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Under what conditions can a counter-flow heat exchanger have an effectiveness of one? What would your answer be for a parallel-flow heat exchanger?

Short Answer

Expert verified
Answer: A counter-flow heat exchanger can approach an effectiveness of one under highly ideal conditions such as infinite heat transfer surface area, no heat loss to the surroundings, and an infinite temperature difference. However, for a parallel-flow heat exchanger, achieving an effectiveness of one is not possible due to the decreasing temperature difference along the flow path, leading to a lower heat transfer rate.

Step by step solution

01

Understand the concept of effectiveness in heat exchangers

Effectiveness (\(\epsilon\)) is a measure of the performance of a heat exchanger. It quantifies how well a heat exchanger transfers heat between two fluids compared to the maximum possible heat transfer. The effectiveness is defined as the ratio of the actual heat transfer rate to the maximum possible heat transfer rate. A value of one indicates that all the available heat has been transferred from one fluid to the other, making it 100% effective.
02

Understand the characteristics of counter-flow and parallel-flow heat exchangers

In a counter-flow heat exchanger, the two fluids flow in opposite directions. This allows for a higher temperature difference along the length of the heat exchanger, which leads to a higher heat transfer rate compared to a parallel-flow heat exchanger. In a parallel-flow heat exchanger, the two fluids flow in the same direction. The temperature difference between the two fluids decreases along the flow path, which leads to a lower heat transfer rate compared to a counter-flow heat exchanger.
03

Counter-flow heat exchanger - Find conditions for effectiveness of one

For a counter-flow heat exchanger to have an effectiveness of one, the heat transfer between the two fluids must be equal to the maximum possible heat transfer. This can be achieved under the following conditions: 1. Infinite heat transfer surface area 2. No heat loss to the surroundings 3. Infinite temperature difference along the heat exchanger In practical applications, it is impossible to achieve these ideal conditions; however, a counter-flow heat exchanger can approach an effectiveness of one under well-insulated conditions and with a sufficient temperature difference between the fluids.
04

Parallel-flow heat exchanger - Find conditions for effectiveness of one

For a parallel-flow heat exchanger, the effectiveness of one cannot be achieved since the temperature difference between the two fluids decreases along the flow path. The decreasing temperature difference results in a diminishing heat transfer rate, which prevents the overall heat transfer from reaching the maximum value. In summary, a counter-flow heat exchanger can approach an effectiveness of one under highly ideal conditions such as infinite heat transfer surface area, no heat loss to the surroundings, and an infinite temperature difference. However, for a parallel-flow heat exchanger, achieving an effectiveness of one is not possible due to the decreasing temperature difference along the flow path, leading to a lower heat transfer rate.

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Key Concepts

These are the key concepts you need to understand to accurately answer the question.

Counter-Flow Heat Exchanger
In a counter-flow heat exchanger, fluid pathways intersect with each other in opposite directions, fostering a fundamentally efficient mode of heat transfer. Picture two pipelines aligned parallel to each other, with hot fluid coursing through one and cold fluid through the other; now imagine the hot fluid heading north while the cold fluid moves south. This opposing flow amplifies the thermal gradient—the difference in temperature between the two fluids—throughout the entire length of the exchanger, leading to a remarkably efficient transfer of heat.

This mechanism paves the way to potentially achieve near-perfect effectiveness, a condition where the actual heat transfer rate is synonymous with the maximum possible rate. Theoretically, an ideal scenario involves infinite thermal conductivity, resulting in infinite heat transfer surface area, impeccable insulation preventing any thermal loss, and an enormous temperature differential between the ingress and egress points. Though such perfection is elusive in real-world applications, advancements in insulation and material technologies allow counter-flow heat exchangers to reach impressively high effectiveness, often making them the preferred choice in industries where maximum heat recovery is essential.
Parallel-Flow Heat Exchanger
Moving on to parallel-flow heat exchangers, where the path of the hot and cold fluids is synchronized—both traveling in the same direction. Visualize two parallel tubes with hot fluid starting at the top end in one tube and cold fluid entering at the same end in the adjacent tube. They flow side-by-side, heading towards the same exit.

The noteworthy aspect of parallel-flow designs is the initial large temperature difference between the fluids that gradually diminishes as they travel together. This decline in temperature differential restricts the performance of the exchanger, as the lower end of the system sees both fluids approaching a similar temperature, reducing the driving force for transfer. Consequently, the heat transfer rate tapers and the effectiveness never quite reaches the pinnacle of one. The inherently lower efficiency compared to the counter-flow design is a significant factor to be considered during the selection process for various applications, particularly those requiring substantial heat recovery.
Heat Transfer Rate
Diving deeper into the core of heat exchanger operations, the heat transfer rate stands as an essential metric that crystallizes the ability of the exchanger to transport thermal energy between fluids per unit time. It's pivotal to note that this rate depends heavily on the temperature gradient between the hot and cold fluids—the larger the temperature difference, the greater the potential for heat transfer.

When evaluating the efficiency of a heat exchanger, augmenting the heat transfer rate is often synonymous with improving effectiveness. This can be achieved through the enhancement of surface area for heat exchange, using materials with high thermal conductivity, or optimizing the flow patterns of the fluids. The heat transfer rate is not just an expression of the thermal dynamics within the exchanger but also a reflection of its design prowess and its suitability for specific thermal tasks in industrial or commercial environments.
Temperature Difference
The temperature difference in a heat exchanger signifies the driving force behind the heat transfer process. It's comparable to a river's current; a steeper gradient results in a swifter stream, and in the realm of heat exchangers, a larger temperature difference equates to a more vigorous heat transfer.

The challenge, however, lies in maintaining this difference. In counter-flow exchangers, the design maximizes this gradient throughout the unit, thus achieving a superior heat transfer rate. However, in parallel-flow models, the gradient dwindles as the fluids move together towards the outlet, leading to a diminished performance. This understanding of temperature difference is not only fundamental in predicting the effectiveness of a heat exchanger but also in crafting iterative design improvements for energy efficiency and operational excellence for all types of exchangers.

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Most popular questions from this chapter

Hot oil \(\left(c_{p}=2.1 \mathrm{~kJ} / \mathrm{kg} \cdot \mathrm{K}\right)\) at \(110^{\circ} \mathrm{C}\) and \(8 \mathrm{~kg} / \mathrm{s}\) is to be cooled in a heat exchanger by cold water \(\left(c_{p}=4.18 \mathrm{~kJ} / \mathrm{kg} \cdot \mathrm{K}\right)\) entering at \(10^{\circ} \mathrm{C}\) and at a rate of \(2 \mathrm{~kg} / \mathrm{s}\). The lowest temperature that oil can be cooled in this heat exchanger is (a) \(10.0^{\circ} \mathrm{C}\) (b) \(33.5^{\circ} \mathrm{C}\) (c) \(46.1^{\circ} \mathrm{C}\) (d) \(60.2^{\circ} \mathrm{C}\) (e) \(71.4^{\circ} \mathrm{C}\)

Consider a recuperative cross flow heat exchanger (both fluids unmixed) used in a gas turbine system that carries the exhaust gases at a flow rate of \(7.5 \mathrm{~kg} / \mathrm{s}\) and a temperature of \(500^{\circ} \mathrm{C}\). The air initially at \(30^{\circ} \mathrm{C}\) and flowing at a rate of \(15 \mathrm{~kg} / \mathrm{s}\) is to be heated in the recuperator. The convective heat transfer coefficients on the exhaust gas and air side are \(750 \mathrm{~W} / \mathrm{m}^{2} \cdot \mathrm{K}\) and \(300 \mathrm{~W} / \mathrm{m}^{2} \cdot \mathrm{K}\), respectively. Due to long term use of the gas turbine the recuperative heat exchanger is subject to fouling on both gas and air side that offers a resistance of \(0.0004 \mathrm{~m}^{2} \cdot \mathrm{K} / \mathrm{W}\) each. Take the properties of exhaust gas to be the same as that of air \(\left(c_{p}=1069 \mathrm{~J} / \mathrm{kg} \cdot \mathrm{K}\right)\). If the exit temperature of the exhaust gas is \(320^{\circ} \mathrm{C}\) determine \((a)\) if the air could be heated to a temperature of \(150^{\circ} \mathrm{C}(b)\) the area of heat exchanger \((c)\) if the answer to part (a) is no, then determine what should be the air mass flow rate in order to attain the desired exit temperature of \(150^{\circ} \mathrm{C}\) and \((d)\) plot variation of the exit air temperature over a temperature range of \(75^{\circ} \mathrm{C}\) to \(300^{\circ} \mathrm{C}\) with air mass flow rate assuming all the other conditions remain the same.

An air-cooled condenser is used to condense isobutane in a binary geothermal power plant. The isobutane is condensed at \(85^{\circ} \mathrm{C}\) by air \(\left(c_{p}=1.0 \mathrm{~kJ} / \mathrm{kg} \cdot \mathrm{K}\right)\) that enters at \(22^{\circ} \mathrm{C}\) at a rate of \(18 \mathrm{~kg} / \mathrm{s}\). The overall heat transfer coefficient and the surface area for this heat exchanger are \(2.4 \mathrm{~kW} / \mathrm{m}^{2} \cdot \mathrm{K}\) and \(1.25 \mathrm{~m}^{2}\), respectively. The outlet temperature of air is (a) \(45.4^{\circ} \mathrm{C}\) (b) \(40.9^{\circ} \mathrm{C}\) (c) \(37.5^{\circ} \mathrm{C}\) (d) \(34.2^{\circ} \mathrm{C}\) (e) \(31.7^{\circ} \mathrm{C}\)

An air handler is a large unmixed heat exchanger used for comfort control in large buildings. In one such application, chilled water \(\left(c_{p}=4.2 \mathrm{~kJ} / \mathrm{kg} \cdot \mathrm{K}\right)\) enters an air handler at \(5^{\circ} \mathrm{C}\) and leaves at \(12^{\circ} \mathrm{C}\) with a flow rate of \(1000 \mathrm{~kg} / \mathrm{h}\). This cold water cools \(5000 \mathrm{~kg} / \mathrm{h}\) of air \(\left(c_{p}=1.0 \mathrm{~kJ} / \mathrm{kg} \cdot \mathrm{K}\right)\) which enters the air handler at \(25^{\circ} \mathrm{C}\). If these streams are in counter-flow and the water-stream conditions remain fixed, the minimum temperature at the air outlet is (a) \(5^{\circ} \mathrm{C}\) (b) \(12^{\circ} \mathrm{C}\) (c) \(19^{\circ} \mathrm{C}\) (d) \(22^{\circ} \mathrm{C}\) (e) \(25^{\circ} \mathrm{C}\)

Consider the flow of saturated steam at \(270.1 \mathrm{kPa}\) that flows through the shell side of a shell-and-tube heat exchanger while the water flows through 4 tubes of diameter \(1.25 \mathrm{~cm}\) at a rate of \(0.25 \mathrm{~kg} / \mathrm{s}\) through each tube. The water enters the tubes of heat exchanger at \(20^{\circ} \mathrm{C}\) and exits at \(60^{\circ} \mathrm{C}\). Due to the heat exchange with the cold fluid, steam is condensed on the tubes external surface. The convection heat transfer coefficient on the steam side is \(1500 \mathrm{~W} / \mathrm{m}^{2} \cdot \mathrm{K}\), while the fouling resistance for the steam and water may be taken as \(0.00015\) and \(0.0001 \mathrm{~m}^{2} \cdot \mathrm{K} / \mathrm{W}\), respectively. Using the NTU method, determine \((a)\) effectiveness of the heat exchanger, \((b)\) length of the tube, and \((c)\) rate of steam condensation.

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