Mechanical Engineering Journal
|
|
- Harry Woods
- 5 years ago
- Views:
Transcription
1 Bulletin of the JSME Mechanical Engineering Journal Vol.3, No.6, 2016 Experimental study on the behavior of the two phase flow shock waves occurring in the ejector refrigeration cycle Haruyuki NISHIJIMA*, Kyohei TSUCHII* and Masafumi NAKAGAWA* * Toyohashi University of Technology 1-1 Hibarigaoka, Tempaku-cho, Toyohashi, Aichi, , Japan nishijima@nak.me.tut.ac.jp Received 20 April 2016 Abstract Conservation of energy is becoming increasingly important for the protection of the environment. Improving the efficiency of a refrigeration cycle is a critical factor to achieve this goal. Recently, an ejector system was developed that reduces the energy requirements of the compressor in the refrigeration cycle. Two-phase-flow shock waves appear in the ejector under certain operating conditions and increase the pressure difference between suction inlet and outlet. Such shock waves play an important role in the ejector s compression mechanism and thus merit a thorough investigation. In this work, we visualize the structure of a two-phase-flow shock wave in an ejector nozzle using a high-speed camera to monitor an optical beam transmitted through a refrigerant (hot water). As the pressure rises in the ejector outlet, the shock wave moves from the outlet to the nozzle throat and changes from an oblique shock wave to a normal shock wave. The shape of the output nozzle may modify the structure of the shock waves. Key words : Multiphase flow, Supersonic flow, Shock waves, Visualization, Ejector 1 Introduction As the problem of global warming becomes increasingly severe, energy conservation has become a global challenge. Improving the efficiency of a refrigeration cycle is a critical factor to achieve this goal. Thus, the compressor used in refrigeration and air-conditioning equipment must be optimized to maximize the efficiency of the refrigeration cycle. Recently, the use of a two-phase flow ejector to obtain a highly efficient refrigeration cycle has drawn increasing attention. A conventional vapor-compression refrigeration cycle loses energy during decompression expansion in the expansion valve, as shown in Fig. 1. This loss is due to kinetic-energy consumption by swirl flow in the expansion valve. Figure 2 summarizes the ejector refrigeration cycle, wherein the expansion energy drives the ejector. Recovering this expansion energy increases the compressor suction pressure. Accordingly, the ejector cycle can reduce compressor energy consumption by recovering the expansion energy lost in the conventional vapor-compression refrigeration cycle (Takeuchi et al., 2004). Although the ejector refrigeration cycle based on the two-phase flow ejector has been commercialized by Takeuchi et al. (2003), further improvements in the ejector efficiency are needed to meet the current demands for energy conservation. The two-phase flow ejector comprises a nozzle, a suction nozzle, a mixing section, and a diffuser, as shown in Fig. 3. The refrigerant accelerates to supersonic speeds in the nozzle and slows down to subsonic speeds in the mixing section and diffuser. As the speed of sound in two-phase flow is lower than that in gas, a two-phase-flow shock wave easily forms in the nozzle and mixing section. Such shock waves increase the pressure difference between the suction inlet and the ejector outlet and play an important role in the ejector s compression mechanism. Thus, the characteristics of these shock waves merit investigation. In previous work, we found that pseudo shock waves (dispersive shock waves) occur when the refrigerant has a large (small) density ratio for the vapor of the liquid and explained these shock waves based on a theory involving momentum relaxation (Nakagawa and Harada, 2010, Harada and Nakagawa 2011). In addition, by monitoring an optical beam Paper No J-STAGE Advance Publication date: 9 December,
2 reflected in the nozzle-outlet expansion chamber, we found that an oblique shock wave forms when there is no upward pressure (Nakagawa et al., 2005). Furthermore, the position of the shock wave in the nozzle depends on the outlet pressure of the nozzle and the nozzle-inlet quality. However, the structure of the two-phase-flow shock wave that occurs in the ejector remains to be confirmed (Yamanaka and Nakagawa, 2012). The structure of these shock waves defines the complex flow in and the performance of the two-phase flow ejector. In general, the energy lost by the shock wave depends on its structure: the energy lost by a normal shock wave is greater than that lost by an oblique shock wave. Therefore, to maximize ejector efficiency, we must understand the structure of two-phase-flow shock waves in the ejector. Experimental visualization of flow is an important method to study shock wave structure in a two-phase flow ejector. Fabri and Siestrunk (1958) used Schlieren methods to visualize the different flow patterns in a supersonic air ejector. Matsuo et al. (1981) also used such methods to analyze the performance of a supersonic air ejector. Dvorak and Safarik (2005) used the Schlieren technique to study the transonic instability in the mixing-section inlet of a high-speed ejector. Bouhanguel et al. (2011) used the laser-sheet flow-imaging technique to investigate flow in the ejector. Most of these visualization techniques are intended for supersonic, high-speed air or vapor flow. A current study (unpublished) clarifies the structure of the shock wave in a two-phase flow ejector that occurs when a vapor and fine droplets flow through the ejector at supersonic speed. The present study expands on the knowledge gained from our previous studies (Yamanaka and Nakagawa, 2012). We use hot water as refrigerant and, to confirm the shock-wave structure, visualize two-phase-flow shock waves in the ejector nozzle by monitoring a transmitted optical beam. Fig.1 (a) A conventional vapor-compression refrigeration cycle consists of compressor, condenser, expansion valve, and evaporator. (b) A P-h diagram of a conventional refrigeration cycle. The red dot-dashed line is the isentropic curve. A conventional refrigeration cycle loses kinetic energy because of swirl flow during decompression expansion in the expansion valve. Fig.2 (a) Schematic illustration of ejector refrigeration cycle. (b) P-h diagram of ejector refrigeration cycle. In this cycle, the expansion energy drives the ejector. Recovering this expansion energy via the pressure rise in the ejector therefore leads to an increase in compressor-suction pressure. Accordingly, the ejector cycle requires less compressor energy by recovering the expansion energy lost in the conventional vapor-compression refrigeration cycle. 2
3 Fig.3 The two-phase flow ejector is composed of a nozzle, a suction nozzle, a mixing section, and a diffuser. The refrigerant flowing through the ejector is accelerated to supersonic, which is more than the two-phase sound speed in the nozzle and slows down to subsonic in the mixing section and the diffuser. Therefore, the twophase shock wave forms easily in the nozzle and the mixing section. 2 Experimental study step The experiment involved three main steps shown in Fig.4.: In the first step, the flow in the ejector has to increase to supersonic speeds to create a two-phase-flow shock wave. By measuring the flow rate through the ejector nozzle under various conditions, we determine the critical conditions required to reach supersonic flow in the nozzle. In step 2, under the critical conditions, we vary the nozzle-inlet and ejector-outlet pressure and measure a pressure distribution in the ejector. Finally, in step 3, the flow is visualized by imaging a transmitted optical beam, which allows us to study the structure of the two-phase-flow shock wave in the ejector nozzle. Fig.4 Experimental study step. 3 Experiment setup 3.1 The summary of the experiment setup Figure 5 shows the experiment setup, which consists of a high-pressure tank, heater, mixer, two-phase flow ejector, condenser, flow meter, a metal halide light, and a high-speed camera. When the temperature inside the tank reaches the steady state at 152 C, saturated steam (liquid) flows out of the upper (lower) side of the tank. The steam mass-flow rate G G is measured with a differential-pressure flow meter, and the mass-flow rate G of the ejector outlet is measured by the Coriolis flow meter downstream from the condenser. The liquid mass-flow rate G L is the difference: G G G. The nozzleinlet quality X n of the ejector is given by X n = (h h G ) (h G h L ) (1) where h = (G G h G + G L h L ) (G G + G L ) (2) is the mean mass enthalpy at the ejector inlet and h L and h G are the enthalpy of liquid and steam, respectively. The 23
4 pressure and temperature in the liquid and gas lines are measured upstream of the mixer, and then X n is calculated by using REFPROP 8.0 (NIST, 2007). By using the two mass-flow adjustment valves to control the two flow rates (i.e., liquid and gas), we vary the nozzle-inlet quality X n of the ejector. The ejector backpressure P b is measured just outside the outlet tube of the ejector and is adjusted by the valve downstream of the condenser. 3.2 Experimental Ejector Fig. 5 Schematic diagram of experiment setup. In this study, we use a two-dimensional ejector (see Fig. 6) to facilitate visualization via a transmitted optical beam. The experimental ejector comprises an ejector plate, an upper plate, and a lower plate. To measure the pressure at the upper plate, three pressure taps are inserted into the convergent section of the nozzle, four taps are inserted into the divergent section of nozzle, three taps are inserted into the mixing section, and one tap is inserted into the diffuser on the side wall of the ejector. By using either polyetheretherketone or polycarbonate for the upper and lower plates, we can simultaneously measure the pressure in the ejector and visualize the flow through the ejector. The ejector plate is made of 2.0-mm-thick stainless steel. Table 1 gives the specification of the experimental ejector. The basic design of the ejector is given in Yamanaka (2013), and this same design (i.e., not optimized) is used for the present work. The divergent section of the nozzle is about 11 mm long. Fig.6 Schematic diagram of experimental ejector. 24
5 Table.1 Specifications of experimental ejector. 3.3 Visualization Method Our conventional study (Yamanaka and Nakagawa, 2012) used a digital camera to monitor an optical beam reflected within the experimental nozzle. In this study, however, we visualize the two-phase-flow shock wave by using a highspeed camera to monitor an optical beam (produced by a metal halide light) transmitted through the experimental ejector (see Fig. 7). Table 2 lists the specifications of the visualization devices used in this work. Fig.7 Schematic diagram showing visualization technique. Table.2 Visualization devices. Figure 8 shows how we interpret this visualization. First, we divide the visualization domain into two zones. The flow velocity decreases downstream of the shock wave, so the number density of the droplets should increase in this zone. As shown in Table 3, the refractive index of the saturated steam is almost unity, whereas that of the saturated water is slightly greater than 1.3. Thus, the transmitted light is refracted and reflected out of the transmitted beam by the droplet, 25
6 leading to less light irradiating the high-speed camera downstream of the shock wave compared with upstream. This allows us to visualize two-phase-flow shock waves by monitoring the transmitted beam. Fig.8 Interpretation of image formed by transmitted optical beam. Table.3 Refractive index of refrigerant. 3.4 Experimental condition Table 4 lists the experimental conditions for this study. The nozzle-inlet temperature is 150 C, which allows twophase flow in the nozzle to accelerate to supersonic speeds for all experimental outlet conditions. In addition, the suction flow rate G s at the ejector is zero to allow us to focus on the shock wave in the nozzle. Under these conditions, the pressure and the enthalpy in the ejector follow the diagram shown in Fig. 9. Because no suction flow occurs, the pressure and enthalpy of the flow at the ejector outlet undergo simple changes: decreasing until the shock wave occurs and increasing afterwards. Figure 10 shows the results of calculations based on the homogeneous equilibrium model (HEM) (Japanese Institution of Mechanical Engineers, 2006), which show the characteristics of flow in the nozzle under these experimental conditions. Initially, the equilibrium speed of sound for the two-phase flow decreases gently with decreasing inlet pressure because the void fraction increases according to the decompression in the nozzle. For a nozzle-inlet quality of 0.3, which corresponds to supersonic flow at about 0.28 MPa, the quality increases gently as the nozzle-inlet pressure drops, and the void fraction increases to ~ The critical pressure required to reach the speed of sound decreases upon increasing the nozzle-inlet quality from 0.3 to 0.6. Thus, because of decompression in the nozzle inlet, the quality 26
7 decreases gently. Based on these calculations, we conclude that a two-phase-flow shock wave with these phase conversion can be triggered in our experiment by varying the nozzle-inlet quality. Table.4 Experimental conditions. Fig.9 Pressure and specific enthalpy under given experimental conditions. Fig.10 Characteristics of nozzle flow under given experimental conditions, as calculated by the HEM. 27
8 4 Results of Experiment 4.1 Flow-Rate Results In two-phase flow, the speed of sound is not easy to estimate because of irreversible processes caused by interphase heat-, mass-, and momentum-transfer phenomena. Because the critical condition cannot be determined based on the speed of sound, we measure the two-phase-flow rates upon varying outlet pressure. This approach clarifies when real choking occurs in the nozzle. To visualize the shock wave, the nozzle flow must be supersonic, so determining when the nozzle flow becomes supersonic is important. Figure 11 shows the nozzle flow rate as measured by the Coriolis mass-flow meter (left side, Fig. 5). Under the critical conditions, the flow rate of the two-phase supersonic nozzle is relatively constant with respect to the upward pressure of the ejector outlet. Therefore, the range indicated by the double dotted line in Fig. 11 gives the range of ejector back pressures corresponding to critical flow in the nozzle. To measure the static pressure and visualize the flow, we set the range of the ejector-outlet pressure to 0.12~0.26 MPa in this experiment. Fig.11 Measured flow rate as a function of ejector back pressure. 4.2 Pressure results Figure 12 shows the static pressure measured at the ejector wall surface under the conditions discussed above as a function of distance from nozzle throat and for the nozzle-inlet qualities X n = 0.3 and 0.6. The solid squares, triangles, and diamonds give the experimental results for P b = 0.26, 0.19, and 0.12 MPa, respectively, These dashed curves are adiabatic expansion curves calculated by the HEM. For both experiment and calculations, the red and blue colors give the results for X n = 0.3 and 0.6, respectively. To calculate the refrigerant properties, we use REFPROT 8.0 (NIST, 2008). As shown in Fig. 12, the slope of the experimental pressure vs distance from the throat of the ejector is less than that of the theoretical curves, which we attribute to the large interphase irreversible process of two-phase flow. The fact that two-phase flow occurs under supercritical conditions is mentioned in section 4.1, and is also confirmed by the decrease in pressure in the divergent section of Fig. 12 (i.e., 0 to mm from ejector throat). Furthermore, the increase in ejector-outlet pressure leads to a shock wave peculiar to the two-phase flow in which pressure increases gently 28
9 in the nozzle at P b = 0.19 and 0.26 MPa, as shown in Fig. 12. The pressure in the nozzle decreases toward the nozzle outlet for P b =0.12 MPa, so we conclude that no shock wave forms in the nozzle under these conditions. Next, we compare the pressure distribution for different values of nozzle-inlet quality (X n = 0.3 and 0.6). Upon increasing the nozzle-inlet quality, the velocity in the nozzle increases. Therefore, the magnitude of decompression in the nozzle is increased by increasing the nozzle-inlet quality. Furthermore, for P b = 0.19 MPa, a clear pressure increase occurs in the nozzle upon increasing the nozzle-inlet quality from 0.3 to 0.6. Therefore, under these experimental conditions, a nozzle-inlet quality X n = 0.6 allows the structure of the shock wave in the nozzle to be easily observed, so it can be monitored as the outlet pressure is varied. In addition, for an outlet pressure P b = 0.19 MPa, the position of the shock wave depends on the nozzle-inlet quality. Fig.12 Static pressure at ejector wall surface as a function of distance from ejector throat. 4.3 Visualization Results Shock wave structure visualized and compared with pressure measurements With the confirmation that the shock wave occurs in the nozzle under the conditions given above, we visualized the shock wave by using the method described above. Figure 13 compares the visualization and the measured pressure for a nozzle-inlet quality X n = 0.6. These images were acquired at frames per second (fps), with a shutter speed of 1/ s, and a resolution of The top and bottom parts of the images are deleted, leaving the nozzle displayed lengthwise. Because less light irradiates the photodetector downstream of the shock wave, as discussed above, a monochromatic high-speed camera allows us to image the shock wave. The gentle pressure increase peculiar to the two-phase-flow shock wave downstream of the black shadow allows us to confirm the visualization of the two-phase-flow shock wave. For comparison, the results of our conventional visualization method (Yamanaka and Nakagawa, 2012) for P b = 0.26 MPa are shown in the lower image of Fig. 13, which further supports the interpretation of the visualization of the two-phase-flow shock wave by the method proposed herein 29
10 and highlights the resolution of the proposed technique. A rise in the outlet pressure is known to cause the shock wave to move from the outlet toward the throat of the nozzle (Yamanaka and Nakagawa, 2012). Furthermore, Fig. 13 shows that an increase in outlet pressure causes the shockwave to change from an oblique shock wave to a normal shock wave. Although a normal shock wave appears in Fig. 13, no sudden pressure increase appears across the normal shock wave. This phenomenon is attributed to a weak normal shock wave occurring first in the gas phase and continuing, with the deceleration of the liquid phase (with its larger inertia) contributing to a gradual increase in pressure. Fig.13 Images of shock wave acquired by proposed visualization method (top three images) and by conventional method (bottom image). Bottom panel allows the images to be compared with the pressure measured with a nozzle-inlet quality of Xn =
11 4.3.2 Dependence of shock wave on nozzle-inlet quality Next, we image the shock wave for several values of nozzle-inlet quality. Figure 14 shows images for an ejector outlet pressure of P b = 0.19 MPa. These images were acquired at fps, a shutter speed of 1/ s, and a resolution of With a decrease in nozzle-inlet quality X n from 0.6 to 0.3, the oblique shock wave moves toward the nozzle outlet, where it causes the velocity in the nozzle to decrease, before disappearing when the quality falls below Fig.14 Images of shock wave for several values of nozzle-inlet quality (Pb = 0.19 MPa) Structural change of the shock waves in two-phase flow ejector. For all conditions tested, a shock wave occurring in the nozzle-outlet region is an oblique shock wave, whereas a shock wave occurring in the nozzle throat region is a normal shock wave. This structural change in the shock wave might be due to the shape of the nozzle outlet. A shock wave occurring in axial flow becomes a normal shock wave, whereas a shock wave occurring where flow has a transverse component (e.g., through a mixing section), such as in the nozzle outlet, becomes an oblique shock wave, as shown in Fig
12 Fig.15 Possible explanations for structural change of shock waves in two-phase flow ejector. 5. Summary and Conclusion In this study, we use a transmitted optical beam and a high speed camera to visualize the structure of two-phase-flow shock waves in an ejector nozzle. The results lead to the following conclusions: i. A rise in ejector-outlet pressure shifts the shock wave from the outlet toward the throat of the nozzle and causes an oblique shock wave to become a normal shock wave. ii. This oblique shock wave moves toward the nozzle outlet and its speed in the nozzle decreases with a drop in nozzle-inlet quality, until it finally disappears from the nozzle. iii. The shape of the output nozzle may modify the structure of the shock waves. Further visualization experiments covering a large set of conditions should clarify the mechanisms behind this structural change. References Bouhanguel, A., Desevaux, P. and Gavignet, E., Flow visualization in supersonic ejectors using laser tomography techniques (2011), International Journal of Refrigeration, Vol.34, No.7, pp Dvorak, V., Safarik, P., Transonic instability in entrance part of mixing chamber of high-speed ejector (2005), Journal of Thermal Science, Vol.14, pp Fabri, J., Siestrunck, R., Supersonic Air Ejectors (1958), Advances in Applied Mechanics, Vol. 5, Academic Press, New York, pp Harada, A., Nakagawa, M., Shock and Expansion Waves in Supersonic Two Phase Jet Flow (2011), JSME Tokai Branch 60th annual meeting, No (in Japanese). Matsuo, K., Sasaguchi, K., Tasaki, K., and Mochizuki, H., Investigation of Supersonic Air Ejector (Part1.Performance in the Case of Zero-Secondary Flow) (1981), Bulletin of JSME, Vol.24, No.198, pp (in Japanese). Nakagawa, M., Hakamada, O., Miyazaki, H., Rarefaction waves and shock waves at the outlet of the supersonic twophase flow nozzle (2005), JSME Tokai Branch 54th annual meeting, No (in Japanese). Nakagawa, M., Harada, A., Two-phase Ejector for refrigeration cycle and shock wave appearing in the supersonic twophase flow nozzle (2010), Maltiphase Flow, Vol.24, No.1, pp (in Japanese). NIST Standard Reference Data Program, REFPROP v8.0, Reference fluid thermodynamic and transport properties (2007). 12 2
13 Takeuchi, H., Nishijima, H., and Ikemoto, T., World's First High Efficiency Refrigeration Cycle with Two-Phase Ejector: EJECTOR CYCLE (2004), SAE Technical Paper The Japanese Society of Mechanical Engineers ed., Handbook of Gas-Liquid Two Phase Flow Technology Second Edition (2006), pp (in Japanese). Yamanaka, H., Nakagawa, O., Supersonic Nozzle Flow in the Two-Phase Ejector as Water Refrigeration System by Using Waste Heat (2012), 9th International Conference on Heat Transfer, Fluid Mechanics and Thermodynamics, pp Yamanaka, H., Nakagawa, M., Two-phase Flow Ejector as Water Refrigerant by Using Waste Heat (2013), Journal of Physics, Conference Series Vol.433, DOI: / /433/1/
Supersonic Nozzle Flow in the Two-Phase Ejector as Water Refrigeration System by Using Waste Heat
HEFAT2012 9 th International Conference on Heat Transfer, Fluid Mechanics and Thermodynamics 16 18 July 2012 Malta Supersonic Nozzle Flow in the Two-Phase Ejector as Water Refrigeration System by Using
More informationCHARACTERISTICS OF PRESSURE RECOVERY IN TWO-PHASE EJECTOR APPLIED TO CARBON DIOXIDE HEAT PUMP CYCLE
- 1 - CHARACTERISTICS OF PRESSURE RECOVERY IN TWO-PHASE EJECTOR APPLIED TO CARBON DIOXIDE HEAT PUMP CYCLE Satoshi Akagi, Chaobin Dang and Eiji Hihara* Division of Environmental Studies, Graduate School
More informationA STUDY ON FLOW BEHAVIOR INSIDE A SIMPLE MODEL OF EJECTOR
A STUDY ON FLOW BEHAVIOR INSIDE A SIMPLE MODEL OF EJECTOR Taketoshi Koita 1 and Junjiro Iwamoto ABSTRACT This paper is concerned with the experimental results on the internal flow of the ejector. To improve
More informationEnhancement of CO2 Refrigeration Cycle Using an Ejector: 1D Analysis
Purdue University Purdue e-pubs International Refrigeration and Air Conditioning Conference School of Mechanical Engineering 2006 Enhancement of CO2 Refrigeration Cycle Using an Ejector: 1D Analysis Elias
More informationHigh-Efficiency Joule-Thomson Cryocoolers Incorporating an Ejector
1 High-Efficiency Joule-Thomson Cryocoolers Incorporating an Ejector H.S. Cao 1, S. Vanapalli 1, H.J. Holland 1, C.H. Vermeer 2, T. Tirolien 3, H.J.M. ter Brake 1 1 University of Twente, 7500 AE, Enschede,
More informationCFD analysis of flow phenomena inside thermo vapor compressor influenced by operating conditions and converging duct angles
Journal of Mechanical Science and Technology 23 (2009) 2366~2375 Journal of Mechanical Science and Technology www.springerlink.com/content/1738-494x DOI 10.1007/s12206-009-0626-7 CFD analysis of flow phenomena
More informationFrance Marie M. Orden and Menandro S. Berana. Proceedings of the World Congress on Engineering 2017 Vol II WCE 2017, July 5-7, 2017, London, U.K.
, July 5-7, 2017, London, U.K. Design and Analysis of Incorporating Two Ejectors for Compression Recovery in the Inlet and Outlet Points of the Compressor in a Vapor Compression System France Marie M.
More informationAREN 2110: Thermodynamics Spring 2010 Homework 7: Due Friday, March 12, 6 PM
AREN 2110: Thermodynamics Spring 2010 Homework 7: Due Friday, March 12, 6 PM 1. Answer the following by circling the BEST answer. 1) The boundary work associated with a constant volume process is always
More informationThermodynamics: An Engineering Approach, 6 th Edition Yunus A. Cengel, Michael A. Boles McGraw-Hill, 2008
Thermodynamics: An Engineering Approach, 6 th Edition Yunus A. Cengel, Michael A. Boles McGraw-Hill, 2008 Chapter 5 MASS AND ENERGY ANALYSIS OF CONTROL VOLUMES SUMMARY 1 CONSERVATION OF MASS Conservation
More informationThree-dimensional Numerical Investigations on Ejector of Vapour Jet Refrigeration System
Purdue University Purdue e-pubs International Refrigeration and Air Conditioning Conference School of Mechanical Engineering 2014 Three-dimensional Numerical Investigations on Ejector of Vapour Jet Refrigeration
More informationStefan Elbel Pega Hrnjak University of Illinois at Urbana-Champaign
Experimental Validation of a CO 2 Prototype Ejector with Integrated High-Side Pressure Control Stefan Elbel (elbel@uiuc.edu), Pega Hrnjak (pega@uiuc.edu) University of Illinois at Urbana-Champaign Saalfelden,
More informationDesign of a Solar-Driven Ejector Cooling System
Design of a Solar-Driven Ejector Cooling System S. du Clou and M.J. Brooks University of KwaZulu-Natal, Durban, 44, South Africa Centre for Renewable and Sustainable Energy Studies Abstract The Pulse Refrigeration
More informationCHAPTER 5 MASS AND ENERGY ANALYSIS OF CONTROL VOLUMES
Thermodynamics: An Engineering Approach 8th Edition in SI Units Yunus A. Ç engel, Michael A. Boles McGraw-Hill, 2015 CHAPTER 5 MASS AND ENERGY ANALYSIS OF CONTROL VOLUMES Objectives Develop the conservation
More informationChapter 5 MASS AND ENERGY ANALYSIS OF CONTROL VOLUMES
Thermodynamics: An Engineering Approach Seventh Edition in SI Units Yunus A. Cengel, Michael A. Boles McGraw-Hill, 2011 Chapter 5 MASS AND ENERGY ANALYSIS OF CONTROL VOLUMES Copyright The McGraw-Hill Companies,
More informationChapter 5 MASS AND ENERGY ANALYSIS OF CONTROL VOLUMES
Thermodynamics: An Engineering Approach Seventh Edition Yunus A. Cengel, Michael A. Boles McGraw-Hill, 2011 Chapter 5 MASS AND ENERGY ANALYSIS OF CONTROL VOLUMES Copyright The McGraw-Hill Companies, Inc.
More informationChapters 5, 6, and 7. Use T 0 = 20 C and p 0 = 100 kpa and constant specific heats unless otherwise noted. Note also that 1 bar = 100 kpa.
Chapters 5, 6, and 7 Use T 0 = 20 C and p 0 = 100 kpa and constant specific heats unless otherwise noted. Note also that 1 bar = 100 kpa. 5-1. Steam enters a steady-flow device at 16 MPa and 560 C with
More informationChapter 5 MASS AND ENERGY ANALYSIS OF CONTROL VOLUMES
Thermodynamics: An Engineering Approach Seventh Edition in SI Units Yunus A. Cengel, Michael A. Boles McGraw-Hill, 2011 Chapter 5 MASS AND ENERGY ANALYSIS OF CONTROL VOLUMES Mehmet Kanoglu University of
More informationCOEFFICIENT OF PERFORMANCE OF TWO PHASE CONDENSING EJECTOR REFRIGERATION SYSTEM WITH R-22
INTERNATIONAL JOURNAL OF RESEARCH IN COMPUTER APPLICATIONS AND ROBOTICS ISSN 2320-7345 COEFFICIENT OF PERFORMANCE OF TWO PHASE CONDENSING EJECTOR REFRIGERATION SYSTEM WITH R-22 Kuldip Kumar 1, Anjani Kumar
More informationA Review on Performance of Air Conditioning System using Two Phase Ejector
International Journal of Current Engineering and Technology E-ISSN 2277 4106, P-ISSN 2347 5161 2016 INPRESSCO, All Rights Reserved Available at http://inpressco.com/category/ijcet Research Article A Review
More informationNUMERICAL INVESTIGATION OF AN R744 LIQUID EJECTOR FOR SUPERMARKET REFRIGERATION SYSTEMS
THERMAL SCIENCE: Year 2016, Vol. 20, No. 4, pp. 1259-1269 1259 NUMERICAL INVESTIGATION OF AN R744 LIQUID EJECTOR FOR SUPERMARKET REFRIGERATION SYSTEMS by Michal HAIDA a, Jacek SMOLKA a*, Michal PALACZ
More informationRevue des Energies Renouvelables Spécial ICT3-MENA Bou Ismail (2015) Numerical study of a single effect ejector-absorption cooling system
Revue des Energies Renouvelables Spécial ICT3-MENA Bou Ismail (2015) 71-77 Numerical study of a single effect ejector-absorption cooling system D. Sioud 1*, M. Bourouis 2 et A. Bellagi 1 1 Unité de Recherche
More informationEjectors in a Compressible Network for Gas Turbine Extended Operability
Ejectors in a Compressible Network for Gas Turbine Extended Operability Stefano Rossin, Debora Sassetti GE Oil & Gas, Via Felice Matteucci 2, Florence, Italy Email: stefano.rossin@ge.com; debora.sassetti@ge.com
More informationsemester + ME6404 THERMAL ENGINEERING UNIT III NOZZLES, TURBINES & STEAM POWER CYCLES UNIT-III
ME6404 THERMAL ENGINEERING UNIT III NOZZLES, TURBINES & STEAM POWER CYCLES UNIT-III 3. 1 CONTENTS 3.1 Flow of steam through nozzles: 3.2 Continuity and steady flow energy equations 3.3 Types of Nozzles
More informationENERGY AND EXERGY ANALYSIS OF HEAT PUMP USING R744/R32 REFRIGERANT MIXTURE
THERMAL SCIENCE, Year 2014, Vol. 18, No. 5, pp. 1649-1654 1649 ENERGY AND EXERGY ANALYSIS OF HEAT PUMP USING R744/R32 REFRIGERANT MIXTURE by Fang WANG, Xiao-Wei FAN, Jie CHEN, and Zhi-Wei LIAN School of
More informationNumerical Investigation of the Flow Dynamics of a Supersonic Fluid Ejector
Proceedings of the International Conference on Heat Transfer and Fluid Flow Prague, Czech Republic, August 11-12, 2014 Paper No. 171 Numerical Investigation of the Flow Dynamics of a Supersonic Fluid Ejector
More informationEffect of Generator, Condenser and Evaporator Temperature on the Performance of Ejector Refrigeration System (ERS)
Journal of Basic and Applied Engineering Research pp. 4-9 Krishi Sanskriti Publications http://www.krishisanskriti.org/jbaer.html Effect of Generator, Condenser and Evaporator Temperature on the Performance
More informationFLOW PATTERN IN CO 2 -LUBURICANT TWO-PHASE FLOW AT SUPERCRITICAL PRESSURE
ISTP-16, 2005, PRAGUE 16 TH INTERNATIONAL SYMPOSIUM ON TRANSPORT PHENOMENA FLOW PATTERN IN CO 2 -LUBURICANT TWO-PHASE FLOW AT SUPERCRITICAL PRESSURE Koji Mori and Kunihiro Shimoki Osaka Electro-Communication
More informationR13. II B. Tech I Semester Regular/Supplementary Examinations, Oct/Nov THERMODYNAMICS (Com. to ME, AE, AME) Time: 3 hours Max.
SET - 1 1. a) Discuss about PMM I and PMM II b) Explain about Quasi static process. c) Show that the COP of a heat pump is greater than the COP of a refrigerator by unity. d) What is steam quality? What
More informationA Validated Numerical Experimental Design Methodology for a Movable Supersonic Ejector Compressor for Waste Heat Recovery
A Validated Numerical Experimental Design Methodology for a Movable Supersonic Ejector Compressor for Waste Heat Recovery Sajad Alimohammadi 1*, Tim Persoons 1, Darina B. Murray 1, Mohamadreza S. Tehrani
More informationEjector Expansion Refrigeration Systems
Research Inventy: International Journal Of Engineering And Science Vol.5, Issue 2 (February 2015), PP 25-29 Issn (e): 2278-4721, Issn (p):2319-6483, www.researchinventy.com Ejector Expansion Refrigeration
More informationCopyright 2012 Neal D. Lawrence
Copyright 2012 Neal D. Lawrence ANALYTICAL AND EXPERIMENTAL INVESTIGATION OF TWO-PHASE EJECTOR CYCLES USING LOW-PRESSURE REFRIGERANTS BY NEAL D. LAWRENCE THESIS Submitted in partial fulfillment of the
More informationEnergy and Buildings
Energy and Buildings 41 (009) 175 181 Contents lists available at ScienceDirect Energy and Buildings journal homepage: www.elsevier.com/locate/enbuild Modeling solar-driven ejector refrigeration system
More information- 2 - SME Q1. (a) Briefly explain how the following methods used in a gas-turbine power plant increase the thermal efficiency:
- 2 - Q1. (a) Briefly explain how the following methods used in a gas-turbine power plant increase the thermal efficiency: i) regenerator ii) intercooling between compressors (6 marks) (b) Air enters a
More informationCERTIFICATES OF COMPETENCY IN THE MERCHANT NAVY MARINE ENGINEER OFFICER
CERTIFICATES OF COMPETENCY IN THE MERCHANT NAVY MARINE ENGINEER OFFICER EXAMINATIONS ADMINISTERED BY THE SCOTTISH QUALIFICATIONS AUTHORITY ON BEHALF OF THE MARITIME AND COASTGUARD AGENCY STCW 95 CHIEF
More informationChapter 8. Vapor Power Systems
Chapter 8 Vapor Power Systems Introducing Power Generation To meet our national power needs there are challenges related to Declining economically recoverable supplies of nonrenewable energy resources.
More informationDevelopment of Terry Turbine Analytical Models for RCIC Off-Design Operation Conditions
Development of Terry Turbine Analytical Models for RCIC Off-Design Operation Conditions Hongbin Zhang Idaho National Laboratory Power Plant Simulation Conference 2019 January 20 23, 2019 Outline Background
More informationME ENGINEERING THERMODYNAMICS UNIT III QUESTION BANK SVCET
1. A vessel of volume 0.04m 3 contains a mixture of saturated water and steam at a temperature of 250 0 C. The mass of the liquid present is 9 kg. Find the pressure, mass, specific volume, enthalpy, entropy
More informationInvestigations Of Low Pressure Two-Phase Steam- Water Injector
Purdue University Purdue e-pubs International Refrigeration and Air Conditioning Conference School of Mechanical Engineering 206 Investigations Of Low Pressure Two-Phase Steam- Water Injector Roman Kwidzinski
More informationEnergy and Exergy Analysis of Combined Ejector-Absorption Refrigeration System
Energy and Exergy Analysis of Combined Ejector- Seyed Reza Fakheri 1, Hadi Kargar Sharif Abad 2, Hossein Sakhaii Nia 3 1 M.A Student, Azad University of Science and Research of Semnan, Mechanics College,
More informationAlpha College of Engineering
Alpha College of Engineering Department of Mechanical Engineering TURBO MACHINE (10ME56) QUESTION BANK PART-A UNIT-1 1. Define a turbomahcine. Write a schematic diagram showing principal parts of a turbo
More informationR13 SET - 1 '' ''' '' ' '''' Code No: RT31035
R13 SET - 1 III B. Tech I Semester Regular/Supplementary Examinations, October/November - 2016 THERMAL ENGINEERING II (Mechanical Engineering) Time: 3 hours Max. Marks: 70 Note: 1. Question Paper consists
More informationPERFORMANCE EVALUATION OF HEAT PUMP SYSTEM USING R744/R161 MIXTURE REFRIGERANT
THERMAL SCIENCE, Year 2014, Vol. 18, No. 5, pp. 1673-1677 1673 PERFORMANCE EVALUATION OF HEAT PUMP SYSTEM USING R744/R161 MIXTURE REFRIGERANT by Xian-Ping ZHANG a,b, Xin-Li WEI b, Xiao-Wei FAN c*, Fu-Jun
More informationReview Questions for the FE Examination
110 THE FIRST LAW OF THERMODYNAMICS [CHAP. 4 4.1FE Review Questions for the FE Examination Select a correct statement of the first law if kinetic and potential energy changes are negligible. (A) Heat transfer
More informationIntroduction. Objective
Introduction In this experiment, you will use thin-film evaporator (TFE) to separate a mixture of water and ethylene glycol (EG). In a TFE a mixture of two fluids runs down a heated inner wall of a cylindrical
More informationR13. (12M) efficiency.
SET - 1 II B. Tech I Semester Regular/Supplementary Examinations, Oct/Nov - 2016 THERMAL AND HYDRO PRIME MOVERS (Electrical and Electronics Engineering) Time: 3 hours Max. Marks: 70 Note: 1. Question Paper
More informationANALYSIS OF REFRIGERATION CYCLE PERFORMANCE WITH AN EJECTOR
000 (06) DOI:.5/ matecconf/067000 ICMER 05 ANALYSIS OF REFRIGERATION CYCLE PERFORMANCE WITH AN EJECTOR Wani J. R., Aklilu T. Baheta,a, Abraham D. Woldeyohannes, and Suhaimi Hassan Department of Mechanical
More informationCFD on Small Flow Injection of Advanced Accumulator in APWR
54 CFD on Small Flow Injection of Advanced Accumulator in APWR TOMOSHIGE TAKATA TAKAFUMI OGINO TAKASHI ISHIBASHI TADASHI SHIRAISHI The advanced accumulator in the advanced pressurized-water reactor is
More informationDISPLACEMENT EFFICIENCY OF WATER IN A CYLINDRICAL TANK
DISPLACEMENT EFFICIENCY OF WATE IN A CYLINDICAL TANK Takahiro Kiwata, 1 Masayuki Saitoh, Shigeo Kimura, 3 Nobuyoshi Komatsu, Taira Kimura and Junko Suginuma ABSTACT The objective of the present study is
More informationCHAPTER 1 BASIC CONCEPTS
GTU Paper Analysis CHAPTER 1 BASIC CONCEPTS Sr. No. Questions Jan 15 Jun 15 Dec 15 May 16 Jan 17 Jun 17 Nov 17 May 18 Differentiate between the followings; 1) Intensive properties and extensive properties,
More informationCompound ejectors with improved off-design performance
Compound ejectors with improved off-design performance Dr M. Dennis 1, Dr K. Garzoli 2 1,2 Centre for Sustainable Energy Systems School of Engineering The Australian National University Canberra, ACT 0200
More informationLaboratory Testing of Safety Relief Valves
Laboratory Testing of Safety Relief Valves Thomas Kegel (tkegel@ceesi.com) and William Johansen (bjohansen@ceesi.com) Colorado Engineering Experiment Station, Inc. (CEESI) 5443 WCR 37, Nunn, Colorado 8648
More informationComponent Performance - Inlet, Burner and Nozzle
Component Performance - Inlet, Burner and Nozzle Introduction Changes in gas properties as it flows through the engine Sources of losses and figures of merit Efficiencies of the inlet, burner and exhaust
More informationSolar Cooling Using Variable Geometry Ejectors
Solar Cooling Using Variable Geometry Ejectors M. Dennis Centre for Sustainable Energy Systems Department of Engineering The Australian National University Canberra, ACT 2 AUSTRALIA E-mail:Mike.Dennis@anu.edu.au
More informationLatest Simulation Technologies for Improving Reliability of Electric Power Systems
Latest Simulation Technologies for Improving Reliability of Electric Power Systems 386 Latest Simulation Technologies for Improving Reliability of Electric Power Systems Kiyoshi Segawa Yasuo Takahashi
More informationRefrigeration Cycle With Two-Phase Condensing Ejector
Purdue University Purdue e-pubs International Refrigeration and Air Conditioning Conference School of Mechanical Engineering 2006 Refrigeration Cycle With Two-Phase Condensing Ejector Mark J. Bergander
More information3d Analysis on Supersonic Ejector
3d Analysis on Supersonic Ejector Arun K R 1, Abraham Antony 2, Eldhose Kurian 3, Frenosh K Francis 4 1,2,3, 4 Assistant Professor Department of Mechanical Engineering, Viswajyothi College of Engineering,
More informationEvaluating Performance of Steam Turbine using CFD
Evaluating Performance of Steam Turbine using CFD Sivakumar Pennaturu Department of Mechanical Engineering KL University, Vaddeswaram, Guntur,AP, India Dr P Issac prasad Department of Mechanical Engineering
More informationComputational Analysis Of Ejector With Oscillating Nozzle
Purdue University Purdue e-pubs International Refrigeration and Air Conditioning Conference School of Mechanical Engineering 2018 Computational Analysis Of Ejector With Oscillating Nozzle Arun Kodamkayath
More informationPerformance Benefits for Organic Rankine Cycles with Flooded Expansion
Purdue University Purdue e-pubs Publications of the Ray W. Herrick Laboratories School of Mechanical Engineering 6-2-2010 Performance Benefits for Organic Rankine Cycles with Flooded Expansion Brandon
More informationMECHANICAL ENGINEERING THERMAL AND FLUID SYSTEMS STUDY PROBLEMS
MECHANICAL ENGINEERING THERMAL AND FLUID SYSTEMS STUDY PROBLEMS PRINCIPLES: THERMODYNAMICS & ENERGY BALANCES 1 Copyright 2018. All rights reserved. How to use this book The exam specifications in effect
More informationPerformance Analysis for Natural Draught Cooling Tower & Chimney through Numerical Simulation
Performance Analysis for Natural Draught Cooling Tower & Chimney through Numerical Simulation Kanteyya A 1, Kiran Kumar Rokhade 2 Assistant Professor, Department of Mechanical Engineering, HKESSLN College
More informationflow work, p. 173 energy rate balance, p. 174 nozzle, p. 177 diffuser, p. 177 turbine, p. 180 compressor, p. 184 (4.4b) p. 166
0 Chapter 4 Control Volume Analysis Using Energy The use of mass and energy balances for control volumes at steady state is illustrated for nozzles and diffusers, turbines, compressors and pumps, heat
More informationEXTRA CREDIT OPPORTUNITY: Due end of day, Thursday, Dec. 14
EXRA CREDI OPPORUNIY: Due end of day, hursday, Dec. 4 his extra credit set of questions is an opportunity to improve your test scores (including an insurance policy for your final exam grade). here are
More informationCOMPARATIVE ANALYSES OF TWO IMPROVED CO 2 COMBINED COOLING, HEATING, AND POWER SYSTEMS DRIVEN BY SOLAR ENERGY
S93 Introduction COMPARATIVE ANALYSES OF TWO IMPROVED CO 2 COMBINED COOLING, HEATING, AND POWER SYSTEMS DRIVEN BY SOLAR ENERGY by Wanjin BAI a* and Xiaoxiao XU b a School of Mechanical and Vehicle Engineering,
More informationCFD ANALYSIS OF STEAM EJECTOR WITH DIFFERENT NOZZLE DIAMETER
CFD ANALYSIS OF STEAM EJECTOR WITH DIFFERENT NOZZLE DIAMETER 1 B. Sampath 2 Dr.A.Raveendra 1 M.Tech, Thermal Engineering student, Department of Mechanical Engineering, Malla Reddy Engineering College (Autonomous),
More informationCFD ANALYSIS OF STEAM EJECTOR WITH DIFFERENT NOZZLE DIAMETER
CFD ANALYSIS OF STEAM EJECTOR WITH DIFFERENT NOZZLE DIAMETER G.Saidulu 1, A.Purender reddy 2, Shreenivas 3 1 Student,Mech Dept,Sphoorthy Engineering College, Hyderabad,(India) 2 Assistant professor,mech
More informationResearch Article A Numerical Study on the Supersonic Steam Ejector Use in Steam Turbine System
Mathematical Problems in Engineering Volume 13, Article ID 65183, 9 pages http://dx.doi.org/1.1155/13/65183 Research Article A Numerical Study on the Supersonic Steam Ejector Use in Steam Turbine System
More informationSJT Steam Jet Thermocompressor
SJT Steam Jet Thermocompressor Description Jet Compressors can be utilized in a number of applications for steam circulation and increasing lower pressures to be functional. Jet Compressors are generally
More informationEFFECT OF THE NOZZLE EXIT POSITION ON THE EFFICIENCY OF EJECTOR COOLING SYSTEM USING R134A
EFFECT OF THE NOZZLE EXIT POSITION ON THE EFFICIENCY OF EJECTOR COOLING SYSTEM USING R134A K. Sopian 1, B. Elhub 1, Sohif Mat 1, A. N. Al-Shamani 1, AM Elbreki 1, Azher M. Abed 1, Husam Abdulrasool Hasan
More informationThermo-fluid Dynamics, Design and Performance
Unit T24: Aircraft Gas Turbine Thermo-fluid Dynamics, Design and Performance Unit code: K/504/0205 QCF level: 6 Credit value: 15 Aim The aim of this unit is to give learners an understanding of the fluid
More informationCFD Analysis of Nozzle Exit Position Effect in Ejector Gas Removal System in Geothermal Power Plant
EMITTER International Journal of Engineering Technology Vol. 3, No. 1, June 2015 ISSN:2443-1168 CFD Analysis of Nozzle Exit Position Effect in Ejector Gas Removal System in Geothermal Power Plant Setyo
More informationParametric Study of a Vapor Compression Refrigeration Cycle Using a Two-Phase Constant Area Ejector
Vol:7, No:, 01 Parametric Study of a Vapor Compression Refrigeration Cycle Using a Two-Phase Constant Area Ejector E. Elgendy International Science Index, Mechanical and Mechatronics Engineering Vol:7,
More informationChapter 10 VAPOR AND COMBINED POWER CYCLES
Thermodynamics: An Engineering Approach, 6 th Edition Yunus A. Cengel, Michael A. Boles McGraw-Hill, 2008 Chapter 10 VAPOR AND COMBINED POWER CYCLES Copyright The McGraw-Hill Companies, Inc. Permission
More informationOUTCOME 2 TUTORIAL 2 STEADY FLOW PLANT
UNIT 47: Engineering Plant Technology Unit code: F/601/1433 QCF level: 5 Credit value: 15 OUTCOME 2 TUTORIAL 2 STEADY FLOW PLANT 2 Be able to apply the steady flow energy equation (SFEE) to plant and equipment
More informationME 215. Mass and Energy Analysis of Control Volumes CH-6 ÇANKAYA UNIVERSITY. Mechanical Engineering Department. Open Systems-Control Volumes (CV)
ME 215 Mass and Energy Analysis of Control Volumes CH-6 ÇANKAYA UNIVERSITY Mechanical Engineering Department Open Systems-Control Volumes (CV) A CV may have fixed size and shape or moving boundaries Open
More informationAnalysis of a Two Phase Flow Ejector for the Transcritical CO 2 Cycle
3, Page Analysis of a Two Phase Flow Ejector for the Transcritical CO Cycle Fang LIU *, Eckhard A. GROLL Purdue University, School of Mechanical Engineering, West Lafayette, IN, USA Tel: 765-494-03, Fax:
More informationAvailable online at ScienceDirect. Energy Procedia 110 (2017 )
Available online at www.sciencedirect.com ScienceDirect Energy Procedia 110 (2017 ) 492 497 1st International Conference on Energy and Power, ICEP2016, 14-16 December 2016, RMIT University, Melbourne,
More informationSIMULATION AND EXPERIMENT RESEARCH ABOUT TWO-PHASE R744 EJECTOR SYSTEM
SIMULATION AND EXPERIMENT RESEARCH ABOUT TWO-PHASE R744 EJECTOR SYSTEM Jinrui Zhang Sustainable Energy Submission date: January 2016 Supervisor: Trygve Magne Eikevik, EPT Co-supervisor: Jingyi Wu, School
More informationInternational Journal of Advance Engineering and Research Development
Scientific Journal of Impact Factor (SJIF): 4.72 International Journal of Advance Engineering and Research Development Volume 4, Issue 9, September -2017 Review of Thermal Characteristics of Diesel Fired
More information20/06/2011 Seminar on Geothermal Exploitation Santiago de Chile
Contents Power Plants Steam Power plants Binary Power plants Geothermal Power Plants Single flash systems Binary systems 1 Equipment Well head Gathering piping system Steam separators and moisture separators
More informationPARAMETRIC STUDY OF GAS TURBINE CYCLE COUPLED WITH VAPOR COMPRESSION REFRIGERATION CYCLE FOR INTAKE AIR COOLING
International Journal of Mechanical Engineering and Technology (IJMET) Volume 9, Issue 9, September 2018, pp. 248 261, Article ID: IJMET_09_09_029 Available online at http://www.iaeme.com/ijmet/issues.asp?jtype=ijmet&vtype=9&itype=9
More informationFlow visualization at suction of a twin screw compressor
Flow visualization at suction of a twin screw compressor A. Kovacevic, M. Arjeneh, S. Rane, N. Stosic, M. Gavaises, City University London Abstract Rotary twin screw machines are commonly used for handling
More informationAC : THE ENERGY SYSTEMS LABORATORY AT KETTERING UNIVERSITY
AC 2007-27: THE ENERGY SYSTEMS LABORATORY AT KETTERING UNIVERSITY Ahmad Pourmovahed, Kettering University Ahmad Pourmovahed is a Professor of Mechanical Engineering at Kettering University. He received
More informationS.Y. Diploma : Sem. III [PG/PT/ME] Thermal Engineering
S.Y. Diploma : Sem. III [PG/PT/ME] Thermal Engineering Time: 3 Hrs. Prelim Question Paper Solution [Marks : 70 Q.1 Attempt any FIVE of the following. [10] Q.1(a) Explain difference between Thermodynamic
More informationANALYSIS OF STEAM EJECTOR BY USING COMPUTATIONAL FLUID DYNAMICS
, pp.41~51 Thomson Reuters ID: L-5236-2015 ANALYSIS OF STEAM EJECTOR BY USING COMPUTATIONAL FLUID DYNAMICS Dr.I Satyanarayana 1 Pricipal &Professor of Mechanical Engineering,Sri Indu Institute of Engineering
More informationC. heating turbine exhaust steam above its saturation temperature. D. cooling turbine exhaust steam below its saturation temperature.
P74 (B2277) Condensate depression is the process of... A. removing condensate from turbine exhaust steam. B. spraying condensate into turbine exhaust steam. C. heating turbine exhaust steam above its saturation
More informationChapter 1 STEAM CYCLES
Chapter 1 STEAM CYCLES Assoc. Prof. Dr. Mazlan Abdul Wahid Faculty of Mechanical Engineering Universiti Teknologi Malaysia www.fkm.utm.my/~mazlan 1 Chapter 1 STEAM CYCLES 1 Chapter Objectives To carry
More informationES Fluid & Thermal Systems Page 1 of 6 STEAM TURBINE LABORATORY
ES 202 - Fluid & Thermal Systems Page 1 of 6 STEAM TURBINE LABORATORY Objective The objective of this laboratory experience is to demonstrate how mechanical power can be generated using a steam turbine
More informationLecture No.1. Vapour Power Cycles
Lecture No.1 1.1 INTRODUCTION Thermodynamic cycles can be primarily classified based on their utility such as for power generation, refrigeration etc. Based on this thermodynamic cycles can be categorized
More informationEffect of Suction Nozzle Pressure Drop on the Performance of an Ejector-Expansion Transcritical CO 2 Refrigeration Cycle
Entropy 2014, 16, 4309-4321; doi:10.3390/e16084309 Article OPEN ACCESS entropy ISSN 1099-4300 www.mdpi.com/journal/entropy Effect of Suction Nozzle Pressure Drop on the Performance of an Ejector-Expansion
More information[4163] T.E. (Mechanical) TURBO MACHINES (2008 Pattern) (Common to Mech. S/W) (Sem. - II)
Total No. of Questions : 12] P1061 SEAT No. : [Total No. of Pages : 7 [4163] - 218 T.E. (Mechanical) TURBO MACHINES (2008 Pattern) (Common to Mech. S/W) (Sem. - II) Time : 3 Hours] [Max. Marks :100 Instructions
More informationVisualization of Unsteady Behavior of Cavitation in Circular Cylindrical Orifice with Abruptly Expanding Part
Visualization of Unsteady Behavior of Cavitation in Circular Cylindrical Orifice with Abruptly Expanding Part Yasuhiro Sugimoto and Keiichi Sato Kanazawa Institute of Technology 7-1 Oogigaoka, Nonoichi-machi,
More informationa. The power required to drive the compressor; b. The inlet and output pipe cross-sectional area. [Ans: kw, m 2 ] [3.34, R. K.
CHAPTER 2 - FIRST LAW OF THERMODYNAMICS 1. At the inlet to a certain nozzle the enthalpy of fluid passing is 2800 kj/kg, and the velocity is 50 m/s. At the discharge end the enthalpy is 2600 kj/kg. The
More informationThe Effect of Swirl Strength on the Flow Characteristics and Separation Efficiency of Supersonic Gas Separator
The Effect of Swirl Strength on the Flow Characteristics and Separation Efficiency of Supersonic Gas Separator Peiqi Liu 1, Wenwen Ren 1, Jianhua Zhao 1 Yingguang Wang 1, Xiaomin Liu 1, Dapeng Hu 1 * 1
More informationCode No: RR Set No. 1
Code No: RR310303 Set No. 1 III B.Tech I Semester Regular Examinations, November 2006 THERMAL ENGINEERING-II (Mechanical Engineering) Time: 3 hours Max Marks: 80 Answer any FIVE Questions All Questions
More informationPerformance of Scroll Expander for CO2 Refrigeration Cycle
Purdue University Purdue e-pubs International Compressor Engineering Conference School of Mechanical Engineering 2006 Performance of Scroll Expander for CO2 Refrigeration Cycle Mitsuhiro Fukuta Shizuoka
More informationPerformance of Scroll Expander for CO2 Refrigeration Cycle
Purdue University Purdue e-pubs International Compressor Engineering Conference School of Mechanical Engineering 2006 Performance of Scroll Expander for CO2 Refrigeration Cycle Mitsuhiro Fukuta Shizuoka
More information