Measurements executed on the CWD 108 D pump provided with a fire hose air chamber

(1)

Measurements executed on the CWD 108 D pump provided

with a fire hose air chamber

Citation for published version (APA):

Diepens, J. F. L. (1988). Measurements executed on the CWD 108 D pump provided with a fire hose air chamber. (TU Eindhoven. Vakgr. Transportfysica : rapport; Vol. R-942-D). Technische Universiteit Eindhoven.

Document status and date: Published: 01/01/1988

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(2)

Measurements executed 'on the CwD 108 D pump

provided!:fith ,,", fireht)se "lIt r:hal'l,ber

DIEPENS. J."

August 1988

WIND ENERGY CROUP

Technical University Eindhoven Faculty of Physics

R 942 D

Laboratory of Fluid Dynamics and Heat Transfer

P.O.

Box

513

5600 MB Eindhoven. the Netherlands

Consultancy Services

Wind Energy

Developing Countries

p.O. box 85 3800 ab amersfoort holland

(3)

1 • INTRODUCT ION

2. DESCRIPTION OF THE TEST STAND

3. DESCRIPTION OF THE MEASURED CONFICURATIONS

3.1 Configuration 1 3.2 Configuration 2

4. ELUCIDATION OF THE MEASUREMENTS

4.1 Ceneral 4.2 Configuration 1 4.3 Configuration 2 S. CONCLUSIONS 6. RECOMMENDAT IONS 7. REFERENCES

ANNEX I Measured results of configuration 1

ANNEX II Measured results of configuration 2

Page 1 3 6 6 6 7 7 7 11 14 14

(4)

1. INTJKXXJCTI<IC

Upto now CWO deepwell pumps always have been equipped with normal air

chambers, see fig. 1.1.

As air will dissolve in the water constantly, it is necessary to add air.

Experiences with air supply systems have been bad up to now. The problem of

air dissolving in the water can be solved by separating air and water by

means of a membrane. Within CWO such a system was designed and baptised as

the fire Hose Air ~amber (FHAC) see fig. 1.2, this because a fire hose is

used as membrane. see fig. 1.2.

Figure 1.1 Figure 1.2

(5)

A CWO 108 0 with a FHAC has been bull t and tested at the TUE laboratory

test rig. Two configurations have been tested to check the influence of the

rate between static pressure in the air chamber and static head.

The part of the test pump, in which the FHAC is mounted, was made out of a

transparant pipe to make visual observation possible. The scope of the

visual observative was to see or the hose makes sharp bends at the places

(6)

2. DESCRIPTI(J{ OF TIlE TEST STAND (see fig. 2.1)

The pump test rig (see description in report 813 A) is provided with an

oscillating guided and sealed stainless steel rod

<p

16 to which the pump

rod can be coupled.

The stroke can be adjusted continuously from 0 upto 200 mm and the speed of

the crank rod from 0 upto 2.6 rps.

The force in the pump rod is measured with a force transducer. type: E.

Brosa + 10 KN and the velocity of the pump rod is measured with a velocity

transducer. type: Schaevitz 7LIOVT-Z.

The flow is measured with an inductive flow meter: Flowtec Dl 651 speed mag

Endress + Hauser. The water level in the pressure vessel is kept constant

automatically by means of a float valve.

The pressure in the pressure vessel can be adjusted on a certain level.

The pump tested is a CWO 108 D pump with a fire hose air chamber. The

delivery side of the pump is coupled to the pressure vessel by means of 5 m

2" and 33 m 1 1/4" CI pipe. The delivery line also counts 14xl 1/4" bends

o 0

of 90 and 2x2" bends of 45 . The used pump stroke was taken at 200 mm.

The data acquisition was done with a IBM.XT personal computer equipped with

a Metrabyte Dash 16 data acquisition board an Intel 8087 Math co-processor

and a Hercules graphics card.

10 collect and process data use was made of the scientific software package

Asyst.

The accuracy of the components of the measuring system are:

force transducer: - linearity 0.15%

- hysteresis 0.15%

(7)

speed transducer

±

1% of output

flow transducer

±

1% of maximum flow range.

The accuracy of the

AID

conversion is:

- 10 V -+ 0 bits

±

0.05

V

(8)

FORCE TRANSDUCER

VELOCITY TR&~SDUCER

FLOW METER BUNCH OF I 1/4" PIPES 3C 171

I

MA.~O METER

SURE VESSEL

--f.-fI-!~- 2 tI RI S INC MAIN

rr-;::::t.4 ....

DRAIN

FIRE HOSE AIR C~~BER VOLl~ 7 1

, ... t + t

-DRUM

CWD 108 D I r I +

(9)

-3. DESCRI PrIm OF mE JIEASUR.EI) <XIW I GURATlms

3.1 Configuration 1

The pressure in the fire hose air chamber was taken 0.94 bar. The pressure

in the pressure vessel was adjusted in a way that the total static head

equals 5 meter.

3.2 Configuration 2

The pressure in the fire hose air chamber was taken 0.94 bar. The pressure

in the pressure vessel was adjusted in a way that the total static head

(10)

-t. El..UCIDATlm OF TIlE MEASUREMENTS

1.1 General

For each configuration force, speed and flow have been measured for a range

of rotation speeds.

The measured results of each configuration are put together in a pump

performance graph. For every measured rotation speed graphs of flow and

force are given in the annexes, configuration 1 annex I and configuration 2

annex II.

1.2 Configuration 1

Calculated versus measured resonance frequency.

The resonance frequency can be calculated with: [1]

J

1 -1

_(4.2.1)

w L tot C [rad s ] 0 0 V P [m

4

s

2

kg-I] C

₌

a a

(4.2.2)

K p2

0 n pI!

_-4

L_tot

=2

_~ [kg m ]

(4.2.3)

1=1

1

p=

P + R -2

[N

m-

2]

(4.2.4)

stat tot q

1 {n

1 m

~

II}

-7 Rtot =

2?

2 c

1

2

+

2 ~

g

2

[kg m ]

(4.2.5)

1=1

A

y=1

g

A.

. i J

(11)

Data configuration 1 air chamber:

v

=

7x10-3 m3 a P

=

190314 N m-2 (absolute pressure). a piping: 2" pipe I

=

5 m -3 2

A

=

1.96x10 m 1 1/4" pipe I

=

33 m head K P P(w=1.57) C _o(w=1.51) -3 2

A

=

0.96x10 m R tot

~

1.5xl0 10 [2J -2

=

5 m

=

147150

N

m (absolute pressure)

=

1.4

=

1000 kg m-3 = 4.212x10-S m4s2 kg- 1

=

4.212x10-S m4s 2 kg- 1 1 -4 L tot

=

3.69xlO kg m -1 w o(w=1.51)

=

0.7S rad s

=

0.124 Hz

The resonance frequency measured (see annex 1-12) is ~ 0.25 Hz. It looks

like the theory isn't valid for the situation that the static pressure of air chamber is higher than the static head).

For rotation speeds ranging from 0.24 upto 0.54 a strange frequency can be seen in the flow annex 1-5 upto I-S.

The maximum volumetric efficiency of 0.141 is bad. normally it is

±

0.9.

(12)

The mechanical efficiency measured was very low (~ h maximum 0.263). The mec

reason for this can be found in the loss of power in the valve gap.

The loss of power due to hp over one valve is

112 AW

=

J

Ap AP Vp dt

o

1 2 AP

=

Cp

2"

p Vp 11" 1

J

,,3 hW

=

Ap Cp

2"

p UI

o

2 3 3 =

3

Ap Cv p w r

The work done lifting the water is

T/2

W

=

J

p g

H

Ap Vp dt

o

11"

=

P

g

H

Ap wr

J

sin wt dwt

o

=

2p g H Ap wr

(4.2.6)

(4.2.7)

(4.2.8)

(4.2.9)

(4.2.10)

(4.2.11)

( 4.2.12)

The loss of power due to pressure losses over the valve can be expressed as

a fraction of the power needed to lift the water (remember a piston pump

(13)

4 3 3 AW

3

Ap Cp p w r

W-

=

2p g

H

Ap w r 2 2 _£Cpw r - 3 g H

For the

CWO

108

D

pump tested:

Cp

~

210

I

H = 5 m r = 0.1 AW -2 2

W-

=

0.285x10 w With measurement p1080105.F01

~ _mech is 0.259 and n

=

0.536 rps for this case

~W

=

0.285x10-2*(0.536x2~)2

=

0.323.

(4.2.13)

(4.2.14)

(4.2.15)

This means that the energy loss in the valves is 0.323 times the energy

needed to lift the water.

Also the cup friction and flow friction of the piping were high and caused

(14)

Deformation of fire hose air chamber

",.,"'//

"""

(

,/tfor".,,/i(ll1

fYlinlmu{

di()l'-"'"

Fig. 4.2.1 Deformation air chamber of configuration 1.

For n=O rps and very low rotation speeds no deformation has been seen of

the membrane due to the over pressure in the air chamber.

At ~.12 the first deformation starts which grow by increasing rotation

speed see fig. 4.2.1. No sharp folds. which can cause damage to the

membrane. have been seen.

4.3. Configuration 2

Calculated versus measured resonance frequency

Data configuration 2

V

=

7xlO-3 m3

a P _a

=

190314 N m-2 (absolute pressure). Piping: 2" pipe 1 = 5

m

-3 2

A

=

1.96xlO

m

(15)

1 1/4" pipe I

=

33 m -3 2

A

=

O.96xlO m head

R

tot

~

1.5xl010 kg m-7 -2

=

11.7 m ~ 212877

N

m (absolute pressure) K = 1.4 p

=

1000 kg m-3

Using equations 4.2.1, 4.2.2, 4.2.3, 4.2.4 gives

P(w::l.26) C (w::1.26) o L tot c.J (w=1.26) o

=

213670

N

m-2

=

208xl0-8 m4s2 kg-1 7 -4

=

3.69xlO kg m -1 = 1.14 rad s

=

0.18 Hz.

The resonance frequency measured (see annex II .12) is ~ 0.2 Hz. So the

theory is a good approximation for the real situation i f the static

pressure of air chamber is less than the static head.

The strange frequency measured in the flow with configuration 1 has not

been measured with configuration 2.

The mechanical efficiency is higher than that of configuration 1 but still

considered very low.

The factor

AW 2

W

= 0.012 w (4.3.1)

(16)

Deformation of fire hose air chamber \ /tII:w 111/6 { '/1/"'"",1..;1 ". i 1ft',.,

,<I

J1"',..,4"

Fig. 4.3.1 Deformation of air chamber with configuration 2.

With this configuration the air chamber is already deformed at n=O rps to

balance the pressure of the static head and air chamber. By increasing

rotation speed the deformation becomes larger (see fig. 4.3.1).

The general impression is that the behaviour of the air chamber is good and

(17)

5. <XKl..USICKS

- The formulas used to calculate the resonance frequency are valid if the

static pressure in the air chamber is smaller than the static head.

- A ratio of P. _{alr c am r}h be

IP

_{s a lC}t t' ~ 0.8 gives good results.

A too high static pressure in the air chamber results in a strange

frequency in the flow.

- If the pressure in the air chamber is ~ 0.8 static head the behaviour of

the fire hose air chamber is the same as that of the standard air

chamber.

- The deformation of the membrane is smooth and no sharp deformations

occur.

The flow resistance of the valves is very high.

6. RECXIIIEMlATICKS

- The pressure ratio air chamber static head must be smaller than ~ O.SS.

- A ratio of air chamber volume static stroke volume ~ 3.5 gives good

results.

- The valve lifting height of the CWO 108 D pump must be increased to

decrease the valve friction.

7. REFERE1tC£S

[1] Pump rod forces due to hydrodynamic effects in piston pumps.

Frits Verheij, R 813 A. October 1986.

(18)

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