is spudded into the downhole solids, which ideally pushes the shoe into the bottom plug, which shears the pin on the bottom plug. An oil or gas well's pressure downhole is always more than atmospheric pressure at surface, due to the formation pressure, and a combination of depth and hydrostatic weight of wellbore fluids. Sometimes fluid will be added to the wellbore to assist in bailing by bringing up the pressure, and also lubricating the downhole solid. Because the pressure inside the bailer is much less than the downhole wellbore pressure, any solids that are loose enough are 'sucked up' by the vacuum formed when the bottom plug is sheared and travels upwards through the barrel, followed by the solids. At the same time, due to the changed from negative pressure to positive pressure, the top plug pops out (and is caught by the top part of the tool), and excess flow is directed out through the 10 mm ports on the sides of the top of the tool. These ports allow the barrel to fill more readily. Then the bailer is returned to surface where it is taken apart, the solids are emptied, and it is cleaned and serviced with new o-ring seals. Care must be taken when disassembling at surface as the tool is potentially charged with the downhole pressure (possibly many tens of thousands of kpa) and may 'blow apart' when being unthreaded if not bled off first.

Running Tools

These tools are primarily used to 'set' plugs into locking profiles (nipples) located in the tubing; however, the term 'running tool' refers to a downhole tool attached to the wireline toolstring that is used to 'run' another tool that is meant to be left downhole when the toolstring returns to surface. In general, a running tool is attached to a downhole 'locking tool' that locates and locks into the selected downhole profile (nipple). The 'locking tool', or 'lock' for short, can be attached via threaded connection to the top of a variety of different tools, including but not limited to, downhole chokes (flow rate restrictors sized according to a pre-determined calculation), one-way check valves (TKX style plugs), instrument hangers, and most commonly, tubing plugs. The lock is fitted onto the running tool and attached using shear pins made of brass or steel. When the target profile is reached the lock can be set by seating the lock into the profile using mechanical jars (spangs) until the locking keys have locked the lock into the profile, whereupon the operator usually 'pull tests' the lock to give an indication it is properly 'set', then shears off the shear pins with his mechanical or hydraulic jars to allow the 'toolstring' to return to surface. There are many different types of running tools, some are mechanically complex and able to be made 'selective' in order to pass through profiles in order to reach one of the same size but a different depth; some are relatively simple, such as an 'F' collarstop running tool, which is essentially a metal rod which fits inside the collarstop downhole tool which is pinned in place


Source : Wikipedia

2/02/2016

CENTRIFULGAL PUMP


HEAD, FLOW, AND PRESSURE
Centrifugal Pumps:
Fundamentals
of Operation


HEAD

Centrifugal pumps are dynamic machines, which means that they convert velocity into feet of head. To explain this concept of converting speed or velocity into feet of head, let’s look at Fig. 29.1. This is the water intake section of the Chicago Water Treatment Plant. Water flows from Lake Michigan into a large concrete sump. The top of this sump is well above the level of Lake Michigan. The line feeding the sump extends three miles (3 mi) out into the lake. 


The long line is needed to draw water into the plant, away from the pollution along the Chicago lakefront. The pipeline diameter is 12 ft. Water flows in this line at a velocity of 8 ft/s. Six pumps, stationed atop the concrete sump, pump water into the water treatment plant holding tanks. One day, the plant experiences a partial power failure. Three of the six pumps shown in Fig. 1 shut down. A few moments later, the manhole covers on top of the sump blow off. Geysers of water spurt out of the manholes. What has happened?


FIGURE 1 Converting momentum into feet of head.

HYDRAULIC HAMMER

This is an example of water, or hydraulic, hammer. But what causes water hammer? Let’s consider the change in the water velocity in the 3-mi pipeline when half the pumps failed. The velocity in the pipeline dropped from 8 down to 4 ft/s. Velocity is a form of energy, called kinetic energy.


Energy can take several different forms:
  • Heat (Btus)
  • Elevation or potential energy
  • Kinetic energy (miles per hour)
  • Pressure (psig)
  • Electrical power (amperes)
  • Work (horsepower)
  • Acceleration
  • Chemical (heat of reaction)

About 250 years ago, Daniel Bernoulli first noticed two important things about energy:
  • Energy in one form can be converted to energy in another form.
  • While energy can be changed from one form to another, it cannot be created or destroyed.

This idea of the conservation of energy is at the heart of any process plant. In the case of the Chicago Water Treatment Plant, the reduced velocity of the water was converted into feet of head. That is,

the elevation of the water in the sump suddenly increased and blew
the manhole covers off the top of the sump.





MOMENTUM


If the length of the pipeline had been a few hundred feet, this incident would not have happened. It is not only the sudden reduction of the velocity of the water that caused an increase of the water level in the sump. It is also the mass of water in the 3-mi pipeline that contributed to the increased height of water in the sump. The combined effect of mass times velocity is called momentum.

The mass of water in our pipeline weighed 160 × 106 lb. This much water, moving at 8 ft/s, represents a tremendous amount of energy (about 500 million Btu per hour). If the flow of water is cut in half, then the momentum of the water flowing in the pipeline is also cut in half. This energy cannot simply disappear. It has to go somewhere. The energy is converted to an increase of feet of head in the sump; that is, the water level in the sump jumps up and blows the manhole covers off the top of the sump. Incidentally, this is a true story. Can you imagine what would have happened if all six pumps failed simultaneously due to an electric power failure? The result would be a dramatic lesson in the meaning of water hammer.


MY WASHING MACHINE

Figure 2 is a picture of our washing machine as it was originally installed. Whenever the shutoff valve on the water supply line closed, water hammer, or hydraulic shock, would shake the water piping. The momentum of the water flowing in the piping would be suddenly converted to pressure. If the end of a piping system is open (as into a sump), then the momentum of the water is converted to feet of head. But if the end of the piping system is closed, then the momentum of the water is converted to pressure. 

To fix this problem, I installed the riser tube shown in Fig. 3. The top of the riser tube is left full of air. Now when the water flow in the supply pipe is shut, the momentum of the water is converted to compression energy. That is, the air in the riser tube is slightly compressed, as indicated by the pressure gauge I installed at the top of the riser tube.








FIGURE 2 ConHydrolic Hammer Hits Home



FIGURE .3 Riser tube stops hydraulic hammer.



ACCELERATION

Let us imagine that the six pumps in Fig. 1 have not run for a few days. The water level in the sump and the level of Lake Michigan will be the same. I now start all six pumps at the same time. An hour later, the water level in the sump is 12 ft below the water level in the lake. This 12 ft is called “feet of head loss.” If the pipeline is 3 mi long, we say we have “lost 4 ft of head per mile of pipeline.” If we look down into the sump, what would we see happening to the water level during this hour? Figure 4 is a graph of what we would observe. The water level in the sump would drop gradually to 15 ft below the level in the lake. Then the water level in the sump would come partly back up to its equilibrium level of 12 ft below the lake level. Why?






FIGURE 4 Effect of acceleration.




The loss of 12 ft of head as the water flows through the pipeline is due to friction; that is, 12 ft of head are converted to heat. But why do we have a temporary loss of an extra 3 ft? The answer lies in the concept of acceleration. Let’s say you are driving your car onto the expressway. To increase the speed of your car from 30 to 65 miles per hour, you press down on the accelerator pedal. Having reached a velocity of 65 miles per hour, you ease off the accelerator pedal to maintain a constant speed. 

Why? Well, according to Newton’s second law of motion, it takes more energy to accelerate your car than to keep it in motion. Referring again to Fig. 1, the water in the 3-mi pipeline is initially stagnant. Its velocity is zero. An hour later, the water has accelerated to 8 ft/s. When you accelerate your car, the extra energy required comes from the engine. But when we accelerate the water in the pipeline, where does the extra energy come from? Does this extra energy come from the pumps? Absolutely not! The pumps are downstream of the pipeline and the sump. 

They cannot contribute any energy to an upstream pipeline. No, dear reader, the energy to accelerate the water in the pipeline must come from Lake Michigan. But what is the only source of energy that the lake possesses? Answer—elevation or potential energy. To accelerate the water in the pipeline to 8 ft/s requires more energy than to keep the water flowing at that same velocity. And this extra energy comes from the 3 ft of elevation difference between the water level in the sump and the water level in the lake. Once the water has reached its steady-state velocity of 8 ft/s, the need for this extra conversion of feet of head to acceleration disappears, and the water level in the sump rises to within 12 ft of the lake’s level

STARTING NPSH REQUIREMENT

The need to accelerate the fluid in the suction of a pump is called the starting net positive suction head (NPSH) requirement. To calculate this starting NPSH requirement, let’s assume:
  • Suction line = 100 ft
  • Eight-in line
  • Fluid = water @ 62 lbs/ft3
  • Initial velocity is zero
  • Final velocity is 10 ft/s Then proceed as follows:
  • Mass in line is 2170 lb

PRESSURE

Loss of Suction Pressure The need to accelerate liquid in the suction line of a pump leads to a difficult operating problem, which occurs on start-up. Just before the pump shown in Fig. 5 is put on line, the velocity in the suction line is zero. The energy to increase the velocity (i.e., accelerate) the liquid in the suction line must come from the pressure of the liquid at the pump’s suction. As the pump’s discharge valve is opened, the velocity







FIGURE 29.5 Loss of suction pressure causes cavitation

In the suction line increases, reducing the pressure at the suction of the pump. The faster the discharge valve is opened, the greater the acceleration in the suction line, and the greater the loss in the pump’s suction pressure. If the pressure at the suction of the pump falls to its bubble or boiling point, the liquid will start to vaporize. This is called cavitation. A cavitating pump will have an erratically low discharge pressure and an erratically low flow. As shown in Fig. 5, the bubble-point pressure of the liquid is the pressure in the vessel.

We usually assume that the liquid in a drum is in equilibrium with the vapor. The vapor is then said to be at its dew point, while the liquid is said to be at its bubble point. To avoid pump cavitation on start-up, the experienced operator opens the pump discharge valve slowly. Slowly opening the discharge valve results in reduced acceleration of the liquid in the suction line and a slower rate of the conversion of suction pressure to velocity. Try this test. To illustrate what I have just explained, try this

experiment:
  1. Open the suction valve to a pump completely.
  2. Crack open the case vent to fill the case with liquid. This is called “priming the pump.”
  3. Open the pump discharge valve completely.
  4. Push the motor START button.
  5. Observe the pump suction pressure.



You will see that the pump suction pressure will drop and then come partly back up. If the pump suction pressure were 15 psig to start with, it might drop to 12 psig and then come up to 14 psig. The permanent difference in the suction pressure between 15 and 14 psig is due to a 1-psig piping friction pressure loss. The temporary difference in the suction pressure between 14 and 12 psig is due to a 2-psig conversion of pressure to velocity or kinetic energy. 

To review—all the energy needed to accelerate the liquid to the suction of a pump comes from the pump’s suction pressure. None of this energy comes from the pump itself. Or, as one clever operator at the Unocal Refinery in San Francisco explained to me, “Pumps push, but they do not suck.”

Pump Discharge Pressure
Figure 6 illustrates the internal components of an “overhung, single-stage” centrifugal pump. The term “overhung” refers to the feature that the pump has only an inboard, but no outboard, bearing. The inboard side of a pump means the end closest to the driver. The term “single-stage” means that there is only one impeller. Multistage pumps can have five or six impellers





FIGURE 6 A centrifugal pump.


The main components of the pump shown in Fig. 6 are

  • Shaft—used to spin the impeller
  • Coupling—attaches the shaft to the turbine or motor driver
  • Bearings—support the shaft
  • Seal—prevents the liquid inside the pump from leaking out around the shaft
  • Impeller wear ring—minimizes internal liquid leakage, from
  • the pump discharge, back to the pump suction
  • Impeller—accelerates the liquid
  • Volute—converts the velocity imparted to the liquid by the impeller to feet of head The impeller is the working part of a centrifugal pump. 

The function of the impeller is to increase the velocity or kinetic energy of the liquid. The liquid flows into the impeller and leaves the impeller at the same pressure. The location of the oval dot

shown at the top of the impeller in Fig. 6 is called the “vane tip.” The pressure at the vane tip is the same as the pump’s suction pressure. However, as the high-velocity liquid escapes from the impeller and flows into the volute, its velocity decreases. The volute (which is also called the diffuser) is shaped like a cone. It widens out in the manner illustrated in Fig. 7. As the liquid flows into the wider section of the volute, its velocity is reduced, and the lost velocity is converted—well, not into pressure, but into feet of head.
FIGURE 7 A volute or diffuser converts velocity into feet of head.




FEET OF HEAD




A centrifugal pump develops the same feet of head regardless of the density of the liquid pumped, as long as the flow is constant. This statement is valid as long as the viscosity of the liquid is below 50 to 100 cP or 200 to 400 SSU (Saybolt Seconds Universal). But, as process operators or engineers, we are not interested in feet of head. We are interested only in pressure. Differential pressure is related to


differential feet of head as follows:

The increase in pressure ΔP is also called head pressure. For example, if I have 231 ft of water in the glass cylinder shown in Fig. 29.8, it would exert a head pressure of 100 psig on the pressure gauge at the bottom of the cylinder. The head pressure would be



FIGURE 8 Head pressure compared to feet of head.


proportionally reduced as the liquid becomes less dense. For example, 231 ft of kerosene (which has 0.75 s.g.) would exert a head pressure of only 75 psig, because it is lighter than water.



EFFECT OF SPECIFIC GRAVITY


Figure 9 shows a centrifugal pump that may pump water through valve B or naphtha through valve A. Question: When water is pumped, the pump’s discharge pressure is 110.4 psig. The pump’s suction pressure is 10.4 psig. When naphtha is pumped, what is the pump’s discharge pressure?
Answer: The head pressure developed by the pump is



and the pump discharge pressure = 10.4 + 60 = 70.4 psig Next question: The pump is driven by an ordinary alternatingcurrent electric motor. It is running at 3600 rpm. When we switch from pumping water to naphtha, what happens to the speed of the pump?


Answer: Nothing. An AC motor is a fixed-speed machine. It will continue to spin at 3600 rpm. Next question: The pump is pulling 100 amps of electrical power. The flow rate is 100 GPM. If we now close valve B and open valve A, what happens to the amp load on the motor driver?


FIGURE 9 Effect of specifi c gravity on pump performance.



Answer: The power demand will go down to 60 amp. Amp(ere)s are a form of electrical work. The units of work are foot-pounds. The feet of head developed by the pump is not affected by the specific gravity of the liquid. But the weight of liquid pumped is proportional to the specific gravity. If the specific gravity drops by 40 percent, and the liquid volume (GPM) stays constant, then the pounds lifted by the pump drops by 40 percent and so does the electrical work.



Last question: Water is being pumped to a tank on a hill at 100 GPM. If we now switch to pumping a lighter fluid at the same rate, can we pump the lighter fluid to a higher elevation, only to a lower elevation, or the same elevation?



Answer: The same elevation. Centrifugal pumps develop the same feet of head at a given volumetric flow rate regardless of the specific gravity of the liquid pumped. This means the ability of the pump to push liquid uphill is the same even if the density of the liquid changes

PUMP CURVE

The feet of head developed by a pump is affected by the volume of liquid pumped. Figure 10 is a typical pump curve. As the flow of liquid from a centrifugal pump increases, the feet of head developed by the pump goes down, as does the pump discharge pressure. A pump curve has two general areas. These are the flat portion of the curve and the steep portion of the curve. We normally design and operate a pump to run toward the end of the flat portion of its curve. A centrifugal pump operating on the flat portion of its curve loses only a small portion of its discharge pressure when flow is increased. 

This is a desirable operating characteristic. A centrifugal pump operating on the steep portion of its curve loses a large portion of its discharge pressure when flow is increased. Pumps operating quite far out on their curve will have an erratic discharge pressure, as the flow through the pump varies. For one such pump, I have seen the discharge pressure drop from 210 to 90 psig as the flow increased by 40 percent. The flow through this pump was regulated by a downstream level-control valve. The discharge pressure varied so erratically that the operators thought the pump was cavitating.

DEVIATION FROM PUMP

Pumps always perform on their performance curve. It is just that they do not always perform on the manufacturer’s performance curve

FIGURE 29.10 Centrifugal pump curve.


The dotted line in Fig. 7 compares an actual performance curve to the manufacturer’s performance curve. Why the deviation?

  • The manufacturer’s curve was generated using water. We are pumping some other fluid, perhaps with a much higher viscosity.
  • The clearance between the impeller and the impeller wear ring (Fig. 6) may have increased as a result of wear.
  • The impeller itself may be worn, or the vane tips at the edge of the impeller might be improperly machined.
  • If the pump is driven by a steam turbine, the pump speed could be lower than in the design.
  • Available NPSH may be marginal.

DRIVER HORSEPOWER



Normally, increasing the flow from a centrifugal pump increases the amperage load on the motor driver, as shown in Fig. 11. Driver horsepower is proportional to GPM times feet of head. As shown in Fig. 10, as the flow increases the feet of head developed by the pump decreases. On the flat part of the pump curve, the flow increases rapidly, while the head slips down slowly. Hence the product of GPM times feet of head increase. On the steep part of the pump curve, the flow increases slowly, while the head drops off rapidly. Hence, the product of GPM times feet of head remains the same, or goes down.
FIGURE 11 Horsepower requirement for a centrifugal pump.



The response of the amp load on the motor driver is an indication of pump performance. A pump operating on the proper, flat portion of its curve will pull more motor amps as flow increases. A pump operating on the poor, steep portion of its curve will not pull more amps. If the manufacturer’s horsepower/flow curve indicates that more horsepower is required as flow is increased, but the motor amp load is not increasing, then something is wrong with the pump. The amp meter for a pump is best located right on the start-stop box next to the motor. Unfortunately, more often, the only amp meter is located on the electrical breaker box, which is at a remote location.




PUMP IMPELLER

Impeller Diameter

The pump impeller resembles a hollow wheel with radial vanes. The diameter of this wheel can be trimmed down on a lathe. If an impeller with a 10-in diameter is trimmed down to 9 in, it will have a new performance curve below its former performance curve. Both the flow and head of the pump will be reduced. Also, the amp load on the motor driver will decrease. As a rough rule of thumb, reducing a pump’s impeller diameter by 10 percent will reduce the amp load by 25 percent. Not only will this save electricity, but the motor will run much cooler. 

Unloading the motor by 25 percent may increase the life of the motor windings by 10 years. When the control valve downstream of a pump is operating in a mostly closed position, the pump is a good candidate to have its impeller trimmed. Sometimes, the pressure drop across a control valve is so huge (≥100 psi) that it makes a roaring sound. The energy represented by this wasteful ΔP is coming from the electricity supplied to the pump’s motor. 

Hence, trimming the impeller also reduces wear because of erosion in downstream control valves. We frequently increase the size of impellers to increase pump capacity and discharge pressure. However, many chemical plants break the law when they do so. State boiler codes require that vessels and heat exchangers downstream of pumps be rated for the
  • Maximum pump discharge pressure
  • At the maximum specific gravity that can reasonably be expected
  • Unless the equipment is protected by a relief valve
Increasing the size of an impeller always increases its maximum discharge pressure. Hence, increasing the impeller diameter may be unlawful, depending on the maximum allowable working
pressure (MAWP) of downstream heat exchangers. The MAWP is shown on the exchanger name plate. Increasing the size of the impeller by 10 percent will increase the amperage load on the motor driver by 30 percent. For many process pumps, this would require a new motor and breaker to support the larger impeller.

Trimming the pump impeller on a lathe also requires the reshaping of the tips of the impeller vanes. Most often, this requirement is ignored, and the revamped pump operates below its expected curve.
Rather than worry about these fine points, it is best to order new impellers directly from the manufacturer. Installing a larger impeller may require an upgrade in the pump bearings and the mechanical seal. While it is good practice to purchase a pump with a seal and bearings rated for the
maximum impeller size, some pumps can have bearings and seals rated only for their purchased impeller size. 

For process people, the only practical method to check that a pump’s seal and bearings are suitable for the larger impeller is to check with the manufacturer. Drilling pressure balancing holes in the hub of the impeller helps to reduce the extra strain on the bearings of a larger impeller. Sometimes installing a full-sized impeller causes the pump to vibrate. This happens because of a disturbance to the liquid as the vanes spin past the volute or diffuser (i.e., the case outlet opening).

Exxon had, at one time, a standard of keeping impeller sizes at not more than 92 percent of the full impeller diameter. This seems a conservative practice to me. I have usually kept impeller sizes in my
revamp designs 0.25 to 0.5 in below maximum. I don’t recall any of my clients complaining that such pumps vibrated as a result of the enlarged impeller. On the other hand, for a new installation, now that I’ve learned of the Exxon standard, I plan to follow it in my process design work.

IMPELLER ROTATION

Motor-driven pumps often are found running backward. If the motor is wired up backward (this is called reversing the polarity of the leads), the pump will run with the impeller spinning backward. This will reduce the pump’s discharge pressure, sometimes by a little (10 percent) and sometimes by a lot (90 percent). It depends on the design of the impeller. You cannot see the direction of rotation of a pump, but if you touch a pencil to the spinning shaft, you can feel the direction of rotation. The correct direction of rotation is indicated by an arrow stamped on the top of the pump case. There are right- and left-handed pumps. So two otherwise identical pumps may have opposite directions of rotation.

Capacity EFFECT OF TEMPERATURE ON PUMP CAPACITY

We wish to increase the capacity of a centrifugal pump. Should we make the liquid hotter or colder? Let’s make a few assumptions:
  • Cooling the liquid will not increase its viscosity above 30 or 40 cSt.
  • We are pumping hydrocarbons. Cooling many hydrocarbons by 100°F increases their density by 5 percent.
  • The pump’s motor is somewhat oversized.
On this basis, cooling the liquid by 100°F will raise the pump’s discharge pressure by 5 percent. If the pump is developing 1000 psig of differential pressure, cooling the liquid by 200°F will increase its discharge pressure to 1100 psig. If the discharge control valve is now opened, the pump’s discharge pressure will drop back to 1000 psig as the flow increases. The discharge pressure drops because the pump develops less feet of head at a higher flow rate.


Source : Digital Engineering Library @ McGraw-Hill