Recent content by JoeyF

Thanks a lot @jrmichler for the suggestions. That would be true if I was feeding water 100% of the time. My system only flows when user opens valve, so you get on and off cooling and thus off and on TSTAT. I also do want some water to get through because it "looks" better than pure invisible...

Update with some comparative data. I was able to isolate and collect the condensate in my "Hose". What I collected was on average 1.5 grams. By a 'Theoretical Definition', I could map out Steam Quality for Saturated Steam Mixture at 18 psi (shown below), and match the mass of Water (which...

poor nomenclature on my end. I meant 0.03 g , alternatively 0.03 mL , (g=mL)

Ok, Thanks! Assuming I have 100% Vapor, that would render only 0.03 g/mL of water, i.e., my excess water is not coming from Condensate likely. It takes less than 1% Steam Quality to begin producing larger amounts of Steam/Condensate. By calculation looks like 1% would give me 2.75 g/mL of...

Based on Steam Table, here are some properties I've started on. Just not entirely sure what to do with them yet. Saturated Steam Properties: Gage Pressure = 18 psi Temp = 124.038 °C Specific Enthalpy = 2711.7 KJ / kg Specific Volume of Saturated Steam = 0.7918 m3 / kg [ assuming quality of 1 ...

I've developed a Steam Cleaner using a through-flow heater (800W) . Solenoid pump is roughly 60 mL/min . Heater Power is limited via Thermostat. The Pump is always running. The Steam Outlet is controlled by a deadman-style valve (normally closed). The Steam outlet is also on a hose that has...

14.24 m/s

In Bernoulli's equation, you have static, dynamic, and hydrostatic pressures equal to a constant. In one sense, I'm wondering if the dynamic part of the equation explains this since -> Pressure = (1/2*rho*velocity^2) and pressure can be expressed as a force / unit area, therefore, an increase in...

Yep, these are the equations I plugged into Wolfram. I varied the theta value and it spit out my N1 variable as well as the Fp variable (push force). A force of 17 N is the external force on the pin. X is my friction coefficient (0.3). N*X*cos(theta)+N*sin(theta)+X(N*X*sin(theta)-N*cos(theta))...

It may be the case, but my graph is showing the output assuming friction. In either case, my model has the Normal force to both the pin and the plunger at contact being equal. And if it was a 45° incline, then I would expect the travel to be the same, so that would be equal amounts of work done...

This is kind of what I was after. In order to move the button 2.8 mm, these are the distances needed with forces to go along with the wedge angle.

Thanks Guys, I think I found my main error. I had the Normal force on the plunger body backwards. This should have been pointing inward to the body rather than outward. I did however, redo my coordinate system like you suggested, split the bodies, and added a roller assumption to the vertical...

I apologize if this is the wrong area to post this in, I've never posted on thisforum before. I'm trying to form a FBD of a mechanism that uses linear motion to actuate a pin in a transverse direction. I've attached the general idea in a picture where the pin is free to move up and down. In...