DEVELOPMENT OF SUCTION SCOOPS FOR MIDAMERICAN ENERGY COMPANY S GEORGE NEAL NORTH CIRCULATING WATER PUMP INTAKE STRUCTURES
|
|
- Marshall Sherman
- 5 years ago
- Views:
Transcription
1 DEVELOPMENT OF SUCTION SCOOPS FOR MIDAMERICAN ENERGY COMPANY S GEORGE NEAL NORTH CIRCULATING WATER PUMP INTAKE STRUCTURES by Tatsuaki Nakato Sponsored by Burns & McDonnell 9400 Ward Parkway Kansas City, Missouri IIHR Technical Report No. 429 IIHR Hydroscience & Engineering College of Engineering The University of Iowa Iowa City, Iowa July 2003
2 ABSTRACT Pump suction scoops were developed and model tested using 1:12 scale models for MidAmerican Energy Company's George Neal North Station to improve circulatingwater pump performance at extremely low river stages. The suction scoops developed were found to reduce head losses at the pump suction bells because they accelerated the pump-approach flows gradually and distributed them uniformly around the pump-suction bells. Furthermore, there were no common free-surface vortex problems surrounding the pump columns because the scoop ceilings prevented any free-surface vortices from forming. ACKNOWLEDGMENTS The model investigation reported herein was conducted for and sponsored by Burns & McDonnell in Kansas City. The project owner was MidAmerican Energy Company. The author thanks Mr. Terry Larson, Burns & McDonnell and Mr. Leon Gertsch of MidAmerican Energy Company s George Neal North Station for their unfailing cooperation throughout the course of this study. The author is also indebted to a variety of IIHR personnel. The IIHR Hydroscience & Engineering shop crew, led by Mr. Darian DeJong, built and modified the model numerous times and demonstrated their skilled craftsmanship. Mr. Michael Kundert also contributed to this project with his skilled draftsmanship with shop drawings. ii
3 TABLE OF CONTENTS Page I. INTRODUCTION 1 II. SIMILARITY LAWS 4 III. SUCTION SCOOP DESIGNED FOR EXISTING UNIT-1 INTAKE 6 IV. SUCTION SCOOP DESIGNED AND TESTED FOR EXISTING UNIT-3 INTAKE 11 V. SUCTION SCOOP DESIGNED AND TESTED FOR EXISTING UNIT-2 INTAKE 29 VI. RECOMMENDATIONS 47 REFERENCES 50 LIST OF TABLES Page Table 3.1 Test result for free-surface vortex formation for Unit-1 intake with suction scoop (note that no surface beam was in place) 10 Table 4.1 A summary of test conditions under as-built conditions and with suction scoop conducted for existing Unit-3 intake 18 Table 4.2 A summary of test results for Cases 1 and 5 for the Unit-3 intake 24 Table 5.1 A summary of test conditions for the as-built conditions and with suction scoop conducted for existing Unit-2 intake 35 Table 5.2 A summary of test results for Cases 1 and 5 for the Unit-2 intake with a vacuum lift wall opening of 3 ft 37 Table 5.3 A summary of test conditions for the as-built conditions and with suction scoop conducted for existing Unit-2 intake with a vacuum lift wall opening of 2 ft 40 Table 5.4 A summary of test results for Cases 1A, 2A, 5A, and 6A 43 Table 5.5 Free-surface vortex types observed in the as-built Unit-2 intake (Case 1A) 46 LIST OF FIGURES Page Figure 1.1 Principal components of suction scoop 3 Figure 3.1 Plan and elevation of existing Unit-1 intake bay 7 Figure 3.2 Pump suction-bell profile of existing Unit-1 intake pump 8 Figure 3.3 Suction scoop layout designed for existing Unit-1 intake 9 iii
4 Figure 3.4 Classification of free-surface and sub-surface pump-intake vortices 10 Figure 4.1 Plan and elevation of existing Unit-3 intake bay 12 Figure 4.2 Pump suction-bell profile of existing Unit-3 intake pump 13 Figure 4.3 Model of existing Unit-3 intake (viewed from upstream) 13 Figure 4.4 Model of existing Unit-3 intake (frontal view) 14 Figure 4.5 Model of existing Unit-3 intake (viewed through backwall) 14 Figure 4.6 Model of existing Unit-3 intake showing model vacuum system 15 Figure 4.7 Model of existing Unit-3 intake with trashracks and traveling screen installed 16 Figure 4.8 Existing Unit-3 intake traveling screen layout 16 Figure 4.9 Suction scoop layout designed for existing Unit-3 intake 19 Figure 4.10 Discharge-river stage relationships obtained in Cases 1 and 5 25 Figure 4.11 Swirl-river stage relationships obtained in Cases 1 and 5 25 Figure 4.12 head losses measured in Cases 1 and 5 26 Figure 4.13 Warm-water supply lines through vacuum lift wall 27 Figure 4.14 Diffusers in vacuum chamber seen through backwall windows 27 Figure 4.15 Relationships between velocity head and total head obtained in Cases 1 and 5 28 Figure 5.1 Plan and elevation of existing Unit-2 intake bay 30 Figure 5.2 Pump suction-bell profile of existing Unit-2 intake pump 31 Figure 5.3 Frontal view of existing Unit 2 intake model 31 Figure 5.4 Rear view of existing Unit-2 intake model 32 Figure 5.5 Side view of existing Unit-2 intake model 32 Figure 5.6 Rear view of model suction scoop for Unit-2 intake 33 Figure 5.7 Suction scoop layout designed for existing Unit-2 intake with 3-ft wall opening 34 Figure 5.8 Discharge-river stage relationships obtained in Cases 1 and 5 38 Figure 5.9 head losses measured in Cases 1 and 5 39 Figure 5.10 Suction scoop layout designed for existing Unit-2 intake with 2-ft wall opening 42 Figure 5.11 Discharge-river stage relationships obtained in Cases 1A and 5A 44 Figure 5.12 head losses measured in Cases 1A and 5A 45 iv
5 DEVELOPMENT OF SUCTION SCOOPS FOR MIDAMERICAN ENERGY COMPANY S EXISTING GEORGE NEAL NORTH CIRCULATING WATER PUMP INTAKE STRUCTURES I. INTRODUCTION The existing fossil-fuel power plant circulating-water pump intake for George Neal North station, owned by MidAmerican Energy Company (MAEC), is located on the left bank of the Missouri River near Sioux City, Iowa. This intake structure for three electric power-generating units consists of six pump-intake bays with two pump bays for each unit. Unit 1 pumps are rated at 37,500 gpm (84 cfs) each, Unit 2 pump are rated at 65,000 gpm (145 cfs) each, and Unit 3 pump are rated at 145,000 gpm (323 cfs) each. The total combined circulating-water cooling capacity is 495,000 gpm (1,102 cfs). To cope with decreased plant availability due to potential circulating-water system failure during low river levels, MAEC was considering construction of a new circulatingwater pump intake. IIHR Hydroscience & Engineering (IIHR) conducted a physical model study of the new water intake (Nakato, et al. 2002). In the meantime, MAEC also considered improving reliabilities of the existing pumps under extremely low river water levels, especially during the wintertime when the release of water from Gavins Point Dam in South Dakota upstream from the power plant is reduced. Subsequently, IIHR was contracted to develop suction scoops for the existing circulating-water pumps at each unit. There is a very unique feature in Units 2 and 3 pump bays in which each pump bay is completely sealed and vacuum is applied therein to raise the water-surface elevation within the pump bay for gaining the net positive suction head. When Gavins Point Dam was constructed in late 1950, along the Missouri River in South Dakota, severe river-bed degradation occurred downstream from the dam. This lowering of the river bed had caused problems with the existing intakes, which necessitated application of vacuum within these pump bays to maintain minimum submergence depths and to satisfy Net Positive Suction Head (NPSH) requirements. 1
6 Conventional vertical pumps employ pump bells to withdraw water radially and accelerate flow toward pump impellers. If a pump is installed at the center of a sufficiently large water body, the present technology may function appropriately. However, the space available for the real pump-intake structure is very limited. The normal pump-sump layout is rectangular, and the pump is installed near the backwall. Therefore, the pump-approach flow generally cannot be distributed uniformly around the pump bell because flow in the pump sump approaches the bell from one direction. The suction scoop under development is intended to accelerate the pump-approach flow gradually toward the pump bell and to distribute it evenly around the bell. A basic layout of the suction scoop is shown in figure 1.1 which consists of floor and backwall splitters to suppress formation of boundary-attached subsurface vortices, floor corner fillets, a sloping scoop ceiling to accelerate pump-approach flow, and a horizontal scoop ceiling to prevent any vertical flow components from approaching toward the pump-suction bell. Often flow-straightening vanes are added to the scoop at the scoop entrance to remove lateral velocity components. The suction scoop reduces head losses at the pump suction bell because it accelerates the pump-approach flow gradually and distributes it uniformly around the pump-suction bell. Furthermore, there will be no common free-surface vortex problems because the scoop ceiling prevents any free-surface vortices from developing adjacent to the pump. The first IIHR-designed suction scoop was implemented in the four pump intake bays at the MAEC s Council Bluffs Unit-3 intake during the period between December 1989 and January Since then, the pumps have been operating superbly without any problems. IIHR constructed two existing pump intake models for Units 2 and 3 at an undistorted geometrical scale of 1:12 within the new intake model basin that was utilized to test the new pump intakes (Nakato, et al. 2002). Suction scoops for Units 2 and 3 were then designed based on IIHR s previous experience in suction scoop designs (Nakato, et al. 1996; Nakato and Goss 1998), and they were model tested for their performance. Two identical suction scoops for Unit-1 pumps were designed, but not model tested. During the suction-scoop development strong emphases were given to determining the lowest river water level under which pumps could be operated satisfactorily. 2
7 Backwall Fillet Floor Corner Fillet 45 Deg. Slope Flow Turning Vanes FLOW Pump Bell Backwall Splitter Floor Splitter Line of Sloping Scoop Ceiling Upstream Edge of Suction Scoop C L PLAN VIEW Structural Beams Vertical Baffle Wall Curtain Wall to Prevent Free-Surface Vortex Formation Horiz. Ceiling Sloping Ceiling Vane FLOW Floor Splitter SECTION VIEW Figure 1.1 Principal components of suction scoop 3
8 II. SIMILARILTY LAWS All the existing intake models were built at an undistorted geometric scale of 1:12, which means that the ratio of all the lengths in every model to their corresponding lengths in the prototype was equal: L r =L m /Lp = 1/12 (3-1) where L r : Length ratio L m : Model length L p : Corresponding prototype length Due to the free-surface flow in the models, it was necessary to include the gravitational influence into the calculations of the model discharges, velocities, and times. Therefore, the Froude number similarity between model and prototype discharges was used. The Froude number ratio, F r, must be unity: Fm F r = = 1 (3.2) F p F r : Froude number ratio F m : Froude number of the model F p : Froude number in the prototype where V F = (3.3) 1 ( gl) 2 V: Characteristic flow velocity g: Gravitational constant L: Characteristic length With equations (3-2) and (3-3) the velocity and the time ratios are given by V = L = (3.4) m V r = V p 1 2 r 4
9 T r T 1 = m = L 2 r = (3.5) Tp The discharge ratio follows from (3-4) as Q Q = = V A = L L = L = (3.6) 1 5 m r r r r r r Qp 5
10 III. SUCTION SCOOP DESIGNED FOR EXISTING UNIT-1 INTAKE The existing Unit-1 intake bays are 47 ft 6 in. long and 9 ft 8 in. wide, as shown in figure 3.1. Note that there is no vacuum chamber provided for the Unit-1 intake bays. The pump-suction bell shown in figure 3.2 is 58-1/2 in. in diameter and the floor clearance of the suction bell is 18-3/8 in. The distance from the backwall to the center of the pump column is 5 ft 7 in. On the basis of previous IIHR experience in designing suction scoops for vertical pumps (Nakato 1992; Nakato, et al. 1996; Nakato and Goss 1998), a suction scoop for the Unit-1 intake was designed. The designed suction scoop shown in figure 3.3 includes the following components: 1. The existing backwall is too far from the edge of the pump bell. Therefore, it should be moved upstream by 1ft 6 in. There is no need to build a new backwall over the entire intake depth. Either a step, 1 ft 6 in. deep, 1 ft 6-3/8 in. high, and 9 ft 8 in. wide, or a 1 ft 6-3/8 in. high vertical backwall as a part of the suction scoop, should be fabricated. 2. Install a triangular-shaped floor splitter, 9 ft 6 in. long, 2 ft wide, and 1 ft tall in the center of the pump bay to suppress floor-attached subsurface vortices. 3. Install a triangular-shaped backwall splitter, 2 ft wide, 1 ft deep, and 1 ft 6-3/8 in. tall, on the backwall to suppress flow circulations around the pump-suction bell. 4. Install two triangular-shaped sidewall floor-corner fillets, 9 ft 6 in. long, 1 ft wide, and 1 ft tall, along two sidewalls of the pump bay to suppress sidewall-attached subsurface vortices. 5. Install a triangular-shaped, backwall floor corner fillet, 9 ft 8 in. long, 1 ft wide, and 1 ft tall, along the backwall floor corner to suppress backwall-attached subsurface vortices. 6. Install two vertical triangular-shaped backwall corner fillets, 2 ft wide, 2 ft deep, and 1 ft 6-3/8 in. tall, in two corners of the backwall to eliminate dead areas. 7. Install a suction-scoop ceiling (a 9 ft 6 in. long horizontal ceiling connected to a 5 ft 7 in. long sloping ceiling). A hole, slightly larger than the bell diameter, say, 0.5 in., should be bored in the horizontal ceiling and its gap should be sealed by a circular rubber gasket that is anchored to the bell mouth. 8. Install five, 2 ft long, flow-turning vanes at 1 ft 8 in. intervals underneath the sloping portion of the suction-scoop ceiling in order to straighten angular pumpapproach flows. 6
11 PLAN VIEW OF ONE BAY OF UNIT 1 9'-8" CL DISCHARGE PIPE SECTION B-B 47'-6" 29'-1" 12'-10" 5'-7" EL ' 12'-11" 9'-2 1/8" EL ' 4'-10" 4'-10" 1'-3" B 3" 5'-2" FLOW CL A STOP A LOG 9'-8" B CL TRASHRACK 1'-3" 47'-6" 18'-5" CL FINE SCREEN GUIDE 12'-10" 5'-7" 1'-0" 29'-1" 12'-11" 9'-2 1/8" 5'-2" 4'-1/8" 3'-8 7/8" EL ' 1'-0" CL DISCHARGE PIPE MEAN HIGH WATER EL ' EL '-0" 10'-9" 2'-0" 2'-0" CONSTANT WATER LEVEL EL ' 7'-9" EL ' EL ' 1'-0" 6'-3" 9'-3" 4'-9" 2'-9" MEAN LOW WATER EL ' MIN. LOW WATER EL ' EXTREME LOW WATER EL ' 3'-3" 12'-9" 2'-0" 13'-3" 3'-3" 1'-11 5/16" '-1 7/16" 11'-7 9/16" 32'-9" 8" 10'-3" 1'-6 3/8" 10" EL EL RIVER BED EL ' " 4'-10 1/2" 3'-1 3/4" SECTION A-A Figure 3.1 Plan and elevation of existing Unit-1 intake bay 7
12 4'-9" 6 1/4" 4'-10 1/2" 58.5" DIAMETER SUCTION BELL FOR EXISTING UNIT 1 (PROTOTYPE DIMENSIONS) Figure 3.2 Pump suction-bell profile of existing Unit-1 intake pump In order to obtain the lowest river stage under which the existing Unit-1 pumps with suction scoops can still run without air entrainment, the Unit-3 intake model with a suction scoop in place was utilized. The Unit-3 intake has two pump-approach-flow bays that become a single bay. One of the bays was used to simulate the Unit-1 intake. The Unit-3 discharge (145,000 gpm) was scaled down to match the Unit-1 discharge (37,500 gpm) for each of the two bays. The river stage was first set at EL ft above Mean Sea Level (MSL) and incrementally reduced until detrimental air ingestion occurred. The test result indicated that a free-surface vortex harmful for satisfactory pump operations forms just upstream from the suction-scoop inlet at a river stage as high as EL ft, as shown in table 3.1. At a river stage of EL ft, significant air was found to burst into the pump. The formation of a free-surface vortex just upstream from the Unit-1 suction scoop was completely suppressed by means of a surface beam, as shown in figure 3.3 (see figure 3.4 for vortex classification). Once this surface beam was installed, the river stage was able to be lowered down to EL ft without any air entrainment to the pump. The pump-sump elevation just upstream from the surface beam under this river stage was 8
13 EL ft. Therefore, it is recommended that the surface beam shown in figure 3.3 be included as part of the suction-scoop design for the Unit-1 pump intake. SUCTION SCOOP DESIGNED FOR EXISTING GEORGE NEAL NORTH UNIT-1 INTAKE 5'-6" 9'-6" 1'-6" 1'-0" 7'-6" 1'-0" FLOW A 1'-8" 1'-8" 1'-8" 1'-8" 1'-6" 1'-6" 1'-0" 2'-0" 1'-0" Five 2' Long Vanes Backwall Floor Corner Fillet Floor Splitter 58.5" Dia D B B C C Sidewall Floor Corner Fillet Pump Bell 7 3/4" Backwall Splitter 2'-0" 1'-0" PLAN VIEW OF MODIFIED EXISTING UNIT-1 INTAKE D 2'-0" 2'-0" 2'-0" New Backwall Vertical Backwall Corner Fillet 1'-0" 3'-10" 3'-10" 1'-0" 9'-8" A Minimum river water level to avoid air entrainment EL EL Minimum sump water level to avoid air entrainment 1'-0" SURFACE BEAM: needed to suppress free-surface vortex formation 3'-0" 4'-0" 2'-6" 2'-0" 3'-6" 8'-6" 1'-0" 1'-6" Horizontal Ceiling Vanes 2'-1 3/4" 5'-7" 1'-0" 15'-0" 5'-7" Sloping Ceiling (angle: 10 ) 5'-6" 9'-6" 1'-6" 1'-6 3/8" EL ' SECTION A-A 1' 1' 2' 1' 1' SECTION B-B SECTION C-C SECTION D-D Figure 3.3 Suction scoop layout designed for existing Unit-1 intake 9
14 SURFACE SWIRL TYPE 1 VORTEX PULLING DEBRIS BUT NOT AIR TYPE 4 SURFACE DIMPLE TYPE 2 VORTEX PULLING AIR BUBBLES TO INTAKE TYPE 5 ORGANIZED CORE AS OBSERVED BY DYE TRACE TYPE 3 VORTEX PULLING AIR CONTINUOUSLY TO INTAKE TYPE 6 TYPE 1 TYPE 2 TYPE 3 WEAK SWIRL (NOT COHERENT CORE) (a) Classification of free-surface vortices ORGANIZED DYE CORE (COHERENT DYE CORE) ORGANIZED AIR CORE (AIR COMING OUT OF SOLUTION) d:\tn\fcad\surface-subsurface_version3.f cw (6"-9") (b) Classification of boundary-attached subsurface vortices Figure 3.4 Classification of free-surface and sub-surface pump-intake vortices River Stage Comments Vortex Classification above MSL (ft) Surface dimple for a short period Type Very small air bubbles withdrawn into the pump Type Very small air bubbles withdrawn into the pump Type 3 & Type Air bubble ingestion twice in 10 sec Type 3 & Type Air bubble ingestion twice in 10 sec Type Air bubble ingestion more frequently Type Air bubble ingestion almost continuously Type 5 Table 3.1 Test result for free-surface vortex formation for Unit-1 intake with suction scoop (note that no surface beam was in place) 10
15 IV. SUCTION SCOOP DESIGNED AND TESTED FOR EXISTING UNIT-3 INTAKE The existing Unit-3 intake bays are 56 ft long with two 11 ft-2 in. channels feeding each pump bay, as shown in figure 4.1. The pump-suction bell shown in 4.2 is 108 in. in diameter and the floor clearance of the suction bell is 2 ft 3 in. The distance from the backwall to the center of the pump column is 6 ft 9 in. Similarly to the Unit-1 suction scoop, IIHR designed a suction scoop for the Unit 3 intake. As mentioned previously, the Unit-3 intake chamber is vacuum controlled to gain the net positive suction head; thereby the pump-sump water surface is raised approximately 6 ft which equates to EL 1056 ft when the low water elevation of EL 1050 ft occurs. The existing Unit-3 intake model was built at an undistorted geometrical scale of 1:12 within the new intake model basin, as shown in figures 4.3 through 4.6. As can be seen in figure 4.6, the model pump-bay vacuum system was installed and vacuum was applied by means of a shop vacuum. Model trashracks and traveling screens were also included in the model in order to accurately predict head losses through them (see figure 4.7). In order to maintain the head-loss coefficient equal both in model and prototype, Papworth's empirical relationship (Papworth 1972) was utilized. The fine screens were modeled for the normal flow condition (145,000 gpm) with the lowest river water level of EL 1050 ft. The prototype wire-cloth dimensions of the screens are such that the opening is 3/8 in., the wire diameter is 1/8 in., and the percent open area is 56.24%. A modified Reynolds number defined by Papworth is given by R e* = Vb ν( 1 s) (4.1) where V = mean approach screen velocity; b = wire diameter; ν = kinematic viscosity of water; and s = solidity parameter = 1 - (screen percent open area) = = in this case. This modified Reynolds number is given by Papworth in terms of K(1-s) 2 /s, where K = head-loss coefficient. The wire cloth designed for this study (Mesh 2 square- 11
16 mesh wire cloth with a wire diameter of in.) produces a K value of 1.31 that is very close to 1.25 in the prototype. The model trashracks (3/8-in. thick, and 3-in. deep bars on 3-in. centers in full size) were also included in the model design (see figure 4.7). 16'-10 1/16" 16'-0" 5'-3" 5'-3" 9'-6 3/8" 6'-6" 3'-3/8" PLAN VIEW 6'-6" 3'-3/8" ELEVATION END VIEW DETAIL OF EXISTING FILLET (Need two of - one opposite hand) (Make both removable) 24'-10" 11'-2" 2'-6" 11'-2" EL ' EL ' 4'-3" EL ' 5'-11" EL ' 5'-11" 3'-3/8" 30.0 EL ' 3'-0" 6'-6" EL ' 5'-3" 7'-2" 7'-2" 5'-3" SECTION B-B 42'-6" 14'-7" 18'-3 3/4" 9'-7 1/4" 10'-4 3/8" 2'-0" 2'-0" 6'-8 3/4" 2'-0" OPNG 76.5 EL '-11" 8'-9" 6'-9" SECTION A-A FLOW 9'-6 3/8" 4'-3" 13'-0" A 5'-3" 7'-2" 7'-2" 5'-3" 6'-6" 9'-6 3/8" 13'-6" CL VACUUM LIFT WALLS 1'-0" 1'-0" 1'-0" 2'-0" CONSTANT WATER LEVEL EL ' 4'-3" 2'-0" BULLNOSE 2'-0" 2'-0" 13'-6" MEAN HIGH WATER EL ' 19'-3" 3'-3" 10'-3" 2'-3" EXTREME EL ' R1'-0" 1'-3" 11'-2" 11'-2" 1'-3" 2'-0" R1'-3" 2'-6" 3'-3/8" 29'-9" 3'-0" 32'-9" 40'-0" 16'-0" 32'-4 3/4" 1'-0" 6" B MEAN LOW WATER EL ' VACUUM LIFT WALL MIN. LOW WATER EL ' 3" 3" 18.2 A UNIT 3 CL TRAVELLING SCREEN GUIDES CL TRASH RACK GUIDES B PLAN VIEW 56'-0" VACUUM LIFT WALL CL DISCHARGE PIPE 8" 10" 8'-3" 2'-0" 9'-3" 80 2'-6" 2'-6" 7'-6" 2'-1" 2'6" 13'-6" 6'-9" 6'-9" 6'-9 7/16" 5'-8 7/16" 13'-6" CL STOP LOG AND FINE SCREEN GUIDES 10'-0" RIVER BED: EL ' SEE DETAIL SAME PAGE SECTION C-C 8'-3 1/4" C C 5" 4'-0" 24'-10" Figure 4.1 Plan and elevation of existing Unit-3 intake bay 12
17 67.00" 56.40" 52.25" R20.620" 98.00" " 108" DIAMETER SUCTION BELL FOR EXISTING UNIT 3 (PROTOTYPE DIMENSIONS) Figure 4.2 Pump suction-bell profile of existing Unit-3 intake pump Figure 4.3 Model of existing Unit-3 intake (viewed from upstream) 13
18 Figure 4.4 Model of existing Unit-3 intake (frontal view) Figure 4.5 Model of existing Unit-3 intake (viewed through backwall) 14
19 Figure 4.6 Model of existing Unit-3 intake showing model vacuum system 15
20 Figure 4.7 Model of existing Unit-3 intake with trashracks and traveling screens installed A 11'-2" 7" 10'-0" 7" 4'-0" 3" 3'-6" 3" 3" 10'-0" FLOW VERTICAL MEMBERS 6"X3"X25'4.5" (NEED 4 PER SCREEN) CROSS BRACES 3"X3" TYPICAL (12 PLACES/FRAME) 3" 25'-4 1/2" 10'-0" SCREEN MESH ON UPSTREAM AND DOWNSTREAM FACES OF FRAME 3" 3" UPSTREAM FACE OF REVOLVING SCREEN FRAME DOWNSTREAM FACE OF REVOLVING SCREEN FRAME 5'-4 1/2" SCREEN BOOT A DOWNSTREAM FACE OF REVOLVING SCREENS NEED TWO OF 3" EL ' CL HEADSHAFT R2'-2" 1 1/2" 1'-4 1/2" 3 1/2" 11" SECTION A-A R5 1/4" 5 11/16" Figure 4.8 Existing Unit-3 intake traveling screen layout 16
21 At the beginning of modeling efforts, multiple tasks listed in table 4.1, including both existing conditions and proposed suction-scoop modifications were specified by MAEC. The suction scoop designed for the Unit-3 intake is shown in figure 4.9, including the following components: 1. Install a triangular-shaped floor splitter, 15 ft long, 3 ft wide, and 1 ft 6 in. tall in the center of the pump bay to suppress floor-attached subsurface vortices. 2. Install a triangular-shaped backwall splitter, 3 ft wide, 1 ft 6 in. deep, and 2 ft 3 in. tall, on the backwall to suppress flow circulations around the pump-suction bell. 3. Install two triangular-shaped sidewall floor-corner fillets, 14 ft 1-9/16 in. long, 1 ft 6 in. wide, and 1 ft 6 in. tall, along two converging sidewalls of the pump bay to suppress sidewall-attached subsurface vortices. 4. Install a triangular-shaped, backwall floor corner fillet, 14 ft 4 in. long, 1 ft 6 in. wide, and 1 ft 6 in. tall, along the backwall floor corner to suppress backwallattached subsurface vortices. 5. Install two vertical triangular-shaped backwall corner fillets, 3 ft 1-7/8 in. by 3 ft 1-7/8 in. by 5 ft 1-3/8 in., and 2 ft 3 in. tall, in two corners of the backwall to eliminate stagnant flow areas. 6. Install a suction-scoop ceiling (a 15 ft 6 in. long horizontal ceiling connected to a 5 ft 11/16 in. long sloping ceiling). A hole, slightly larger than the bell diameter, say, 0.5 in., should be bored in the horizontal ceiling and its gap should be sealed by a circular rubber gasket that is anchored to the bell mouth. 7. Install six vanes, as specified in figure 4.9, underneath the sloping portion of the suction-scoop ceiling in order to straighten angular pump-approach flows. The distance between the first and the last vanes from the sidewalls should be 1 ft 9 in. It should be noted that throughout the model tests, the mean river flow velocity was maintained at 3 ft/s in full scale. As the river stage was decreased or increased, the model river discharge was altered accordingly. It should also be noted that no detailed classification of free-surface vortices was made with the Unit-3 intake model because it was not originally included in the scope of work. As the study progressed to investigate the Unit-1 and Unit-2 intakes, IIHR was asked by MAEC to document the vortex types for some test cases. 17
22 Test Case For Unit 3 Intake Vacuum Lift Wall Opening (ft) As-Built or Suction Scoop Winter Discharge Line (Yes/No) Task 1 4 As-Built No Produce relationship between pump discharge and river stage and relationship between pump swirl and river stage 2 4 As-Built No Find critical river stage for safe vacuum chamber operation 3 3 As-Built No Find critical river stage for safe vacuum chamber operation 4 4 As-Built Yes Design and fabricate a winter discharge supply line downstream from the vacuum lift wall to supply a discharge of 15,000 gpm to the vacuum chamber/investigate its effect in raising the critical water depth in front of the vacuum lift gate for safe vacuum chamber operation 5 4 Suction Scoop No Produce relationship between pump discharge and river stage and relationship between pump swirl and river stage 6 4 Suction Scoop No Find critical river stage for safe vacuum chamber operation 7 3 Suction Scoop No Find critical river stage for safe vacuum chamber operation 8 4 New Suction Scoop Extended Upstream from Vacuum Lift Wall * Head Loss Measurements Yes Modify suction-scoop layout so that it extends upstream from the vacuum lift gate/supply a discharge of 15,000 gpm to the vacuum chamber and investigate its effect in raising the critical water depth in front of the vacuum lift gate for safe vacuum chamber operation Design and fabricate model trashracks and traveling screens to simulate head losses within each pump-intake bay *All test cases will be conducted with model trashracks and traveling screens installed. Table 4.1 A summary of test conditions under as-built conditions and with suction scoop conducted for existing Unit-3 intake 18
23 24'-6" 2" 11'-2" 2'-6" 1'-6" 9'-0" 1'-6" 3'-0" 1'-6" 5'-3" 7'-2" 7'-2" 5'-3" CL VACUUM LIFT WALLS SECTION B-B B B EL VACUUM RAISED TO EL.1056' A SECTION A-A FLOW A VACUUM LIFT WALL LOW WATER EL.1050' 1'-6" Backwall Splitter Backwall Floor Corner Fillet 2'-3" 9" Floor Corner Fillet Bell Diam: 9' 9" Floor Splitter 1'-6" Vane C 12'-0" 1'-6" 1'-6" 12'-7 9/16" Floor Corner Fillet 5'-0" 15'-6" Horizontal Ceiling Sloping Ceiling PLAN VIEW Pier Nose C 5'-11/16" 9'-0" 3'-0" 15'-6" 2'-1 1/4" 5'-0" 2'-6" 5'-3" 14'-4" 5'-3" 2'-3" Ø9'-0" 24'-10" 6'-9" 11'-2" 6" 16'-10" 4'-6" 16'-0" 2" PLAN VIEW OF SUCTION SCOOP 24'-10" 9" 1'-6" 2'-3" '-10" 3'-6" 3'-1 7/8" 2'-8" Vane A 3'-6" Vane B 5'-1 3/8" Vane C 3'-4" 2'-6" 2'-6" 2'-6" 3'-0" Vane B Vane A 1'-6" 12'-0" 11'-2" Vane A: 5'- 3 1/4" Long Vane B: 5'-13/16" Long Vane C: 5'-0" Long 4'-0" 5'-8" 5'-8" 3'-1 7/8" 3'-0" 5'-3" 14'-4" 5'-3" Figure 4.9 Suction scoop layout designed for existing Unit-3 intake 19
24 Case 1 and Case 5 To obtain relationships between the pump discharge and the river stage, Case 1 under the as-built condition and Case 5 with the model suction scoop were run with the river stage incrementally varied. In Case 5, the vacuum lift wall opening was maintained at 4 ft. In each case the discharge passing through the withdrawal pipe was measured by means of an orifice meter. The empirical relationships obtained are shown in figure In both Cases 1 and 5, the pump discharge generally decreased as the river stage increased. Although figure 4.10 shows that the discharge was higher in Case 1 than in Case 5, their differences are insignificantly small. For example, a difference of 600 gpm in prototype discharge is merely 0.42% (600 gpm/142,000 gpm), which is within experimental errors. Note that the horizontal axis in figure 4.10 is drawn for a very narrow range of prototype discharge. We were not able to demonstrate in this model that the suction scoop can deliver more flow than the as-built intake layout. It may well be due to the small model scale that was used. However, the pump-column swirl speed with the suction scoop was much smaller than that under as-built conditions, as shown in figure The swirl angle, θ, is defined by θ = tan -1 (V θ /V z ) (4.2) where V θ = 2πrω/60 = tangential velocity at the tip of the vortimeter blade; r = radius of pump column; ω = angular velocity of vortimeter in rpm; and V z = average axial velocity of pump-column flow. The maximum swirl angle in Case 1 was 10.5 which is much higher than the critical swirl angle of 5. On the other hand, the maximum swirl angle in Case 5 was 4.9, as can be seen in table 4.2. The measured head losses through the trashracks and traveling screens are also shown in table 4.2 and plotted in figure At a river stage of EL 1051 ft, the total head loss through the clean trashracks and traveling screens was found to be about 1.0 ft and it generally decreased as the river stage increased, as can be seen in figure
25 Case 2 and Case 3 To obtain critical river stages for two different vacuum lift wall openings at which the intake vacuum system fails, Cases 2 and 3 were conducted under the as-built conditions. The river stage was gradually reduced from EL 1051 ft at an interval of 0.1 ft. With a 4-ft vacuum lift wall opening, small air bubbles started entering the vacuum chamber at a river stage of EL ft, and the vacuum system completely failed when the river stage was set at EL ft. When the vacuum lift gate was lowered by 1 ft (3 ft opening), this critical river stage value was found to be at EL ft. The critical river stage was reduced by only 0.3 ft by lowering the gate by 1 ft. It should be pointed out that because the mean velocity ratio by lowering the gate by 1 ft from a 4-ft opening to a 3-ft opening becomes 4/3, the head loss through the vacuum lift gate would become (4/3) 2 = 1.78 times larger when the gate is lowered. Case 4 and Case 8 Case 4 involved design and fabrication of a warm winter-discharge supply line downstream from the vacuum lift wall to feed a prototype discharge of 15,000 gpm to the vacuum chamber in an attempt to raise the critical sump water level in front of the vacuum lift wall. In the model, two 3-in. diameter warm-water supply lines were brought in just upstream from the vacuum lift walls, as shown in figure Each supply line was then connected to a 2-in. diameter and 10-in. long tee diffuser which was attached to the downstream face of the vacuum lift wall, as shown in figure On either side of the tee, a 2-1/2 in. long and 5/16-in. wide rectangular diffuser slot was provided. Each diffuser slot was located such that the discharge jet impinges downward against the vacuum lift wall at 45 to minimize flow disturbances. Because the higher water level within the vacuum chamber is maintained by vacuum, there is little differential head produced across the vacuum lift gate. Therefore, there should not be any flow moving upstream underneath the vacuum lift wall even if we supply warm water to the vacuum 21
26 chamber. Furthermore, surface flow disturbances produced by winter-water discharge had negative impacts on the critical low river stage under which the pumps operate satisfactorily. Unstable water-surface elevations within the vacuum chamber prohibited us from collecting any experimental data. Case 8 was tested for two discharges, 7,500 gpm and 15,000 gpm each. However, the surface disturbance produced by the warm discharge was found to cause airentrainment problems in which air was eventually withdrawn by the pump. Although the plant vacuum system may be able to lift the water level higher than 6 ft, it is still a major task to discharge warm water without creating surface disturbance within the vacuum chamber. We were unable to complete Case 8 due to this air-entrainment problem. Case 6 and Case 7 Tests similar to Cases 2 and 3 were conducted with the suction scoop in Cases 6 and 7. The test results were very similar to those obtained in Cases 2 and 3. The critical river stage when the vacuum lift gate opening was 4 ft was found to be EL ft, and that when the gate was lowered by 1 ft was EL ft. Head Loss Prediction Using the experimental data obtained in Case 1 and Case 5, head-loss coefficients through trashracks and traveling screens were obtained for these two cases. The head loss coefficient, λ, is defined by the following relationship: 2 V H = λ 2g (4.3) 22
27 where H is the head loss, and V 2 /2g is the velocity head based on the mean velocity (pump discharge divided by the pump-bay width and the water depth based on the river stage). Relationships between H and V 2 /2g for Case 1 and Case 5 are shown in figure Because the model scale is 1:12, extremely small head losses at higher river stages (for velocity heads lower than 0.03, approximately) were not able to be measured accurately. As can be seen in figure 4.15, the data are seen to scatter at lower head losses. Regression analyses produced λ = for the as-built condition (Case 1) and λ = for the suction-scoop case (Case 5) although the correlation coefficient in Case 5 was lower than that in Case 1. Note that these values are for clean trashracks and traveling screens. Summary The most convincing aspect of using the suction scoop developed for the Unit-3 intake is the fact that the suction scoop stabilizes the water surface elevation within the vacuum chamber. Under the as-built conditions, strong unsteady surging actions were found to occur within the vacuum chamber. It was estimated that the amplitude of this water surface surging was on the order of more than a foot in prototype dimensions. This type of unsteady surging is not good for pumps. Furthermore, the suction scoop reduced the swirl angle within the critical value of 5 and improved the pump-approach-flow distributions significantly as compared with the as-built pump-bay layout. Therefore, it is recommended that the suction scoop whose layout is shown in figure 4.9 be installed. 23
28 River Stage above MSL River Bed EL above MSL As-Built Condition - Unit-3 Intake (Case 1) Head Loss Through Clean Trash Racks (ft) Head Loss Through Clean Traveling Screens (ft) Total Head Loss Discharge Swirl Speed in CCW Direction Swirl Angle in CCW Direction (ft) (ft) (ft) (gpm) (rpm) (degree) , , , , , , , , River Stage above MSL River Bed EL above MSL Suction Scoop - Unit-3 Intake (Case 5) Head Loss Through Clean Trash Racks (ft) Head Loss Through Clean Traveling Screens (ft) Total Head Loss Discharge Swirl Speed in CCW Direction Swirl Angle in CCW Direction (ft) (ft) (ft) (gpm) (rpm) , , , , , , , , (degree) Table 4.2 A summary of test results for Cases 1 and 5 for the Unit-3 intake 24
29 Unit-3 Intake d:\gnn1\test results\q-h_ab1.spw (9-4-01) Q-H Relationship - As Built (Case 1) (Vacuum Liftwall Opening = 4 ft) Regression Curve Q-H Relationship with Suction Scoop (Case 5) (Vacuum Liftwall Opening = 4 ft) Regression Curve - Suction Scoop River Stage above MSL, H (ft) Discharge, Q (gpm) Figure 4.10 Discharge-river stage relationships obtained in Cases 1 and Unit-3 Intake d:\gnn1\test results\swirl.spw ( ) River Stage above MSL, H (ft) Case 1 - As Built Regression Curve for Case 1 Case 5 - Suction Scoop Regression Curve for Case Swirl, Ù (rpm) - Counterclockwise Figure 4.11 Swirl-river stage relationships obtained in Cases 1 and 5 25
30 1065 Unit-3 Intake (As-Built) d:\gnn1\test results\htr_ab.spw ( ) River Stage above MSL, H (ft) Through Trashracks Through Traveling Screens Total Loss Regression Curve for Total Loss Head Losses (ft) 1065 Unit-3 Intake (Suction Scoop) River Stage above MSL, H (ft) Through Trashracks Through Traveling Screens Total Loss Regression Curve for Total Loss Head Losses (ft) Figure 4.12 head losses measured in Cases 1 and 5 26
31 Figure 4.13 Warm-water supply lines through vacuum lift wall Figure 4.14 Diffusers in vacuum chamber seen through backwall window 27
32 1.2 Head Loss Through Trashracks & Traveling Screens Unit-3 Intake: Vacuum Lift Wall Opening = 4 ft Total Head Loss, H (ft) Measured Regression Line AS-BUILT (Case 1) H = 12.29(V 2 /2g) (r 2 = 0.95) Velocity Head, V 2 /2g (ft) 1.2 Total Head Loss, H (ft) Measured Regression Line SUCTION SCOOP (Case 5) H = 10.99(V 2 /2g) (r 2 = 0.79) Velocity Head, V 2 /2g (ft) Figure 4.15 Relationships between velocity head and total head obtained in Cases 1 and 5 28
33 V. SUCTION SCOOP DESIGNED AND TESTED FOR EXISTING UNIT-2 INTAKE The existing Unit-2 intake bays are 47 ft 6 in. long and 11 ft 2 in. wide, as shown in figure 5.1. The pump-suction bell shown in figure 5.2 is 80 in. in diameter and the floor clearance of the suction bell is 3 ft. The distance from the backwall to the center of the pump column is 5 ft 7 in. Similarly to the Unit-1 suction scoop, IIHR designed a suction scoop for the Unit 2 intake. As mentioned previously, the Unit-2 intake chamber is vacuum controlled to gain the net positive suction head and the pump-sump water surface is raised to EL 1056 ft which is 6 ft above the low water elevation of EL 1050 ft. The existing Unit-2 model constructed is shown in figures 5.3 through 5.6. As in the Unit-3 intake tests, test cases shown in table 5.1 were specified by MAEC. The suction scoop designed for the Unit-2 intake is shown in figures 5.7 (vacuum lift wall opening of 3 ft), including the following components: 1. Install a triangular-shaped floor splitter, 12 ft 6 in. long, 3 ft 6 in. wide, and 1 ft 9 in. tall in the center of the pump bay to suppress floor-attached subsurface vortices. 2. Install a triangular-shaped backwall splitter, 3 ft 6 in. wide, 1 ft 9 in. deep, and 3 ft tall, on the backwall to suppress flow circulations around the pump-suction bell. 3. Install two triangular-shaped sidewall floor-corner fillets, 12 ft 6 in. long, 1 ft 9 in. wide, and 1 ft 9 in. tall, along two sidewalls of the pump bay to suppress sidewallattached subsurface vortices. 4. Install a triangular-shaped, backwall floor corner fillet, 11 ft 2 in. long, 1 ft 9 in. wide, and 1 ft 9 in. tall, along the backwall floor corner to suppress backwallattached subsurface vortices. 5. Install two vertical triangular-shaped backwall corner fillets, 1 ft 9 in. wide, 1 ft 9 in. deep, and 3 ft tall, in two corners of the backwall to eliminate stagnant flow areas. 6. Install a suction-scoop ceiling (a 12 ft 6 in. long horizontal ceiling connected to a 4 ft 3/4 in. long sloping ceiling). A hole, slightly larger than the bell diameter, say, 0.5 in., should be bored in the horizontal ceiling and its gap should be sealed by a circular rubber gasket that is anchored to the bell mouth. 29
34 7. Install five, 2 ft long, flow-turning vanes at 1 ft 11 in. intervals underneath the sloping portion of the suction-scoop ceiling in order to straighten angular pumpapproach flows. The distance between the first and the last vanes from the sidewalls should be 1 ft 9 in. PLAN VIEW OF ONE BAY OF UNIT 2 47'-6" 18'-5" 11'-2" SECTION B-B EL ' EL ' 1'-3" FLOW 12'-10" 5'-7" CL VACUUM LIFT WALLS 1'-0" 29'-1" 12'-11" 9'-2 1/8" 5'-2" 4'-1/8" 3'-8 7/8" EL ' 1'-0" CL DISCHARGE PIPE VACUUM LIFT WALL (Adjustable) EL '' 47'-6" 29'-1" 12'-10" 5'-7" 12'-11" B 9'-2 1/8" 5'-2" 1'-0" CL A STOP A LOG EL ' 26'-4" C.L. Traveling Screen 3" 5'-7" 5'-7" B CL TRASHRACK 1'-3" 11'-2" 15'-0" 3'-0" C.L. of Traveling Screen MEAN HIGH WATER EL ' EL '-0" 10'-9" 29'-9" 2'-0" 2'-0" CONSTANT WATER LEVEL EL ' 7'-9" 6'-3" 9'-3" 4'-9" 2'-9" MEAN LOW WATER EL ' MIN. LOW WATER EL ' 2'-0" BULLNOSE 3'-0" 3'-3" EXTREME LOW WATER EL ' 12'-9" 2'-0" 1'-11 5/16" 13'-3" 3'-3" 3 2'-0" 32'-9" 12 21'-1 7/16" 11'-7 9/16" 32'-9" 3'-0" 9'-9" 8" 3'-0" 10" 10'-3" 6'-8" 2'-3" EL RIVER BED: EL ' R1'-0" " SECTION A-A Figure 5.1 Plan and elevation of existing Unit-2 intake bay 30
35 66.480" " PIPE O.D " " 4.500" 0.240" 0.240" 9.000" " PIPE I.D " " 9.000" " " " " " " " THROAT R28.200" " " " " " 80" DIAMETER SUCTION BELL FOR EXISTING UNIT 2 (PROTOTYPE DIMENSIONS) Figure 5.2 Pump suction-bell profile of existing Unit-2 intake pump Figure 5.3 Frontal view of the existing Unit 2 intake model 31
36 Figure 5.4 Rear view of existing Unit-2 intake model Figure 5.5 Side view of existing Unit-2 intake model 32
37 Figure 5.6 Rear view of model suction scoop for Unit-2 intake 33
38 SUCTION SCOOP DESIGNED FOR EXISTING GEORGE NEAL NORTH UNIT-2 INTAKE 16'-6" 1'-5" 2'-0" 2'-0" 1'-9" 9'-0" 1'-9" Backwall Floor Corner Fillet FLOW A 1'-9" 1'-11" 1'-11" 1'-11" 1'-11" 1'-9" Floor Splitter Five 2-ft Long Vanes B B C Ø6'-8 1/4" 6" D D A 1'-9" 2'-1" 3'-6" 2'-1" 1'-9" 11'-2" Sidewall Floor Corner Fillet C Backwall Splitter PLAN VIEW OF ONE BAY OF UNIT 2 (Suction scoop ceiling not shown) Vertical Backwall Corner Fillet 12'-4" 17'-11" 5'-7" CL Pump Column 1'-5" Sloping Ceiling (angle: 10 deg.) 4'-3/4" 6'-8 1/4" 12'-6" 6" 1'-3" 3'-0" 3'-8 1/2" 1'-3" 1'-9" 1'-9" 3'-0" 2'-0" 2'-0" 3'-6" 1'-9" 9'-0" 1'-9" SECTION A-A 1'-9" 1'-9" 1'-9" 1'-9" '-9" 1'-9" '-9" ( Dimensions) October 3, 2001 SECTION B-B SECTION C-C SECTION D-D Figure 5.7 Suction scoop layout designed for existing Unit-2 intake with 3-ft wall opening 34
39 Test Case For Unit 2 Intake Vacuum Lift Wall Opening Sump Condition: As-Built or Suction Scoop Winter Discharge Line (Yes/No) Task (ft) 1 3 As-Built No Produce (Q-H)/(H-Head Loss) curves 2 3 As-Built No Find critical river stage for safe vacuum chamber operation 3 2 As-Built No Find critical river stage for safe vacuum chamber operation 4 3 As-Built Yes Design and fabricate a winter discharge supply line downstream from the vacuum lift wall to supply a discharge of 15,000 gpm to the vacuum chamber/investigate its effect in raising the critical water depth in front of the vacuum lift gate for safe vacuum chamber operation NOT applicable based on the Unit-3 intake study 5 3 Suction Scoop No Produce (Q-H)/(H-Head Loss) curves 6 3 Suction Scoop No Find critical river stage for safe vacuum chamber operation 7 2 Suction Scoop No Find critical river stage for safe vacuum chamber operation *All test cases were conducted with model trashracks and traveling screens in place. Table 5.1 A summary of test conditions for the as-built conditions and with suction scoop conducted for existing Unit-2 intake Case 1 and Case 5 Table 5.2 shows the principal test results for Case 1 and Case 5 that were operated at different river stages between EL 1051 ft and EL 1058 ft. Under the as-built conditions there was a strong prerotation within the pump column at each river stage (note exclusively counterclockwise). The measured swirl angle varied between 1.3 for a river stage at EL 1058 ft and 5.2 at EL 1056 ft. The critical swirl angle for satisfactory pump operations is 5. When the suction scoop was in place, the swirl angle became very small, as shown in table 5.2. The maximum swirl angle, 2.1, was observed at the lowest river stage of EL 1051 ft. The suction scoop produced very stable vacuum-chamber conditions, as compared to those without the suction scoop in which the water surface elevation fluctuated considerably, approximately 6 in. to 1 ft in prototype dimensions. 35
40 There were no unstable water-surface surges with the suction scoop. The measured discharges and head losses in Cases 1 and 5 are also shown in table 5.2 and are plotted in figure 5.8 and 5.9, respectively. Cases 2 and 6 Cases 2 and 6 indicated that the critical river stage to operate the vacuum system safely without any air entrainment was at EL ft in both cases. Cases 3 and 7 When the vacuum lift wall is lowered to a 2-ft deep opening, the mean pumpapproach flow velocity through a 11 ft 2-in. wide and 2-ft high cross section becomes 6.48 ft/s (145 (cfs)/11.17 (ft)/2 (ft) = 6.48 ft/s) which is excessively high as pumpapproach flow velocity. The mean velocity for a 3-ft opening on the other hand is 4.32 ft/s (145 (cfs)/11.17 (ft)/3 (ft) = 4.32 ft/s). This means that the high velocity head will produce extremely high head losses at the vacuum lift wall when it is lowered to a 2-ft opening. Therefore, tests for Cases 3 and 7 were not conducted. MAEC was interested in lowering the vacuum lift wall to a 2-ft opening to secure safe pump operations under extremely low river stages. Based on their successful pump operations at a lift wall opening of 3 ft, MAEC was interested in lowering the pumping capacity from 65,000 gpm to 45,000 gpm at a lift wall opening of 2 ft, yielding a mean velocity through the opening of 4.49 ft/s which is comparable with that under the existing operation (65,000 gpm at a 3-ft lift wall opening). It should be noted that reduction of pumping capacity during the winter period does not significantly affect the power production because the river water temperature is extremely low during the winter. Therefore, new test cases different from Cases 3 and 7 for a vacuum lift wall opening of 2 ft were added to the study program, as shown in table 5.3. The suction scoop layout in these cases is shown in figure
41 River Stage above MSL EXISTING UNIT-2 INTAKE As-Built Condition - Existing Unit-2 Intake (Case 1) River Bed EL above MSL Head Loss Through Clean Trash Racks (ft) (1) Head Loss Through Clean Traveling Screens (ft) (2) Total Head Loss Discharge Swirl Speed in CW/CCW Direction Swirl Angle in CW/CCW Direction (ft) (ft) (ft) (gpm) (rpm) (degree) (1)+(2) , (CW) 3.2 (CW) , (CW) 3.4 (CW) , (CW) 3.8 (CW) , (CW) 4.6 (CW) , (CW) 4.7 (CW) , (CW) 5.2 (CW) , (CW) 3.7 (CW) , (CW) 1.3 (CW) River Stage above MSL River Bed EL above MSL Suction Scoop - Existing Unit-2 Intake (Case 5) Head Loss Through Clean Trash Racks (ft) (1) Head Loss Through Clean Traveling Screens Total Head Loss Discharge Swirl Speed in CW/CCW Direction Swirl Angle in CW/CCW Direction (ft) (ft) (ft) (ft) (gpm) (rpm) (degree) (2) (1)+(2) , (CW) 2.3 (CW) , (CW) 0.6 (CW) , (CCW) 0.9 (CCW) , (CW) 0.6 (CW) , (CW) 0.2 (CW) , (CCW) 0.3 (CCW) , (CCW) 0.3 (CCW) , (CCW) 2.1 (CCW) Table 5.2 A summary of test results for Cases 1 and 5 for the Unit-2 intake with a vacuum lift wall opening of 3 ft 37
42 Unit-2 Intake Q-H Relationship - As Built (Case 1) (Vacuum Lift Wall Opening = 3 ft) Q-H Relationship - Suction Scoop (Case 5) (Vacuum Lift Wall Opening = 3 ft) 1058 River Stage above MSL, H (ft) Discharge, Q (gpm) Figure 5.8 Discharge-river stage relationships obtained in Cases 1 and 5 38
43 Unit-2 Intake (As-Built) 1065 River Stage above MSL, H (ft) Through Trashracks Through Traveling Screens Total Loss Regression Curve for Total Loss Head Losses (ft) River Stage above MSL, H (ft) Unit-2 Intake (Suction Scoop) Through Trashracks Through Traveling Screens Total Loss Regression Curve for Total Loss Head Losses (ft) Figure 5.9 head losses measured in Cases 1 and 5 39
44 Existing Unit-2 Intake 2-ft Vacuum Lift Wall Opening & Lower Pump Discharge of 45,000 gpm Test Case For Unit-2 Intake Vacuum Lift Wall Opening Sump Condition: As- Built or Suction Scoop Task (ft) 1A 2 As-Built Produce (Q-H)/(H-Head Loss) curves 2A 2 As-Built Find critical river stage for safe vacuum chamber operation 5A 2 Suction Scoop Produce (Q-H)/(H-Head Loss) curves 6A 2 Suction Scoop Find critical river stage for safe vacuum chamber operation *All test cases were conducted with model trashracks and traveling screens in place. Table 5.3 A summary of test conditions for the as-built conditions and with suction scoop conducted for existing Unit-2 intake with a vacuum lift wall opening of 2 ft Cases 1A and 5A Case 1A was conducted for a river stage varying between EL ft and EL 1058 ft. The critical river stage which allows safe pump operation under the as-built condition was found to be EL ft. The test results are shown in table 5.4. The measured swirl angle varied between 3.1 for a river stage at EL 1052 ft and 7.7 at EL 1055 ft. The swirl angle with a river stage at EL ft was 1.5 and that at EL ft was 5.1. The lower swirl angle at EL ft was a result of the vortimeter rotating in both clockwise and counterclockwise directions. At the lowest river stage of EL ft, the prototype water-surface disturbance within the vacuum chamber was observed in the model. It is expected to be about 6 in. to 9 in. near the vacuum lift wall and about 1.5 in. near the backwall. The reason for the higher fluctuation near the lift wall as compared to the backwall is due to upward flows created by reverse flows after high velocity flows impinge the backwall and bounce back from the backwall. It should be pointed out that no surface disturbance was observed with the suction scoop in place. 40
Agitation and Mixing
Agitation and Mixing Agitation: Agitation refers to the induced motion of a material in a specified way, usually in a circulatory pattern inside some sort of container. Purpose is to make homogeneous phase.
More informationCENTRIFUGAL PUMPS. STATE the purposes of the following centrifugal pump components:
Pumps DOE-HDBK-1018/1-93 CENTRIFUGAL PUMPS CENTRIFUGAL PUMPS Centrifugal pumps are the most common type of pumps found in DOE facilities. Centrifugal pumps enjoy widespread application partly due to their
More informationFan Laws. Keith Miller. Samuel Tepp Associates. Paul Cenci, P. E.-Principal Brian England-Principal. Samuel Tepp Associates 1/6/10
Fan Laws Keith Miller Samuel Tepp Associates Paul Cenci, P. E.-Principal Brian England-Principal Basic Terms CFM - Cubic Feet per Minute, volume (amount) of air being moved SP - Static Pressure, resistance
More informationKerala, India. I. Introduction
Efficiency improvement of an axial flow propeller pump for dewatering in kole lands of Kerala, India Ayisha, M. 1, Jayan, P.R. 2, Nithin, J.G. 3 and Saranya, R.N 4 1 Department of Farm Power Machinery
More informationModeling of Ceiling Fan Based on Velocity Measurement for CFD Simulation of Airflow in Large Room
Modeling of Ceiling Fan Based on Velocity Measurement for CFD Simulation of Airflow in Large Room Y. Momoi 1, K. Sagara 1, T. Yamanaka 1 and H. Kotani 1 1 Osaka University, Graduate School of Eng., Dept.
More informationICSV14. Cairns Australia 9-12 July, Noise reduction of handheld vacuum cleaners according to geometric optimization of air passages
ICSV14 Cairns Australia 9-12 July, 2007 Noise reduction of handheld vacuum cleaners according to geometric optimization of air passages M.J. Mahjoob and H.Ashrafi Noise, Vibration, Acoustics (NVA) research
More informationCEE:3371 Principles of Hydraulics and Hydrology Project #2 Flow Measurement with a Weir
CEE:3371 Principles of Hydraulics and Hydrology Project #2 Flow Measurement with a Weir Problem Statement The Iowa DNR plans to monitor a proposed prairie restoration project in eastern Iowa as an experiment.
More informationFAN TYPES CENTRIFUGAL FAN Forward Curve Centrifugal Fan
FAN TYPES In order to cover a wide range of applications, fans are manufactured in a variety of type. They can be classified under three general types : (a) Centrifugal, (b) Axial and (c) Mixed flow. Table
More informationDesign And Analysis Of Centrifugal Pump
Design And Analysis Of Centrifugal Pump GUIDED BY: Assistant Professor Jayendra B. Patel PRESENTED BY: Makwana Hardik Modh Hiren Patel Gaurang Patel Dhaval 1 Introduction It Convert the mechanical energy
More informationHeat Transfer in Evacuated Tubular Solar Collectors
Heat Transfer in Evacuated Tubular Solar Collectors Graham L. Morrison, Indra Budihardjo and Masud Behnia School of Mechanical and Manufacturing Engineering University of New South Wales Sydney 2052 Australia
More informationMECHANICAL SCIENCE Module 2 Heat Exchangers
Department of Energy Fundamentals Handbook MECHANICAL SCIENCE Module 2 Heat Exchangers Heat Exchangers DOE-HDBK-1018/1-93 TABLE OF CONTENTS TABLE OF CONTENTS LIST OF FIGURES... ii LIST OF TABLES... iii
More informationFans: Features and Analysis
Technical Development Program COMMERCIAL HVAC EQUIPMENT Fans: Features and Analysis PRESENTED BY: Michael Ho Version 1.2 Menu Section 1 Section 2 Section 3 Section 4 Section 5 Section 6 Section 7 Section
More informationWater engineers and utilities are often
FWRJ Horizontal or Vertical? High-Service Pump Selection Mark Ludwigson, Len Rago, and Jeff Greenfield Water engineers and utilities are often faced with a decision concerning the best type of pump when
More informationwe make air move Double Inlet Centrifugal Fans (Forward Curved) FBD Series (Square Outlet Metric Size)
we make air move Double Inlet Centrifugal Fans (Forward Curved) FBD Series (Square Outlet Metric Size) www.blowtech.in we make air move Blowtech Air Devices Pvt. Ltd. was founded in 1988 and quickly established
More informationThe Role of Computational Fluid Dynamic and Aeroacoustic Simulations in Reducing the Noise of a Forward-Curved Blade Radial Fan
The Role of Computational Fluid Dynamic and Aeroacoustic Simulations in Reducing the Noise of a Forward-Curved Blade Radial Fan Manoochehr Darvish Bastian Tietjen Stefan Frank darvish@htw-berlin.de tietjen@htw-berlin.de
More informationConceptual Design of a Better Heat Pump Compressor for Northern Climates
Purdue University Purdue e-pubs International Compressor Engineering Conference School of Mechanical Engineering 1976 Conceptual Design of a Better Heat Pump Compressor for Northern Climates D. Squarer
More informationEffect of Flow Distortion in Inlet Duct on the Performance of Centrifugal Blower
Effect of Flow Distortion in Inlet Duct on the Performance of Centrifugal Blower Kalpesh W. Shirsath 1, S.R. Patil 2, Sumit M. Naik 3 PG Student 1,3, Assistant Professor 2 Department of Mechanical Engineering
More informationInterSeptor Centrifugal Separators Operating & Maintenance Manual
General Information: This manual was prepared to assist in the installation, operation, and maintenance of PEP ICS centrifugal separator systems. For immediate response to questions not covered in this
More informationEXPERIMENTAL PERFORMANCE INVESTIGATION OF SWIRLING FLOW ENHANCEMENT ON FLUIDIZED BED DRYER
EXPERIMENTAL PERFORMANCE INVESTIGATION OF SWIRLING FLOW ENHANCEMENT ON FLUIDIZED BED DRYER P. Sundaram and P. Sudhakar Department of Mechanical Engineering, SRM University, Kattankulathur, Chennai, India
More informationSmoke Layer Height and Heat Flow through a Door
Smoke Layer Height and Heat Flow through a Door 2018 Smoke Layer Height and Heat Flow through a Door In this tutorial you will simulate a growing fire in the corner of a 5m x 5m room. The room has a 1m
More informationIn-Field Quantification of Fan Performance in Tunnel-Ventilated Freestall Barns ABSTRACT INTRODUCTION
In-Field Quantification of Fan Performance in Tunnel-Ventilated Freestall Barns by Katherine Lankering, Research Associate Curt Gooch, P.E., Senior Extension Associate Scott Inglis, Research Associate
More informationHigh Performance Diesel Fueled Cabin Heater. Abstract
High Performance Diesel Fueled Cabin Heater Tom Butcher and James Wegrzyn Energy Science and Technology Division Building 526 Upton, N.Y. 11973 Brookhaven National Laboratory Abstract Recent DOE-OHVT studies
More informationTHE CONTROL METHOD OF THE INFLOW TURBU- LENCE INTERACTION NOISE FOR ROUTER COOLING FAN
The 21 st International Congress on Sound and Vibration 13-17 July, 2014, Beijing/China THE CONTROL METHOD OF THE INFLOW TURBU- LENCE INTERACTION NOISE FOR ROUTER COOLING FAN Yingbo Xu, Xiaodong Li School
More informationA STUDY ON COMPACT HEAT EXCHANGERS AND PERFORMANCE ANALYSIS
A STUDY ON COMPACT HEAT EXCHANGERS AND PERFORMANCE ANALYSIS V. BHOGESWARA RAO Research Scholar Email:pallivayala@gmail.com Dr. S. CHAKRADHAR GOUD Principal, Sri Sarada Institute of Science and Technology
More information2. HEAT EXCHANGERS MESA
1. INTRODUCTION Multiport minichannel and microchannel aluminium tubes are becoming more popular as components in heat exchangers. These heat exchangers are used in various industrial applications and
More informationRefinery Vacuum Towers. State of the Art. (Extended Abstract)
Paper 357b Refinery Vacuum Towers State of the Art (Extended Abstract) Andrew W. Sloley CH2M HILL 21 Bellwether Way, Unit 111 Bellingham, WA 98225 Prepared for Presentation at the American Institute of
More informationThe Performance of Thermocompressors as Related to Paper Machine Dryer Drainage Systems
The Performance of Thermocompressors as Related to Paper Machine Drainage Systems C. G. Blatchley and H. J. Stratton Schutte and Koerting, Bensalem, Bucks County, PA Thermocompressors have been successfully
More information2 A e ( I ( ω t k r)
Introduction : Baffle Step Response Calculations Over the past few years, I have become very aware of the baffle step response phenomenon associated with drivers mounted in rectangular baffles. My first
More informationThermal Performance Enhancement of Inclined Rib Roughness Solar Air Heater
Thermal Performance Enhancement of Inclined Rib Roughness Solar Air Heater Gurpreet Singh and Satwant Singh Lala Lajpat Rai Institute of Engineering and Technology, Moga (Punjab) 142001 Abstract : Artificial
More informationSTAFFORD TRACT NORTH OF US90A 1.0 INTRODUCTION 1.1 OBJECTIVE
1.0 INTRODUCTION 1.1 OBJECTIVE This report, prepared for submittal to TxDOT, analyzes existing and proposed detention facilities draining into the TxDOT US90A storm sewer system. The results of the detailed
More informationFinned Heat Sinks for Cooling Outdoor Electronics under Natural Convection
Finned s for Cooling Outdoor Electronics under Natural Convection Lian-Tuu Yeh, Ph D & PE Thermal Consultant, Dallas, TX, 75252 USA Abstract For tower or poled mounted electronics, the heat sink weight
More informationDRAFT ONONDAGA LAKE CAPPING AND DREDGE AREA AND DEPTH INITIAL DESIGN SUBMITTAL H.3 STATIC SLOPE STABILITY ANALYSES
DRAFT ONONDAGA LAKE CAPPING AND DREDGE AREA AND DEPTH INITIAL DESIGN SUBMITTAL H.3 STATIC SLOPE STABILITY ANALYSES Parsons P:\Honeywell -SYR\444576 2008 Capping\09 Reports\9.3 December 2009_Capping and
More informationRESPONSE OF ANCHOR IN TWO-PHASE MATERIAL UNDER UPLIFT
IGC 29, Guntur, INDIA RESPONSE OF ANCHOR IN TWO-PHASE MATERIAL UNDER UPLIFT K. Ilamparuthi Professor and Head, Division of Soil Mechanics and Foundation Engineering, Anna University, Chennai 25, India.
More informationOptimized Finned Heat Sinks for Natural Convection Cooling of Outdoor Electronics
Journal of Electronics and Information Science (2018) 3: 22-33 Clausius Scientific Press, Canada Optimized Finned Heat Sinks for Natural Convection Cooling of Outdoor Electronics Lian-Tuu Yeh, ASME Fellow
More informationAXICO ANTI-STALL CONTROLLABLE PITCH-IN-MOTION AND ADJUSTABLE PITCH-AT-REST VANEAXIAL FANS
Twin City Fan INDUSTRIAL PROCESS AND COMMERCIAL VENTILATION SYSTEMS AXICO ANTI-STALL CONTROLLABLE PITCH-IN-MOTION AND ADJUSTABLE PITCH-AT-REST VANEAXIAL FANS FPAC FPMC FPDA CATALOG AX351 JULY 2001 WWW.TCF.COM
More informationCHECK VALVES INSTALLATION
CHECK VALVES 35 CHECK VALVES APPLICATIONS The check valves illustrated herein are designed for use with refrigerant fluids CFC, HCFC and HFC. Castel check valves can be used on any section of a refrigerating
More informationRotodynamic Pumps INTRODUCTION:
Rotodynamic Pumps INTRODUCTION: Liquids have to be moved from one location to another and one level to another in domestic, agricultural and industrial spheres. The liquid is more often water in the domestic
More informationSlope stability assessment
Engineering manual No. 25 Updated: 03/2018 Slope stability assessment Program: FEM File: Demo_manual_25.gmk The objective of this manual is to analyse the slope stability degree (factor of safety) using
More informationDynamic Simulation of a CFB Boiler System
71th IEA-FBC Technical Meeting Dynamic Simulation of a CFB Boiler System 2015. 11. 05, Seoul, Korea Sang Min CHOI Thermal Engineering Lab Thermal Engineering Laboratory KAIST Introduction Dynamic Performance
More informationSCHULTE & ASSOCIATES Building Code Consultants 880D Forest Avenue Evanston, IL /
SCHULTE & ASSOCIATES Building Code Consultants 880D Forest Avenue Evanston, IL 60202 fpeschulte@aol.com 504/220-7475 A CRITIQUE OF HUGHES ASSOCIATES, INC. PAPER TITLED: Analysis of the Performance of Ganged
More informationExperimental Investigation of Elliptical Tube Bank Cross Flow Heat Exchanger with Inline Arrangement & 45 Angle of Attack
Experimental Investigation of Elliptical Tube Bank Cross Flow Heat Exchanger with Inline Arrangement & 45 Angle of Attack #1 Digvijay A. Shelar, #2 N.S. Gohel, #3 R. S. Jha #1 Mechanical Engineering Department,
More informationExperimental study on heat transfer characteristics of horizontal concentric tube using twisted wire brush inserts
International Journal of Current Engineering and Technology E-ISSN 2277 416, P-ISSN 2347 5161 216 INPRESSCO, All Rights Reserved Available at http://inpressco.com/category/ijcet Research Article Experimental
More informationSANTA ROSA FIRE DEPARTMENT FIRE PREVENTION BUREAU PLAN REVIEW CHECKLIST
July 1, 2010 SANTA ROSA FIRE DEPARTMENT FIRE PREVENTION BUREAU PLAN REVIEW CHECKLIST FIRE PUMP REVIEW Address: Permit #: Inspector: Date: Status: Inspector: Date: Status: A-Approved; AC-Approved w/comments;
More informationHeat transfer enhancement in an air process heater using semi-circular hollow baffles
Available online at www.sciencedirect.com Procedia Engineering 56 ( 2013 ) 357 362 5 th BSME International Conference on Thermal Engineering Heat transfer enhancement in an air process heater using semi-circular
More informationEAT 212 SOIL MECHANICS
EAT 212 SOIL MECHANICS Chapter 4: SHEAR STRENGTH OF SOIL PREPARED BY SHAMILAH ANUDAI@ANUAR CONTENT Shear failure in soil Drained and Undrained condition Mohr-coulomb failure Shear strength of saturated
More informationROTARY DRYER CONSTRUCTION
ROTARY DRYER The Rotary Dryer is a type of industrial dryer employed to reduce or to minimize the liquid moisture content of the material it is handling by bringing it into direct contact with a heated
More informationFan Performance and Selection. Overview
Fan Performance and Selection References Burmeister, L.C., Elements of Thermal-Fluid System Design, Prentice Hall, 1998. ASHRAE Handbook: HVAC Systems and Equipment, 1992. Overview Common fan types: centrifugal
More informationSelecting Circulators TD10 EFFECTIVE: SUPERSEDES:
TACO COMFORT SOLUTIONS : HOME HEATING BASICS Selecting Circulators TD EFFECTIVE:.3. SUPERSEDES:.. This article shows you how to select a Taco circulator that lets the hydronic system you re designing perform
More informationHigh-efficiency Turbo Chiller (NART Series)
67 High-efficiency Turbo Chiller (NART Series) Wataru Seki* 1 Kenji Ueda* 1 Jyou Masutani* 2 Yoichirou Iritani* 2 Turbo chillers are widely used for district heating and cooling, heat storage (regeneration)
More informationEffects of Volute Tongue Clearance and Rotational Speed on Performance of Centrifugal Blower Nitin S. Jadhav *, S. R. Patil
2016 IJSRSET Volume 2 Issue 4 Print ISSN : 2395-1990 Online ISSN : 2394-4099 Themed Section: Engineering and Technology Effects of Volute Tongue Clearance and Rotational Speed on Performance of Centrifugal
More informationMultistage Centrifugal Pumps with Shaft Sealing Type HZ / HZA / HZAR
Multistage Centrifugal Pumps with Shaft Sealing Type HZ / HZA / HZAR General DICKOW-pumps of series HZ/HZA are single- or multistage centrifugal pumps with shaft sealing. Application HZ/HZA-pumps are applied
More informationFLIGHT UNLOADING IN ROTARY SUGAR DRYERS. P.F. BRITTON, P.A. SCHNEIDER and M.E. SHEEHAN. James Cook University
FLIGHT UNLOADING IN ROTARY SUGAR DRYERS By P.F. BRITTON, P.A. SCHNEIDER and M.E. SHEEHAN James Cook University Paul.Britton@jcu.edu.au, Phil.Schnieder@jcu.edu.au, Madoc.Sheehan@jcu.edu.au Keywords: Drying,
More informationPOWER VENTER SYSTEM. Model: PVO-300, PVO-600
POWER VENTER SYSTEM Model: PVO-300, PVO-600 Included is one ETL and cetl listed Power Venter to be used primarily with a single 120VAC controlled oil fired furnace, boiler, or water heater. The PVO may
More informationVisualization of Evaporatively Cooled Heat Exchanger Wetted Fin Area
Purdue University Purdue e-pubs International Refrigeration and Air Conditioning Conference School of Mechanical Engineering 2014 Visualization of Evaporatively Cooled Heat Exchanger Wetted Fin Area Sahil
More informationINFLUENCE OF SOLAR RADIATION AND VENTILATION CONDITIONS ON HEAT BALANCE AND THERMAL COMFORT CONDITIONS IN LIVING-ROOMS
INFLUENCE OF SOLAR RADIATION AND VENTILATION CONDITIONS ON HEAT BALANCE AND THERMAL COMFORT CONDITIONS IN LIVING-ROOMS Staņislavs GENDELIS, Andris JAKOVIČS Laboratory for mathematical modelling of environmental
More informationCFD Analysis of a 24 Hour Operating Solar Refrigeration Absorption Technology
IJIRST International Journal for Innovative Research in Science & Technology Volume 1 Issue 11 April 2015 ISSN (online): 2349-6010 CFD Analysis of a 24 Hour Operating Solar Refrigeration Absorption Technology
More informationCHAPTER 2 EXPERIMENTAL APPARATUS AND PROCEDURES
CHAPTER 2 EXPERIMENTAL APPARATUS AND PROCEDURES The experimental system established in the present study to investigate the transient flow boiling heat transfer and associated bubble characteristics of
More informationPVE SERIES POWER VENTER SYSTEM MANUAL
PVE SERIES POWER VENTER SYSTEM MANUAL Contents Page I. Typical Venting System Components 2 II. System Operation 3 III. Power Venter Sizing 3,4 IV. Installation Safety Instructions 5,6 V. Installation of
More informationOperator s Manual. Linear Asphalt Compactor. Jesse D. Doyle Isaac L. Howard, PhD Mississippi State University. January 2010 CMRC M 10-1 Version 1
Operator s Manual Linear Asphalt Compactor Mississippi Department of Transportation Jesse D. Doyle Isaac L. Howard, PhD Mississippi State University An Industry, Agency & University Partnership January
More informationDrive Power and Torque in Paper Machine Dryers
Drive Power and Torque in Paper Machine Dryers 2 nd Edition Gregory L. Wedel President Kadant Johnson Inc. Gerald L. Timm Vice President, Research & Development Kadant Johnson Inc. Technical White Paper
More informationSSRG International Journal of Thermal Engineering (SSRG-IJTE) volume 1 Issue1 Jan to April 2015
Time Domain Sound Spectrum Measurements in Ducted Axial Fan under Stall Region Dr.S.Divya Sree, B.Yuvan Asst. Prof., M.Tech Student, Thermal Engineering, University of Calicut ABSTRACT: An axial fan is
More informationStudy on the Effect of Blade Angle on the Performance of a Small Cooling Tower
Kasetsart J. (Nat. Sci.) 42 : 378-384 (2008) Study on the Effect of Blade Angle on the Performance of a Small Cooling Tower Montri Pirunkaset* and Santi Laksitanonta ABSTRACT This paper presents the effect
More informationA Novel Approach for the Thermal Management. of PC Power Supply
ISTP-16, 005, PRAGUE 16 TH INTERNATIONAL SYMPOSIUM ON TRANSPORT PHENOMENA A Novel Approach for the Thermal Management of PC Power Supply Fu-Sheng Chuang*, Sheam-Chyun Lin, Jon-Ting Kuo, Chien-An Chou Department
More informationDevelopment of Motor Fan Noise Prediction Method in Consideration of Operating Temperature during Engine Idling
New technologies Development of Motor Fan Noise Prediction Method in Consideration of Operating Temperature during Engine Idling Yasuhito Suzuki* Masahiro Shimizu* Abstract In these years there is an increasing
More information2nd International Workshop. Labyrinth and Piano Key Weirs Paris - Chatou, France November 2013
2nd International Workshop on Labyrinth and Piano Key Weirs Paris - Chatou, France 20-22 November 2013 Improvement of the form of labyrinth weirs Ahmed OUAMANE François LEMPERIERE Laboratory of hydraulic
More informationNumerical Stability Analysis of a Natural Circulation Steam Generator with a Non-uniform Heating Profile over the tube length
Numerical Stability Analysis of a Natural Circulation Steam Generator with a Non-uniform Heating Profile over the tube length HEIMO WALTER Institute for Thermodynamics and Energy Conversion Vienna University
More informationSelection V 1 INTRODUCTION PAGE V-2 V 2 SUMP/WELL PUMP SELECTION GUIDE PAGE V-3 V 3 CAN PUMP SELECTION GUIDE PAGE V-4
V Selection V 1 INTRODUCTION PAGE V-2 V 2 SUMP/WELL PUMP SELECTION GUIDE PAGE V-3 V 3 CAN PUMP SELECTION GUIDE PAGE V-4 V 4 SUBMERSIBLE PUMP SELECTION GUIDE PAGE V-5 V 5 LOW LIFT PUMP SELECTION GUIDE PAGE
More informationGIVE A FAN A CHANCE Installation Dos & Don ts
GIVE A FAN A CHANCE Installation Dos & Don ts 1 Give a Fan a Chance Installation Dos & Don ts Choosing the right fan for the right application is paramount, which is why every product in our range is designed
More informationStudy of air circulation inside the oven by computational fluid dynamics.
The 8 th International TIChE Conference (ITIChE 2018) "Designing Tomorrow Towards Sustainable Engineering and Technology" @A-ONE The Royal Cruise Hotel Pattaya, Thailand, November 8-9, 2018 Study of air
More informationEXPERIMENTAL AND CFD STUDIES ON SURFACE CONDENSATION
Eighth International IBPSA Conference Eindhoven, Netherlands August 11-14, 2003 EXPERIMENTAL AND CFD STUDIES ON SURFACE CONDENSATION Liu Jing 1, Yoshihiro Aizawa 2, Hiroshi Yoshino 3 1 School of Municipal
More informationWater Piping and Pumps
Technical Development Program DISTRIBUTION SYSTEMS Water Piping and Pumps PRESENTED BY: Michael Ho carriertdp@gmail.com 424-262-2144 Menu Section 1 Section 2 Section 3 Section 4 Section 5 Section 6 Section
More informationModeling and Simulation of Axial Fan Using CFD Hemant Kumawat
Modeling and Simulation of Axial Fan Using CFD Hemant Kumawat Abstract Axial flow fans, while incapable of developing high pressures, they are well suitable for handling large volumes of air at relatively
More informationCHAPTER I INTRODUCTION. In the modern life, electronic equipments have made their way
1 CHAPTER I INTRODUCTION In the modern life, electronic equipments have made their way in to practically every part, which is from electronic gadgets to high power computers. Electronic components have
More informationExperimental study of the influence of geometrical parameters on the cavitation of a small centrifugal pump
Fluid Structure Interaction and Moving Boundary Problems 89 Experimental study of the influence of geometrical parameters on the cavitation of a small centrifugal pump A. Nemdili Laboratory LRTTFC, Department
More informationHeat Transfer Enhancement using Herringbone wavy & Smooth Wavy fin Heat Exchanger for Hydraulic Oil Cooling
Enhancement using Herringbone wavy & Smooth Wavy fin Exchanger for Hydraulic Oil Cooling 1 Mr. Ketan C. Prasadi, 2 Prof. A.M. Patil 1 M.E. Student, P.V.P.I.T.,Budhagaon,Sangli AP-India 2 Associate Professor,
More informationSome Modeling Improvements for Unitary Air Conditioners and Heat Pumps at Off-Design Conditions
Purdue University Purdue e-pubs International Refrigeration and Air Conditioning Conference School of Mechanical Engineering 2006 Some Modeling Improvements for Unitary Air Conditioners and Heat Pumps
More informationFAN ENGINEERING. Surge, Stall and Instabilities in Fans
FAN ENGINEERING Industrial Fans & Services Information and Recommendations for the Engineer Surge, Stall and Instabilities in Fans Introduction Users of fan systems would like to experience a steady, continuous
More informationDevelopment of Large Size Hybrid Fan
Technical Paper Toshihiko Nishiyama Kengo Koshimizu Keiichi Inaba A lot of small fans with three-dimensional, wide chord length, forward swept figure, and/or shroud ring have been developed and manufactured
More informationInstallation, Operation and Maintenance Guide. Steam Coil Installation, Operation and Maintenance. steam coils
Installation, Operation and Maintenance Guide Steam Coil Installation, Operation and Maintenance Guidelines for the installation, operation and maintenance of the Heatcraft brand of steam heating coils
More informationExposed geomembrane covers: Part 1 - geomembrane stresses
Exposed geomembrane covers: Part 1 - geomembrane stresses By Gregory N. Richardson, Ph.D. P.E., principal of GN Richardson and Assoc. During the late 1980s and early 1990s, many mixed-waste disposal areas
More informationEnergy Conservation with PARAG Energy Efficient Axial Flow FRP Fans
PARAG FANS & COOLING SYSTEMS LTD. Energy Conservation with PARAG Energy Efficient Axial Flow FRP Fans Registered Office & Works Plot No.1/2B & 1B/3A, Industrial Area No.1 A.B.Road, Dewas 455001 (M.P.)
More informationTheoretical and Experimental Analysis of the Superheating in Heat Pump Compressors. * Corresponding Author ABSTRACT 1.
568, Page Theoretical and Experimental Analysis of the Superheating in Heat Pump Compressors Jose N. FONSECA *, Rodrigo KREMER, Thiago DUTRA 2 EMBRACO, Research & Development Group, Joinville, Santa Catarina,
More informationINSTALLATION DO S AND DON TS
4.0 NOISE CONTROL Figure 4.1. - Transitions Abrupt transitions immediately adjacent to an attenuator will cause the attenuator pressure drop to increase. Ensure transitions close to attenuators are gradual
More informationPhysical Mechanism of Convection. Conduction and convection are similar in that both mechanisms require the presence of a material medium.
Convection 1 Physical Mechanism of Convection Conduction and convection are similar in that both mechanisms require the presence of a material medium. But they are different in that convection requires
More informationKeywords: slope stability, numerical analysis, rainfall, infiltration. Yu. Ando 1, Kentaro. Suda 2, Shinji. Konishi 3 and Hirokazu.
Proceedings of Slope 25, September 27-3 th 25 SLOPE STABLITY ANALYSIS REGARDING RAINFALL-INDUCED LANDSLIDES BY COUPLING SATURATED-UNSATURATED SEEPAGE ANALYSIS AND RIGID PLASTIC FINITE ELEMENT METHOD Yu.
More informationNumerical Analysis of the Bearing Capacity of Strip Footing Adjacent to Slope
International Journal of Science and Engineering Investigations vol. 4, issue 46, November 25 ISSN: 225-8843 Numerical Analysis of the Bearing Capacity of Strip Footing Adjacent to Slope Mohammadreza Hamzehpour
More informationCERBERUS: A NEW MODEL TO ESTIMATE SIZE AND SPREAD FOR FIRES IN TUNNELS WITH LONGITUDINAL VENTILATION
- 69 - CERBERUS: A NEW MODEL TO ESTIMATE SIZE AND SPREAD FOR FIRES IN TUNNELS WITH LONGITUDINAL VENTILATION R.O. Carvel, A.N. Beard & P.W. Jowitt Department of Civil and Offshore Engineering, Heriot-Watt
More informationME 410 MECHANICAL ENGINEERING SYSTEMS LABORATORY MASS & ENERGY BALANCES IN PSYCHROMETRIC PROCESSES EXPERIMENT 3
ME 410 MECHANICAL ENGINEERING SYSTEMS LABORATORY MASS & ENERGY BALANCES IN PSYCHROMETRIC PROCESSES EXPERIMENT 3 1. OBJECTIVE The objective of this experiment is to observe four basic psychrometric processes
More informationPlan Submittal Checklist
City of Aurora Public Works Department HIGH-PILED COMBUSTIBLE STORAGE Plan Submittal Checklist Building Division 15151 E. Alameda Parkway, Ste 2400 Aurora, CO 80012 303-739-7420 Fax: 303-739-7551 Project
More informationFan Selection. and Energy Savings
Fan Selection and Energy Savings Reducing power consumption by minimizing system pressure loss and choosing the right equipment HBy BRIAN MLEZIVA Greenheck Fan Corp. Schofield, Wis. Power Consumption HVAC
More informationPerformance Comparison of Ejector Expansion Refrigeration Cycle with Throttled Expansion Cycle Using R-170 as Refrigerant
International Journal of Scientific and Research Publications, Volume 4, Issue 7, July 2014 1 Performance Comparison of Ejector Expansion Refrigeration Cycle with Throttled Expansion Cycle Using R-170
More informationBy: D K Singhal
Suggestive Improvements in Yankee Internal Design By: D K Singhal deveshksinghal@gmail.com Objective The objective of this presentation is to indicate the possibility of a modified design yankee tray for
More informationOSCAR-LOWeFLOW Treatment System Design Manual January 2018
! OSCAR-LOWeFLOW Treatment System Design Manual January 2018 Manufactured by: Lowridge Onsite Technologies PO Box 1179 Lake Stevens, WA 98258 877 476-8823 info@lowridgetech.com!1 Introduction: This manual
More informationEXPERIMENTAL STUDY OF CENTRIFUGAL HUMIDIFIER FITTED IN AN INDUSTRIAL SHED LOCATED IN TROPICAL CLIMATES
THERMAL SCIENCE, Year 2011, Vol. 15, No. 2, pp. 467-475 467 EXPERIMENTAL STUDY OF CENTRIFUGAL HUMIDIFIER FITTED IN AN INDUSTRIAL SHED LOCATED IN TROPICAL CLIMATES by Krishnasamy SENTHILKUMAR a* and Pss
More informationWater Pumps. turbo-hydraulic pumps, positive-displacement pumps.
WATER PUMPS Water Pumps Water pumps are devices designed to convert mechanical energy to hydraulic energy. All forms of water pumps may be classified into two basic categories: turbo-hydraulic pumps, positive-displacement
More informationGear Tooth Profile Error caused by Hob Misalignment
AIJSTPME (2013) 6(1): 51-55 Gear Tooth Profile Error caused by Hob Misalignment Satayotin K. Pathumwan Institute of Technology, Bangkok, Thailand Email address: kosuchon@ptwit.ac.th Prachprayoon P. Pathumwan
More informationTITLE: Improvement in Heat Transfer Rate and Dynamics of Shrouded Fanned Radiator System
TITLE: Improvement in Heat Transfer Rate and Dynamics of Shrouded Fanned Radiator System Prof. G.L.Allampallewar 1, Divyal P. Bagul 2, Abhiraj S. Galande 3, Amol M. Rathod 4, Ketan R. Behere 5. 1 Assistant
More informationIntroduction to Fans. The Basics of Fan Principles and Terminology
Introduction to Fans The Basics of Fan Principles and Terminology Airflow Principles A fan is a rotating device that creates pressure differential that results in air movement Pressure rise in a fan Downstream
More informationPOWER VENTER. Model: PVE Series
POWER VENTER Model: PVE Series CONTENTS Typical Venting System Components... System Operation... Power Venter Sizing... Installation Safety Instructions... Installation of Power Venter... Connecting Power
More informationPumps for Florida Irrigation and Drainage Systems 1
CIR832 1 Dorota Z. Haman 2 The primary function of a pump is to transfer energy from a power source to a fluid, and as a result to create flow, lift, or greater pressure on the fluid. A pump can impart
More information