**4.1 ****The**** ****Energy**** ****Equation**

The ﬁrst law of thermodynamics, or simply, the energy equation, is of use whenever heat transfer or work is desired. If there is essentially no heat transfer and no external work from a pump or some other device, the energy equation allows us to relate the pressure, the velocity, and the elevation. We will begin with the energy equation (4.8) in its general form:

Most applications allow a simpliﬁed energy equation by assuming a steady, uniform ﬂow with one entrance and one exit, so that

where we have used **n**ˆ ⋅ **V **= −*V*1 at the entrance. Using the continuity equation (4.14),

this is written as

The work rate term results from a force moving with a velocity: *W** *= **F **⋅ **V**. The force can be a pressure or a shear multiplied by an area. If the ﬂow is in a conduit, e.g., a pipe or a channel, the walls do not move so there is no work done by the walls. If there is a moving belt, there could be an input of work due to the shear between the belt and the ﬂuid. The most common work rate terms result from the pressure forces at the entrance and the exit (pressure is assumed to be uniform over each area) and from any device located between the entrance and the exit. The work rate term is expressed as

where power output is considered positive and *W *is the shaft power output from the control volume (a pump would provide a negative power and a turbine, a positive power output). Using the expression for *e *given in Eq. (1.33), Eq. (4.19) takes the form

The heat transfer term and the internal energy terms form the losses in the ﬂow (viscous effects result in heat transfer and/or an increase in internal energy). Divide Eq. (4.21) by *m g *and simplify2:

where *V *is some characteristic velocity in the ﬂow; if it is not obvious it will be speciﬁed. Some loss coefﬁcients are listed in Table 7.2; in this chapter they will be given. The term *h*

is called the head loss because it has the dimension of length. We also refer to *V *2/2*g *as the *velocity head*, *p*/*g *as the *pressure head*, and *z *as the *head*. The sum of these three terms is the *total head*.An incompressible ﬂow occurs in many applications so that *g*1 = *g*2. Recall that *g *for water is 9810 N/m3.

The shaft-work term in Eq. (4.22) is typically due to either a pump or a turbine. If it is a pump, we can deﬁne the *pump head H *as

where *W *is the power output of the turbine and η*T *is the *turbine efﬁciency*. Power has units of watts or horsepower.

If the ﬂow is not uniform over the entrance and exit, an integration must be per- formed to obtain the kinetic energy. The rate at which the kinetic energy crosses an area is [see Eqs. (4.17) and (1.33)]

If the velocity distribution is known, the integration can be performed. A *kinetic- energy correction factor **a *is deﬁned as

so that, for nonuniform ﬂows, the energy equation takes the form

where *V *1 and *V *2 are the average velocities at sections 1 and 2, respectively. Equation (4.30) is used if the values for *a *are known; for parabolic proﬁles, *a *= 2 in apipe and *a *= 1.5 between parallel plates. For turbulent ﬂows (most ﬂows in engineering applications), α ≅ 1.

**EXAMPLE 4.3**

Water ﬂows from a reservoir with an elevation of 30 m through a 5-cm-diameter pipe that has a 2-cm-diameter nozzle attached to the end, as shown. The loss coefﬁcient for the entire pipe is given as *K *= 1.2. Estimate the ﬂow rate of water through the pipe. Also, predict the pressure just upstream of the nozzle (neglect the losses through the nozzle). The nozzle is at an elevation of 10 m.

The energy equation is written in the form

where the pressure is zero at surface 1 and at the exit 2, the velocity is zero at the surface, and there is no shaft work (there is no pump or turbine). The loss coefﬁcient would be based on the characteristic velocity *V *in the pipe, not the exit velocity *V *. Use the continuity equation to relate the velocities:

The energy equation provides

The pressure just before the nozzle is found by applying the energy equation across the nozzle assuming no losses (Bernoulli’s equation could also be used):

**EXAMPLE 4.4**

An energy conscious couple decides to dam up the creek ﬂowing next to their cabin and estimates that a head of 4 m can be established above the exit to a turbine they bought on eBay. The creek is estimated to have a ﬂow rate of 0.8 m3/s. What is the maximum power output of the turbine assuming no losses and a velocity at the turbine’s exit of 3.6 m/s?

**Solution**

The energy equation is applied as follows:

It is only the head of the water above the turbine that provides the power; the exiting velocity subtracts from the power. There results, using *m *= ρ*Q *= 1000 × 0.8 = 800 kg/s,

When a force is involved in a calculation, it is often necessary to apply Newton’s second law, or simply, the *momentum equation*, to the problem of interest. For some general volume, using the Eulerian description of motion, the momentum equation was presented in Eq. (4.10) in its most general form for a ﬁxed control volume as

When applying this equation to a control volume, we must be careful to include all forces acting on the control volume, so it is very important to sketch the control volume and place the forces on the sketch. The control volume takes the place of the free-body diagram utilized in mechanics courses.

Most often, steady, uniform ﬂows with one entrance and one outlet are encountered. For such ﬂows, Eq. (4.31) reduces to

Using continuity the momentum equation takes the simpliﬁed form

This is the form most often used when a force is involved in a calculation. It is a vector equation that contains the following three scalar equations (using rectangular coordinates):

If the proﬁles at the entrance and exit are not uniform, Eq. (4.31) must be used and the integration performed or, if the *momentum-correction factor **b *is known, it can be used. It is found from

The momentum equation for a steady ﬂow with one entrance and one outlet then takes the form

where **V _{1}**and

**V**represent the average velocity vectors over the two areas. For parabolic proﬁles,

_{2 }*b*= 1.33 for a pipe and

*b*= 1.2 for parallel plates. For turbulent ﬂows (most ﬂows in engineering applications),

*b*≅ 1.

One of the more important applications of the momentum equation is on the deﬂectors (or vanes) of pumps, turbines, or compressors. The applications involve both stationary deﬂectors and moving deﬂectors. The following assumptions are made for both:

• The frictional force between the ﬂuid and the deﬂector is negligible.

• The pressure is constant as the ﬂuid moves over the deﬂector.

• The body force is assumed to be negligible.

• The effect of the lateral spreading of the ﬂuid stream is neglected.

A sketch is made of a stationary deﬂector in Fig. 4.3. Bernoulli’s equation predicts that the ﬂuid velocity will not change ( *V*2 = *V*1 ) as the ﬂuid moves over the deﬂector.

**F****i****g****u****re 4.3 **A stationary deﬂector.

**F****i****g****u****re 4.4 **A single moving deﬂector.

Since the pressure does not change, there is no friction, it is a steady ﬂow, and the body forces are neglected. The component momentum equations appear as follows:

Given the necessary information, the force components can be calculated. The analysis of a moving deﬂector is more complicated. Is it a single deﬂector (a water scoop to slow a high-speed train), or is it a series of deﬂectors as in a turbine? First, let us consider a single deﬂector moving with speed *V *, as shown in Fig. 4.4. The reference frame is attached to the deﬂector so the ﬂow is steady from such a reference frame3. The deﬂector sees the velocity of the approaching ﬂuid as the relative velocity *V *and it is this relative velocity that Bernoulli’s equation predicts will remain constant over the deﬂector, i.e., *V *= *V *. The velocity of the ﬂuid exiting the ﬁxed nozzle is *V *. The momentum equation then provides

3If the deﬂector is observed from the ﬁxed jet, the deﬂector moves away from the jet and the ﬂow is not a steady ﬂow. It is steady if the ﬂow is observed from the deﬂector.

**F****i****g****u****re 4.5 **A series of vanes.

where *m** **r *is that part of the exiting ﬂuid that has its momentum changed. As the deﬂector moves away from the nozzle, the ﬂuid represented by the length *V**B *Δ*t *does not experience a change in momentum. The mass ﬂux of ﬂuid that experiences a momentum change is

which provides us with the relative mass ﬂux used in the expressions for the force components.

For a series of vanes, the nozzles are typically oriented such that the ﬂuid enters the vanes from the side at an angle *b*1 and leaves the vanes at an angle *b*2, as shown in Fig. 4.5. The vanes are designed so that the relative inlet velocity *V *enters the vanes tangent to a vane (the relative velocity always leaves tangent to the vane) as shown in Fig. 4.6. It is the relative speed that remains constant in magnitude as the ﬂuid moves over the vane, i.e., *V*

= *V *. We also note that all of the ﬂuid exiting the ﬁxed jet has its momentum changed. So, the expression to determine the *x*-component of the force is

**F****i****g****u****re 4.6 **(*a*) Average position of the jet, (*b*) the entrance velocity polygon, and (*c*) the exit velocity polygon.

It is this *x*-component of the force that allows the power to be calculated; the *y*-component does no work and hence does not contribute to the power. The power is found fromwhere *N *is the number of jets in the device and we have observed that the force *R *moves with velocity *V _{B} .*

__EXAMPLE 4.5__

A 10-cm-diameter hose maintained at a pressure of 1600 kPa provides water from a tanker to a ﬁre. There is a nozzle on the end of the hose that reduces the diameter to 2.5 cm. Estimate the force that the water exerts on the nozzle. The losses can be neglected in a short nozzle.

**Solution**

A sketch of the water contained in the nozzle is important so that the control volume is carefully identiﬁed. It is shown. Note that *p*2 = 0 and we expect

that the force *F *of the nozzle on the water acts to the left. The velocities are needed upstream and at the exit of the nozzle. Continuity provides

__EXAMPLE 4.6__

A steam turbine contains eight 4-cm-diameter nozzles each accelerating steam to 200 m/s, as shown. The turbine blades are moving at 80 m/s and the density of the steam is 2.2 kg/m3. Calculate the maximum power output.

The angle *a*1 is determined from the velocity polygon of Fig. 4.6*b*. For the *x- *and *y*-components, using *V *= 200 m/s and *V **B* = 80 m/s, we have

There are two unknowns in the above two equations: *V**r*_{1 }and α_{1}. A simultaneous solution provides

Neglecting losses allows *V**r *_{2} = *V**r _{}*

_{1}= 136.7 m/s so the velocity polygon at the exit (see Fig.4.6

*c*) provides

**EXAMPLE 4.7**

The relatively rapid ﬂow of water in a horizontal rectangular channel can sud- denly “jump” to a higher level (an obstruction downstream may be the cause). This is called a *hydraulic jump*. For the situation shown, calculate the higher depth downstream. Assume uniform ﬂow.

This equation is a cubic but with a little ingenuity it’s a quadratic. Let’s factor:

This rather interesting effect is analogous to the shock wave that occurs in a supersonic gas ﬂow. It is nature’s way of moving from something traveling quite fast to something moving relatively slow while maintaining continuity and momentum. The energy that is lost when making this sudden change through the hydraulic jump can be found by using the energy equation.

__Quiz No. 1__

1. The time derivative can be moved inside the volume integral in the system- to-control-volume transformation because

(A) The integrand is time independent

(B) The limits of integration are time independent

(C) The integral is over space coordinates

(D) The volume is allowed to deform

2. Air at 25°C and 240 kPa ﬂows in a 10-cm-diameter pipe at 40 m/s. The mass ﬂux is nearest

(A) 0.94 kg/s

(B) 1.14 kg/s

(C) 1.25 kg/s

(D) 1.67 kg/s

3. Water ﬂows in a 2- by 4-cm rectangular duct at 16 m/s. The duct undergoes a transition to a 6-cm-diameter pipe. Calculate the velocity in the pipe.

(A) 2.76 m/s

(B) 3.14 m/s

(C) 3.95 m/s

(D) 4.53 m/s

4. A balloon is being ﬁlled with water at an instant when the diameter is 50 cm.

If the ﬂow rate into the balloon is 0.01 m3/s, the rate of increase in the diameter is nearest

(A) 2.1 cm/s

(B) 2.6 cm/s

(C) 3.2 cm/s

(D) 3.8 cm/s

5. A sponge is contained in a volume that has one 4-cm-diameter inlet *A *into mwhich water ﬂows and two 2-cm-diameter outlets, *A *and *A *. The sponge is to have *dm/dt *= 0. Find *V*1 if *Q*2 = 0.002 m /s and *m*· 3 = 2.5 kg/s.

(A) 3.58 m/s

(B) 3.94 m/s

(C) 4.95 m/s

(D) 5.53 m/s

6. The energy equation does not assume which of the following

(A) Steady ﬂow

(B) Incompressible ﬂow

(C) Uniform ﬂow

(D) Viscous effects

7. Water enters a horizontal nozzle with diameter *d*1 = 8 cm at 10 m/s and exits to the atmosphere through a 4-cm-diameter outlet. The pressure upstream of the nozzle is nearest

(A) 600 kPa

(B) 650 kPa

(C) 700 kPa

(D) 750 kPa

8. Water is transported from one reservoir with surface elevation of 135 m to a lower reservoir with surface elevation of 25 m through a 24-cm-diameter pipe. Estimate the ﬂow rate through the pipe if the loss coefﬁcient between the two surfaces is 20.

(A) 0.23 m3/s

(B) 0.34 m3/s

(C) 0.47 m3/s

(D) 0.52 m3/s

9. A turbine extracts energy from water ﬂowing through a 10-cm-diameter pipe at a pressure of 800 kPa with an average velocity of 10 m/s. If the turbine is 90 percent efﬁcient, how much energy can be produced if the water is emitted from the turbine to the atmosphere through a 20-cm- diameter pipe?

(A) 65 kW

(B) 70 kW

(C) 75 kW

(D) 80 kW

10. A 10-cm-diameter hose delivers 0.04 m3/s of water through a 4-cm- diameter nozzle. The force of the water on the nozzle is nearest

(A) 1065 N

(B) 1370 N

(C) 1975 N

(D) 2780 N

11. A *hydraulic jump *(a sudden jump for no apparent reason) can occur in a rectangular channel with no apparent cause. The momentum equation allows the height downstream to be calculated if the upstream height and velocity are known. Neglect any frictional force on the bottom and sidewalls and determine *y*2 in the rectangular channel if *V*1 = 10 m/s and *y*1 = 50 cm.

(A) 2.75 m

(B) 2.95 m

(C) 3.15 m

(D) 3.35 m

12. A 6-cm-diameter horizontal stationary water jet having a velocity of 40 m/s strikes a vertical plate. The force needed to hold the plate if it moves away from the jet at 20 m/s is nearest

(A) 1365 N

(B) 1270 N

(C) 1130 N

(D) 1080 N

13.The blades of Fig. 4.5 deﬂect a jet of water having *V *= 40 m/s. Determine

the required blade angle *a _{ 1 }*if

*b*

_{1 }= 30°,

*a*

_{2}= 45°, and

*V*

*= 20 m/s. (A) 53.8°*

_{B}(B) 56.4°

(C) 58.2°

(D) 63.4°

14. If the jet in Prob. 13 is 2 cm in diameter, estimate the force of the jet on the blade.

(A) 387 N

(B) 404 N

(C) 487 N

(D) 521 N

__Quiz No. 2__

1. Water ﬂows in a 2- by 4-cm rectangular duct at 16 m/s. The duct undergoes a transition to a 6-cm-diameter pipe. Calculate the velocity in the pipe.

2. Air ﬂows in a 20-cm-diameter duct at 120°C and 120 kPa with a mass ﬂux of 5 kg/s. The circular duct converts to a 20-cm square duct in which the temperature and pressure are 140°C and 140 kPa, respectively. Determine the velocity in the square duct.

3. Air at 40°C and 250 kPa is ﬂowing in a 32-cm-diameter pipe at 10 m/s. The pipe changes diameter to 20 cm and the density of the air changes to 3.5 kg/m3. Calculate the velocity in the smaller diameter pipe.

4. Atmospheric air ﬂows over the ﬂat plate as shown. Viscosity makes the air stick to the surface creating a thin boundary layer. Estimate the mass ﬂux *m*· of the air across the surface that is 10 cm above the 120-cm-wide plate if *u*(*y*) = 800 *y*.

5. A sponge is contained in a volume that has one 4-cm-diameter inlet *A *into which water ﬂows and two outlets, *A *and *A *. Determine *dm/dt *of the sponge if *V *= 5 m/s, *Q*2 = 0.002 m3/s, and *m*· = 2.5 kg/s.

6. Water ﬂows from a reservoir with an elevation of 25 m out to a 12-cm- diameter pipe that has a 4-cm-diameter nozzle attached to the end. The loss coefﬁcient for the entire pipe is given as *K *= 2. Estimate the ﬂow rate of water through the pipe. The nozzle is at an elevation of 10 m.

7. A dam is proposed on a remote stream that measures approximately 25-cm deep by 350-cm wide with an average velocity of 2.2 m/s. If the dam can be constructed so that the free surface above a turbine is 10 m, estimate the maximum power output of an 88 percent efﬁcient turbine.

8. An 85 percent efﬁcient pump is used to increase the pressure in water from 120 to 800 kPa in a 10-cm-diameter pipe. What is the required horsepower of the pump for a ﬂow rate of 20 L/s?

9. Air enters a compressor at 25°C and 10 kPa with negligible velocity. It exits through a 2-cm-diameter pipe at 400 kPa and 160°C with a velocity of 200 m/s. Determine the heat transfer if the power required is 18 kW.

10. A turbine is located in a 24-cm-diameter pipe. A piezometer tube upstream of a turbine measures the same pressure as a pitot tube downstream of the turbine. If the upstream velocity is 20 m/s and the turbine is 90 percent efﬁcient, what is the turbine output?

11. A nozzle with exit diameter *d *is attached to a hose of diameter 3*d *with upstream pressure of 200 kPa. The nozzle changes the direction of the water ﬂow from the hose through an angle of 90°. Calculate the magnitude of the force of the water on the nozzle if *d *= 1 cm.

12. A *hydraulic jump *(a sudden jump for no apparent reason) can occur in a rectangular channel with no apparent cause. The continuity and momentum equations allow the variables to be related. Neglect any frictional force on the bottom and sidewalls and determine *V*1 in the rectangular channel if *V*2 = *V*1/4.

13. A 4-cm-diameter horizontal stationary water jet having a velocity of 50 m/s strikes a cone having an included angle at the apex of 60°. The water leaves the cone symmetrically. Determine the force needed to hold the cone if it moves into the jet at 20 m/s.

14. The blades of Fig. 4.6 deﬂect a 2-cm-diameter jet of water having *V*1 = 40 m/s. Determine the blade angle *a*1 and the power produced by the jet assuming no losses if *b*1 = 20°, *a*2 = 50°, and *V**B *= 15 m/s.