Download presentation

1
**MECH 221 FLUID MECHANICS (Fall 06/07) Chapter 9: FLOWS IN PIPE**

Instructor: Professor C. T. HSU

2
**9.1 General Concept of Flows in Pipe**

As a uniform flow enters a pipe, the velocity at the pipe walls must decrease to zero (no-slip boundary condition). Continuity indicates that the velocity at the center must increase. Thus, the velocity profile is changing continuously from the pipe entrance until it reaches a fully developed condition. This distance, L, is called the entrance length.

3
**9.1 General Concept of Flows in Pipe**

For fully developed flows (x>>L), flows become parallel, , the mean pressure remains constant over the pipe cross-section

4
**9.1 General Concept of Flows in Pipe**

Flows in a long pipe (far away from pipe entrance and exit region, x>>L) are the limit results of boundary layer flows. There are two types of pipe flows: laminar and turbulent

5
**9.1 General Concept of Flows in Pipe**

Whether the flow is laminar or turbulent depends on the Reynolds number, where Um is the cross-sectional mean velocity defined by Transition from laminar to turbulent for flows in circular pipe of diameter D occur at Re=2300

6
**9.1 General Concept of Flows in Pipe**

When pipe flow is turbulent. The velocity is unsteadily random (changing randomly with time), the flow is characterized by the mean (time-averaged) velocity defined as: Due to turbulent mixing, the velocity profile of turbulent pipe flow is more uniform then that of laminar flow.

7
**9.1 General Concept of Flows in Pipe**

Hence, the mean velocity gradient at the wall for turbulent flow is larger than laminar flow. The wall shear stress, ,is a function of the velocity gradient. The greater the change in with respect to y at the wall, the higher is the wall shear stress. Therefore, the wall shear stress and the frictional losses are higher in turbulent flow.

8
9.2 Poiseuille Flow Consider the steady, fully developed laminar flow in a straight pipe of circular cross section with constant diameter, D. The coordinate is chosen such that x is along the pipe and y is in the radius direction with the origin at the center of the pipe. y x D b

9
9.2 Poiseuille Flow For a control volume of a cylinder near the pipe center, the balance of momentum in integral form in x-direction requires that the pressure force, acting on the faces of the cylinder be equal to the shear stress acting on the circumferential area, hence In accordance with the law of friction (Newtonian fluid), have: since u decreases with increasing y

10
**9.2 Poiseuille Flow Therefore: when is constant (negative)**

Upon integration: The constant of integration, C, is obtained from the condition of no-slip at the wall. So, u=0 at y=R=D/2, there fore C=R2/4 and finally:

11
9.2 Poiseuille Flow The velocity distribution is parabolic over the radius, and the maximum velocity on the pipe axis becomes: Therefore, The volume flow rate is:

12
9.2 Poiseuille Flow The flow rate is proportional to the first power of the pressure gradient and to the fourth power of the radius of the pipe. Define mean velocity as Therefore, This solution occurs in practice as long as, Hence,

13
9.2 Poiseuille Flow The relation between the negative pressure gradient and the mean velocity of the flow is represented in engineering application by introducing a resistance coefficient of pipe flow, f. This coefficient is a non-dimensional negative pressure gradient using the dynamic head as pressure scale and the pipe diameter as length scale, i.e., Introducing the above expression for (-dp/dx), so,

14
**9.2 Poiseuille Flow At the wall, So,**

As a result, the wall friction coefficient is:

15
9.3 Head Loss in Pipe For flows in pipes, the total energy per unit of mass is given by where the correction factor is defined as, with being the mass flow rate and A is the cross sectional area.

16
9.3 Head Loss in Pipe So the total head loss between section 1 and 2 of pipes is: hl=head loss due to frictional effects in fully developed flow in constant area conduits hlm=minor losses due to entrances, fittings, area changes, etcs.

17
9.3 Head Loss in Pipe So, for a fully developed flow through a constant-area pipe, And if y1=y2,

18
9.3 Head Loss in Pipe For laminar flow, Hence

19
9.4 Turbulent Pipe Flow For turbulent flows’ we cannot evaluate the pressure drop analytically. We must use experimental data and dimensional analysis. In fully developed turbulent pipe flow, the pressure drop, , due to friction in a horizontal constant-area pipe is know to depend on: Pipe diameter, D Pipe length, L Pipe roughness, e Average flow velocity, Um Fluid density, Fluid viscosity,

20
**9.4 Turbulent Pipe Flow Therefore, Dimensional analysis,**

Experiments show that the non-dimensional head loss is directly proportional to L/D, hence

21
**9.4 Turbulent Pipe Flow Defining the friction factor as, , hence**

where f is determined experimentally. The experimental result are usually plotted in a chart called Moody Diagram.

22
9.4 Turbulent Pipe Flow In order to solve the pipe flow problems numerically, a mathematical formulation is required for the friction factor, f, in terms of the Reynolds number and the relative roughness. The most widely used formula for the friction factor is that due to Colebrook, This an implicit equation, so iteration procedure is needed to determine.

23
9.4 Turbulent Pipe Flow Miller suggested to use for the initial estimate, That produces results within 1% in a single iteration

24
**9.5 Minor Loss The minor head loss may be expressed as,**

where the loss coefficient, K, must be determined experimentally for each case. Minor head loss may be expressed as where Le is an equivalent length of straight pipe

25
**9.5 Minor Loss Source of minor loss: 1. Inlets & Outlets**

2. Enlargements & Contractions 3. Valves & Fittings 4. Pipe Bends

26
9.6 Non-Circular Ducts Pipe flow results sometimes can be used for non-circular ducts or open channel flows to estimate the head loss Use Hydraulic Diameter, A - Cross section area; P - Wetted perimeter For a circular duct, For rectangular duct, where Ar =b/a is the geometric aspect ratio

27
**9.6 Non-Circular Ducts Effect of Aspect Ratio (b/a): For square ducts:**

For wide rectangular ducts with b>>a: Thus, flows behave like channel flows However, pipe flow results can be used with good accuracy only when: b a a=b Ar=1 Dh=a b a Ar Dh2a b a b a 1/3<Ar<3

Similar presentations

© 2019 SlidePlayer.com Inc.

All rights reserved.

To make this website work, we log user data and share it with processors. To use this website, you must agree to our Privacy Policy, including cookie policy.

Ads by Google