Turbulence modeling is considered an country which can further better the anticipation of flow procedures in a prison guard compressor utilizing CFD. Therefore, an extended survey on turbulency modeling in CFD on prison guard compressor flow procedure is done as a portion of this undertaking. Three standard RANS turbulency theoretical accounts: k-N” , k-I© and Reynolds Stress theoretical account are used in order to foretell the flow.

Hence, the purpose aim of the undertaking is to execute a 3D analysis of turbulent flow through the multiphase surface twin screw compressor by utilizing Star CCM+ package and analyzing the difference in using different turbulency theoretical accounts.

Screw compressor is a rotational machine of volumetric action, which transforms mechanical work of the electromotor, turbine or IC engine into possible energy of the working medium of higher force per unit area. They operate on gases, vapour or multi-phase mixtures with stage alterations taking topographic point within the machine with or without internal lubrication. [ 1 ]

The chief users of tight gases supplied by prison guard compressors today are constructing technology, nutrient, procedure and pharmaceutical industry, metallurgy and pneumatic conveyance. For optimal public presentation from such machines, a specific design and operating manner is needed for each application. They are simple machines capable of high-velocity operation over a broad scope of operating force per unit areas and flow rates with high efficiencies [ 2 ] .

Multiples characteristics of the prison guard compressor procedure and its design inside informations give certain advantage compared with all other compaction machines. Before others, these is a pure rotational motion of the compressor elements, which allow higher velocities and higher efficiency per compressor unit mass, less wear and longer life of the machine [ 2 ] .

Therefore, screw compressors are up to five times lighter than their reciprocating opposite numbers of the same capacity and their length of service can be about 10 times higher. Since they are both dependable and compact, they comprise a big part of all positive supplanting compressors sold and presently in operation. However, volumetric and adiabatic efficiency of screw compressors are extremely dependent upon the preciseness of fabrication of their rotors every bit good as other constituents, lodgings and bearings [ 2 ] . Such a preciseness can be achieved merely by usage of specialized machine tools.

During the past 30 old ages, for many applications, traditional reciprocating compressors have been replaced by those of the twin-screw type. The chief grounds for this alteration are the development of improved rotor profiles, which have drastically reduced internal escape, and machine tools, which can fabricate the most complex forms to tolerances of the order of 5 Micro metres at an low-cost cost. Although progresss have besides been made in analytical methods, which are bit by bit being adopted by interior decorators to foretell compressor public presentation more faithfully, their range and truth slowdown behind that of modern NC machine tools and assembly processs [ 3 ] .

## A

1.2 Working Principle of Screw Compressors

Screw compressors basically consist of a brace of engaging coiling lobate rotors, contained in a shell. Together, these form a series of working Chamberss [ 4 ] , as shown in Figure 1 by agencies of positions from opposite terminals and sides of the machine.

The dark shaded parts show the enclosed part where the rotors are surrounded by the shell and compaction takes topographic point, while the visible radiation shaded countries show the parts of the rotors, which are exposed to external force per unit area [ 4 ] .

The big visible radiation shaded country in Figure iˆ¤A ) corresponds to the low-pressure port.

The little visible radiation shaded part between shaft ends B and D in Figure iˆ¤B ) corresponds to the hard-hitting port. Admission of the gas to be compressed occurs through the low-pressure port, which is formed by opening the shell environing the top and front face of the rotors [ 4 ] .

Exposure of the infinite between the rotor lobes and the suction port, as their front terminals pass across it, allows the gas to make full the transitions formed between them and the shell. Further rotary motion so leads to cut off of the port and progressive decrease in the at bay volume in each transition, until the rear terminals of the transitions between the rotors are exposed to the hard-hitting discharge port. [ 4 ]

Figure A Figure B

Figure 1: The existent and bottom position for the prison guard compressor chief constituents ( Figure A- position from forepart and top, Figure B- position from underside and rear ) [ 4 ]

In order to run efficaciously, a line of contact must be formed between the two rotors and between the rotors and the shell. The length of the contact line between the rotors varies harmonizing to the angle of rotary motion and must be maintained throughout the on the job chamber formed between the two lobes and the shell [ 4 ] .

1.3 Computational Fluid Dynamics ( CFD )

Computation Fluid Dynamic ( CFD ) is a numerical method to analyze and work out the job relevant to fluid flow and unstable mechanics. The aim of CFD is to work out the numerical solution of the preservation of mass, impulse and energy, derived for a given measure of affair, called control mass with the assistance of computing machine. [ 5 ] The numerical solutions used to work out the equations depicting the Newtonian fluid flow gesture are the Navier-Stokes equations and the continuity equation which can non be solved analytically. [ 5 ]

1.4 General stairss in CFD

This chapter describes the general stairss in CFD. There are a few stairss to for the numerical solution of a fluid mechanicals job, viz. :

## 1 ) Specify the Mathematical Model

## A

A mathematical theoretical account is a set of partial derived function of integro-differential equations and boundary conditions used to depict the flow. This set includes the continuity equation, Newtonian fluids and Navier-Stokes equations. Depending on the type of flow, the equations take the appropriate signifier i.e. two or three dimensional, for compressible or incompressible fluids, for syrupy or inviscid fluid etc. [ 5 ]

## 2 ) Select the Discretization Method

An appropriate discretization method has to be selected which approximates the differential equations by a system of algebraic equations for variables at some set of distinct locations in infinite and in clip. The three common methods are finite difference, finite component method and finite volume methods. [ 5 ]

## 3 ) Select the Coordinate and base vector system

The choice of the co-ordinate system is dependent on the geometry of fluid flow. The pick of choice may act upon the discretization methods and the grid type to be used. The common available co-ordinate systems are: Cartesian, Cylindrical, Spherical, Curvilinear Orthogonal or Non-Orthogonal. [ 5 ]

## 4 ) Select Computation/Numerical Grid

The distinct locations are the variables which are to be calculated and defined by a numerical grid or computational grid. The numerical grid is a distinct stand foring the geometric sphere on which the job is to be solved. The available types of grids are structured grids, block-structured grids and unstructured grids. [ 5 ]

## 5 ) Select the Finite Estimates

The finite estimates are to be selected to be used in the discretization procedure. The estimate for the derived functions at the grid points have to be selected, in a finite difference method. The estimate surface and volume integrals have to be selected in the finite volume method. The form map and burdening maps have to be selected in finite component method. [ 5 ]

## 6 ) Solution Method

The discretization leads to a big system of non-linear algebraic equations which whose is dependent on the job. The iterative method is used to work out the additive and non-linear algebraic equations jobs. For the additive jobs, the system is solved by iterative techniques i.e. an initial solution is improved through loops ( named as interior loops ) .The pick of the convergent thinker depends on the grid type and the figure of nodes involved in each algebraic equation. For non-linear jobs, the equations are linearised foremost and so followed by the solution of the additive systems. The iterative process is employed to decide the non-linearity ( named as outer loops ) . [ 5 ]

## 7 ) Convergence Criteria

The last measure is to put the convergence standard for the iterative method. The convergence standard decides on when to halt the loops depending on the degree of truth and efficiency required. [ 5 ]

## 1.5 CFD in Screw Compressors

## A

Computation Fluid Dynamics ( CFD ) is established as the most modern technique for cardinal and applied research for screw compressors. Screw compressors were designed based on the premise of an ideal gas, = invariable, which undergoes a compaction procedure in footings of pressure-volume alterations by the pick of a suited value of the advocate “ n ” . [ 6 ]

Due to the changeless flow through the transitions and as an equation to explicate the province of the working fluid, a set of non-linear differential equations was developed to depict the instantaneous rates of heat and fluid flow work across the boundaries of the compressor system. [ 6 ] Pressure -volume alterations through the suction compaction and bringing phases, the net torsion, power input and fluid flow, isentropic and volumetric efficiencies in a prison guard compressor can be solved numerically. Despite the velocity and comparatively accurate consequences, the prison guard compressor public presentation can be estimated more exactly by a three dimension Computation Fluid Dynamic ( CFD ) .

The early theoretical accounts of prison guard compressor by CFD methods were unsuccessful due to inability to bring forth an appropriate numerical method grid for complex moving spheres. The interface grid coevals plan is called SCROG ( Screw Compressor Rotor Geometry Grid Generator ) . This was developed to be used for grid coevals to analyze the procedures in screw compressors. This package enables the numerical function of both the moving and stationary portion of the machine and direct integrating in commercial CFD of CCM ( Computation Continuum Mechanics ) . [ 6 ]

The grid coevals method played an of import function for application of CFD in the analysis of screw machines. These methods were used to decide the moving, stretching and skiding mesh required for mapping the working chamber which can non be produced within commercial grid generator bundles. DISCO ( Design Integration for Screw Compressors ) was developed in 2006, by Centre for Positive Displacement Compressor Technology, City London University. This package provided the platform for the integrating of Computer Aided Design ( CAD ) and Computation Fluid Dynamic ( CFD ) of prison guard compressors. This package managed both geometric and non geometric information transportation between several package constituents. [ 6 ]

## 1.6 Grid Coevals

An appropriate numerical grid must be generated as a necessary preliminary to a CFD computation. The grid must specify both the stationary and traveling parts of the compressor. The rotors form the most complex portion of the prison guard compressor grid and are the most of import constituents since it is within the rotor inter lobe Chamberss where the compaction procedure occurs. [ 7 ]

Depending on the comparative place of the rotors and the lodging, the procedures of suction, compaction and discharge will happen within the compressor. Rotor rotary motion consequences in alterations in the volume of the Chamberss, which increases the force per unit area, while internal force per unit area alterations cause escape flow between the Chamberss [ 7 ] .

To use a CFD process, the compressor spacial sphere must be replaced by a grid which contains distinct volumes. The figure of these volumes depends on the job dimensionality and truth required. A composite grid, made of several structured grids patched together and based on a individual boundary fitted co-ordinate system is used to transform the compressor geometry into distinct volumes [ 7 ] . Grids are so connected over defined parts on their boundaries which coincide with other parts of the full numerical mesh.

## 1.7 Turbulence Modeling

## A

Turbulence patterning played an of import function in Computational Fluid Dynamics ( CFD ) . In making a mathematical theoretical account that approximates the physical behavior of turbulent flows, grid coevals and algorithm development were the two cardinal elements to bring forth a really precise consequence in CFD. [ 8 ]

Turbulence is inherently three dimensional and clip dependant. In order to wholly depict a turbulent flow, an tremendous sum of information is required. Therefore, the complexness of the theoretical account is extremely required for the turbulency modeling.

Turbulent flows are occurred when the Reynolds figure is big. When we analyse the solutions to the Navier-Stokes Equation, or more typically to its boundary-layer signifier, they showed that turbulency developed as an instability of laminar flow. For a syrupy fluid, the instabilities resulted from interaction between the Navier-Stokes equation ‘s nonlinear inertial footings and syrupy footings. The intersection which occurred from the equations is really complex because it is rotational, to the full dimensional and clip dependant. [ 8 ]

The rotational nature of turbulency flow in three dimensional and clip dependent nature of turbulency is the grounds turbulency was the most notable unresolved scientific jobs. [ 8 ] Furthermore, when the ratio of smallest to largest graduated tables decreases quickly as the Reynolds figure additions, it made the job more complicated and hard.

Turbulence consists of a uninterrupted spectrum of graduated tables runing from largest to smallest, as opposed to a distinct set of graduated tables. In order to visualize a turbulency flow with a spectrum of graduated tables, we frequently refer to turbulent Eddies. A disruptive Eddy can be defined as a local swirling gesture whose characteristic dimension is the local turbulency graduated table. [ 8 ] Eddies overlap in infinite, where the larger 1s carry the smaller 1s and its kinetic energy are transfered from larger Eddies to smaller Eddies. We can specify that, the smallest Eddies dissipate into heat through the action of molecular viscousness. Therefore, we observe that turbulent flows are ever dissipative.

Turbulent flow diffusivity is an of import characteristic of turbulency. Disruptive diffusion greatly enhances the transportation of mass, impulse and energy. Apparent stresses which developed in turbulent flows are several orders of magnitude larger than in matching laminar flows. [ 8 ]

## 1.8 K-Epsilon Model

## A

k-N” is the most popular turbulency theoretical account, which was developed based on the attempts by Chou ( 1945 ) , Davidov ( 1961 ) , and Harlow and Nakayama ( 1968 ) . However, Jones and Lauder proposed a paper in 1972, which about reached the position of the Boussinesq and Reynolds documents. The theoretical account is so good known and it is named as the Standard k-N” theoretical account.

The Standard k-N” theoretical account is as follows:

Eddy Viscosity:

A A A A A A A ( Equation 1.6.1 ) A

where CI? is a invariable of the theoretical account.

Turbulence Kinetic Energy

I?+I?A =A A -A I?N”A +A [ ( I?+ ]

( Equation 1.6.2 )

Dissipation Rate

I?+I? = – I? + [ ( I?+ ] ( Equation 1.6.3 )

Closing Coefficients

=1.44, =1.92, =0.09, ?±k=1.0, ?±N”=1.3 ( Equation 1.6.4 )

Auxiliary Relationss

I‰ = N” / ( K ) and fifty = / N” ( Equation 1.6.5 )

## A

## 1.9 K-Omega Model

## A

k-I‰ Model was proposed by Kolmogorov in 1942 with the first two-equation theoretical account of turbulency. The kinetic energy of the turbulency as one of the turbulency parametric quantities, and the 2nd parametric quantity was the dissipation per unit turbulency kinetic energy, I‰ . As from Kolmogorov, we referred to I‰ as the rate of dissipation of energy in unit volume and clip. He besides defined its physical relation to the external graduated table of turbulency, cubic decimeter, he besides referred it to some average frequence determined by I‰ = / cubic decimeter, where C is changeless. [ 8 ]

Wilcox and Speziale wrote the equation for I‰ in term of I‰ in 1990. Most of the k-I‰ theoretical accounts use an equation for, because it has been tested more extensively than other k-I‰ theoretical accounts. [ 8 ]

Eddy Viscosity

I?T = I?k/I‰ ( Equation 1.7.1 )

Turbulence Kinetic Energy

I?I? = – I?kI‰ + [ ( I?+I?* ] ( Equation 1.7.2 )

Specific Dissipation Rate

I?+I?A =A A -+A A [ ( I?+I? ] A A A A A

( Equation 1.7.3 )

Closing Coefficients

I±=5/9, I?=3/40, =9/100, =1/2, =1/2 ( Equation 1.7.4 )

Auxiliary Relationss

?„=I‰k and cubic decimeter = /I‰ ( Equation 1.7.5 )

## 1.10 Reynolds Stress Model

## A

Reynolds emphasis is defined as the forces ( per unit country ) imposed to the mean flow by disruptive fluctuation. It arises from the nonlinear advection term when Navier-Stokes equations are Reynolds decomposed,

aˆ?iiiu

And Reynolds averaged,

The speed correlativity represents the impulse flux in the way jua?’

across a plane perpendicular to way, iE†jx

or the impulse flux in the way across a plane perpendicular to way jxE†

In a turbulent flow, the divergency of the Reynolds emphasis is of taking order in the average impulse budgets. Typically, it is several orders of magnitude larger than the syrupy emphasis. In the boundary bed, the Reynolds emphasis is perpendicular fluxes of horizontal impulse.

Reynolds emphasis theoretical account is closest to the Reynolds-Averaged Navier-Stokes equations by work outing extra conveyance equations for the Reynolds emphasiss. The conveyance equations derived by Reynolds averaging the merchandise of the impulse equations with a fluctuating belongings. Reynolds emphasis theoretical account has high potency for accurately foretelling the complex flows.

## +

## – – +

## – – +

The assorted footings in these exact equations, , , , and do non necessitate any modeling. However, , and need to be modelled to shut the equations.

## A

## Chapter 2: Literature Reappraisal

## A

## 2.1 Introduction

## A

This chapter will look into publications and other old work done which are presently undertaken by the others related to this undertaking. Therefore, this chapter presents past and current province of theoretical and methodological cognition behind the Computational of Fluid Dynamic in Screw Compressor and will briefly summarise every bit good as discuss some recent advancement on CFD in prison guard compressor.

## 2.2 CFD analysis of a multiphase prison guard compressor

## A

A CFD analysis of the escape flow and force per unit area distribution in assorted polyphase down-hole pumps has been calculated. Star CCM+ was the package used in the analysis. SCORG grid generator was used to bring forth the numerical grid in this analysis. The consequence showed that the machine with three female rotors have a smaller force per unit area bead between its inter lobes compared to the pump with two female rotors. It concluded that the lower escape flows are achieved in the machine with more female rotors and the burden on the female rotors is more or less independent of their figure.

## 2.3 SCORG- Screw COmpressor Rotor Geometry Grid generator

## A

SCORG- Screw Compressor Rotor Geometry Grid generator is an interface grid coevals plan. It used to suite enable numerical analysis of fluid flow and stress analysis in prison guard compressor by usage of Computational Continuum Mechanics ( CCM ) .

An experiment has been done by Prof.A. Kovacevic in 2002, and his study in 2004, concluded that the fluctuations in the mesh size, different turbulency theoretical accounts and differencing strategies did non impact the overall computation truth significantly. In the study, it stated that, although those differences have a low impact upon the overall public presentation, those influence upon flow development need farther probe. [ 6 ]

It was confirmed in the study that a full apprehension of the local speeds in the machine suction, compaction and discharge chamber was needed. Due to the farther proof of full 3-D CFD computation, consequences could non be obtained by the usage of simplified numerical of experimental methods. [ 6 ]

## 2.4 Cavitation in gear pumps

An probe on eroding harm, caused by cavitation, was done by Steinman in 2006. A numerical mesh was generated by the SCORG package for the probe in gear pump. From the CFD computation, it showed that the cavitation occurred in the flow through the inter lobe spreads in the way towards the suction chamber. [ 6 ]

## 2.5 Effectss of turbulency flow in prison guard compressor

An analysis was done by Vimmr, in 2006. It analysed the flow of a individual escape way through a inactive mesh at the male rotor tip and concluded that rotor comparative speed does non impact flow speeds significantly and that none of turbulency theoretical accounts used change the modeling result significantly. [ 10 ] The experiment analysed the Standard k-N” , Wilcox k-Omega, Renormalization Group ( RNG ) k-N” theoretical accounts internal flows in screw compressors.

The decision made by Vimmr, which was agreed by Prof. Kovacevic, was that farther proof of full 3-D CFD computation consequences could non be obtained by the usage of simplified numerical or experimental methods. The usage of different differencing strategies and turbulency methods significantly influences local speed and force per unit area values in certain machine parts. [ 10 ]

## 2.6 Laser Doppler Velocimetry in Screw Compressor

## A

In 2007, an experiment by utilizing Laser Doppler Velocimetry ( LDV ) was done by City University to mensurate the flow speeds inside a prison guard compressor. The subsequent consequence was obtained and represented in the graph below:

Figure 2: LDV measurings [ 6 ]

3 zones were identified in the on the job chamber near the discharge port.

Zone 1: Covers most of the chief trapped working sphere with unvarying speeds, the chamber- to-chamber speed fluctuations were up to 10 % more marked near the taking border of the rotor.

Zone 2: The gap of the discharge port, the speeds and turbulency in this zone is much higher than zone 1. The flow in zone 2 is driven by the force per unit area difference between rotors and the discharge chamber

Zone 3: Association with the escape flows between the rotors and the shell, where the speeds were higher than zone 1 but are non every bit helter-skelter as in zone 2.

Below are the decisions deducted by Guerra, in 2007, based on the experiment that had been done:

1 ) The chamber-to-chamber speed fluctuations are up to 10 % more marked near the taking border of the rotor.

2 ) The average axial flow within the on the job chamber lessenings from the draging to the taking border with speeds up to 1.75 times larger than the rotor surface speed near the tracking border part.

3 ) The consequence on speeds of the gap of the discharge port is important near the taking border of the rotors and causes a complex and unstable flow with really steep speed gradients.

## 2.7 LDV measurings compared with CFD consequences

## A

The CFD computations were generated based on the numerical mesh. The in-between sized mesh, which consisted of 935000 numerical cells, was used for comparing with LDV measurings.

Figure 3: Numeric mesh for CFD computation of prison guard compressor [ 6 ]

Figure 4: Comparison of the LDV and CFD axial speeds in the compaction chamber near to the discharge port [ 1 ]

The comparing shows a really good understanding throughout zone 1 and zone 2, but as the measured and calculated speeds in zone 3 increased, the value was larger than in the mensural 1s. [ 6 ] This was due to the inability of the k- N” turbulency theoretical account to get by with near wall flows in the big numerical cells.

Figure 5: Comparison of the measured and calculated axial speeds in the discharge port. [ 6 ]

The comparing shows that the differences appear to be instead big but the tendencies and average values are really similar. Based on the comparing that was obtained, we concluded that turbulency theoretical account plays a important function in the discharge port where narrow transitions connect the compaction chamber and the discharge sphere. The chief ground for the differences in the CFD consequences and measurings is because of the inability of the bing turbulency theoretical account to get by with near wall speeds. [ 6 ] The theoretical account ‘s truth can be developed by doing local betterments in CFD modeling, including usage of turbulency theoretical accounts suited for complex force per unit area driven internal flows.

## 2.8 CFD for Noise Prediction

## A

A 3-D CFD theoretical account was set up by Dr. Mujic in 2008 to look into force per unit area oscillations as a map of the discharge port form and the cross sectional country of the connecting rim. The force per unit area fluctuations in the discharge port can bring on mechanical noise due to rotor rattling. Besides that, the old surveies showed that equal porting can diminish the noise degree and better machine public presentation.

## A

## A

## Chapter 3: Methodology

## 3.1 Introduction

## A

This chapter will detail the methods and the stairss that had been used to make CFD analysis of the prison guard compressors. There are two packages which are used in this undertaking, Solids Works and StarCCM+ . Solids Works is a 3D CAD ( Computer Aided Design ) plan, and StarCCM+ is commercial CFD package.

## 3.2 CAD Modelling

Solid Works was used to plan and piece the assorted parts of the prison guard compressor i.e. Inlet Port, Discharge Port and the rotors. Then, a mesh was generated utilizing Star CCM+ to execute the analysis in order to foretell the flow.

Figure 6: Screw compressor rotors designed utilizing Solid Works

Figure 7: Discharge port of the prison guard compressor designed utilizing Solid Works

Figure 8: Suction port for the prison guard compressor designed utilizing Solid Works

Figure 9: The assembly for the suction port, rotor and discharge port for the prison guard compressor in showed in StarCCM+

## A

## 3.3 Mesh Generation

## A

The mesh is generated after importing the geometry from solid plants to Star CCM+ . Table ( x ) was the mesh informations obtained from the StarCCM+ . 560,464 cells have been generated for the prison guard compressor.

Figure 10: The volume mesh of the prison guard compressor that has been generated with approximately 560,000 cells

## 3.4 Defined the Continuum

## A

After bring forthing the mesh, the theoretical account continuums need to be defined. The continuum basically represents the substance ( fluid or solid ) being modelled. In this analysis, the flow is analysed utilizing laminar, K-Epsilon, K-Omega and RSM theoretical accounts of turbulency.

In StarCCM+ , certain theoretical accounts require other theoretical accounts besides to be enabled in that continuum. For case, one time a continuum contains a liquid or a gas, it needs a flow theoretical account. Once it has a flow theoretical account, it is in demand of a syrupy theoretical account ( inviscid, laminal, or turbulent ) . Once turbulency is enabled within a fluid continuum, a turbulency theoretical account must be selected.

## 1 ) Laminar Model

Figure 11: The physical theoretical account choice for laminar theoretical account

## 2 ) Standard k-N” theoretical account

Figure 12: The physical theoretical account choice for standard k-N” theoretical account

## 3 ) Standard Wilcox k-I‰ Model

Figure 13: The physical theoretical account choice for Standard Wilcox k-I‰ Model

## 4 ) Reynolds Stress turbulency theoretical account

## A

Figure 14: The physical theoretical account choice for Reynolds Stress theoretical account

## 3.5 Defined the Boundary and Initial Conditions

## A

The boundary conditions defined for the theoretical account are:

1 ) Discharge – Mass flow recess

2 ) Suction – Flow Split Outlet

3 ) Main Compressor domains – No Slip Wall

Figure 15: The suction port was defined as flow-split mercantile establishment in the theoretical account

Figure 16: The discharge port was defined as mass flow recess in the theoretical account

Figure 17: No Slip wall defined for the theoretical account

The initial conditions in a continuum specify the initial field informations for the analysis. The theoretical account requires sufficient information so that the theoretical account ‘s primary variables can be set. The initial conditions for this theoretical account are changeless force per unit area ( 0.0 Pa ) , inactive temperature ( 300K ) and changeless speed ( 0.1m/s at [ 0.0, 0.0, -0.1 ] ) .

Figure 18: The Initial status which has been set up in the theoretical account

## 3.6 Stoping Standards

## A

The fillet standards are used to stipulate how many loops the simulation will run. 1000 loops are used to obtain a converged solution. Each analysis took approximate about 5 hours running clip on the Intel Core 2 Duo Processor ( 1.66 GHz with 2 GB RAM ) .

Figure 19: The halting standards set in the theoretical accounts for analysis

## Chapter 4: Consequence AND DISCUSSIONS

## A

In order to analyze and compare the consequences obtained by the application of assorted theoretical accounts to the flow across a prison guard compressor, graphs for flow parametric quantities are drawn against the axial distance from suction along the chief rotor to the discharge.

## 4.1 Consequences for Laminar Model

## A

Graph 1: Speed Distribution for Laminar Model

Very high fluctuations are observed in all the spheres of the compressor. The mean speed is about 60m/s where the amplitude of maximal fluctuations is about 220m/s. Figure 20 shows the distribution of force per unit area across the prison guard compressor sphere.

## A

Figure 20: Pressure Distribution within the prison guard compressor for Laminar theoretical account

## 4.2 Consequences for K-Epsilon Model

## A

Graph 2: Speed distribution for K-Epsilon Model

Graph 2 and 3 show the speed distribution and the disruptive dissipation rate graphs severally across the prison guard compressor sphere chosen to analyze the consequences and figure 21 shows the force per unit area distribution across all the prison guard compressor spheres.

## A

Graph 3: Disruptive Dissipation Rate Graph for K-Epsilon Model

Figure 21: Pressure Distribution within the prison guard compressor for K-epsilon theoretical account

The amplitude of fluctuations in the chief rotors near the suction port is relatively lower for K-epsilon theoretical account when compared to the laminal theoretical account but similar amplitudes are seen towards the discharge. The norm is about 50m/s where the maximal speed is observed as 210m/s about. The disruptive dissipation rate is observed to be really low in the part exposed to suction which easy rises during the compaction and dies down towards the discharge. Distinct extremum in observed at the discharge terminal demoing some dissipation in that part.

## 4.3 Consequences for K-Omega Model

## A

Graph 4: Speed Distribution for K-Omega ModelA

## A

Graph 5: Disruptive Dissipation Rate for K-Omega Model

Figure 22: Pressure Distribution within the prison guard compressor for K-omega theoretical account

The speed distribution and disruptive dissipation rate are shown in graphs 4 and 5 severally. The consequences from K-Omega theoretical account does non differ much from those of the K-epsilon theoretical account. Figure 22 shows the force per unit area distribution in prison guard compressor domains utilizing K-Omega theoretical account. The maximal amplitude of speed is observed to be about 225m/s with an norm of about 70m/s.A

## 4.4 Consequences for RSM

## A

The speed distribution and disruptive dissipation rate are shown in graphs 6 and 7 severally. Figure 23 shows the force per unit area distribution in prison guard compressor domains utilizing Reynold ‘s Stress Model.

The consequences obtained from RSM differ significantly from the consequences obtained from the standard two equation eddy viscousness theoretical accounts. The amplitude of fluctuations is higher for the speed distribution and higher dissipation rates are observed in all the spheres of the prison guard compressor.

## A

## A

Graph 6: Speed distribution for Reynolds Stress Model

## A

Graph 7: Disruptive Dissipation Rate for Reynolds Stress Model

Figure 23: Pressure Distribution within the prison guard compressor for RSM

## 4.5 Comparison of consequences from assorted theoretical accounts

## A

The undermentioned observations have been made after analyzing the consequences obtained from all the four CFD simulations:

1. Lower amplitude of fluctuations are obtained in the speeds for all the turbulency theoretical accounts compared to the laminar theoretical account in the part near the suction sphere bespeaking that the consequence of turbulency is important in the lower compressor velocities.

2. The fluctuations in the chief compressor sphere lessening with turbulency patterning from laminal bespeaking notable alterations to the flow parametric quantities in the rotors.

3. Although the profiles for speed and dissipation rate are the same for the RANS theoretical accounts used, important alterations are observed from those obtained from the RSM and are summarised as:

a. The mean speed and maximal amplitude of fluctuations for RSM are significantly higher compared to the RANS theoretical accounts in all the spheres of the prison guard compressor. Shown in Graph 8.

B. Higher dissipation rate, are observed in the part of the male rotor exposed to the discharge by utilizing the RSM turbulency theoretical account. Shown in Graph 9.

Graph 8: Speed for Laminar, K-Epsilon, K-Omega, RSM Models

## A

## A

Graph 9: Disruptive Dissipation Rate for Reynolds Stress, K-Omega and K-Epsilon Model

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## Chapter 5: Decision

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Based on the consequences, the undermentioned decisions have been drawn:

1. Significant alterations in flow parametric quantities have been observed from laminar to turbulency theoretical accounts. Hence, it is apparent that turbulency plays a important portion in the prison guard compressor flow processes.

2. The effects of turbulency are non merely seen in the discharge sphere but besides in the suction and the chief compressor spheres.

3. The two equation eddy viscousness theoretical accounts used predict the flow good but as they suffer from some basic failings due to the premises of isotropic emphasiss, they fail to find the exact flow features in complex flows such as a prison guard machine.

4. The RSM takes into history the streamline curvature of the flow, revolving system, high strain rates while analyzing the flow and hence, better determines the flow processes within a prison guard compressor than the standard two equation theoretical accounts.

Therefore, it can be concluded that turbulency modeling is decidedly a measure in front in the modeling of screw machines to accomplish better truth and public presentation during design.

## A

## Chapter 6: RECOMMANDATIONS FOR FUTHER WORK

The undermentioned sweetenings are suggested in order to better the truth in design and public presentation of the screw machines in the field of turbulency modeling:

1. As ascertained, the RSM theoretical accounts provide better consequences in screw machine flow procedure anticipation. Hence, it is recommended that farther work is needed in implementing the RSM for the transeunt analysis of the prison guard machine.

2. Survey of consequence of turbulency in the prison guard machines, utilizing other turbulency theoretical accounts, are available in other commercial CFD package like CFX and Fluent.

3. Extensive survey can be done in the field of turbulency patterning so that a turbulency theoretical account suited for screw machines can be found and validated. Development of a new turbulency theoretical account is out of range of an MSc undertaking maintaining the clip frame in head.

4. Compare the effects of turbulency modeling in screw compressors utilizing LES and RANS turbulency theoretical accounts.