text:
Eggs Benedict
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Eggs Benedict
Course
Breakfast, brunch
Place of origin
New York City, United States
Main ingredients
Eggs, English muffin, Canadian bacon, hollandaise sauce
Variations
multiple
Cookbook: Eggs Benedict Media: Eggs Benedict
Eggs Benedict is a traditional American brunch or breakfast dish that consists of two halves of an English muffin each of which is topped with Canadian bacon, ham or sometimes bacon, a poached egg, and hollandaise sauce. The dish was first popularized in New York City. Many variations on the basic recipe are served.
Contents
[hide]
1 Origin
2 Variations
3 See also
4 References
5 External links
Origin[edit]
There are conflicting accounts as to the origin of Eggs Benedict.
Delmonico's in lower Manhattan claims on its menu that "Eggs Benedict was first created in our ovens in 1860."[1] One of its former chefs, Charles Ranhofer, also published the recipe for Eggs à la Benedick in 1894.[2]
In an interview recorded in the "Talk of the Town" column of The New Yorker in 1942, the year before his death,[3] Lemuel Benedict, a retired Wall Street stock broker, claimed that he had wandered into the Waldorf Hotel in 1894 and, hoping to find a cure for his morning hangover, ordered "buttered toast, poached eggs, crisp bacon, and a hooker of hollandaise". Oscar Tschirky, the famed maître d'hôtel, was so impressed with the dish that he put it on the breakfast and luncheon menus but substituted ham for the bacon and a toasted English muffin for the toast.[4]
Eggs Benedict with smoked salmon in place of Canadian bacon, also known as Eggs Royale
Another, later claim to the creation of Eggs Benedict was circuitously made by Edward P. Montgomery on behalf of Commodore E. C. Benedict. In 1967 Montgomery wrote a letter to then The New York Times food columnist Craig Claiborne which included a recipe he claimed to have received through his uncle, a friend of the commodore. Commodore Benedict's recipe — by way of Montgomery — varies greatly from Ranhofer's version, particularly in the hollandaise sauce preparation — calling for the addition of a "hot, hard-cooked egg and ham mixture".[5]
Variations[edit]
Eggs Benedict with bacon
Several variations of Eggs Benedict exist.
Eggs Blackstone substitutes streaky bacon for the ham and adds a tomato slice.[6][7][8]
Eggs Blanchard substitutes Béchamel sauce for Hollandaise.[9]
Eggs Florentine substitutes spinach for the ham or adds it underneath.[10][11][12] Older versions of eggs Florentine add spinach to poached or shirred eggs.
Eggs Chesapeake substitutes a Maryland blue crab cake in place of the ham.[13]
Eggs Mornay substitutes Mornay (cheese) sauce for the Hollandaise.[14]
Eggs Trivette adds Creole mustard to the Hollandaise and adds a topping of Crayfish.[15]
Eggs Omar (also known as a steak benedict) substitutes a small steak in place of the ham, and sometimes replaces the hollandaise with béarnaise.
Eggs Atlantic, Eggs Hemingway,[16] or Eggs Copenhagen (also known as Eggs Royale and Eggs Montreal in New Zealand) substitutes salmon or smoked salmon for the ham. This is a common variation found in Australia, New Zealand, Canada and the United Kingdom.[17] This is also known as "Eggs Benjamin" in some restaurants in Canada.[18]
Huevos Benedictos substitutes sliced avocado and/or Mexican chorizo for the ham, and is topped with both a salsa (such as salsa roja or salsa brava) and hollandaise sauce.[19]
Eggs Hussarde substitutes Holland rusks for the English muffin and adds Bordelaise sauce.[20][21]
Irish Benedict replaces the ham with corned beef or Irish bacon.[22][23][24]
Dutch Benedict replaces the ham or bacon with scrapple. Popular in the eastern region of Pennsylvania.[25]
Eggs Hebridean replaces the ham with black pudding,[26] often from Stornoway.[27]
Eggs Cochon, a variation from New Orleans restaurants which replaces the ham with pork "debris" (slow roasted pork shredded in its own juices) and the English muffin with a large buttermilk biscuit.[28][29]
See also[edit]
Food portal
List of breakfast foods
List of brunch foods
List of egg dishes
List of foods named after people
List of regional dishes of the United States
References[edit]
Jump up ^ "Delmonico's Menu". Delmonico's Restaurant. Retrieved 2016-09-28.
Jump up ^ "The epicurean — A complete treatise of analytical and practical studies on the culinary art, including table and wine service, how to prepare and cook dishes, etc., and a selection of interesting bills of fare of Delmonico's from 1862 to 1894". The Internet Archive. Retrieved 2014-04-17.
Jump up ^ Benedict, Cutts. "Eggs Benedict New York: Feedback". Archived from the original on December 1, 1998. Retrieved February 23, 2007.
Jump up ^ "Talk of the Town". The New Yorker. December 19, 1942. Notes: This hasn't been verified at the source, but is instead taken from the letter to Karpf by Cutts Benedict and the page of J. J. Schnebel.
Jump up ^ Claiborne, Craig (September 9, 1967). "American Classic: Eggs Benedict". The New York Times. Retrieved 2014-04-17.
Jump up ^ Rombauer, Irma S.; Marion Rombauer Becker (1995) [1975]. "Egg Dishes". The Joy of Cooking. Illustrated by Ginnie Hofmann and Ikki Matsumoto (1st Scribner Edition 1995 ed.). New York, NY: Scribner. p. 222. ISBN 0-02-604570-2. Notes: Title of recipe is poached eggs Blackstone. Uses fried slice of flour dipped tomato, minced bacon, poached eggs, and hollandaise. No bread for base.
Jump up ^ "The Heritage House – Menu". Archived from the original on May 1, 2006. Retrieved February 26, 2007. Eggs Blackstone, poached eggs served with house made English muffin, apple smoked bacon, tomatoes and hollandaise. Notes: Located in Mendocino, California.
Jump up ^ "Rulloff's – Sunday Brunch Menu". Archived from the original on November 9, 2005. Retrieved February 26, 2007. Eggs Blackstone poached eggs over crispy bacon and thin sliced tomatoes on a toasted English muffin, with hollandaise sauce Notes: Located in Ithaca, New York.
Jump up ^ Hirtzler, Victor (1988). The 1910 Hotel St. Francis cook book (1st ed.). Sausalito, Calif.: Windgate Press. ISBN 978-0915269068.
Jump up ^ "Rich mix of patrons makes Moto's special". The Atlanta Journal and The Atlanta Constitution. December 18, 1986. pp. A/6. "eggs Florentine ($3.95), eggs poached and topped with Hollandaise sauce, served on spinach and English muffin" Notes: Not directly verified. Viewed through Google News Archive snippet view.
Jump up ^ "Good Stuff Hermosa Beach – Menu". Good Stuff Restaurants. Archived from the original on April 18, 2006. Retrieved March 8, 2007. Eggs Florentine The same good stuff as the benedict, only with fresh spinach instead of ham Notes: Located in Hermosa Beach, California.
Jump up ^ "The Buff Restaurant – Menu". The Buff Restaurant. Archived from the original on April 20, 2006. Retrieved March 8, 2007. EGGS FLORENTINE – SPINACH, CREAM CHEESE, TOMATO, AND MUSHROOMS TOPPED WITH HOLLANDAISE ON A MUFFIN Notes: Located in Boulder, Colorado.
Jump up ^ The Editors of Saveur Magazine (28 October 2014). SAVEUR: The New Classics Cookbook: 1,000 Recipes + Expert Advice, Tips, and. Weldon Owen. p. 461. ISBN 978-1616287351. Retrieved 28 July 2017.
Jump up ^ Claiborne, Craig (May 26, 1960). "Maligned Vegetable Has Loyal Fans". The New York Times. p. 28.
Jump up ^ Thomson, Julie R. "17 Twists On The Classic Eggs Benedict Recipe".
Jump up ^ "Eggs Hemingway (or eggs Atlantic) with smoked salmon | Shelf5". Shelf5. Retrieved September 28, 2016.
Jump up ^ "Eggs Hemingway". Instructables. Retrieved September 28, 2016.
Jump up ^ "Eggs Benjamin breakfast - Picture of Symposium Cafe Restaurant & Lounge, Markham - TripAdvisor". www.tripadvisor.com. Retrieved September 28, 2016.
Jump up ^ "Huevos Benedictos". Instructables.
Jump up ^ DeMers, John (1998). Food of New Orleans: Authentic Recipes from the Big Easy. Food photography by John Hay (1st ed.). Boston: Periplus Editions. p. 44. ISBN 962-593-227-5.
Jump up ^ "Recipes – Eggs Hussarde". Brennan's Restaurant. Archived from the original on February 6, 2006. Retrieved September 28, 2016. Notes: Located in New Orleans, Louisiana.
Jump up ^ Townsend, Elisabeth (July 24, 2005). "Dining Out". The Boston Globe. "Irish Benedict ($7.50): two poached Eggs and corned beef hash on an English muffin covered with hollandaise sauce" Notes: Not directly verified. Viewed through Google News Archive snippet view.
Jump up ^ "Breakfast Menu". The Field Irish Pub. Retrieved March 30, 2007. Toasted muffin topped with Irish bacon & poached eggs finished with Hollandaise sauce. Notes: Located in San Diego, California.
Jump up ^ "Breakfast Menu". Strafford Farms Restaurant. Archived from the original on May 12, 2006. Retrieved March 30, 2007. IRISH BENEDICT 3.95 two poached eggs on an English muffin with corn beef hash topped with a hollandaise sauce Notes: Located in Dover, New Hampshire.
Jump up ^ Watts, Phyllis (December 8, 2009). Where Food and People Meet (1st ed.). Xlibris. p. 532. ISBN 1441571906.
Jump up ^ "Glad Café Menu" (PDF). The Glad Café. Retrieved January 26, 2014. Eggs... Hebridean w. black pudding Notes: Located in Glasgow, Scotland.
Jump up ^ "Breakfast Menu Café Gandolfi". Café Gandolfi. Retrieved January 26, 2014. Eggs Hebridean with Stornoway black pudding. Notes: Located in Glasgow, Scotland.
Jump up ^ "Eggs Cochon du Lait" Eat Your World
Jump up ^ "Five places for great cochon du lait" Gambit
External links[edit]
Wikimedia Commons has media related to Eggs Benedict and variations.
Wikiquote has quotations related to: Eggs Benedict
Who Cooked That Up? page on origin of the dish with a recipe
“Was He the Eggman?” An account in The New York Times about Lemuel Benedict and the efforts of Jack Benedict, the son of Lemuel's first cousin, to promote Lemuel's story. Article includes link to an audio slide show.
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text:
Axial compressor
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Further information: Axial fan design
An animated simulation of an axial compressor. The static blades are the stators.
An axial compressor is a compressor that can continuously pressurize gases. It is a rotating, airfoil-based compressor in which the gas or working fluid principally flows parallel to the axis of rotation, or axially. This differs from other rotating compressors such as centrifugal compressors, axi-centrifugal compressors and mixed-flow compressors where the fluid flow will include a "radial component" through the compressor. The energy level of the fluid increases as it flows through the compressor due to the action of the rotor blades which exert a torque on the fluid. The stationary blades slow the fluid, converting the circumferential component of flow into pressure. Compressors are typically driven by an electric motor or a steam or a gas turbine.[1]
Axial flow compressors produce a continuous flow of compressed gas, and have the benefits of high efficiency and large mass flow rate, particularly in relation to their size and cross-section. They do, however, require several rows of airfoils to achieve a large pressure rise, making them complex and expensive relative to other designs (e.g. centrifugal compressors).
Axial compressors are integral to the design of large gas turbines such as jet engines, high speed ship engines, and small scale power stations. They are also used in industrial applications such as large volume air separation plants, blast furnace air, fluid catalytic cracking air, and propane dehydrogenation. Due to high performance, high reliability and flexible operation during the flight envelope, they are also used in aerospace engines.[2]
Typical application
Type of flow
Pressure ratio per stage
Efficiency per stage[2]
Industrial Subsonic 1.05–1.2 88–92%
Aerospace Transonic 1.15–1.6 80–85%
Research Supersonic 1.8–2.2 75–85%
Contents
[hide]
1 Description
2 Working
3 Design
4 Kinetics and energy equations
5 Performance characteristics
6 Instabilities
7 Steady-state performance
7.1 Off-design operation
7.2 Surging
7.3 Surge cycle
7.4 Stalling
7.4.1 Rotating stalling
7.4.2 Effects
8 Development
9 Axial-flow jet engines
9.1 Spools
9.2 Bleed air, variable stators
10 Design notes
10.1 Energy exchange between rotor and fluid
10.2 Compressor maps
10.3 Compression stability
11 See also
12 References
13 Bibliography
Description[edit]
The compressor in a Pratt & Whitney TF30 turbofan engine.
Axial compressors consist of rotating and stationary components. A shaft drives a central drum, retained by bearings, which has a number of annular airfoil rows attached usually in pairs, one rotating and one stationary attached to a stationary tubular casing. A pair of rotating and stationary airfoils is called a stage. The rotating airfoils, also known as blades or rotors, accelerate the fluid. The stationary airfoils, also known as stators or vanes, convert the increased rotational kinetic energy into static pressure through diffusion and redirect the flow direction of the fluid, preparing it for the rotor blades of the next stage.[3] The cross-sectional area between rotor drum and casing is reduced in the flow direction to maintain an optimum Mach number using variable geometry as the fluid is compressed.
Working[edit]
As the fluid enters and leaves in the axial direction, the centrifugal component in the energy equation does not come into play. Here the compression is fully based on diffusing action of the passages.The diffusing action in stator converts absolute kinetic head of the fluid into rise in pressure. The relative kinetic head in the energy equation is a term that exists only because of the rotation of the rotor. The rotor reduces the relative kinetic head of the fluid and adds it to the absolute kinetic head of the fluid i.e., the impact of the rotor on the fluid particles increases its velocity (absolute) and thereby reduces the relative velocity between the fluid and the rotor. In short, the rotor increases the absolute velocity of the fluid and the stator converts this into pressure rise. Designing the rotor passage with a diffusing capability can produce a pressure rise in addition to its normal functioning. This produces greater pressure rise per stage which constitutes a stator and a rotor together. This is the reaction principle in turbomachines. If 50% of the pressure rise in a stage is obtained at the rotor section, it is said to have a 50% reaction.
Design[edit]
The increase in pressure produced by a single stage is limited by the relative velocity between the rotor and the fluid, and the turning and diffusion capabilities of the airfoils. A typical stage in a commercial compressor will produce a pressure increase of between 15% and 60% (pressure ratios of 1.15–1.6) at design conditions with a polytropic efficiency in the region of 90–95%. To achieve different pressure ratios, axial compressors are designed with different numbers of stages and rotational speeds. As a rule of thumb we can assume that each stage in a given compressor has the same temperature rise (Delta T). Therefore, at the entry, temperature (Tstage) to each stage must increase progressively through the compressor and the ratio (Delta T)/(Tstage) entry must decrease, thus implying a progressive reduction in stage pressure ratio through the unit. Hence the rear stage develops a significantly lower pressure ratio than the first stage. Higher stage pressure ratios are also possible if the relative velocity between fluid and rotors is supersonic, but this is achieved at the expense of efficiency and operability. Such compressors, with stage pressure ratios of over 2, are only used where minimizing the compressor size, weight or complexity is critical, such as in military jets. The airfoil profiles are optimized and matched for specific velocities and turning. Although compressors can be run at other conditions with different flows, speeds, or pressure ratios, this can result in an efficiency penalty or even a partial or complete breakdown in flow (known as compressor stall and pressure surge respectively). Thus, a practical limit on the number of stages, and the overall pressure ratio, comes from the interaction of the different stages when required to work away from the design conditions. These “off-design” conditions can be mitigated to a certain extent by providing some flexibility in the compressor. This is achieved normally through the use of adjustable stators or with valves that can bleed fluid from the main flow between stages (inter-stage bleed). Modern jet engines use a series of compressors, running at different speeds; to supply air at around 40:1 pressure ratio for combustion with sufficient flexibility for all flight conditions.
Kinetics and energy equations[edit]
Velocity triangle of the swirling fluid entering and exiting the rotor blade
The law of moment of momentum states that the sum of the moments of external forces acting on a fluid which is temporarily occupying the control volume is equal to the net change of angular momentum flux through the control volume.
The swirling fluid enters the control volume at radius, r 1 {\displaystyle r_{1}\,} , with tangential velocity, V w 1 {\displaystyle V_{w1}\,} , and leaves at radius, r 2 {\displaystyle r_{2}\,} , with tangential velocity, V w 2 {\displaystyle V_{w2}\,} .
V 1 {\displaystyle V_{1}\,} and V 2 {\displaystyle V_{2}\,} are the absolute velocities at the inlet and outlet respectively.
V f 1 {\displaystyle V_{f1}\,} and V f 2 {\displaystyle V_{f2}\,} are the axial flow velocities at the inlet and outlet respectively.
V w 1 {\displaystyle V_{w1}\,} and V w 2 {\displaystyle V_{w2}\,} are the swirl velocities at the inlet and outlet respectively.
V r 1 {\displaystyle V_{r1}\,} and V r 2 {\displaystyle V_{r2}\,} are the blade-relative velocities at the inlet and outlet respectively.
U {\displaystyle U\,} is the linear velocity of the blade.
α {\displaystyle \alpha } is the guide vane angle and β {\displaystyle \beta } is the blade angle.
Rate of change of momentum, F is given by the equation:
F = m ˙ ( V w 2 − V w 1 ) = m ˙ ( V f 2 tan  α 2 − V f 1 tan  α 1 ) {\displaystyle F={\dot {m}}\left(V_{w2}-V_{w1}\right)={\dot {m}}\left(V_{f2}\tan \alpha _{2}-V_{f1}\tan \alpha _{1}\right)\,} (from velocity triangle)
Power consumed by an ideal moving blade, P is given by the equation:
P = m ˙ U ( V f 2 tan  α 2 − V f 1 tan  α 1 ) {\displaystyle P={\dot {m}}U\left(V_{f2}\tan \alpha _{2}-V_{f1}\tan \alpha _{1}\right)\,}
Change in enthalpy of fluid in moving blades:
P = m ˙ ( h 02 − h 01 ) = m ˙ c p ( T 02 − T 01 ) {\displaystyle P={\dot {m}}\left(h_{02}-h_{01}\right)={\dot {m}}c_{p}\left(T_{02}-T_{01}\right)\,}
Therefore,
P = m ˙ U ( V f 2 tan  α 2 − V f 1 tan  α 1 ) = m ˙ c p ( T 02 − T 01 ) {\displaystyle P={\dot {m}}U\left(V_{f2}\tan \alpha _{2}-V_{f1}\tan \alpha _{1}\right)={\dot {m}}c_{p}\left(T_{02}-T_{01}\right)\,}
which implies,
δ ( T 0 ) isentropic = U c p ( V f 2 tan  α 2 − V f 1 tan  α 1 ) {\displaystyle \delta (T_{0})_{\text{isentropic}}={\frac {U}{c_{p}}}\left(V_{f2}\tan \alpha _{2}-V_{f1}\tan \alpha _{1}\right)\,}
Isentropic compression in rotor blade,
p 2 − p 1 = p 1 ( [ T 2 T 1 ] γ γ − 1 − 1 ) {\displaystyle p_{2}-p_{1}=p_{1}\left(\left[{\frac {T_{2}}{T_{1}}}\right]^{\frac {\gamma }{\gamma -1}}-1\right)\,}
Therefore,
( p 02 ) actual p 01 = ( 1 + η stage δ ( T 0 ) isentropic T 01 ) γ γ − 1 {\displaystyle {\frac {(p_{02})_{\text{actual}}}{p_{01}}}=\left(1+{\frac {\eta _{\text{stage}}\delta (T_{0})_{\text{isentropic}}}{T_{01}}}\right)^{\frac {\gamma }{\gamma -1}}\,}
which implies
( p 02 ) actual p 01 = ( 1 + η stage U T 01 c p [ V f 2 tan  α 2 − V f 1 tan  α 1 ] ) γ γ − 1 {\displaystyle {\frac {(p_{02})_{\text{actual}}}{p_{01}}}=\left(1+{\frac {\eta _{\text{stage}}U}{T_{01}c_{p}}}\left[V_{f2}\tan \alpha _{2}-V_{f1}\tan \alpha _{1}\right]\right)^{\frac {\gamma }{\gamma -1}}\,}
Degree of Reaction, The pressure difference between the entry and exit of the rotor blade is called reaction pressure. The change in pressure energy is calculated through degree of reaction.
R = h 2 − h 1 h 02 − h 01 P = m ˙ c p ( T 2 + V 2 2 2 c p − [ T 1 + V 1 2 2 c p ] ) P = m ˙ ( h 2 − h 1 + [ V 2 2 2 − V 1 2 2 ] ) h 2 − h 1 = V r 1 2 2 − V r 2 2 2 T 2 − T 1 = V r 1 2 2 c p − V r 2 2 2 c p {\displaystyle {\begin{aligned}R&={\frac {h_{2}-h_{1}}{h_{02}-h_{01}}}\\P&={\dot {m}}c_{p}\left(T_{2}+{\frac {V_{2}^{2}}{2c_{p}}}-\left[T_{1}+{\frac {V_{1}^{2}}{2c_{p}}}\right]\right)\\P&={\dot {m}}\left(h_{2}-h_{1}+\left[{\frac {V_{2}^{2}}{2}}-{\frac {V_{1}^{2}}{2}}\right]\right)\\h_{2}-h_{1}&={\frac {V_{r1}^{2}}{2}}-{\frac {V_{r2}^{2}}{2}}\\T_{2}-T_{1}&={\frac {V_{r1}^{2}}{2c_{p}}}-{\frac {V_{r2}^{2}}{2c_{p}}}\end{aligned}}}
Therefore,
R = V r 1 2 − V r 2 2 V r 1 2 − V r 2 2 + V 1 2 − V 2 2 {\displaystyle R={\frac {V_{r1}^{2}-V_{r2}^{2}}{V_{r1}^{2}-V_{r2}^{2}+V_{1}^{2}-V_{2}^{2}}}\,}
Performance characteristics[edit]
Reasons stating difference in ideal and actual performance curve in an axial compressor
Instabilities[edit]
Greitzer[4] used a Helmholtz resonator type of compression system model to predict the transient response of a compression system after a small perturbation superimposed on a steady operating condition. He found a non-dimensional parameter which predicted which mode of compressor instability, rotating stall or surge, would result. The parameter used the rotor speed, Helmholtz resonator frequency of the system and an "effective length" of the compressor duct. It had a critical value which predicted either rotating stall or surge where the slope of pressure ratio against flow changed from negative to positive.
Steady-state performance[edit]
Axial compressor performance is shown on a compressor map, also known as a characteristic, by plotting pressure ratio and efficiency against corrected mass flow at different values of corrected compressor speed.
Axial compressors, particularly near their design point are usually amenable to analytical treatment, and a good estimate of their performance can be made before they are first run on a rig. The compressor map shows the complete running range, ie off-design, of the compressor from ground idle to its highest corrected rotor speed, which for a civil engine may occur at top-of-climb, or, for a military combat engine, at take-off on a cold day.[5] Not shown is the sub-idle performance region needed for analyzing normal ground and in-flight windmill start behaviour.
The performance of a single compressor stage may be shown by plotting stage loading coefficient ( ψ {\displaystyle \psi \,} ) as a function of flow coefficient ( ϕ {\displaystyle \phi \,} )
Stage pressure ratio against flow rate is lower than for a no-loss stage as shown. Losses are due to blade friction, flow separation, unsteady flow and vane-blade spacing.
Off-design operation[edit]
Off design characteristics curve of an axial compressor. Stage loading coefficient ( ψ {\displaystyle \psi \,} ) as function of flow coefficient ( ϕ {\displaystyle \phi \,} )
The performance of a compressor is defined according to its design. But in actual practice, the operating point of the compressor deviates from the design- point which is known as off-design operation.
ψ = ϕ ( tan  α 2 − tan  α 1 ) {\displaystyle \psi =\phi (\tan \alpha _{2}-\tan \alpha _{1})\,}
(1)
tan  α 2 = 1 ϕ − tan  β 2 {\displaystyle \tan \alpha _{2}={\frac {1}{\phi }}-\tan \beta _{2}\,}
(2)
from equation (1) and (2)
ψ = 1 − ϕ ( tan  β 2 + tan  α 1 ) {\displaystyle \psi =1-\phi (\tan \beta _{2}+\tan \alpha _{1})\,}
The value of ( tan  β 2 + tan  α 1 ) {\displaystyle (\tan \beta _{2}+\tan \alpha _{1})\,} doesn't change for a wide range of operating points till stalling. Also α 1 = α 3 {\displaystyle \alpha _{1}=\alpha _{3}\,} because of minor change in air angle at rotor and stator, where α 3 {\displaystyle \alpha _{3}\,} is diffuser blade angle.
J = tan  β 2 + tan  α 3 ) {\displaystyle J=\tan \beta _{2}+\tan \alpha _{3})\,} is constant

Representing design values with (')
ψ ′ = 1 − J ( ϕ ′ ) J = 1 − ψ ′ ϕ ′ {\displaystyle {\begin{aligned}\psi '&=1-J(\phi ')\,\\J&={\frac {1-\psi '}{\phi '}}\end{aligned}}}
(3)
for off-design operations (from eq. 3):
ψ = 1 − J ( ϕ ) ψ = 1 − ϕ ( 1 − ψ ′ ϕ ′ ) {\displaystyle {\begin{aligned}\psi &=1-J(\phi )\,\\\psi &=1-\phi \left({\frac {1-\psi '}{\phi '}}\right)\,\end{aligned}}}
for positive values of J, slope of the curve is negative and vice versa.
Surging[edit]
Various points on the performance curve depending upon the flow rates and pressure difference
In the plot of pressure-flow rate the line separating graph between two regions- unstable and stable is known as the surge line. This line is formed by joining surge points at different rpms. Unstable flow in axial compressors due to complete breakdown of the steady through flow is termed as surging.[1] This phenomenon affects the performance of compressor and is undesirable.
Surge cycle[edit]
The following explanation for surging refers to running a compressor at a constant speed on a rig and gradually reducing the exit area by closing a valve. What happens, ie crossing the surge line, is caused by the compressor trying to deliver air, still running at the same speed, to a higher exit pressure. When the compressor is operating as part of a complete gas turbine engine, as opposed to on a test rig, a higher delivery pressure at a particular speed can be caused momentarily by burning too-great a step-jump in fuel which causes a momentary blockage until the compressor increases to the speed which goes with the new fuel flow and the surging stops.
Suppose the initial operating point D ( m ˙ , P D {\displaystyle {\dot {m}},P_{D}\,} ) at some rpm N. On decreasing the flow- rate at same rpm along the characteristic curve by partial closing of the valve, the pressure in the pipe increases which will be taken care by increase in input pressure at the compressor. Further increase in pressure till point P (surge point), compressor pressure will increase. Further moving towards left keeping rpm constant, pressure in pipe will increase but compressor pressure will decrease leading to back air-flow towards the compressor. Due to this back flow, pressure in pipe will decrease because this unequal pressure condition cannot stay for a long period of time. Though valve position is set for lower flow rate say point G but compressor will work according to normal stable operation point say E, so path E-F-P-G-E will be followed leading to breakdown of flow, hence pressure in the compressor falls further to point H( P H {\displaystyle P_{H}\,} ). This increase and decrease of pressure in pipe will occur repeatedly in pipe and compressor following the cycle E-F-P-G-H-E also known as the surge cycle.
This phenomenon will cause vibrations in the whole machine and may lead to mechanical failure. That is why left portion of the curve from the surge point is called unstable region and may cause damage to the machine. So the recommended operation range is on the right side of the surge line.
Stalling[edit]
Stalling is an important phenomenon that affects the performance of the compressor. An analysis is made of rotating stall in compressors of many stages, finding conditions under which a flow distortion can occur which is steady in a traveling reference frame, even though upstream total and downstream static pressure are constant. In the compressor, a pressure-rise hysteresis is assumed.[6] It is a situation of separation of air flow at the aero-foil blades of the compressor. This phenomenon depending upon the blade-profile leads to reduced compression and drop in engine power.
Positive stalling
Flow separation occur on the suction side of the blade.
Negative stalling
Flow separation occur on the pressure side of the blade.
Negative stall is negligible compared to the positive stall because flow separation is least likely to occur on the pressure side of the blade.
In a multi-stage compressor, at the high pressure stages, axial velocity is very small. Stalling value decreases with a small deviation from the design point causing stall near the hub and tip regions whose size increases with decreasing flow rates. They grow larger at very low flow rate and affect the entire blade height. Delivery pressure significantly drops with large stalling which can lead to flow reversal. The stage efficiency drops with higher losses.
Rotating stalling[edit]
Non-uniformity of air flow in the rotor blades may disturb local air flow in the compressor without upsetting it. The compressor continues to work normally but with reduced compression. Thus, rotating stall decreases the effectiveness of the compressor.
In a rotor with blades moving say towards right. Let some blades receives flow at higher incidence, this blade will stop positively. It creates obstruction in the passage between the blade to its left and itself. Thus the left blade will receive the flow at higher incidence and the blade to its right with decreased incidence. The left blade will experience more stall while the blade to its right will experience lesser stall. Towards the right stalling will decrease whereas it will increase towards its left. Movement of the rotating stall can be observed depending upon the chosen reference frame.
Effects[edit]
This reduces efficiency of the compressor
Forced vibrations in the blades due to passage through stall compartment.
These forced vibrations may match with the natural frequency of the blades causing resonance and hence failure of the blade.
Development[edit]
Early axial compressors offered poor efficiency, so poor that in the early 1920s a number of papers claimed that a practical jet engine would be impossible to construct. Things changed after A. A. Griffith published a seminal paper in 1926, noting that the reason for the poor performance was that existing compressors used flat blades and were essentially "flying stalled". He showed that the use of airfoils instead of the flat blades would increase efficiency to the point where a practical jet engine was a real possibility. He concluded the paper with a basic diagram of such an engine, which included a second turbine that was used to power a propeller.
Although Griffith was well known due to his earlier work on metal fatigue and stress measurement, little work appears to have started as a direct result of his paper. The only obvious effort was a test-bed compressor built by Hayne Constant, Griffith's colleague at the Royal Aircraft Establishment. Other early jet efforts, notably those of Frank Whittle and Hans von Ohain, were based on the more robust and better understood centrifugal compressor which was widely used in superchargers. Griffith had seen Whittle's work in 1929 and dismissed it, noting a mathematical error, and going on to claim that the frontal size of the engine would make it useless on a high-speed aircraft.
Real work on axial-flow engines started in the late 1930s, in several efforts that all started at about the same time. In England, Hayne Constant reached an agreement with the steam turbine company Metropolitan-Vickers (Metrovick) in 1937, starting their turboprop effort based on the Griffith design in 1938. In 1940, after the successful run of Whittle's centrifugal-flow design, their effort was re-designed as a pure jet, the Metrovick F.2. In Germany, von Ohain had produced several working centrifugal engines, some of which had flown including the world's first jet aircraft (He 178), but development efforts had moved on to Junkers (Jumo 004) and BMW (BMW 003), which used axial-flow designs in the world's first jet fighter (Messerschmitt Me 262) and jet bomber (Arado Ar 234). In the United States, both Lockheed and General Electric were awarded contracts in 1941 to develop axial-flow engines, the former a pure jet, the latter a turboprop. Northrop also started their own project to develop a turboprop, which the US Navy eventually contracted in 1943. Westinghouse also entered the race in 1942, their project proving to be the only successful one of the US efforts, later becoming the J30.
As Griffith had originally noted in 1929, the large frontal size of the centrifugal compressor caused it to have higher drag than the narrower axial-flow type. Additionally the axial-flow design could improve its compression ratio simply by adding additional stages and making the engine slightly longer. In the centrifugal-flow design the compressor itself had to be larger in diameter, which was much more difficult to "fit" properly on the aircraft. On the other hand, centrifugal-flow designs remained much less complex (the major reason they "won" in the race to flying examples) and therefore have a role in places where size and streamlining are not so important. For this reason they remain a major solution for helicopter engines, where the compressor lies flat and can be built to any needed size without upsetting the streamlining to any great degree.
Axial-flow jet engines[edit]
Low-pressure axial compressor scheme of the Olympus BOl.1 turbojet.
In the jet engine application, the compressor faces a wide variety of operating conditions. On the ground at takeoff the inlet pressure is high, inlet speed zero, and the compressor spun at a variety of speeds as the power is applied. Once in flight the inlet pressure drops, but the inlet speed increases (due to the forward motion of the aircraft) to recover some of this pressure, and the compressor tends to run at a single speed for long periods of time.
There is simply no "perfect" compressor for this wide range of operating conditions. Fixed geometry compressors, like those used on early jet engines, are limited to a design pressure ratio of about 4 or 5:1. As with any heat engine, fuel efficiency is strongly related to the compression ratio, so there is very strong financial need to improve the compressor stages beyond these sorts of ratios.
Additionally the compressor may stall if the inlet conditions change abruptly, a common problem on early engines. In some cases, if the stall occurs near the front of the engine, all of the stages from that point on will stop compressing the air. In this situation the energy required to run the compressor drops suddenly, and the remaining hot air in the rear of the engine allows the turbine to speed up[citation needed] the whole engine dramatically. This condition, known as surging, was a major problem on early engines and often led to the turbine or compressor breaking and shedding blades.
For all of these reasons, axial compressors on modern jet engines are considerably more complex than those on earlier designs.
Spools[edit]
All compressors have an optimum point relating rotational speed and pressure, with higher compressions requiring higher speeds. Early engines were designed for simplicity, and used a single large compressor spinning at a single speed. Later designs added a second turbine and divided the compressor into low-pressure and high-pressure sections, the latter spinning faster. This two-spool design, pioneered on the Bristol Olympus, resulted in increased efficiency. Further increases in efficiency may be realised by adding a third spool, but in practice the added complexity increases maintenance costs to the point of negating any economic benefit. That said, there are several three-spool engines in use, perhaps the most famous being the Rolls-Royce RB211, used on a wide variety of commercial aircraft.
Bleed air, variable stators[edit]
See also: Bleed air
As an aircraft changes speed or altitude, the pressure of the air at the inlet to the compressor will vary. In order to "tune" the compressor for these changing conditions, designs starting in the 1950s would "bleed" air out of the middle of the compressor in order to avoid trying to compress too much air in the final stages. This was also used to help start the engine, allowing it to be spun up without compressing much air by bleeding off as much as possible. Bleed systems were already commonly used anyway, to provide airflow into the turbine stage where it was used to cool the turbine blades, as well as provide pressurized air for the air conditioning systems inside the aircraft.
A more advanced design, the variable stator, used blades that can be individually rotated around their axis, as opposed to the power axis of the engine. For startup they are rotated to "closed", reducing compression, and then are rotated back into the airflow as the external conditions require. The General Electric J79 was the first major example of a variable stator design, and today it is a common feature of most military engines.
Closing the variable stators progressively, as compressor speed falls, reduces the slope of the surge (or stall) line on the operating characteristic (or map), improving the surge margin of the installed unit. By incorporating variable stators in the first five stages, General Electric Aircraft Engines has developed a ten-stage axial compressor capable of operating at a 23:1 design pressure ratio.
Design notes[edit]
Energy exchange between rotor and fluid[edit]
The relative motion of the blades to the fluid adds velocity or pressure or both to the fluid as it passes through the rotor. The fluid velocity is increased through the rotor, and the stator converts kinetic energy to pressure energy. Some diffusion also occurs in the rotor in most practical designs.
The increase in velocity of the fluid is primarily in the tangential direction (swirl) and the stator removes this angular momentum.
The pressure rise results in a stagnation temperature rise. For a given geometry the temperature rise depends on the square of the tangential Mach number of the rotor row. Current turbofan engines have fans that operate at Mach 1.7 or more, and require significant containment and noise suppression structures to reduce blade loss damage and noise.
Compressor maps[edit]
A map shows the performance of a compressor and allows determination of optimal operating conditions. It shows the mass flow along the horizontal axis, typically as a percentage of the design mass flow rate, or in actual units. The pressure rise is indicated on the vertical axis as a ratio between inlet and exit stagnation pressures.
A surge or stall line identifies the boundary to the left of which the compressor performance rapidly degrades and identifies the maximum pressure ratio that can be achieved for a given mass flow. Contours of efficiency are drawn as well as performance lines for operation at particular rotational speeds.
Compression stability[edit]
Operating efficiency is highest close to the stall line. If the downstream pressure is increased beyond the maximum possible the compressor will stall and become unstable.
Typically the instability will be at the Helmholtz frequency of the system, taking the downstream plenum into account.
See also[edit]
Centrifugal compressor
Axial fan design
References[edit]
^ Jump up to: a b Yahya, S.M. (2011). Turbines, Compressors and Fans. Tata McGraw Hill Education Private Limited. ISBN 978-0-07-070702-3.
^ Jump up to: a b Meherwan, P.Boyce. "2.0 Axial Flow Compressors".
Jump up ^ Perry, R.H. and Green, D.W. (Eds.) (2007). Perry's Chemical Engineers' Handbook (8th ed.). McGraw Hill.ISBN 0-07-142294-3.
Jump up ^ Greitzer, E. M. (1 April 1976). "Surge and Rotating Stall in Axial Flow Compressors—Part I: Theoretical Compression System Model". Eng. Gas Turbines Power. 98 (2): 190–198. doi:10.1115/1.3446138.
Jump up ^ https://www.sto.nato.int/publications/AGARD/AGARD-LS-183/AGARD-LS-183.pdf Practical considerations in designing the engine cycle, Philpott, pp. 2-8, 2-17
Jump up ^ McDougall, NM; Cumpsty, NA; Hynes, TP (2012). "Stall inception in axial compressors". Journal of Turbomachinery. 112 (1): 116–123. doi:10.1115/1.2927406.
Bibliography[edit]
Treager, Irwin E. 'Aircraft Gas Turbine Engine Technology' 3rd edn, McGraw-Hill Book Company, 1995, ISBN 978-0-02-8018287
Hill, Philip and Carl Peterson. 'Mechanics and Thermodynamics of Propulsion,' 2nd edn, Prentice Hall, 1991. ISBN 0-201-14659-2.
Kerrebrock, Jack L. 'Aircraft Engines and Gas Turbines,' 2nd edn, Cambridge, Massachusetts: The MIT Press, 1992. ISBN 0-262-11162-4.
Rangwalla, Abdulla. S. 'Turbo-Machinery Dynamics: Design and Operation,' New York: McGraw-Hill: 2005. ISBN 0-07-145369-5.
Wilson, David Gordon and Theodosios Korakianitis. 'The Design of High-Efficiency Turbomachinery and Turbines,' 2nd edn, Prentice Hall, 1998. ISBN 0-13-312000-7.
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The Best FIFA Football Awards 2016
From Wikipedia, the free encyclopedia
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The Best FIFA Football Awards 2016
Date
9 January 2017 (2017-01-09)
Location
Zurich, Switzerland
Presented by
FIFA
Hosted by
Eva Longoria and Marco Schreyl
Highlights
The Best FIFA Men's Player
Cristiano Ronaldo
The Best FIFA Women's Player
Carli Lloyd
The Best FIFA Men's Coach
Claudio Ranieri
The Best FIFA Women's Coach
Silvia Neid
The FIFA Puskás Award
Mohd Faiz Subri
Website
fifa.com
← 2015
The Best FIFA Football Awards
2017 →
The Best FIFA Football Awards 2016 were held on 9 January 2017 in Zurich, Switzerland.[1] The Best FIFA Football Awards are the annual recognitions awarded by FIFA to several individuals across different categories, including: best eleven players of the year, known as FIFA FIFPro World XI (awards goalkeeper, best defenders l, midfielders, attackers), FIFA World Coach of the Year for men's and for women's football, best female player of the year, 2nd best male player of the year, and best goal of the year (known as FIFA Puskás Award). The FIFA Fair Play Award is the only award that usually goes to groups or entities instead of individuals.
The selection criteria for the (men's and women's) players of the year were: sporting performance, as well as general conduct on and off the pitch from 20 November 2015 to 22 November 2016. The selection criteria for the coaches of the year were: performance and general behaviour of their teams on and off the pitch from 20 November 2015 to 22 November 2016.
The votes were decided by media representatives, national team coaches, and national team captains. In October 2016, it was announced that the general public would also be allowed to vote.[2] Each group contributed 25% of the overall vote.
The ceremony was hosted by Eva Longoria and Marco Schreyl.[3][4]
Contents
1 Winners and nominees
1.1 The Best FIFA Men's Player
1.2 The Best FIFA Women's Player
1.3 The Best FIFA Men's Coach
1.4 The Best FIFA Women's Coach
1.5 FIFA Fair Play Award
1.6 FIFA Award for an Outstanding Career
1.7 FIFA Puskás Award
1.8 FIFA Fan Award
1.9 FIFA FIFPro World11
2 See also
3 References
4 External links
Winners and nominees[edit]
The Best FIFA Men's Player[edit]
See also: The Best FIFA Men's Player
The Football Committee compiled a shortlist of 23 male players for The Best FIFA Men's Player.[1]
The 23 candidates were announced on 4 November.[5] The three finalists were announced on 1 December 2016.[6]
Cristiano Ronaldo won the award with nearly 35% of the vote.[7]
Cristiano Ronaldo
Lionel Messi
Antoine Griezmann
Rank
Name
Club(s) played for
National team
Percent
The finalists
1 Cristiano Ronaldo Real Madrid Portugal 34.54%
2 Lionel Messi Barcelona Argentina 26.42%
3 Antoine Griezmann Atlético Madrid France 7.53%
Other candidates
4 Neymar Barcelona Brazil 6.23%
5 Luis Suárez Barcelona Uruguay 5.11%
6 Gareth Bale Real Madrid Wales 4.62%
7 Riyad Mahrez Leicester City Algeria 2.20%
8 Gianluigi Buffon Juventus Italy 1.85%
9 Andrés Iniesta Barcelona Spain 1.69%
10 Toni Kroos Real Madrid Germany 1.25%
11 Alexis Sánchez Arsenal Chile 1.19%
12 Robert Lewandowski Bayern Munich Poland 0.93%
13 Luka Modrić Real Madrid Croatia 0.89%
14 Mesut Özil Arsenal Germany 0.86%
15 Jamie Vardy Leicester City England 0.81%
16 Manuel Neuer Bayern Munich Germany 0.80%
17 Sergio Ramos Real Madrid Spain 0.70%
18 Zlatan Ibrahimović
Paris Saint-Germain
Manchester United
Sweden 0.50%
19 Paul Pogba
Juventus
Manchester United
France 0.47%
20 Kevin De Bruyne Manchester City Belgium 0.46%
21 N'Golo Kanté
Leicester City
Chelsea
France 0.40%
22 Sergio Agüero Manchester City Argentina 0.38%
23 Dimitri Payet West Ham United France 0.17%
The Best FIFA Women's Player[edit]
See also: The Best FIFA Women's Player
Carli Lloyd
Marta
Melanie Behringer
The Committee for Women's Football and the FIFA Women's World Cup compiled a shortlist of 10 female players for The Best FIFA Women's Player.[1]
The 10 candidates were announced on 3 November.[8] The three finalists were announced on 2 December.[9]
Carli Lloyd won the award with nearly 21% of the vote.[7]
Rank
Name
Club(s) played for
National team
Percent
The finalists
1 Carli Lloyd Houston Dash United States 20.68%
2 Marta FC Rosengård Brazil 16.60%
3 Melanie Behringer Bayern Munich Germany 12.34%
Other candidates
4 Dzsenifer Marozsán
1. FFC Frankfurt
Lyon
Germany 11.68%
5 Sara Däbritz Bayern Munich Germany 8.19%
6 Saki Kumagai Lyon Japan 6.94%
7 Lotta Schelin Lyon Sweden 6.58%
8 Christine Sinclair Portland Thorns Canada 5.99%
9 Amandine Henry Portland Thorns France 5.96%
10 Camille Abily Lyon France 5.04%
The Best FIFA Men's Coach[edit]
See also: The Best FIFA Football Coach
The Football Committee compiled a shortlist of 10 men's football coaches for The Best FIFA Men's Coach.[1]
The 10 candidates were announced on 2 November.[10] The three finalists were announced in December 2016.[11]
Claudio Ranieri won the award with over 22% of the vote.[7]
Rank
Name
Team(s) managed
Percent
The finalists
1 Claudio Ranieri Leicester City 22.06%
2 Zinedine Zidane Real Madrid 16.56%
3 Fernando Santos Portugal 16.24%
Other candidates
4 Diego Simeone Atlético Madrid 12.98%
5 Pep Guardiola
Bayern Munich
Manchester City
11.13%
6 Luis Enrique Barcelona 8.32%
7 Jürgen Klopp Liverpool 7.71%
8 Didier Deschamps France 1.97%
9 Chris Coleman Wales 1.82%
10 Mauricio Pochettino Tottenham Hotspur 1.21%
The Best FIFA Women's Coach[edit]
See also: The Best FIFA Football Coach
The Committee for Women's Football and the FIFA Women's World Cup compiled a shortlist of 10 women's football coaches for The Best FIFA Women's Coach.[1]
The 10 candidates were announced on 1 November.[12] The three finalists were announced on 2 December 2016.[13]
Silvia Neid won the award with nearly 30% of the vote.[7]
Rank
Name
Team(s) managed
Percent
The finalists
1 Silvia Neid Germany 29.99%
2 Jill Ellis United States 16.68%
3 Pia Sundhage Sweden 16.47%
Other candidates
4 John Herdman Canada 7.85%
5 Gérard Prêcheur Lyon 7.26%
6 Vadão Brazil 6.00%
7 Martina Voss-Tecklenburg Switzerland 4.07%
8 Vera Pauw South Africa 3.99%
9 Thomas Wörle Bayern Munich 3.96%
10 Philippe Bergeroo France 3.73%
FIFA Fair Play Award[edit]
See also: FIFA Fair Play Award
Colombian club Atlético Nacional won the award due to their gesture of asking CONMEBOL to award the 2016 Copa Sudamericana title to Brazilian club Chapecoense following the LaMia Flight 2933 disaster, which resulted in the deaths of 19 players and 23 staff members of the Brazilian club.[14]
Winner
Reason
Atlético Nacional Requested CONMEBOL to award Chapecoense with the 2016 Copa Sudamericana title following LaMia Flight 2933 crash
FIFA Award for an Outstanding Career[edit]
Brazilian futsal player Falcão won the award for his 27 years of contribution to the sport.[15]
Player
Reason
Falcão As a result of his remarkable contribution to the sport
FIFA Puskás Award[edit]
See also: FIFA Puskás Award
External video
Mohd Faiz Subri (MAS) - FIFA PUSKAS AWARD 2016 WINNER! on YouTube
THE FIFA PUSKAS AWARD 2016 - Mohd Faiz Subri WINNER on YouTube
The shortlist was announced on 21 November 2016.[16] The three finalists were announced on 2 December 2016.[17]
Mohd Faiz Subri won the award with over 59% of the vote.[18]
Rank
Player
Match
Competition
Date
Percent
The finalists
1 Mohd Faiz Subri Penang – Pahang 2016 Liga Super 16 February 2016 59.46%
2 Marlone Corinthians – Cobresal 2016 Copa Libertadores 21 April 2016 22.86%
3 Daniuska Rodríguez Venezuela – Colombia 2016 South American Under-17 Women's Football Championship 14 March 2016 10.01%
Other candidates
Mario Gaspar Spain – England International friendly 13 November 2015 7.68%
Hlompho Kekana Cameroon – South Africa 2017 Africa Cup of Nations qualification 26 March 2016
Lionel Messi United States – Argentina Copa América Centenario 21 June 2016
Neymar Barcelona – Villarreal 2015–16 La Liga 8 November 2015
Saúl Ñíguez Atlético Madrid – Bayern Munich 2015–16 UEFA Champions League 27 April 2016
Hal Robson-Kanu Wales – Belgium UEFA Euro 2016 1 July 2016
Simon Skrabb Gefle IF – Åtvidabergs FF 2015 Allsvenskan 31 October 2015
FIFA Fan Award[edit]
The three nominees were announced on 9 December 2016.[19] It was the first time that this award was given.
Borussia Dortmund and Liverpool supporters won the award with nearly 46% of the vote.[20]
Rank
Fans
Match
Competition
Date
Percent
1 Borussia Dortmund and Liverpool supporters Liverpool – Borussia Dortmund 2015–16 UEFA Europa League 14 April 2016 45.92%
2 Iceland supporters France – Iceland UEFA Euro 2016 3 July 2016 31.37%
3 ADO Den Haag supporters Feyenoord – ADO Den Haag 2016–17 Eredivisie 11 September 2016 22.71%
FIFA FIFPro World11[edit]
See also: FIFA FIFPro World11
The 55–player men's shortlist was announced on 1 December 2016.[21]
The players chosen included Manuel Neuer as goalkeeper, Dani Alves, Gerard Piqué, Sergio Ramos, and Marcelo as defenders, Luka Modrić, Toni Kroos, and Andrés Iniesta as midfielders, and Lionel Messi, Luis Suárez, and Cristiano Ronaldo as forwards.[22]
9 out of the 11 players played in La Liga.
Neuer
Piqué
Ramos
Alves
Marcelo
Kroos
Modrić
Iniesta
Suárez
Messi
Ronaldo
FIFA FIFPro World11 2016
Name
Club(s)
Goalkeeper
Manuel Neuer Bayern Munich
Defenders
Dani Alves
Barcelona
Juventus
Gerard Piqué Barcelona
Sergio Ramos Real Madrid
Marcelo Real Madrid
Midfielders
Luka Modrić Real Madrid
Toni Kroos Real Madrid
Andrés Iniesta Barcelona
Forwards
Lionel Messi Barcelona
Luis Suárez Barcelona
Cristiano Ronaldo Real Madrid
Other candidates
Name
showClub(s)
Goalkeepers
Claudio Bravo
Barcelona
Manchester City
Gianluigi Buffon Juventus
David de Gea Manchester United
Keylor Navas Real Madrid
Defenders
David Alaba Bayern Munich
Jordi Alba Barcelona
Serge Aurier Paris Saint-Germain
Héctor Bellerín Arsenal
Jérôme Boateng Bayern Munich
Leonardo Bonucci Juventus
Dani Carvajal Real Madrid
Giorgio Chiellini Juventus
David Luiz
Paris Saint-Germain
Chelsea
Diego Godín Atlético Madrid
Mats Hummels
Borussia Dortmund
Bayern Munich
Philipp Lahm Bayern Munich
Javier Mascherano Barcelona
Pepe Real Madrid
Thiago Silva Paris Saint-Germain
Raphaël Varane Real Madrid
Midfielders
Xabi Alonso Bayern Munich
Sergio Busquets Barcelona
Kevin De Bruyne Manchester City
Eden Hazard Chelsea
N'Golo Kanté
Leicester City
Chelsea
Mesut Özil Arsenal
Dimitri Payet West Ham United
Paul Pogba
Juventus
Manchester United
Ivan Rakitić Barcelona
David Silva Manchester City
Marco Verratti Paris Saint-Germain
Arturo Vidal Bayern Munich
Forwards
Sergio Agüero Manchester City
Gareth Bale Real Madrid
Karim Benzema Real Madrid
Paulo Dybala Juventus
Antoine Griezmann Atlético Madrid
Gonzalo Higuaín
Napoli
Juventus
Zlatan Ibrahimović
Paris Saint-Germain
Manchester United
Robert Lewandowski Bayern Munich
Thomas Müller Bayern Munich
Neymar Barcelona
Alexis Sánchez Arsenal
Jamie Vardy Leicester City
See also[edit]
Ballon d'Or
FIFA Ballon d'Or
FIFA World Player of the Year
FIFPro World XI
References[edit]
^ Jump up to: a b c d e "Circular no. 1560" (PDF). FIFA.com. 21 October 2016. Archived from the original (pdf) on 25 October 2016. Retrieved 24 October 2016.
Jump up ^ "The fans take centre stage". FIFA.com. 31 October 2016. Retrieved 31 October 2016.
Jump up ^ "Eva Longoria to host Best FIFA Football Awards with Marco Schreyl". ESPN. 3 January 2017. Retrieved 10 January 2017.
Jump up ^ "The Best Fifa Football Awards 2016: Cristiano Ronaldo wins best in show as Claudio Ranieri and Liverpool carry the torch for English game". Telegraph. 9 January 2017. Retrieved 10 January 2017.
Jump up ^ "Who will be The Best FIFA Men's Player 2016?". FIFA.com. 4 November 2016. Retrieved 4 November 2016.
Jump up ^ "Griezmann joins Ronaldo & Messi in battle to be The Best". FIFA.com. 1 December 2016. Retrieved 2 December 2016.
^ Jump up to: a b c d "The Best FIFA Footbal Awards - Results" (PDF). FIFA.com. Fédération Internationale de Football Association. 9 January 2017. Retrieved 9 January 2017.
Jump up ^ "Who will be The Best FIFA Women's Player 2016?". FIFA.com. 3 November 2016. Retrieved 3 November 2016.
Jump up ^ "The Best FIFA Football Awards 2016 - The Best FIFA Women's Player - FIFA.com". FIFA.com. Retrieved 2 December 2016.
Jump up ^ "Who will be The Best FIFA Men's Coach 2016?". FIFA. 2 November 2016.
Jump up ^ "The Best FIFA Football Awards 2016 - The Best FIFA Men's Coach - FIFA.com". FIFA.com. Retrieved 2 December 2016.
Jump up ^ "The Best FIFA Women's Coach". FIFA.com. 1 November 2016.
Jump up ^ "The Best FIFA Football Awards 2016 - The Best FIFA Women's Coach - FIFA.com". FIFA.com. Retrieved 2 December 2016.
Jump up ^ "The FIFA Fair Play Award". FIFA.com. Fédération Internationale de Football Association. 9 January 2016. Retrieved 9 January 2016.
Jump up ^ "The FIFA Award for an Outstanding Career". FIFA.com. Fédération Internationale de Football Association. 9 January 2016. Retrieved 9 January 2016.
Jump up ^ "The Best FIFA Football Awards 2016 - Puskás Award - FIFA.com". FIFA.com. 21 November 2016. Retrieved 21 November 2016.
Jump up ^ "The Best FIFA Football Awards 2016 - Puskás Award - FIFA.com". FIFA.com. Retrieved 2 December 2016.
Jump up ^ "The FIFA Puskás Award 2016 results" (PDF). FIFA.com. Fédération Internationale de Football Association. 9 January 2017. Retrieved 9 January 2017.
Jump up ^ "The Best FIFA Football Awards 2016 - Fan Award - FIFA.com". FIFA.com. Retrieved 23 December 2016.
Jump up ^ "The FIFA Fan Award 2016 results" (PDF). FIFA.com. Fédération Internationale de Football Association. 9 January 2017. Retrieved 9 January 2017.
Jump up ^ Beaard, Raymond (1 December 2016). "Nine new faces on World 11 shortlist - FIFPro World Players' Union". FIFPro World Players' Union.
Jump up ^ "FIFA FIFPro World11". FIFA.com. Fédération Internationale de Football Association. 9 January 2016. Retrieved 9 January 2016.
External links[edit]
Official Facebook website
show
v
t
e
FIFA Player of the Year
FIFA World Player of the Year
1991: Matthäus
1992: Van Basten
1993: Baggio
1994: Romário
1995: Weah
1996: Ronaldo
1997: Ronaldo
1998: Zidane
1999: Rivaldo
2000: Zidane
2001: Figo
2002: Ronaldo
2003: Zidane
2004: Ronaldinho
2005: Ronaldinho
2006: Cannavaro
2007: Kaká
2008: C. Ronaldo
2009: Messi
FIFA Ballon d'Or
2010: Messi
2011: Messi
2012: Messi
2013: C. Ronaldo
2014: C. Ronaldo
2015: Messi
The Best FIFA Men's Player
2016: C. Ronaldo
2017: C. Ronaldo
2018: Modrić
See also: Ballon d'Or
show
v
t
e
FIFA Women's Player of the Year
FIFA Women's World Player of the Year
2001: Hamm
2002: Hamm
2003: Prinz
2004: Prinz
2005: Prinz
2006: Marta
2007: Marta
2008: Marta
2009: Marta
2010: Marta
2011: Sawa
2012: Wambach
2013: Angerer
2014: Keßler
2015: Lloyd
The Best FIFA Women's Player
2016: Lloyd
2017: Martens
2018: Marta
show
v
t
e
FIFA Coach of the Year
FIFA World Coach of the Year
2010: Mourinho
2011: Guardiola
2012: Del Bosque
2013: Heynckes
2014: Löw
2015: Luis Enrique
The Best FIFA Football Coach
2016: Ranieri
2017: Zidane
2018: Deschamps
show
v
t
e
FIFA Women's Coach of the Year
FIFA World Coach of the Year
2010: Neid
2011: Sasaki
2012: Sundhage
2013: Neid
2014: Kellermann
2015: Ellis
The Best FIFA Football Coach
2016: Neid
2017: Wiegman
2018: Pedros
show
v
t
e
FIFA Puskás Award
2009: C. Ronaldo
2010: Altıntop
2011: Neymar
2012: Stoch
2013: Ibrahimović
2014: J. Rodríguez
2015: Wendell Lira
2016: Mohd Faiz
2017: Giroud
2018: Salah
show
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values: جوائز الفيفا للأفضل كرويا 2016 – Arabic

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