Name: Uncoupling Coriolis Force and Rotating Buoyancy Effects on Full-Field Heat Transfer Properties of a Rotating Channel (Video) | JoVE Journal
Uploaded: 2018-10-05T12:30:00.000+00:00
Duration: 10 min 3 s
Description: Learn to decouple Coriolis force and rotating buoyancy effects on heat transfer in rotating channels using a rotating rig and infrared thermography. This method reveals individual contributions to local heat transfer properties.

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5 minutes

The present research work was financially sponsored by the Ministry of Science and Technology of Taiwan under the grant NSC 94-2611-E-022-001, NSC 95-2221-E-022-018, NSC 96-2221-E-022-015MY3 and NSC 97-2221-E-022-013-MY3.

NOTE: The details of rotating test facilities, data acquisition, data processing and the heat transfer test module emulating an internal cooling channel of a gas turbine rotor blade are in our previous works29,30,31,32.
1. Preparation of Heat Transfer Tests
<ol>
	<li>Formulate the experimental conditions in terms of Re, Ro and Bu from the targeted operation conditions of a gas turbine rotor blade.</li>
	<li>Determine the N, P, d, R, and Tw - Tb needed for acquiring the tested Re, Ro and Bu using equations (14) and (15).</li>
	<li>Re-define the targeting Re, Ro and Bu if N, P, d, R, and Tw - Tb exceeds the limit of the experimental facilities.</li>
	<li>Design and construct the scaled heat transfer test module emulating a practical internal coolant channel in a gas turbine rotor blade2.</li>
</ol>
2. Determination of Thermal Emissivity Coefficient for Infrared Thermography System
<ol>
	<li>Install the calibrated thermocouple on the back side of the scanned stainless-steel heating foil.</li>
	<li>Spray a thin layer of black paint on the stainless-steel heating foil scanned by the infrared camera.</li>
	<li>Create symmetrical flow fields on two sides of the stainless-steel heating foil by placing a vertical thin stainless-steel foil in a space with the free convective flows over the two sides of the vertical heating foil.</li>
	<li>Feed electrical heating power through the heating foil and measure temperatures simultaneously by thermocouple and infrared thermography system from the computer display at steady state.</li>
	<li>Repeat step 2.4 at least four times using elevated heater powers. Ensure that the wall temperatures corresponding to the heater powers used by steps 2.3 and 2.4 cover the Tw range determined by step 1.2.</li>
	<li>Calculate the Tw values scanned by the infrared thermography system using a number of selective thermal emissivity coefficients for the program that converts the infrared signals into temperature data.</li>
	<li>Compare the Tw data measured by the calibrated thermocouple and the infrared thermography system at the location corresponding to the thermocouple spot with the standard deviations evaluated.</li>
	<li>Select the thermal emissivity coefficient with the minimum standard deviation determined by step 2.7.</li>
	<li>Determine the maximum precision error for the infrared thermography system using the thermal emissivity coefficient determined by step 2.8.</li>
</ol>
3. Dynamic Balance of Rotating Rig
<ol>
	<li>Install the heat transfer test module, the infrared camera, the enveloping frame and all accessories on the rotating rig.</li>
	<li>Adjust the counterbalancing weight gradually until the running condition of the rotating rig satisfies the vibrational limitation for the infrared thermographic measurements to exhibit the stable thermal image on the computer display.</li>
</ol>
4. Evaluation of Heat Loss Coefficients
<ol>
	<li>Fill the coolant channel of the heat transfer test module with thermal insulation material.</li>
	<li>Install the filled test module on the rotating test rig by fitting the test module on the rotating platform and connecting the heater power supply and all the instrumental cables.</li>
	<li>Activate the data acquisition system to scan the temporal Tw variation at a heating power until the steady state condition is satisfied. Ensure that the temporal Tw variations during several successive scans are less than +0.3 K at each steady state condition.</li>
	<li>Record the heater power, steady-state Tw data and the corresponding ambient temperature, T&#8734;.</li>
	<li>Repeat steps 4.3 and 4.4 at least five times using different heating powers at a fixed rotating speed.</li>
	<li>Repeat steps 4.2 - 4.4 with at least five rotating speeds. Ensure that the test range of the rotating speed covers all the N values determined by step 1.2.</li>
	<li>Repeat steps 4.3 - 4.6 with a reversed rotating direction.</li>
	<li>Construct the plots of heat loss flux against wall-to-ambient temperature difference at each rotating speed.</li>
	<li>Correlate the heat loss coefficients as the functions of wall-to-ambient temperature difference, rotating speed and direction of rotation.</li>
	<li>Incorporate the heat loss correlation into the post data process program for Nu accountancy.</li>
</ol>
5. Baseline Heat Transfer Tests
<ol>
	<li>Perform heat transfer tests at the targeting Reynolds numbers at zero rotating speed (Ro = N = 0) by feeding coolant flows and heater powers to the test module. Ensure the supplied coolant mass flow rate is constantly adjusted in order to control Reynolds number at the flow entry plane at the targeting value.</li>
	<li>Record all the relevant raw data, including the steady state wall temperatures, fluid temperatures, heater powers, flow pressures and ambient pressures and temperatures, for subsequent data processing.</li>
	<li>Evaluate the local and area-averaged Nusselt numbers (Nu0) over the scanned static channel walls.</li>
</ol>
6. Rotating Heat Transfer Tests
<ol>
	<li>Install the on-line monitoring program to monitor the test conditions at the targeting Re and Ro.</li>
	<li>Feed the measured coolant mass flow rate, airflow pressure, rotating speed and fluid temperature at channel entrance into the monitoring program to calculate the instant Re and Ro.</li>
	<li>Record all the relevant raw data, such as rotating speed, heater power, airflow and ambient pressures, as well as the wall and fluid temperatures for subsequent data processing after the pre-defined steady-state condition is satisfied.</li>
	<li>Repeat steps 6.2 and 6.3 with at least four ascending or descending heater powers at a set of fixed Re and Ro. Ensure that the test Re and Ro fall within &#177;1% differences from the targeting values by adjusting the rotating speed or the coolant mass flow rate or both.</li>
	<li>Ensure that the heat transfer tests at each set of fixed Re and Ro with different heater powers are continuously performed as the development of buoyancy induced flows is associated with the &#34;history&#34; of the flow development.</li>
	<li>Repeat steps 6.4 and 6.5 with four or five targeting Reynolds numbers (Re) at a fixed rotation number (Ro). Ensure the rotating speed is appropriately adjusted at each test Re to control both Re and Ro at the targeting values within &#177;1% differences.</li>
	<li>Repeat step 6.6 using four or five targeting rotation numbers (Ro).</li>
	<li>Repeat steps 6.2 to 6.7 with reversed rotating direction.</li>
	<li>Evaluate the local and area-averaged Nusselt numbers (Nu) over the scanned rotating channel walls using a post data processing program.</li>
</ol>
7. Parametric Analysis
<ol>
	<li>Correlate the area-averaged Nusselt numbers (Nu0) collected from the static channel into the functions of Reynolds number.</li>
	<li>Evaluate the full-field local Nu/Nu0 ratios at each fixed Re and Ro tested with the area-averaged Nu/Nu0 ratios calculated.</li>
	<li>Verify the applicability of isolation Re effect by plotting the local and area-averaged Nu/Nu0 ratios obtained with different Re but at identical Ro.</li>
	<li>Disclose the isolated impacts of rotating buoyancy on heat transfer properties of the rotating test channel by plotting the area-averaged Nu/Nu0 ratios collected at the same Ro with different Re against Bu or density ratio (&#916;&#961;/&#961;). Ensure the preferable selection of Bu or &#916;&#961;/&#961; to construct this type of plot for obtaining the consistent data trend with a simple functional structure for heat transfer correlation.</li>
	<li>Extrapolate each Nu/Nu0 data trend collected at a fixed Ro but different Re into the limiting condition of Bu&#8594;0 or &#916;&#961;/&#961;&#8594;0.</li>
	<li>Collect all the extrapolated Nu/Nu0 results with Bu&#8594;0 or &#916;&#961;/&#961;&#8594;0 at all the tested Ro.</li>
	<li>Plot the extrapolated Nu/Nu0 results with vanished buoyancy interaction against Ro to disclose the uncoupled Coriolis force effects on the heat transfer properties.</li>
	<li>Correlate the test results collected by steps 7.4 and 7.7 into the functions of Ro and Bu.</li>
</ol>

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<li>Rallabandi, A., Lei, J., Han, J. C., Azad, S., Lee, C. P. <a target="_blank" href="http://turbomachinery.asmedigitalcollection.asme.org/article.aspx?articleid=1838162">Heat transfer measurements in rotating blade-shape serpentine coolant passage with ribbed walls at high Reynolds numbers.</a> ASME Journal of Turbomachinery. 136 (9), (2014).</li>
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<li>Chang, S. W., Yang, T. L., Liou, T. M., Fang, H. G. <a target="_blank" href="https://www.sciencedirect.com/science/article/pii/S1359431108003232">Heat transfer in rotating scale-roughened trapezoidal duct at high rotation numbers.</a> Applied Thermal Engineering. 29 (8), 1682-1693 (2009).</li>
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<li>Xu, G., Li, Y., Deng, H. <a target="_blank" href="https://www.sciencedirect.com/science/article/pii/S1359431115001192">Effect of rib spacing on heat transfer and friction in a rotating two-pass square channel with asymmetrical 90-deg rib turbulators.</a> Applied Thermal Engineering. 80 (5), 386-395 (2015).</li>
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</ol>

The authors have nothing to disclose.

While the endwall temperatures of a rotating channel are detected by an infrared thermography system, the fluid temperatures are measured by thermocouples. As the alternative magnetic field of an AC motor that drives a rotating rig induces electrical potential to interfere the thermocouple measurements, the DC motor must be adopted to drive a rotating test rig.
The fluid temperature distribution over the exit plane of a heated channel is not uniform. At least five thermocouples on the existing...

<table><tbody><tr><td>Rotating test rig</td><td>In-house made</td><td></td><td>Design by this research group</td></tr><tr><td>Heat transfer test module</td><td>In-house made</td><td></td><td>Design by this research group</td></tr><tr><td>Mass flow meter</td><td>Eldride Product, Inc.</td><td>3100301-01-01&lt;br/&gt; 359-1007</td><td></td></tr><tr><td>Infrared thermography system</td><td>NEC P384A-8</td><td>3100401-04&lt;br/&gt; 3127A-4</td><td></td></tr><tr><td>Instrumentation slip ring</td><td>Michigan Scientific SR36M</td><td>3100506-62&lt;br/&gt; 3553-372</td><td></td></tr></tbody></table>

uncoupling coriolis force and rotating buoyancy effects on full-field heat transfer properties of a rotating channel

Uncoupling Coriolis Force and Rotating Buoyancy Effects on Full-Field Heat Transfer Properties of a Rotating Channel

An experimental method for exploring the heat transfer characteristics of an axially rotating channel is proposed. The governing flow parameters that characterize the transport phenomena in a rotating channel are identified via the parametric analysis of the momentum and energy equations referring to a rotating frame of reference. Based on these dimensionless flow equations, an experimental strategy that links the design of the test module, the experimental program and the data analysis is formulated with the attempt to reveal the isolated Coriolis-force and buoyancy effects on heat transfer performances. The effects of Coriolis force and rotating buoyancy are illustrated using the selective results measured from rotating channels with various geometries. While the Coriolis-force and rotating-buoyancy impacts share several common features among the various rotating channels, the unique heat transfer signatures are found in association with the flow direction, the channel shape and the arrangement of heat transfer enhancement devices. Regardless of the flow configurations of the rotating channels, the presented experimental method enables the development of physically consistent heat transfer correlations that permit the evaluation of isolated and interdependent Coriolis-force and rotating-buoyancy effects on the heat transfer properties of rotating channels.

Realistic operating conditions for the internal coolant flows inside a rotating gas turbine blade in terms of Re, Ro and Bu are compared with the emulated laboratory conditions in Figure 1. The data points fall in the realistic engine conditions using the present experimental method summarized in the protocols11,14,17,20,<sup c...

Here, we present an experimental method for decoupling the interdependent Coriolis-force and rotating-buoyancy effects on full-field heat transfer distributions of a rotating channel.

An experimental method for exploring the heat transfer characteristics of an axially rotating channel is proposed. The governing flow parameters that ...

uncoupling-coriolis-force-rotating-buoyancy-effects-on-full-field

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Learn to decouple Coriolis force and rotating buoyancy effects on heat transfer in rotating channels using a rotating rig and infrared thermography. This method reveals individual contributions to local heat transfer properties.

Uncoupling Coriolis Force and Rotating Buoyancy Effects on Full-Field Heat Transfer Properties of a Rotating Channel

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