6.5 Physical Applications

In this section, we examine some physical applications of integration. Let’s begin with a look at calculating mass from a density function. We then turn our attention to work, and close the section with a study of hydrostatic force.

Mass and Density

We can use integration to develop a formula for calculating mass based on a density function. First we consider a thin rod or wire. Orient the rod so it aligns with the $x -axis,$ with the left end of the rod at $x = a$ and the right end of the rod at $x = b$ (Figure 6.48). Note that although we depict the rod with some thickness in the figures, for mathematical purposes we assume the rod is thin enough to be treated as a one-dimensional object.

This figure has the x and y axes. On the x-axis is a cylinder, beginning at x=a and ending at x=b. — Figure 6.48We can calculate the mass of a thin rod oriented along the $x -axis$ by integrating its density function.

If the rod has constant density $ρ,$ given in terms of mass per unit length, then the mass of the rod is just the product of the density and the length of the rod: $(b - a) ρ .$ If the density of the rod is not constant, however, the problem becomes a little more challenging. When the density of the rod varies from point to point, we use a linear density function, $ρ (x),$ to denote the density of the rod at any point, $x .$ Let $ρ (x)$ be an integrable linear density function. Now, for $i = 0, 1, 2, \dots, n$ let $P = {x_{i}}$ be a regular partition of the interval $[a, b],$ and for $i = 1, 2, \dots, n$ choose an arbitrary point $x_{i}^{*} \in [x_{i - 1}, x_{i}] .$ Figure 6.49 shows a representative segment of the rod.

This figure has the x and y axes. On the x-axis is a cylinder, beginning at x=a and ending at x=b. The cylinder has been divided into segments. One segment in the middle begins at xsub(i-1) and ends at xsubi. — Figure 6.49A representative segment of the rod.

The mass $m_{i}$ of the segment of the rod from $x_{i - 1}$ to $x_{i}$ is approximated by

m_{i} \approx ρ (x_{i}^{*}) (x_{i} - x_{i - 1}) = ρ (x_{i}^{*}) Δ x .

Adding the masses of all the segments gives us an approximation for the mass of the entire rod:

m = i = 1 \sum n m_{i} \approx i = 1 \sum n ρ (x_{i}^{*}) Δ x .

This is a Riemann sum. Taking the limit as $n \to \infty,$ we get an expression for the exact mass of the rod:

m = n \to \infty lim i = 1 \sum n ρ (x_{i}^{*}) Δ x = \int_{a}^{b} ρ (x) d x .

We state this result in the following theorem.

We apply this theorem in the next example.

We now extend this concept to find the mass of a two-dimensional disk of radius $r .$ As with the rod we looked at in the one-dimensional case, here we assume the disk is thin enough that, for mathematical purposes, we can treat it as a two-dimensional object. We assume the density is given in terms of mass per unit area (called area density), and further assume the density varies only along the disk’s radius (called radial density). We orient the disk in the $x y -plane,$ with the center at the origin. Then, the density of the disk can be treated as a function of $x,$ denoted $ρ (x) .$ We assume $ρ (x)$ is integrable. Because density is a function of $x,$ we partition the interval from $[0, r]$ along the $x -axis .$ For $i = 0, 1, 2, \dots, n,$ let $P = {x_{i}}$ be a regular partition of the interval $[0, r],$ and for $i = 1, 2, \dots, n,$ choose an arbitrary point $x_{i}^{*} \in [x_{i - 1}, x_{i}] .$ Now, use the partition to break up the disk into thin (two-dimensional) washers. A disk and a representative washer are depicted in the following figure.

This figure has two images. The first is labeled “a” and is a circle with radius r. The center of the circle is labeled 0. The circle also has the positive x-axis beginning at 0, extending through the circle. The second figure is labeled “b”. It has two concentric circles with center at 0 and the x-axis extending out from 0. The concentric circles form a washer. The width of the washer is from xsub(i-1) to xsubi and is labeled delta x. — Figure 6.50(a) A thin disk in the xy-plane. (b) A representative washer.

We now approximate the density and area of the washer to calculate an approximate mass, $m_{i} .$ Note that the area of the washer is given by

A_{i} = π (x_{i})^{2} - π (x_{i - 1})^{2} = π [x_{i}^{2} - x_{i - 1}^{2}] = π (x_{i} + x_{i - 1}) (x_{i} - x_{i - 1}) = π (x_{i} + x_{i - 1}) Δ x .

You may recall that we had an expression similar to this when we were computing volumes by shells. As we did there, we use $x_{i}^{*} \approx (x_{i} + x_{i - 1}) / 2$ to approximate the average radius of the washer. We obtain

A_{i} = π (x_{i} + x_{i - 1}) Δ x \approx 2 π x_{i}^{*} Δ x .

Using $ρ (x_{i}^{*})$ to approximate the density of the washer, we approximate the mass of the washer by

m_{i} \approx 2 π x_{i}^{*} ρ (x_{i}^{*}) Δ x .

Adding up the masses of the washers, we see the mass $m$ of the entire disk is approximated by

m = i = 1 \sum n m_{i} \approx i = 1 \sum n 2 π x_{i}^{*} ρ (x_{i}^{*}) Δ x .

We again recognize this as a Riemann sum, and take the limit as $n \to \infty.$ This gives us

m = n \to \infty lim i = 1 \sum n 2 π x_{i}^{*} ρ (x_{i}^{*}) Δ x = \int_{0}^{r} 2 π x ρ (x) d x .

We summarize these findings in the following theorem.

Work Done by a Force

We now consider work. In physics, work is related to force, which is often intuitively defined as a push or pull on an object. When a force moves an object, we say the force does work on the object. In other words, work can be thought of as the amount of energy it takes to move an object. According to physics, when we have a constant force, work can be expressed as the product of force and distance.

In the English system, the unit of force is the pound and the unit of distance is the foot, so work is given in foot-pounds. In the metric system, kilograms and meters are used. One newton is the force needed to accelerate $1$ kilogram of mass at the rate of $1$ m/sec². Thus, the most common unit of work is the newton-meter. This same unit is also called the joule. Both are defined as kilograms times meters squared over seconds squared $(kg \cdot m^{2} / s^{2}) .$

When we have a constant force, things are pretty easy. It is rare, however, for a force to be constant. The work done to compress (or elongate) a spring, for example, varies depending on how far the spring has already been compressed (or stretched). We look at springs in more detail later in this section.

Suppose we have a variable force $F (x)$ that moves an object in a positive direction along the x-axis from point $a$ to point $b .$ To calculate the work done, we partition the interval $[a, b]$ and estimate the work done over each subinterval. So, for $i = 0, 1, 2, \dots, n,$ let $P = {x_{i}}$ be a regular partition of the interval $[a, b],$ and for $i = 1, 2, \dots, n,$ choose an arbitrary point $x_{i}^{*} \in [x_{i - 1}, x_{i}] .$ To calculate the work done to move an object from point $x_{i - 1}$ to point $x_{i},$ we assume the force is roughly constant over the interval, and use $F (x_{i}^{*})$ to approximate the force. The work done over the interval $[x_{i - 1}, x_{i}],$ then, is given by

W_{i} \approx F (x_{i}^{*}) (x_{i} - x_{i - 1}) = F (x_{i}^{*}) Δ x .

Therefore, the work done over the interval $[a, b]$ is approximately

W = i = 1 \sum n W_{i} \approx i = 1 \sum n F (x_{i}^{*}) Δ x .

Taking the limit of this expression as $n \to \infty$ gives us the exact value for work:

W = n \to \infty lim i = 1 \sum n F (x_{i}^{*}) Δ x = \int_{a}^{b} F (x) d x .

Thus, we can define work as follows.

Note that if F is constant, the integral evaluates to $F \cdot (b - a) = F \cdot d,$ which is the formula we stated at the beginning of this section.

Now let’s look at the specific example of the work done to compress or elongate a spring. Consider a block attached to a horizontal spring. The block moves back and forth as the spring stretches and compresses. Although in the real world we would have to account for the force of friction between the block and the surface on which it is resting, we ignore friction here and assume the block is resting on a frictionless surface. When the spring is at its natural length (at rest), the system is said to be at equilibrium. In this state, the spring is neither elongated nor compressed, and in this equilibrium position the block does not move until some force is introduced. We orient the system such that $x = 0$ corresponds to the equilibrium position (see the following figure).

This figure has three images. The first is the x-axis. On the left is a vertical block. Attached to the block is a spring that ends at the y-axis and has the label x=0. The image is labeled equilibrium. The second image is the same spring that ends before the y-axis. It has x<0 and is labeled compressed. The third image is the same spring that is beyond the y-axis. It has x>0 and is labeled stretched. — Figure 6.51A block attached to a horizontal spring at equilibrium, compressed, and elongated.

According to Hooke’s law, the force required to compress or stretch a spring from an equilibrium position is given by $F (x) = k x,$ for some constant $k .$ The value of $k$ depends on the physical characteristics of the spring. The constant $k$ is called the spring constant and is always positive. We can use this information to calculate the work done to compress or elongate a spring, as shown in the following example.

Work Done in Pumping

Consider the work done to pump water (or some other liquid) out of a tank. Pumping problems are a little more complicated than spring problems because many of the calculations depend on the shape and size of the tank. In addition, instead of being concerned about the work done to move a single mass, we are looking at the work done to move a volume of water, and it takes more work to move the water from the bottom of the tank than it does to move the water from the top of the tank.

We examine the process in the context of a cylindrical tank, then look at a couple of examples using tanks of different shapes. Assume a cylindrical tank of radius $4$ m and height $10$ m is filled to a depth of 8 m. How much work does it take to pump all the water over the top edge of the tank?

The first thing we need to do is define a frame of reference. We let $x$ represent the vertical distance below the top of the tank. That is, we orient the $x -axis$ vertically, with the origin at the top of the tank and the downward direction being positive (see the following figure).

This figure is a right circular cylinder that is vertical. It represents a tank of water. The radius of the cylinder is 4 m, the height of the cylinder is 10 m. The height of the water inside the cylinder is 8 m. There is also a horizontal line on top of the tank representing the x=0. A line is drawn vertical beside the cylinder with a downward arrow labeled x. — Figure 6.52How much work is needed to empty a tank partially filled with water?

Using this coordinate system, the water extends from $x = 2$ to $x = 10.$ Therefore, we partition the interval $[2, 10]$ and look at the work required to lift each individual “layer” of water. So, for $i = 0, 1, 2, \dots, n,$ let $P = {x_{i}}$ be a regular partition of the interval $[2, 10],$ and for $i = 1, 2, \dots, n,$ choose an arbitrary point $x_{i}^{*} \in [x_{i - 1}, x_{i}] .$ Figure 6.53 shows a representative layer.

This figure is a right circular cylinder representing a tank of water. Inside of the cylinder is a layer of water with thickness delta x. The thickness begins at xsub(i-1) and ends at xsubi. — Figure 6.53A representative layer of water.

In pumping problems, the force required to lift the water to the top of the tank is the force required to overcome gravity, so it is equal to the weight of the water. Given that the weight-density of water is $9800$ N/m³, or $62.4$ lb/ft³, calculating the volume of each layer gives us the weight. In this case, we have

V = π (4)^{2} Δ x = 16 π Δ x .

Then, the force needed to lift each layer is

F = 9800 \cdot 16 π Δ x = 156, 800 π Δ x .

Note that this step becomes a little more difficult if we have a noncylindrical tank. We look at a noncylindrical tank in the next example.

We also need to know the distance the water must be lifted. Based on our choice of coordinate systems, we can use $x_{i}^{*}$ as an approximation of the distance the layer must be lifted. Then the work to lift the $i th$ layer of water $W_{i}$ is approximately

W_{i} \approx 156, 800 π x_{i}^{*} Δ x .

Adding the work for each layer, we see the approximate work to empty the tank is given by

W = i = 1 \sum n W_{i} \approx i = 1 \sum n 156, 800 π x_{i}^{*} Δ x .

This is a Riemann sum, so taking the limit as $n \to \infty,$ we get

W = lim_{n \to \infty} \sum_{i = 1}^{n} 156, 800 π x_{i}^{*} Δ x = 156, 800 π \int_{2}^{10} x d x = 156, 800 π [\frac{x ^{2}}{2}] ∣_{2}^{10} = 7, 526, 400 π \approx 23, 644, 883.

The work required to empty the tank is approximately 23,650,000 J.

For pumping problems, the calculations vary depending on the shape of the tank or container. The following problem-solving strategy lays out a step-by-step process for solving pumping problems.

We now apply this problem-solving strategy in an example with a noncylindrical tank.

Example 6.26A Pumping Problem with a Noncylindrical Tank

Assume a tank in the shape of an inverted cone, with height $12$ ft and base radius $4$ ft. The tank is full to start with, and water is pumped over the upper edge of the tank until the height of the water remaining in the tank is $4$ ft. How much work is required to pump out that amount of water?

Solution

The tank is depicted in Figure 6.54. As we did in the example with the cylindrical tank, we orient the $x -axis$ vertically, with the origin at the top of the tank and the downward direction being positive (step 1).

Figure 6.54A water tank in the shape of an inverted cone.

The tank starts out full and ends with $4$ ft of water left, so, based on our chosen frame of reference, we need to partition the interval $[0, 8] .$ Then, for $i = 0, 1, 2, \dots, n,$ let $P = {x_{i}}$ be a regular partition of the interval $[0, 8],$ and for $i = 1, 2, \dots, n,$ choose an arbitrary point $x_{i}^{*} \in [x_{i - 1}, x_{i}] .$ We can approximate the volume of a layer by using a disk, then use similar triangles to find the radius of the disk (see the following figure).

Figure 6.55Using similar triangles to express the radius of a disk of water.

From properties of similar triangles, we have

\frac{r _{i}}{12 - x _{i}^{*}} 3 r_{i} r_{i} = = = = \frac{4}{12} = \frac{1}{3} 12 - x_{i}^{*} \frac{12 - x _{i}^{*}}{3} 4 - \frac{x _{i}^{*}}{3} .

Then the volume of the disk is

V_{i} = π (4 - \frac{x _{i}^{*}}{3})^{2} Δ x (step 2).

The weight-density of water is $62.4$ lb/ft³, so the force needed to lift each layer is approximately

F_{i} \approx 62.4 π (4 - \frac{x _{i}^{*}}{3})^{2} Δ x (step 3).

Based on the diagram, the distance the water must be lifted is approximately $x_{i}^{*}$ feet (step 4), so the approximate work needed to lift the layer is

W_{i} \approx 62.4 π x_{i}^{*} (4 - \frac{x _{i}^{*}}{3})^{2} Δ x (step 5).

Summing the work required to lift all the layers, we get an approximate value of the total work:

W = i = 1 \sum n W_{i} \approx i = 1 \sum n 62.4 π x_{i}^{*} (4 - \frac{x _{i}^{*}}{3})^{2} Δ x (step 6).

Taking the limit as $n \to \infty,$ we obtain

W = lim_{n \to \infty} \sum_{i = 1}^{n} 62.4 π x_{i}^{*} (4 - \frac{x _{i}^{*}}{3})^{2} Δ x = \int_{0}^{8} 62.4 π x (4 - \frac{x}{3})^{2} d x = 62.4 π \int_{0}^{8} x (16 - \frac{8 x}{3} + \frac{x ^{2}}{9}) d x = 62.4 π \int_{0}^{8} (16 x - \frac{8 x ^{2}}{3} + \frac{x ^{3}}{9}) d x = 62.4 π [8 x^{2} - \frac{8 x ^{3}}{9} + \frac{x ^{4}}{36}] ∣_{0}^{8} = 10, 649.6 π \approx 33, 456.7.

It takes approximately $33, 450$ ft-lb of work to empty the tank to the desired level.

Hydrostatic Force and Pressure

In this last section, we look at the force and pressure exerted on an object submerged in a liquid. In the English system, force is measured in pounds. In the metric system, it is measured in newtons. Pressure is force per unit area, so in the English system we have pounds per square foot (or, perhaps more commonly, pounds per square inch, denoted psi). In the metric system we have newtons per square meter, also called pascals.

Let’s begin with the simple case of a plate of area $A$ submerged horizontally in water at a depth s (Figure 6.56). Then, the force exerted on the plate is simply the weight of the water above it, which is given by $F = ρ A s,$ where $ρ$ is the weight density of water (weight per unit volume). To find the hydrostatic pressure—that is, the pressure exerted by water on a submerged object—we divide the force by the area. So the pressure is $p = F / A = ρ s .$

This image has a circular plate submerged in water. The plate is labeled A and the depth of the water is labeled s. — Figure 6.56A plate submerged horizontally in water.

By Pascal’s principle, the pressure at a given depth is the same in all directions, so it does not matter if the plate is submerged horizontally or vertically. So, as long as we know the depth, we know the pressure. We can apply Pascal’s principle to find the force exerted on surfaces, such as dams, that are oriented vertically. We cannot apply the formula $F = ρ A s$ directly, because the depth varies from point to point on a vertically oriented surface. So, as we have done many times before, we form a partition, a Riemann sum, and, ultimately, a definite integral to calculate the force.

Suppose a thin plate is submerged in water. We choose our frame of reference such that the x-axis is oriented vertically, with the downward direction being positive, and point $x = 0$ corresponding to a logical reference point. Let $s (x)$ denote the depth at point x. Note we often let $x = 0$ correspond to the surface of the water. In this case, depth at any point is simply given by $s (x) = x .$ However, in some cases we may want to select a different reference point for $x = 0,$ so we proceed with the development in the more general case. Last, let $w (x)$ denote the width of the plate at the point $x .$

Assume the top edge of the plate is at point $x = a$ and the bottom edge of the plate is at point $x = b .$ Then, for $i = 0, 1, 2, \dots, n,$ let $P = {x_{i}}$ be a regular partition of the interval $[a, b],$ and for $i = 1, 2, \dots, n,$ choose an arbitrary point $x_{i}^{*} \in [x_{i - 1}, x_{i}] .$ The partition divides the plate into several thin, rectangular strips (see the following figure).

This image is the overhead view of a submerged circular plate. The x-axis is to the side of the plate. The plate’s diameter goes from x=a to x=b. There is a strip in the middle of the plate with thickness of delta x. On the axis this thickness begins at x=xsub(i-1) and ends at x=xsubi. The length of the strip in the plate is labeled w(csubi). — Figure 6.57A thin plate submerged vertically in water.

Let’s now estimate the force on a representative strip. If the strip is thin enough, we can treat it as if it is at a constant depth, $s (x_{i}^{*}) .$ We then have

F_{i} = ρ A s = ρ [w (x_{i}^{*}) Δ x] s (x_{i}^{*}) .

Adding the forces, we get an estimate for the force on the plate:

F \approx i = 1 \sum n F_{i} = i = 1 \sum n ρ [w (x_{i}^{*}) Δ x] s (x_{i}^{*}) .

This is a Riemann sum, so taking the limit gives us the exact force. We obtain

F = n \to \infty lim i = 1 \sum n ρ [w (x_{i}^{*}) Δ x] s (x_{i}^{*}) = \int_{a}^{b} ρw (x) s (x) d x .

Evaluating this integral gives us the force on the plate. We summarize this in the following problem-solving strategy.

Example 6.27Finding Hydrostatic Force

A water trough 15 ft long has ends shaped like inverted isosceles triangles, with base 8 ft and height 3 ft. Find the force on one end of the trough if the trough is full of water.

Solution

Figure 6.58 shows the trough and a more detailed view of one end.

Figure 6.58(a) A water trough with a triangular cross-section. (b) Dimensions of one end of the water trough.

Select a frame of reference with the $x -axis$ oriented vertically and the downward direction being positive. Select the top of the trough as the point corresponding to $x = 0$ (step 1). The depth function, then, is $s (x) = x .$ Using similar triangles, we see that $w (x) = 8 - (8 / 3) x$ (step 2). Now, the weight density of water is $62.4$ lb/ft³ (step 3), so applying Physical Applications, we obtain

F = \int_{a}^{b} ρw (x) s (x) d x = \int_{0}^{3} 62.4 (8 - \frac{8}{3} x) x d x = 62.4 \int_{0}^{3} (8 x - \frac{8}{3} x^{2}) d x = 62.4 [4 x^{2} - \frac{8}{9} x^{3}] ∣_{0}^{3} = 748.8.

The water exerts a force of 748.8 lb on the end of the trough (step 4).

Example 6.28Chapter Opener: Finding Hydrostatic Force

We now return our attention to the Hoover Dam, mentioned at the beginning of this chapter. The actual dam is arched, rather than flat, but we are going to make some simplifying assumptions to help us with the calculations. Assume the face of the Hoover Dam is shaped like an isosceles trapezoid with lower base $750$ ft, upper base $1250$ ft, and height $750$ ft (see the following figure).

When the reservoir is full, Lake Mead’s maximum depth is about 530 ft, and the surface of the lake is about 10 ft below the top of the dam (see the following figure).

Figure 6.59A simplified model of the Hoover Dam with assumed dimensions.

Find the force on the face of the dam when the reservoir is full.
The southwest United States has been experiencing a drought, and the surface of Lake Mead is about 125 ft below where it would be if the reservoir were full. What is the force on the face of the dam under these circumstances?

Solution

We begin by establishing a frame of reference. As usual, we choose to orient the $x -axis$ vertically, with the downward direction being positive. This time, however, we are going to let $x = 0$ represent the top of the dam, rather than the surface of the water. When the reservoir is full, the surface of the water is $10$ ft below the top of the dam, so $s (x) = x - 10$ (see the following figure).
To find the width function, we again turn to similar triangles as shown in the figure below.
From the figure, we see that $w (x) = 750 + 2 r .$ Using properties of similar triangles, we get $r = 250 - (1 / 3) x .$ Thus,
$w (x) = 1250 - \frac{2}{3} x (step 2).$
Using a weight-density of $62.4$ lb/ft³ (step 3) and applying Physical Applications, we get
$F = \int_{a}^{b} ρw (x) s (x) d x = \int_{10}^{540} 62.4 (1250 - \frac{2}{3} x) (x - 10) d x = 62.4 \int_{10}^{540} - \frac{2}{3} [x^{2} - 1885 x + 18750] d x = - 62.4 (\frac{2}{3}) [\frac{x ^{3}}{3} - \frac{1885 x ^{2}}{2} + 18750 x] ∣_{10}^{540} \approx 8, 832, 245, 000 lb = 4, 416, 122.5 t .$
Note the change from pounds to tons $(2000$ lb = $1$ ton) (step 4).
Notice that the drought changes our depth function, $s (x),$ and our limits of integration. We have $s (x) = x - 135.$ The lower limit of integration is $135.$ The upper limit remains $540.$ Evaluating the integral, we get

F = \int_{a}^{b} ρw (x) s (x) d x = \int_{135}^{540} 62.4 (1250 - \frac{2}{3} x) (x - 135) d x = - 62.4 (\frac{2}{3}) \int_{135}^{540} (x - 1875) (x - 135) d x = - 62.4 (\frac{2}{3}) \int_{135}^{540} (x^{2} - 2010 x + 253125) d x = - 62.4 (\frac{2}{3}) [\frac{x ^{3}}{3} - 1005 x^{2} + 253125 x] ∣_{135}^{540} \approx 5, 015, 230, 000 lb = 2, 507, 615 t .

Key Concepts

Several physical applications of the definite integral are common in engineering and physics.
Definite integrals can be used to determine the mass of an object if its density function is known.
Work can also be calculated from integrating a force function, or when counteracting the force of gravity, as in a pumping problem.
Definite integrals can also be used to calculate the force exerted on an object submerged in a liquid.

Key Equations

Mass of a one-dimensional object	$m = \int_{a}^{b} ρ (x) d x$
Mass of a circular object	$m = \int_{0}^{r} 2 π x ρ (x) d x$
Work done on an object	$W = \int_{a}^{b} F (x) d x$
Hydrostatic force on a plate	$F = \int_{a}^{b} ρw (x) s (x) d x$

Mass and Density

The mass $m_{i}$ of the segment of the rod from $x_{i - 1}$ to $x_{i}$ is approximated by

m_{i} \approx ρ (x_{i}^{*}) (x_{i} - x_{i - 1}) = ρ (x_{i}^{*}) Δ x .

Adding the masses of all the segments gives us an approximation for the mass of the entire rod:

m = i = 1 \sum n m_{i} \approx i = 1 \sum n ρ (x_{i}^{*}) Δ x .

This is a Riemann sum. Taking the limit as $n \to \infty,$ we get an expression for the exact mass of the rod:

m = n \to \infty lim i = 1 \sum n ρ (x_{i}^{*}) Δ x = \int_{a}^{b} ρ (x) d x .

We state this result in the following theorem.

We apply this theorem in the next example.

We now approximate the density and area of the washer to calculate an approximate mass, $m_{i} .$ Note that the area of the washer is given by

A_{i} = π (x_{i})^{2} - π (x_{i - 1})^{2} = π [x_{i}^{2} - x_{i - 1}^{2}] = π (x_{i} + x_{i - 1}) (x_{i} - x_{i - 1}) = π (x_{i} + x_{i - 1}) Δ x .

A_{i} = π (x_{i} + x_{i - 1}) Δ x \approx 2 π x_{i}^{*} Δ x .

Using $ρ (x_{i}^{*})$ to approximate the density of the washer, we approximate the mass of the washer by

m_{i} \approx 2 π x_{i}^{*} ρ (x_{i}^{*}) Δ x .

Adding up the masses of the washers, we see the mass $m$ of the entire disk is approximated by

m = i = 1 \sum n m_{i} \approx i = 1 \sum n 2 π x_{i}^{*} ρ (x_{i}^{*}) Δ x .

We again recognize this as a Riemann sum, and take the limit as $n \to \infty.$ This gives us

m = n \to \infty lim i = 1 \sum n 2 π x_{i}^{*} ρ (x_{i}^{*}) Δ x = \int_{0}^{r} 2 π x ρ (x) d x .

We summarize these findings in the following theorem.

Work Done by a Force

W_{i} \approx F (x_{i}^{*}) (x_{i} - x_{i - 1}) = F (x_{i}^{*}) Δ x .

Therefore, the work done over the interval $[a, b]$ is approximately

W = i = 1 \sum n W_{i} \approx i = 1 \sum n F (x_{i}^{*}) Δ x .

Taking the limit of this expression as $n \to \infty$ gives us the exact value for work:

W = n \to \infty lim i = 1 \sum n F (x_{i}^{*}) Δ x = \int_{a}^{b} F (x) d x .

Thus, we can define work as follows.

Note that if F is constant, the integral evaluates to $F \cdot (b - a) = F \cdot d,$ which is the formula we stated at the beginning of this section.

Work Done in Pumping

V = π (4)^{2} Δ x = 16 π Δ x .

Then, the force needed to lift each layer is

F = 9800 \cdot 16 π Δ x = 156, 800 π Δ x .

Note that this step becomes a little more difficult if we have a noncylindrical tank. We look at a noncylindrical tank in the next example.

W_{i} \approx 156, 800 π x_{i}^{*} Δ x .

Adding the work for each layer, we see the approximate work to empty the tank is given by

W = i = 1 \sum n W_{i} \approx i = 1 \sum n 156, 800 π x_{i}^{*} Δ x .

This is a Riemann sum, so taking the limit as $n \to \infty,$ we get

W = lim_{n \to \infty} \sum_{i = 1}^{n} 156, 800 π x_{i}^{*} Δ x = 156, 800 π \int_{2}^{10} x d x = 156, 800 π [\frac{x ^{2}}{2}] ∣_{2}^{10} = 7, 526, 400 π \approx 23, 644, 883.

The work required to empty the tank is approximately 23,650,000 J.

For pumping problems, the calculations vary depending on the shape of the tank or container. The following problem-solving strategy lays out a step-by-step process for solving pumping problems.

We now apply this problem-solving strategy in an example with a noncylindrical tank.

Example 6.26A Pumping Problem with a Noncylindrical Tank

Solution

Figure 6.54A water tank in the shape of an inverted cone.

Figure 6.55Using similar triangles to express the radius of a disk of water.

From properties of similar triangles, we have

\frac{r _{i}}{12 - x _{i}^{*}} 3 r_{i} r_{i} = = = = \frac{4}{12} = \frac{1}{3} 12 - x_{i}^{*} \frac{12 - x _{i}^{*}}{3} 4 - \frac{x _{i}^{*}}{3} .

Then the volume of the disk is

V_{i} = π (4 - \frac{x _{i}^{*}}{3})^{2} Δ x (step 2).

The weight-density of water is $62.4$ lb/ft³, so the force needed to lift each layer is approximately

F_{i} \approx 62.4 π (4 - \frac{x _{i}^{*}}{3})^{2} Δ x (step 3).

Based on the diagram, the distance the water must be lifted is approximately $x_{i}^{*}$ feet (step 4), so the approximate work needed to lift the layer is

W_{i} \approx 62.4 π x_{i}^{*} (4 - \frac{x _{i}^{*}}{3})^{2} Δ x (step 5).

Summing the work required to lift all the layers, we get an approximate value of the total work:

W = i = 1 \sum n W_{i} \approx i = 1 \sum n 62.4 π x_{i}^{*} (4 - \frac{x _{i}^{*}}{3})^{2} Δ x (step 6).

Taking the limit as $n \to \infty,$ we obtain

W = lim_{n \to \infty} \sum_{i = 1}^{n} 62.4 π x_{i}^{*} (4 - \frac{x _{i}^{*}}{3})^{2} Δ x = \int_{0}^{8} 62.4 π x (4 - \frac{x}{3})^{2} d x = 62.4 π \int_{0}^{8} x (16 - \frac{8 x}{3} + \frac{x ^{2}}{9}) d x = 62.4 π \int_{0}^{8} (16 x - \frac{8 x ^{2}}{3} + \frac{x ^{3}}{9}) d x = 62.4 π [8 x^{2} - \frac{8 x ^{3}}{9} + \frac{x ^{4}}{36}] ∣_{0}^{8} = 10, 649.6 π \approx 33, 456.7.

It takes approximately $33, 450$ ft-lb of work to empty the tank to the desired level.

Hydrostatic Force and Pressure

Let’s now estimate the force on a representative strip. If the strip is thin enough, we can treat it as if it is at a constant depth, $s (x_{i}^{*}) .$ We then have

F_{i} = ρ A s = ρ [w (x_{i}^{*}) Δ x] s (x_{i}^{*}) .

Adding the forces, we get an estimate for the force on the plate:

F \approx i = 1 \sum n F_{i} = i = 1 \sum n ρ [w (x_{i}^{*}) Δ x] s (x_{i}^{*}) .

This is a Riemann sum, so taking the limit gives us the exact force. We obtain

F = n \to \infty lim i = 1 \sum n ρ [w (x_{i}^{*}) Δ x] s (x_{i}^{*}) = \int_{a}^{b} ρw (x) s (x) d x .

Evaluating this integral gives us the force on the plate. We summarize this in the following problem-solving strategy.

Example 6.27Finding Hydrostatic Force

A water trough 15 ft long has ends shaped like inverted isosceles triangles, with base 8 ft and height 3 ft. Find the force on one end of the trough if the trough is full of water.

Solution

Figure 6.58 shows the trough and a more detailed view of one end.

Figure 6.58(a) A water trough with a triangular cross-section. (b) Dimensions of one end of the water trough.

F = \int_{a}^{b} ρw (x) s (x) d x = \int_{0}^{3} 62.4 (8 - \frac{8}{3} x) x d x = 62.4 \int_{0}^{3} (8 x - \frac{8}{3} x^{2}) d x = 62.4 [4 x^{2} - \frac{8}{9} x^{3}] ∣_{0}^{3} = 748.8.

The water exerts a force of 748.8 lb on the end of the trough (step 4).

Example 6.28Chapter Opener: Finding Hydrostatic Force

When the reservoir is full, Lake Mead’s maximum depth is about 530 ft, and the surface of the lake is about 10 ft below the top of the dam (see the following figure).

Figure 6.59A simplified model of the Hoover Dam with assumed dimensions.

Find the force on the face of the dam when the reservoir is full.
The southwest United States has been experiencing a drought, and the surface of Lake Mead is about 125 ft below where it would be if the reservoir were full. What is the force on the face of the dam under these circumstances?

Solution

We begin by establishing a frame of reference. As usual, we choose to orient the $x -axis$ vertically, with the downward direction being positive. This time, however, we are going to let $x = 0$ represent the top of the dam, rather than the surface of the water. When the reservoir is full, the surface of the water is $10$ ft below the top of the dam, so $s (x) = x - 10$ (see the following figure).
To find the width function, we again turn to similar triangles as shown in the figure below.
From the figure, we see that $w (x) = 750 + 2 r .$ Using properties of similar triangles, we get $r = 250 - (1 / 3) x .$ Thus,
$w (x) = 1250 - \frac{2}{3} x (step 2).$
Using a weight-density of $62.4$ lb/ft³ (step 3) and applying Physical Applications, we get
$F = \int_{a}^{b} ρw (x) s (x) d x = \int_{10}^{540} 62.4 (1250 - \frac{2}{3} x) (x - 10) d x = 62.4 \int_{10}^{540} - \frac{2}{3} [x^{2} - 1885 x + 18750] d x = - 62.4 (\frac{2}{3}) [\frac{x ^{3}}{3} - \frac{1885 x ^{2}}{2} + 18750 x] ∣_{10}^{540} \approx 8, 832, 245, 000 lb = 4, 416, 122.5 t .$
Note the change from pounds to tons $(2000$ lb = $1$ ton) (step 4).
Notice that the drought changes our depth function, $s (x),$ and our limits of integration. We have $s (x) = x - 135.$ The lower limit of integration is $135.$ The upper limit remains $540.$ Evaluating the integral, we get

F = \int_{a}^{b} ρw (x) s (x) d x = \int_{135}^{540} 62.4 (1250 - \frac{2}{3} x) (x - 135) d x = - 62.4 (\frac{2}{3}) \int_{135}^{540} (x - 1875) (x - 135) d x = - 62.4 (\frac{2}{3}) \int_{135}^{540} (x^{2} - 2010 x + 253125) d x = - 62.4 (\frac{2}{3}) [\frac{x ^{3}}{3} - 1005 x^{2} + 253125 x] ∣_{135}^{540} \approx 5, 015, 230, 000 lb = 2, 507, 615 t .

Key Concepts

Several physical applications of the definite integral are common in engineering and physics.
Definite integrals can be used to determine the mass of an object if its density function is known.
Work can also be calculated from integrating a force function, or when counteracting the force of gravity, as in a pumping problem.
Definite integrals can also be used to calculate the force exerted on an object submerged in a liquid.

Key Equations

Mass of a one-dimensional object	$m = \int_{a}^{b} ρ (x) d x$
Mass of a circular object	$m = \int_{0}^{r} 2 π x ρ (x) d x$
Work done on an object	$W = \int_{a}^{b} F (x) d x$
Hydrostatic force on a plate	$F = \int_{a}^{b} ρw (x) s (x) d x$