Modeling and Simulation of Rotary Screw Compressors

8/15/2019 Modeling and Simulation of Rotary Screw Compressors

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Purdue University

Purdue e-Pubs

I2$2* C+$ E&$$& C%$$$ S'* % M$'* E&$$&

1980

Modeling and Simulation of Rotary Screw CompressorsD. S. Szarkowicz

M. A. Firnhaber

F**5 2' # ##2* 5 2: '://#.*!.#$.$#/$

S757, D. S. # F'!$, M. A., "M#$*& # S+*2 % R26 S$5 C+$" (1980). International Compressor f

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REFER

ENCE

S

1

. C

oates

D .A

., D

es ig

n Tec

hniqu

e for

the

Per fo

rm an

ce O

ptim i

za t io

n of

a Sm

all R

otary

V

ane

Com pre ss or , Ph.D. Thesis,

Ray

W

H errick

L

abor

atori

es ,

Schoo

l

o

f

Mech

anica

l E n

ginee

r ing,

Pu

rdue U

nive

rs ity

, Janu

ary,

19 7

0.

2. H

amilto

n, J.F. ,

Exte

nsio n

s of

M ath

em at

ical

Mode

ling of

Pos i

tive

Dis

place

m ent T

ype

Co

m pre

ssors

,

R

ay W

H erri

ck La

borat

or ies

,

Pu r

due

U

nive

rsity,

Ju

ly,

19

74.

3. S

chw e

rzle r

, D. D

., M

athe

m at ic

al M

odelin

g

o

f

a

Mu

lti p 1

e C y

l inde r

Refr

igera

tion

Com

pr ess

or ,

Ph.D. Thesis,

Ray

W

H errick

Laboratories,

Sc

hool

of M

echan

ical

E ng in

eer in

g , P

urdue

Univ

ersity

,

Ju

ne 1

97 1.

4

.

S o e

d e l,

W. In tr

oduct

ion t

o

the

Com

puter

S

im ula

tion

of Po

si tiv

e D

isplac

em en

t

Com

pre s

sors ,

S

hort

Co

urse Te

st, Ray

W

H

erric

k

L

abora

to rie

s,

P

urdue

Univ

ersity

, July,

19 72.

5.

St

evens

o n , M.J.

,

A C

om pu

ter S

im u la

tion

of a

R ot

ary Va

ne C

om p

ressor

, M

.S.M.E

.

T

hesis

,

Ray

W

H errick

Labora tor ies,

School

of

Me

chani

cal E

n gine

er in g

, Pu

rdue U

nive r

si ty ,

A

ug us

t, 19

69.

6.

Wam

bsgan

ass, M.W.

Mat

hema

tic M

odelin

g an

d

De

sign

Ev alu

ation

of

High

Speed

R ec

iproc

at ing

Com

presso

rs ,

Ph.D.

Th

esis,

Ray

W

H e

rrick

La

bora

tories

, Sc

hool

of M

echan

ical

En gi

n ee ri

ng ,

Pu rdu

e

Un

ivers

ity,

Ja

nuar

y,

1966.


6/7

Y

ES

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RE

1

COMPUTER

SIMULATION F

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7/7

w

1-'

«

V l

0...

w·

cr:

>

V l

V l

LLl

cr:

0...

DISCHARGE

PRESSURE

0

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cr:

>

«

cr:

L1J

0...

co

_J

Vl·

V l

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l

SUCTION PRESSUR

iii L-=:::----;;==== = :::...._

~ ~

DEGREES

OF MALE

ROTATION

DEGREES

OF

MALE

ROTATION

DEGREES

OF MALE

ROTATIDN

INPUT DATA

Rotor Diameter -

127.5mm

L/D Ratio - 1.65

Built-in Pressure Ratio - 8.00

Inlet Configuration - Radial only

Discharge Configuration -

Both

radial

and

axial

Ratio of Specific Heats - 1.40

Gas

Constant -

1545 ft-lb/ lb.-mole.-

0

R

Critical

Pressure Ratio - 0.52828

Polytropic Exponent - 1

.50

for compression

Suction Pressure - -0.10 psig

Suction Temperature - 70°F.

Discharge Pressure -

100

psig

Barometric Pressure - 29.910 in. hg.

Male

Rotor Speed - 5000 rpm

Inlet

Flow

Coefficient - .10

Discharge

Flow

Coeffici€nt - .90

OUTPUT DATA

Total delivered

mass

= 21.78468 lb/min

Percent

mass enterinq

radial inlet

= 100

Percent

mass

entering axial inlet = 0.0

Percent

mass

exiting radial discharge= 17.375

Percent

mass

exitinq

axial discharge

=

82.625

Total volume flow at inlet conditions = 292.68

cfm

Indicated

power

(gas only) 57.338 hp

Suction process power loss = .756 hp

Discharge process power loss= 1.551

hp

Specific

power

= 19.591 hp/100

cfm

Volumetric efficiency

= 99.512

Adiabatic

efficiency= 91.227

Isothermal efficiency =

66.976

FIGURE 2 -

COMPUTER

SIMULATION SAMPLE OUTPUT

Modeling and Simulation of Rotary Screw Compressors

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