LAB 13: PNEUMATIC DRILLING STATION
PURPOSE: The purpose of this laboratory exercise is to provide an overview of the function and operation a pneumatic distribution system, work station operation, and electrical control. System components related to compressor horsepower, pressure drops due to friction, receiver size, and workstation consumption will be evaluated.
OBJECTIVES: After completing this laboratory exercise, you should be able to do the following:
1. Determine the
cycle time for a pneumatic workstation (WS #4) given a production
rate of 720 pieces per hour.
2. Identify
pneumatic components represented by ISO/ANSI graphic symbols;
3. Determine the
consumption rate of pneumatic cylinders;
4. Determine the
consumption rate of pneumatic motors;
5. Calculate the
pressure loss due to friction in a pneumatic distribution line;
6. Calculate the
required receiver size under the specifications given;
7. Determine the
horsepower and power required to run a compressor;
PROCEDURE: Complete the following steps in order to
carry out the requirements for this laboratory:
1. Determine the
consumption rate of all individual actuators for workstation 4 and
calculate the total consumption rate;
2. Calculate the
appropriate SCFM required;
3. Assuming 1/2
inch steel pipe is used for distribution, determine the pressure
loss due to friction from the receiver to work station # 4.
Note: Assume ONLY Work station # 4 is operating and the
compressor is NOT running.
4. Under the
maximum consumption conditions given for the system, calculate the
appropriate receiver size (in gallons);
(Note: You do not need to account for over sizing, just the
calculated values, for this lab).
5. From the
equation given in class, determine the maximum horsepower being
consumed at the drive shaft of the compressor.
6. Submit a
formal report for the lab.
SYSTEM: PNEUMATIC DRILLING WORK STAION
Note: Production Rate = 720
Parts per hour.
PNEUMATIC CIRCUIT
Feed/Clamp Cylinder: 2.0
Inch Bore, 12 inch stroke, 1/2 inch Rod
Drill Cylinder: 2.5 inch bore; 10 inch stroke; .625 inch
rod.
Drill Motor: Vd=.150 cubic inches per revolution; RPM =
6800
Eject Cylinder: 1.5 inch bore; 8 inch stroke; 1/2 inch
rod.
NOTE: WS1 = 2 CFM, WS2=4 CFM, and
WS3=3 CFM
Maximum
consumption condition: Workstations 1, 2, 3, and 4
are running simultaneously for 5 minutes.
ELECTRICAL CONTROL CIRCUIT:
Programmble Logic Controller - Allen Bradley
KEY EQUATIONS:
COMPRESSION RATIO: CR =
(atmospheric pressure + gage pressure) / atmospheric pressure;
Based on standard air,
atmospheric pressure is assumed to be 14.7 pisa for the English
System, 101 KPa for the Metric System.
CR = (14.7 + gage pressure) /
14.7
CONSUMPTION RATES: (Qr)
Qr(cylinder) = (A x S x N x CR) / K Note: In the English System: A= in sq. S = in. N=cpm ; CR=compression rate; K = 1728
Qr (cylinder) = (A x S x N X CR)/ 1728
Qr(motor) = (Vd x N x CR) / K ; Note In the English system: Vd in cubed / rev; N = rpm; CR = compresstion ration; K = 1728
Qr(motor) = (Vd x N x CR) / 1728
SIZING RECEIVERS: (an example problem is also shown in your text)
Vr = atmospheric pressure x (t) x (Qr-Qc) / (Pmax - Pmin)
t is the time the system is consuming air (usually the
maximum flow condition);
For the English system, using standard air and SCFM for Q the
equation is as follows:
Vr = [14.7 x (time in minutes) x (Qr - Qc)] / [ PSI(max) - PSI(min) ]
PRESSURE LOSSES DUE TO FRICTION: ( English System - assuming schedule 40, commercial steel pipe)
General equation for Delta P = c x L x Q2 / CR x d5
Specifically for commercial steel pipe, schedule 40, English system only.
Delta P = (0.1025 x L x Q2) / ( 3600 x CR x d 5. 31 )
Where 0.1025 = friction factor for commercial steel pipe
(these coefficients are experimentally derived
based
on the type of conduit being used.
L
= Total length of pipe + equivalent lenght for valves and
fittings.
Q
= flow in SCFM
3600
= Constant to convert units
CR
= Compression ratio
d
= pipe diameter in inches (use actual inside diameter for
schedule 40 pipe).
POWER AND HORSE POWER (For adiabatic conditions which assumes no loss or gain of heat).
To determine the horsepower and power required to drive an air compressor, the following formulae can be used:
For the English System, Use:
HP = [ (Pin x Q) / (65.4)] x [ (Pout / Pin)0.286 - 1 ]
Where:
Pin = inlet atmospheric pressure ( psia)
Pout
= outlet pressure (psia)
Q
= Flow rate (standard cubic feet per minute)
Note: This is a variation of the formula used in the
Norvelle text. The 0.0286 constant is for air under
adiabatic conditions.
For the metric System to determine theoretical power (kW) use:
Power (kW) = [ (Pin x Q) / 17.1 ] x [ ( Pout / Pin) 0.286) - 1 ]
Where: Pin = inlet atmospheric pressure (kPa abs)
Pout
= outlet pressure (kPa abs)
Q
= flow rate (standard meters cubed per minute)