Difference between revisions of "HP Deskjet 600c"
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==Cool Animated Videos==
==Cool Animated Videos==
Revision as of 21:43, 24 March 2007
This inkjet printer is manufactured by Hewlett Packard, and is used to transpose displayed digital data onto a physical medium.
How It Prints
The computer sends a data stream to the printer through a serial, or usb cable. The control unit inside the printer deciphers the data and instructs the mechanical components to act accordingly. The following is an illustrated outline of the mechanical aspect.
1) Paper is advanced into position by the rubber rollers, which are powered by a stepper motor.
2) Another stepper motor, undocks the printer carriage. The dock is used to secure the carriage, and to keep the printer head clean.
3) The printer carriage is operated by a drive belt, which is powered by a third stepper motor.
4) The printer cartridge applies ink onto the paper according to the instructions supplied by the CPU through the copper contacts.
The table belows lists the components for the HP Deskjet 600c printer:
|Part #||Part Name||Category||Function||Material||Picture|
|1||Paper Tray||Structural Component||Holds Paper that is to be loaded in place||Plastic|
|2||Printer Housing||Structural Component||Protects internal components from the environment||Plastic|
|3||Large Stepper Motor||Input||Provides motion to the paper feeder mechanism||Metal casing, copper wire, magnet, gear|
|4||Docking Station Motor||Input||Controls the motion of the docking station||Metal casing, copper wire, magnet, gear|
|5||Printer Cartridge Holder and Rail||Output||Slides the Printer head along the railing from left to right||Plastic housing and metal rail|
|6||Paper Feed Gears||Transmission||Takes the input from the feed motor and controls the feeding of the paper||One plastic gear and one metal gear|
|7||CPU and Power Source||Input||Controls the entire printer and modulates the power input||Silicon, lead, copper, resistors, capacitors|
|8||Paper Ejector and Advancer Mechanism||Motion Conversion||Lowers the black bar so paper ejects cleanly, and raises bottom tray||Plastic|
|9||Print Head Motor||Input||Provides motion to print head||Metal case, copper wire, magnet, gear|
|10||Docking Station||Motion Conversion / Structural||Cleans and houses printer head when not printing||Plastic|
Computer Rendered Components
Drive Belt System
Paper Advancing Rollers
Cool Animated Videos
<embed src="http://www.youtube.com/v/8_iTSznToHU" type="application/x-shockwave-flash" width="425" height="350"></embed>
Animated Printer Carriage
<embed src="http://www.youtube.com/v/iayt04lR08E" type="application/x-shockwave-flash" width="425" height="350"></embed>
Animated Paper Feed Mechanism
Analysis Of The Belt System
Scope of Analysis
The two engineering specifications that are quantified for the printer belt tensioning system, are the force on the belt required to accelerate the printer head to its maximum speed, and the force to stop the printer carriage and change direction. Both of these specifications pertain to the Dots Per Inch design parameter. The best design is to obtain the maximum DPI rating in the quickest printing time. To achieve this goal, the belt must be able to cope with the forces to accelerate the printer carriage.
- Printer Prints 4 pages a minute at 300 DPI
- Mass of Carriage With Ink Cartridge = 0.14 kg
- Moment of Inertia of Pulley = 0.5 (.002kg)(0.005^2m) = 2.5 x 10^8
- The belt is a trapezoidal design, meaning each tooth has the shape of the trapezoid
- The belt is made out of polyurethane which has good wear resistance and low friction
Friction force exerted by the slider on the carriage is always constant when moving, and should have been reduced to a minimum by the manufacturer. Lower friction would reduce the force the stepper motor has to supply to move the carriage. Since it is difficult to measure the exact amount of friction force, and it is relatively small compared to the acceleration forces, friction can be neglected.
Finding The Speed
Since, the actual printer head speed I could not be found, a few assumptions had to be made with the available information. The printer has a 300 DPI rating, which means that it can print 90,000 dots per square inch. It can print 4 pages of text per minute. Assuming that it prints 8.5” x 11” pages with a 1” top and bottom margin, and 1.25” side margins, it leaves a total of 54 square inches of text. This equates to 4.86 x 10^6 dots per page. Multiply the dots per page by the pages per minute, and that results in 2.43 x 10^7 dots per minute. 2.43 x 10^7 dots per minute is the average printing rate for the printer. However, if we assume the format is 12 point, Times New Roman font, the total area per line of text is 1.95 in^2 (6.5” x .3”) 0.54 square inches per page multiplied by 4 pages per minute, divided by 1.95 square inches per pass, and taking the reciprocal, yields .009 minutes per line, which is 0.54 seconds per line. Every line is 6.5 inches long, which means that the printer head moves at 12 inches per second. Since information on the acceleration of the printer carriage could not be obtained, it was instead estimated. After careful observation of other inkjet printers, the carriages reach their top speed almost instantaneously, so it was estimated that it takes 0.2 seconds to reach maximum velocity, and 0.25 seconds to stop and change direction.
- Acceleration of Carriage From Rest
Acceleration of Carriage = max velocity/ time = (0.3048 m/s) / 0.2 s = 0.15 m/s2
Mass of Carriage With Ink Cartridge = 0.14 kg
F = ma = (0.14)(0.15) = 0.021 N
Therefore, it takes .021 N to accelerate the carriage from rest to the max velocity
- Stopping and Changing Direction
Change in velocity = (0.3048+.03048) = 0.6096 m/s
Change in Time = 0.25 s
F = (Mass*Change in Velocity)/ Change in time = 0.34 N
Therefore, the maximum force exerted on the belt due to the change in direction is 0.34 N.
As seen in Figure 10 below, the maximum force to pull the carriage is related to the torque supplied by the motor pulley. Furthermore, the carriage is fixed to one side of the belt, so it translates directly with the belt. During the analysis, the entire carriage is treated as a point mass and represented as a block. Figure 11 shows the free body diagram of the motor pulley. It is evident that the torque from the pulley is directly related to the force on the belt during acceleration.
The analysis through Adams produced results that were similar to the calculated values. The maximum force, as seen in Figure 12, reached 1 N which was very close to the calculated value of 0.34 N.
To increase the maximum force that the belt could handle, a few options are available. The cross-sectional area could be increased to decrease the stress on the belt. According the stress equation, stress = load / area , the stress can be reduced by increasing the cross sectional area to compensate for load force. The cross sectional area can be increased by making the belt wider or thicker. Making it wider would be more beneficial because it would provide a greater surface area for the toothed pulley to grip onto. The drawbacks for increasing the surface are the increase in stiffness and cost of manufacturing. Making the belt thicker would reduce its flexibility, making it harder for it to move around the pulley. It would require more torque form the input motor to compensate. Making the belt wider would force the pulleys to be wider, which drives up the cost of the system.
Another method to increase the stress capacity of the belt would be to use a curvilinear design instead of the current trapezoidal design. The curvilinear design looks very similar to the gear sprocket of a bicycle. Instead of a trapezoid shape, the curvilinear design uses a half circle shape. Therefore, the teeth are deeper in the gear which makes it less probable for tooth jumping during high accelerations. Furthermore, there is less material at the edges of the gear, which lowers the moment of inertia, allowing the gear to accelerate faster.
Figure 13 shows the photoelastic stress pattern of both designs, and it is evident that the curvilinear shape distributes stress more evenly. This is due to the larger tooth cross section. Since the curvilinear shape handles stress better than the trapezoidal shape, a narrower curvilinear belt could be used in place of a wider trapezoidal belt, thus, saving material and cost.