Overview
Our objective is to design and analyze a mechanism prototype that can locate the tab of a can and produce enough force to open the tab. In this section, the kinematics analysis of three distinct mechanisms are shown to decide which motion pattern, velocity, and force output will be best to lift the tab of a canned beverage. Our analysis will be focused on 2 variations of the four bar mechanism, where one is in an open configuration and the other is a closed configuration. Our goal is to find the best combination of position, velocity, and mechanical advantage that is able to position the last link under the minimal space under a tab and produce enough force to lift the tab up. We hypothesize that the desired path of the end effector will look similar to the path shown in the image below. Through research and empirical testing, we have determined that our mechanism will need to output approximately 30 Newtons of force to reliably pop open the tab on a can. To achieve our force requirement, we need to minimize the velocity of the end-effector on link 3 and maximize the mechanical advantage during its interaction with the tab.
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Figure 1: Open 4-bar configuration (Mechanism 1). Figure 2: Closed 4-bar configuration (Mechanism 2).
Kinematic Analysis
In this section, each mechanism will be thoroughly analyzed to find the specific kinematic profiles that fits our needs for this project. Our intention is to follow the path shown in Figure 3 and constrain the position to fit the area on the top of the can. The end-effector needs to first begin at the initial contact within the 8 mm area between the lip of the can and the tab. Then, the end-effector is positioned within that area, a sliding motion will transfer the end-effector to be under the 25 mm tab. After that sliding motion, the mechanism will need to pull the tab open with enough force to open the can. The force to input angular velocity relationship needs to be defined with a high mechanical advantage at that specific time frame from the initial contact to when the mechanism pulls up. Once we define the link lengths and configuration of the best mechanism, we can continue with creating the prototype.
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Figure 3: Position diagram of how and when the motion of the end-effector on link 3 in the 4-bar open configuration will open the tab of the can.
Mechanism 1: Open 4-Bar Configuration
Position Analysis
Pictured below are the varying position profiles of the end-effector link for mechanism 1. We iterated through different lengths for each link, besides link 2, the length of link 2 had to remain constant as it determined the length that the end effector was in contact with the can. We also wanted to only use lengths that would satisfy the Grashof condition and produce a path that was closer to the desired position (drawn above) to be able to get under the tab of the can. Due to the size of the can, this path is very small and must be very precise. The mechanism achieved the desired path about halfway through each of the iterations, with the link lengths established in the table below.
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The original value of the angle of link one was 0 degrees, which produced the first velocity plot shown above for the mechanism's end link. From our analysis in Motion Gen we know that the end-effector (attached to link 3 as shown in the photo above) interacts with the tab of the can when the crank angle is around 180 degrees. In the first plot we can see that with a theta1 = 0 degrees the velocity is decreasing as it pulls the tab up, but it is not the slowest that it could be. When we change our mechanism such that theta1 = 120 degrees, the lowest velocity is achieved where the end-effector needs to impart the most force.
Mechanical Advantage
Figure 6: Analysis of the mechanical advantage after changing the angle of link 1.
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Figure 8: Final open 4-bar mechanism after kinematic analysis
Mechanism 2: Closed 4-Bar Configuration
For the Crossed 4-Bar configuration, the team has found a patent that modeled the segments of the human finger with a crossed 4-bar linkage. The idea is that the crossed 4-bar is able to induce a rotation of the the coupler linkage and the extension on the coupler linkage is able to curve similar to a human finger. For our model, we designed the crossed 4-bar linkage similar to the picture shown in Figure 8 and attached another link at position 104 to describe the tip of the finger. There were link lengths given within the patent that the team used as a starting point to the mechanism design. These link length values values are given in Table 1.
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Table 2: Link lengths given from patent
Position Analysis
Our team modified the link lengths individually to find the best position profile that can curl the end-effector under the tab and lift the tab. In figure x, each link is varied to find a position profile that best matches our desired profile.
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Figure 11: Position Analysis with Theta 1 of 0 Degrees and 45 Degrees
Velocity Analysis
For the velocity analysis, the team calculated the velocity profiles of the corresponding link length modifications and Figure X depicts the velocity profile for the different link lengths.
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Figure 13: Velocity Analysis with Theta 1 of 0 Degrees and 45 Degrees
Mechanical Advantage
For the mechanical advantage, we calculated the ratio between the angular velocity of the input link to the output velocity calculated in the above section and Figure X depicts the mechanical advantage as the link lengths are altered.
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Figure 15: Mechanical Advantage with Theta 1 of 0 Degrees and 45 Degrees
Mobility and Grashof Analysis
Similar to the previous mechanism, the Grashof and mobility equations were used to calculate if the preferred mechanism is able to have full continuous motion about the input joint. The mobility of the crossed 4-bar mechanism is 1, which is described by the rotational movement that is created. however, the preferred mechanism design is not Grashof, highlighted with the non-continuous motion. However, because we are looking for a hooking mechanism, this non-Grashoff design we created is still able to complete the goals we need.
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Figure 17: Final crossed 4-bar mechanism after kinematic analysis
Selected Design
Our team has chosen to continue with the open 4-bar design as the position profile is closely matching the continuous motion we described at the beginning. Not only is the path very similar, the distance that the end effector needs to travel when in contact with the can is more easily controlled with the open 4-bar. Furthermore, the velocity and resulting mechanical advantage from the best open 4-bar configuration provides a desirable location to apply a high force to the tab. Following this kinematic analysis is documentation of the prototype iterations we have created.
Iterative Documentation
Prototype #1: Cardboard
When starting our prototype, we began creating the mechanism with cardboard to map out the movement with physical pieces. We measured the the link lengths to approximately the desired lengths that were defined in Motion Gen. The goal for this prototype is to observe and understand the motion of the mechanism using physical components. However, cardboard is very flimsy and susceptible to breaking down after repetitive use.
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Figure 19: Laser cur prototype of our open 4-bar mechanism.
Final Prototype
The final prototype is similar to the previous in that we laser cut linkages; however, we replaced the rods with M6 screws and mounted it to a board to produce smooth motion. In the gif below you can see that the position profile of the end-effector models the position profile we determined in our kinematic analysis.
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Figure 20: Moving prototype of our open 4-bar mechanism.
Bill of Materials
Our bill of materials are given within this spreadsheet . We expect to collect all the parts by 4/15.
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