Under-Expanded Gaseous Flow at a Straight Micro-Tube Exit

2014 ◽  
Vol 136 (8) ◽  
Author(s):  
Takahiro Yoshimaru ◽  
Yutaka Asako ◽  
Toru Yamada
Keyword(s):  
Total Pressure ◽  
Gas Flow ◽  
Numerical Results ◽  
Pitot Tube ◽  
Outer Diameter ◽  
Flow Rates ◽  
Gaseous Flow ◽  
Mass Flow Rates ◽  
Tube Exit ◽  
Slight Discrepancy

This paper focuses on under-expanded gaseous flow at a straight micro-tube exit. The pitot total pressure of gas flow (jet) in the downstream region from a straight micro-tube exit was measured by a total pressure pitot tube to accumulate data for validation of numerical results. A micro-tube of 495μm in diameter and 56.3 mm in length and a total pressure pitot tube of 100 μm in outer diameter were used. The pitot total pressure was measured at intervals of 0.1 mm in both the flow and radial directions. The measurement was done for the mass flow rates of 9.71 × 10−5 kg/s and 1.46 × 10−4 kg/s. The data were accumulated for validation of the numerical results to reveal the characteristics of the under-expanded gas flow at the exit of a micro-tube. Comparisons were conducted for numerical results of corresponding cases and a slight discrepancy can be seen between numerical and experimentally measured pitot total pressures.

Under-Expanded Gas Flow at a Straight Mini-Tube Exit

2013 ◽  
Author(s):  
Takahiro Yoshimaru ◽  
Yutaka Asako ◽  
Toru Yamada
Keyword(s):  
Mass Flow ◽  
Total Pressure ◽  
Gas Flow ◽  
Pitot Tube ◽  
Outer Diameter ◽  
Flow Rates ◽  
Numerical Result ◽  
Mass Flow Rates ◽  
Tube Exit ◽  
Slight Discrepancy

This paper focuses on under-expanded gas flow at a straight mini-tube exit. Pitot total pressure of gas flow (jet) in downstream region from a straight mini-tube exit was measured to give data for validation of numerical results. A mini-tube of 495μm in diameter & 56.3 mm in length and a pitot tube of 100 μm in outer diameter were used. The pitot total pressure was measured every 0.1 mm interval in the flow and radial directions. The measurement was done for the mass flow rates of 9.71×10−5 kg/s and 1.46×10−4 kg/s. The data were accumulated for validation of the numerical result to reveal the characteristics of the under-expanded gas flow at the exit of a mini-tube. Comparisons were conducted for sample computations and a slight discrepancy can be seen between numerical and experimentally measured pitot total pressures.

Investigation of the Influence of Different Rim Seal Geometries in a Low-Pressure Turbine

2011 ◽  
Author(s):  
P. Schuler ◽  
K. Dullenkopf ◽  
H.-J. Bauer
Keyword(s):  
Mass Flow ◽  
Total Pressure ◽  
Gas Flow ◽  
Low Pressure ◽  
Flow Rates ◽  
Low Pressure Turbine ◽  
Hot Gas ◽  
Seal Design ◽  
Compound Design ◽  
Mass Flow Rates

The sealing of the machine’s inside against hot-gas ingestion is commonly provided by blowing relative cold compressor air radially out through the turbine wheelspace. Rim-seals located inside the wheelspace are primarily designed to keep the required amount of sealing at a minimum. A further possible function of the rim-seal follows from the desire to reduce the aerodynamic losses contributed by the interaction of the emerging sealing flow with the boundary layer of the incoming main flow. Investigations performend in the EU project MAGPI concentrate on the interaction between the sealing flow and the main gas flow and in particular on the effect of different rim seal designs regarding the loss-mechanism in a low-pressure turbine passage. Two different rim seal designs inside a linear low-pressure turbine cascade rig have been analysed in detail. Both, the simple axial gap and the more complex compound design were investigated under the influence of different sealing mass flow rates. Furthermore, a configuration without any cavity in the main gas flow served as a reference case. Extensive measurements of the total pressure loss over the turbine blade have been conducted by means of a five-hole probe. Additionally, the blade loading has been measured at several blade heights. A considerable increase of total pressure losses was observed due to the presence of a cavity with any rim seal design, even for no sealing flow. Higher sealing mass flow rates intensified this effect which becomes manifested in a strengthening of the secondary flows downstream the cascade. Experiments revealed also significant differences in loss-increment depending on the rim seal design used. Deeper insight into the interaction of the flows close to the rim seal is given by results of Laser-Doppler-Velocimetry measurements. The rounded shape of the compound design, which implies an axial overlapping, represents a promising prevention against hot-gas ingestion. While the axial gap design is characterized by higher losses, it also suffers considerable hot-gas ingestion in front of the blade leading edge. A parametric study regarding a possible optimization of the axial gap design is presented in this work.

scholarly journals Simulation and Modeling of Flow in a Gas Compressor

2015 ◽  
Vol 2015 ◽  
pp. 1-7
Author(s):  
Anna Avramenko ◽  
Alexey Frolov ◽  
Jari Hämäläinen
Keyword(s):  
Steady State ◽  
Mass Flow ◽  
Gas Flow ◽  
Simulation Method ◽  
High Mass ◽  
Ansys Fluent ◽  
Flow Rates ◽  
Mass Flow Rates ◽  
Low Mass ◽  
Flow Through

The presented research demonstrates the results of a series of numerical simulations of gas flow through a single-stage centrifugal compressor with a vaneless diffuser. Numerical results were validated with experiments consisting of eight regimes with different mass flow rates. The steady-state and unsteady simulations were done in ANSYS FLUENT 13.0 and NUMECA FINE/TURBO 8.9.1 for one-period geometry due to periodicity of the problem. First-order discretization is insufficient due to strong dissipation effects. Results obtained with second-order discretization agree with the experiments for the steady-state case in the region of high mass flow rates. In the area of low mass flow rates, nonstationary effects significantly influence the flow leading stationary model to poor prediction. Therefore, the unsteady simulations were performed in the region of low mass flow rates. Results of calculation were compared with experimental data. The numerical simulation method in this paper can be used to predict compressor performance.

Review of Critical Flowmeters for Gas Flow Measurements

1962 ◽  
Vol 84 (4) ◽  
pp. 447-457 ◽  
Author(s):  
B. T. Arnberg
Keyword(s):  
Mass Flow ◽  
Flow Measurement ◽  
Gas Flow ◽  
Flow Measurements ◽  
Flow Rates ◽  
Real Gas ◽  
Discharge Coefficients ◽  
Critical Nozzles ◽  
Mass Flow Rates ◽  
Flow Functions

Critical flowmeters for accurately measuring the mass flow rates of nonreacting real gases were reviewed. Discussions were presented on theoretical flow functions, on parameters for correlating discharge coefficients, and on the importance of real gas properties. The performance characteristics of critical nozzles and orifices of several designs were reviewed. Approaches were discussed to problems which must be researched before the fullest potential of this type of flow measurement can be realized.

scholarly journals Flow study in structure of the plasma torch for microwave plasma spray

2020 ◽  
Vol 4 (2) ◽  
pp. 56-60
Author(s):  
Muhammad Fahmi Izuwan Samion ◽  
Nur Ziana Norizat ◽  
Ahmad Redza Ahmad Mokhtar
Keyword(s):  
Reynolds Number ◽  
Laminar Flow ◽  
Plasma Spray ◽  
Plasma Torch ◽  
Gas Flow ◽  
Microwave Plasma ◽  
Microwave Oven ◽  
Outer Diameter ◽  
Flow Rates ◽  
Suitable Structure

Microwave oven induced plasma method is a novel application of microwave oven to generate plasma for coating process. It uses 2.45 GHz microwave power and only 0.8 kW input power to produce the plasma which capable of spraying all materials that are considered sprayable. However, the research regarding this microwave plasma spray are more to be discovered. Suitable structure of plasma torch is needed for microwave plasma spray that can produce laminar flow to produce desire plasma for coating application. Therefore, this paper will discuss about the suitable structure of plasma torch needed for laminar flow by Reynolds number calculation. Reynolds number calculated by applying the outlet diameter of antenna which is 2, 3 and 4 mm. From this research, Reynolds number from all outer diameter of antenna are below 2000 which indicate laminar flow. The widest plasma diameter achieved at 6.59 mm with 4 mm outlet diameter of antenna and 15 lpm working gas flow rate while the narrowest plasma diameter achieved at 1.26 mm with 3 mm outlet diameter of antenna and 10 lpm flow rates of working gas. The most acceptable condition for producing plasma plume was at 3 mm of antenna diameter with 25 lpm of Ar gas flow rates.

scholarly journals Inert Gas and Refrigerating Vapor Mass Flow Rates Ratio: A Much Promising Parameter for Diffusion-Absorption-Refrigeration Systems Performances Evaluation

2021 ◽  
Vol 8 (2) ◽  
pp. 253-258
Author(s):  
Djallel Zebbar ◽  
Souhila Zebbar ◽  
Sahraoui Kherris ◽  
Kouider Mostefa
Keyword(s):  
Mass Flow ◽  
Gas Flow ◽  
Inert Gas ◽  
Coefficient Of Performance ◽  
Working Fluid ◽  
Absorption Refrigeration ◽  
Flow Rates ◽  
Mass Flow Rates ◽  
Diffusion Absorption ◽  
Vapor Mass

This paper is consecrated to the thermodynamic study and analysis of diffusion-absorption-refrigeration (DAR) plants. The mass and energy balances analysis at the evaporator has allowed to highlight a new and original parameter, which can be used to analyze DAR system performances. It is the ratio of inert gas to refrigerant vapor mass flow rates at the evaporator inlets. This coefficient, which expression has been for the first time deduced mathematically, informs about the quality of the cycle and its performance, which are deeply affected by the growth of the inert gas flow energy expended to drive the refrigerant through the evaporator. The study shows that the coefficient of performance is decreasing with the increase of the mass flow rates ratio. The latter can be also used to find the optimal operating mode for the DAR machine with a specified working fluid.

Investigation of Effects of Radial Distortion on Transonic Fan Behavior

2010 ◽  
Author(s):  
Dmytro M. Voytovych ◽  
Guoping Xia ◽  
Chenzhou Lian ◽  
Charles L. Merkle
Keyword(s):  
Mass Flow Rate ◽  
Mass Flow ◽  
Flow Rate ◽  
Total Pressure ◽  
Pressure Ratio ◽  
Tip Vortex ◽  
Flow Rates ◽  
Mass Flow Rates ◽  
Transonic Fan ◽  
Total Pressure Ratio

The flow analysis around blades of a transonic fan is presented for both clean and radially distorted inlets. Computations are shown for four-blade passages that are accomplished with a second order accurate code using a k-ω turbulence model. The mass flow rate along a speed line is controlled by varying a choked nozzle downstream of the fan. The results show good agreement with data for three speed lines. In the near-stall region, the flow first becomes unsteady and then unstable with the unsteadiness increasing at lower speeds. The four-blade simulations remained stable to lower mass flow rates than the single-blade simulations. In the near-stall vicinity, tip vortex breakdown occurred creating a low momentum zone near the blade tip on the pressure side that grew as the mass flow was decreased until it eventually blocked the passage. The presence of distortion reduced the operational range and moved the stall line to higher mass flow rates. At high speeds distortion reduced both the mass flow rate and total pressure ratio while at lower speeds, the choking mass flow rate was reduced, but the total pressure ratio was slightly improved. The flow separation near the hub on the suction side was caused by the distortion. Its size was decreasing with rotational speed.

Experimental and Numerical Study on Hydraulic Performances of a Turbopump With and Without an Inducer

2018 ◽  
Author(s):  
Yanxia Fu ◽  
Meng Fan ◽  
Giovanni Pace ◽  
Dario Valentini ◽  
Angelo Pasini ◽  
...  
Keyword(s):  
Total Pressure ◽  
Pressure Rise ◽  
Hydraulic Performance ◽  
Numerical Results ◽  
Operating Conditions ◽  
Design Flow ◽  
Low Flow ◽  
Flow Rates ◽  
Lower Flow ◽  
Inlet Duct

The hydraulic performance of a centrifugal turbopump with and without a 3-bladed axial inducer has been studied both experimentally and numerically. A 3D numerical model has been used to simulate the flow through from the inlet to the outlet ducts of the turbopump with and without an inducer using the ANSYS CFX code. The sensitivity of the numerical results has been analyzed with reference to the adopted turbulent flow models, to the length of the input and output ducts included in the simulations, to the reference positions used for the evaluation of the total pressure rise and to the temperature of the operating fluid. The measured and predicted hydraulic performances of the turbopump with and without the inducer have been compared under different operating conditions. As expected, the predicted hydraulic performance of the turbopump is significantly influenced by the lengths of the inlet and outlet ducts, the turbulence models and, at low flow rates, the reference positions of the total pressure rise measurements. The pressure rise coefficients obtained from the simulations using an inlet duct with length of 3 rTi and 10 rTi were significantly lower than the experimental results, while at low flow rates those referring to the inlet duct with length greater than 10 rTi were significantly higher than those obtained for the shorter inlet duct. With reference to the effect of the pressure measurement locations, the difference between the numerical results of the pressure rise coefficient and the experimental values was much higher when the data were obtained at the locations where the transducers was mounted in the experimental tests at lower flow rates. Moreover, the hydraulic performance of the turbopump at lower flow rates can be significantly influenced by the use of the upstream inducer, with a pressure drop of 20% in particular at 60% of the design flow rate.

scholarly journals Simulation of Impeller Exit Flows of a Centrifugal Blower

2019 ◽  
Vol 8 (4) ◽  
pp. 10037-10042
Keyword(s):  
Energy Level ◽  
Total Pressure ◽  
Suction Side ◽  
Uniform Flow ◽  
Centrifugal Impeller ◽  
Pressure Side ◽  
Centrifugal Blower ◽  
Flow Rates ◽  
Mass Flow Rates ◽  
Flow Through

The flow through centrifugal impeller is highly non uniform due to formation of regions with different energy level. These region mixes at the exit of the impeller leading to loss and bringing down the efficiency of the centrifugal impeller. The present study focus on analyzing the flow through an impeller and investigating the impeller exit flows. The simulations are carried out for various mass flow rates at design and off design conditions. The velocity vectors observed depicts the regions of jet along the pressure side and wake at the suction side. The contours of total pressure and velocity depict the diffusion process that occurs within the impeller and its exit. Non uniform flow is observed along the circumferential direction of the impeller. These non uniform flow leads to secondary flow as well as loss in total pressure thereby reducing the efficiency of the centrifugal impeller.

Experiments of Liquid Loading and Intermittent Production Using a Lab-Scale Reservoir-Tubing Setup

2021 ◽  
Author(s):  
Jos van 't Westende ◽  
Dries van Nimwegen ◽  
Stefan Belfroid ◽  
Harmen Slot
Keyword(s):  
Total Pressure ◽  
Gas Flow ◽  
Experimental Setup ◽  
Reservoir Model ◽  
Liquid Loading ◽  
Flow Rates ◽  
Pressure Losses ◽  
Set Up ◽  
Start Ups ◽  
Production Tubing

Abstract Experiments were performed to investigate the physics behind intermittent production and liquid loading, using a setup containing a reservoir model coupled to a vertical production tubing. In the experiments both gas and liquid are injected into the reservoir, which is a container in which sand with two different permeabilities is placed. Quick closing valves are incorporated into the experimental setup in order to simulate well shut-ins and start-ups. The experimental results show that the addition of the reservoir to the experimental set-up shifts the minimum in the total pressure losses over the system to lower gas flow rates as the permeability of the reservoir decreases. When performing shut-ins where a significant liquid column is present in the tubing, as is the case in liquid loaded wells, performing a sufficiently long shut-in can lead to the deliquification of the system.

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