"If you want to find the secrets of the universe, think in terms of energy, frequency and vibration." ― Nikola Tesla
Could Tesla's secret be the energy wasted due to vibration at a frequency equal to shaft speed all caused by rotor unbalance?
Balanced rotors are critical for achieving production and profit goals. Unbalance creates high vibration, which leads to other faults resulting in decreased machine life, wasted energy and reduced efficiency. Smooth-running machines are required for producing products that meet customer specifications. The IOSR Journal of Mechanical and Civil Engineering states that rotor unbalance is the major cause of vibration problems. A good balancing process is essential for successful physical asset management.
A rotor that operates at a rotational speed below 70 percent of its critical speed is considered to be a rigid rotor. The critical speed is the speed at which resonance occurs by exciting its natural frequency. Ninety percent or more of rotors are rigid.
Rotor unbalance can be defined as a condition that exists when the geometric center and the center of mass (also known as the center of gravity) do not coincide. In reality, these centers never coincide exactly, but the goal of rotor balancing is to reduce the unbalance to the point that machine life is not negatively impacted by the residual unbalance. The balancing technician attempts to bring the center of mass and the geometric center to the same point or close enough to meet a predetermined balance standard. There will always be some residual unbalance.
Several standards organizations have developed balancing standards for use on various machines. ISO and API are a couple of examples. Some companies develop their own standards. Which standard should you use? Choose standards that will allow you to achieve the required machine life and preserve equipment functions to the levels required by your processes. This may sound like a political answer, but in reality, the standards may vary depending on your plant's requirements. The requirements will already be known if you are using a well-defined physical asset management process.
Unbalance is measured in units of ounce/inches or gram/millimeters. However, when you balance in the field, you usually balance to a vibration standard because it is easier to determine machine vibration levels than to determine residual unbalance.
The vibration due to unbalance is directionally proportional to the amount of unbalance. If the vibration levels due to unbalance are lowered to an acceptable level, the amount of unbalance is also brought to within an acceptable standard.
Balancing is performed after acquiring vibration and phase measurements. There are three requirements for balancing: steady vibration, steady phase, and the vibration and phase measured must be due to rotor unbalance.
Before attempting to field balance a rotor, follow these basic steps:
Data collectors/analyzers such as the Vibxpert can be used to perform the vibration analysis necessary to identify unbalance.
Unbalance is a radial force and produces a vibration frequency equal to shaft speed. The radial force can sometimes produce a vibration in an axial direction, especially in overhung or cantilevered rotors. In these rotors, the axial vibration may be even greater than the radial vibration. The radial force causes the shaft to deflect, producing an axial direction vibration in the bearings.
Normally, unbalance will produce a 1× or shaft speed vibration that is 80 percent or more of the total vibration. If 1× vibration is less than 80 percent, suspect other problems in addition to the unbalance. This is the same as stating that the vibration at other frequencies should not exceed 20 percent of the overall vibration. It may be necessary to correct the other problems before the rotor can be properly balanced.
Unbalance always exerts an equal force in all radial directions, but the vibration due to the unbalance is almost never equal in all directions. The horizontal vibration is usually the highest in amplitude because most machines are less stiff in that direction. Be careful because there are exceptions such as looseness in the bearings and vertical resonance.
If vibration amplitudes in the radial positions differ by 5:1 or more, other problems usually exist. If more than three harmonics of shaft speed are visible in the spectrum, other problems could be present, with the most likely being looseness. All other problems should be corrected before attempting to balance the rotor. The image below shows the corresponding measurement and weight correction planes.
Phase is a very important tool when diagnosing unbalance because 1× vibration can be generated by several other problems. Phase numbers shown below may vary by 15 degrees.
Force unbalance phase difference: 0 degrees when comparing the same radial positions on two bearings.
Couple unbalance phase difference: 180 degrees when comparing the same radial positions on two bearings.
Dynamic unbalance phase difference: 0 to 180 degrees when comparing the same radial positions on two bearings.
The phase shift from horizontal to vertical should be approximately 90 degrees for all types of rotor unbalance when measured on the same bearing. The phase should be steady and repeatable when attempting to balance. (It may become unstable after a trim balance because other problems tend to become more dominant.) A good indication of unbalance is that the phase difference between inboard horizontal (IBH) and outboard horizontal (OBH) should equal the phase difference between inboard vertical (IBV) and outboard vertical (OBV).
Phase errors drastically affect balancing. For example,
All rotors regardless of their diameter/width (D/W) ratio should be balanced in two planes.
However, on overhung rotors, if vibration in the bearing nearest the overhung mass has an amplitude of approximately four times the vibration in the other bearing, single-plane balancing may work. Overhung rotors with a D/W ratio of 4:1 or more may sometimes be balanced within the tolerance by a single-plane balance.
In addition, sometimes narrow overhung rotors don't respond well to two-plane balancing. On overhung narrow rotors, it becomes more difficult to separate the influence of the two weight planes on the two measurement planes. This is simply because narrow rotor weight planes are in close proximity to each other.
To determine if a two-plane balance job is needed, set up and take four measurements but enter only one correction plane (single plane). Ask the program for estimated reductions. If the estimates are within tolerance, continue with a single-plane balance. If the estimated reduction is out of tolerance, change the setup to two correction planes and continue.
The time waveform should contain a strong sine wave component. Acceleration measurements distort the time waveform because higher frequencies are amplified.
Steady phase and steady amplitude are also requirements for balancing. If either is not steady, don't diagnose the problem as unbalance. Sometimes it may be wise to make vibration measurements and then shut down the machine. Start the machine again and see if the vibration and phase measurements can be duplicated.
Proper trial weight (TW) selection is important because a weight that is too light may not provide an adequate response for calculating correction weights and placement. A trial weight that is too large may wreck the machine. Trial weights should adhere to the 30/30 rule: change the phase by 30 degrees or the amplitude by at least 30 percent.
F = Rotor weight × 10 percent
F = (1.77) × (TW) × (R) × (rpm ÷ 1,000)2
Where: F = Force in pounds, TW = Trial weight in ounces, R = Radius in inches
Example: 5,400-pound rotor, 1,800 rpm, 13.5-inch radius
F = 5,400 × 10 percent; F = 540
540 = (1.77) x (TW) x (13.5) x (3.24)
540 = 77.4 TW
TW = 6.98 ounces
When rotors won't stay in balance, the following problems should be suspected:
The mindset of "It's a fan and it shakes so it must need balancing," is referred to as the balancing syndrome and can get you into trouble. Here are some tips that will help you avoid such pitfalls.
Rotors do not become unbalanced without a cause. If a rotor has been acceptably balanced and becomes unbalanced, always try to detect and correct the root cause of the unbalance. Sometimes rotor-reinforcing gussets may crack, allowing the rotor to deform and resulting in a sudden unbalance. If the rotor is rebalanced without repairing the cracks, sudden and catastrophic machine failure may occur if the gussets fail completely. Such problems can usually be avoided by performing a thorough cleaning and inspection.
Vibration is measured in displacement, velocity and acceleration. Velocity and acceleration are generally the most often used units, but when you balance rotors, you usually use displacement measured in mils. This is because displacement gives the best indication at low frequencies, and you are dealing with 1× shaft speed when balancing. The technician needs to be aware that 1 mil of vibration on a machine running at 900 rpm is not comparable to 1 mil of vibration on a machine operating at 3,600 rpm. There is considerably more force exerted on the 3,600 rpm machine.
The top causes for failing to achieve the required standard when balancing include:
Becoming proficient at rotor balancing requires having good tools and being knowledgeable in their use. A fundamental knowledge of balancing theory and balancing procedures is also critical for success. Having a good grasp of vibration analysis will help to ensure that the technician performs balancing only when the problem is unbalance. Because of many variables, there remains some art to balancing. With better tools and an improved knowledge, base balancing has become less of an art and more of an applied science.