The jet pump is a low-pressure high volume flow rate pump. Simplicity of design, absence of any moving parts, ability to handle muddy water, reliability, ruggedness, and low cost, more than compensate for the relatively poor efficiency of the pump. There has been little commercial interest in the development of low area jet pumps because of their characteristically low head rise. The basic components of jet pump are inlet nozzle, throat and diffuser.

Beside the later mentioned advantages of the jet pumps the applications through industry are too numerous to mention but some of the most common ones are, in power stations jet pump has been considered as an auxiliary boost pump in Rankine cycle, in ventilation and air conditioning, pneumatic or hydraulic conveyance of products in power form, coal and cinder transport in power plants, pumping of slug from shafts bore holes and pits, solid handling eductor is a special type called a hopper eductor, pumping sand from filter beds and sparkler nozzle which is the simplest type of eductors and steam lined eductors used to remove condensate from vessels under vacuum.

A model for jet pumps is driven under the assumption that the power and the well fluids are incompressible liquids several times. When either the well or the power fluid contains gas, Lisowski [1] used liquid water as motive and driven fluids. A flow phenomenon that appears during jet pump operation is investigated. Three designs of motive nozzle: standard, with additional circumferential holes and with set of circumferential holes are examined on motive nozzle. By modification of motive nozzle it is possible to increase pumping height with almost 45%.

The same equations driven for incompressible liquids are used with modifying the mass flow rate ratio and the friction loss coefficient, in order to obtain an acceptable conformity between the theory and observation, we have to increase the hydraulic loss coefficient—up to 30 times for the present case study, which is closed-conduits, this level of correction has been determined by means of the trial and error method, Jerzy [2].

Zhu [3] studied the influence of different hydraulic structure on the efficiency, calculation results show that area ratio determines the suction capacity, throat length determines the mixing efficiency, and spray distance determines the outlet pressure. Most of the papers in the literature on the design of liquid-liquid jet pumps contain empirical information on the coefficient S/D_th. I. El-Sawaf [4] Study the effects of the pump operating conditions and geometries on the performance, the experimental investigations that the jet pump head and the head ratio decrease with increasing suction capacity and the area ratio R (A_n/A_MC) of 0.25 gives the maximum highest efficiency and the area ratio of 0.155 gives a lowest efficiency. The optimum value for S/D_th for pumping water is about 1.0. Ibrahim [5] insure the same investigations and the driving pressure of 1 bar gives the maximum delivered concentration in case of R = 0.25 and 0.4 but at R = 0.155 the driving pressure of 1.5 bar gives the maximum delivered concentration.

In addition to promoting cavitation, interference between the nozzle exterior and the throat entry interior surfaces is an important cause of the large losses in the jet pumps. The distance between the driving nozzle to the beginning of mixing chamber to driving nozzle diameter ratio of 1.5, gives the maximum for all tested cases. The mixing chamber length of 7.25 Dmix had proven superiority over the other two mixing chambers length of 6.75 and 7.86 Dmix. Mixing throat length ranging from 3.5 to approximately 10 times the throat diameters has been studied. Mueller [6] was one of the few investigators who measured the throat entry loss coefficient and his results graphically illustrate the profound effect of an adequate nozzle to throat spacing on the loss coefficient K_en (If S/D_th = 0.55 where the measured K_en value was 0.061). When the nozzle is inserted to S/D_th = 0.023, the measured K_en values were increased by an order of magnitude to 0.745, actually this radical increase in the throat entry loss coefficient reflects a combination of the main flow losses and a secondary flow losses.

Vogal [7] measured the static pressure rise in a very long throat length up to 20 diameters in length, the results illuminated an often over looked point that is the dependence of optimum throat length on the flow ratio M, regardless, of the design area ratio of the pump. For an area ratio of R = 0.219 he found that the pressure rise in the mixing throat is at 5.3 diameters at low secondary flows approaching the cut-off point, and the required or optimum mixing length increased many times the diameters at high values of the flow ratio m, i.e., under low P_d conditions.

Schulz [8] used a larger area of area ratio R = 0.219 found that the pressure peaked at L/D_th = 4.2 for (M) goes to zero as contracted with a required mixing length of L/D_th > 8.3 at a maximum flow ratio.

The mixing length required to achieve maximum pressure rise in the throat is properly viewed as the total distance from the tip of the nozzle to completion of mixing. i.e. (S/D_th + L/D_th). Note that the optimum S/D_th increased from zero for the longest throat to 2.3 throat diameters for the shortest length. Since the L/D_th values declined at a more rapid rate than growth in S/D_th, the totals declined somewhat. Note that the peak efficiency was obtained with the intermediate case, i.e., 1 diameter spacing and a 5.66 diameter mixing throat length show in the same table for two short-throat pumps.

The same trend is evident; namely, a reduction in throat length requires a doubling in nozzle to throat spacing. Sanger’s [9] study provides further information on one of the undesirable effects of excessive S/Dth values when used with a long (7.25)-mixing throat. The corresponding static pressure profiles with S/D_th = 0 or 0.96 showed continuous pressure rise through the throat and leveling off at the exit, indicating an optimum length. In contrast, a similar profile with S/D_th = 2.68 resulted in a throat pressure rise, which peaked at about 4.5 diameters and then declined due to frictional losses in the throat.

Unfortunately, the liquid jet pump is increasingly prone to cavitation as the throat spacing (S/D_th) is reduced to zero. Static pressure measurements at the throat entry show that zero spacing causes large pressure drops at the throat entry and consequently promotes cavitation. For S/D_th = 0 optimum nozzle setting for pump efficiency.

Hammoud [10] show that nozzle to throat spacing to nozzle diameter ratio (L/D), for optimum jet pump performance the drive pressure was of 1.5 bar, while increasing the motive pump pressure the pump performance decreased. Kumaraswamy [11] insures that nozzle to mixing tube spacing play an important role in the performance of the jet pump.

The test rig description and components are herein introduced to demonstrate its ability to determine the value performance and to study the different parameters affecting this value. Consequently, the operational concept, detailed design of the jet pump and its internal components are illustrated. Subsequently, the measurement techniques and uncertainty analysis are introduced. Finally test rig tuning up is achieved. The experimental apparatus of steam jet pump is shown in Figure 1. It consists of compressed air tank, feed water tank, delivered water tank, manometer, orifice meter, jet pump, and other associated equipment’s for flow control and measurement.

A 500 liter pressurized air tank is connected to a secondary 150-liter tank to increase the pressure feeding stability. The secondary tank is connected by a control valve to the orifice meter designed according to the BRITCH STANDERED (BS-1042 Part-1 1964). The orifice meter is connected to the nozzle-tube by a galvanized 18 mm pipe. A pressure gauge is inserted just before the nozzle-tube to measure the driving air pressure.

The Jet Pump consists of a converging diverging tube fabricated from Perspex plastic for visual observations studies, see Figure 2.

The upstream air pressure is measured using Bourdon gauge with measuring range of 0 - 10 bar with ±2% accuracy of full scale, while downstream air pressure is measured using Digital compound gauge with measuring range of 0 - 10 bar with ±0.1% accuracy of full scale. water mass flow rate is measured using graduated cylinder and stop watch. Air mass flow rate is measured using an orifice meter, of discharge coefficient (C_d) 62.5%, with measuring range 0 - 500 mm and ±2 mm accuracy as shown in Figure 3.

In this work the jet pump is studied experimentally to investigate the effect of Suction head, driving air pressure and the percentage of the distance between throat section and nozzle on the pump performance. Such parameters are studied and discussed below.

Figures 4(a)-(c) shows the relation between the driving air mass flow rate, and water mass flow rate at a constant S/D_th = 0.5, 1.5, and 3.0, respectively for different suction heads (H_s = −10, 10, 20, 30 cm). The driving air momentum starts to entrain water at flow rate of 1.1 × 10⁻² Kg/sec (corresponding to a supply pressure of approximately 6.5 atm.). The results show that mw is directly proportional to ma at various values of both H_s and S/D_th. Also, increasing the suction head improves the pump performance, where the water mass flow rate increases at the same driving air flow rate. Besides, decreasing S/D_th causes a slight increase in the water mass flow rate.

Figures 5(a)-(c) shows the variations of water to air mass ratio, against the driving pressure at S/D_th = 0.5, 1.5 and 3.0 respectively for different suction heads (H_s = 10, 20, 30 cm). The results reveal that increasing the driving pressure increases the driving air momentum that responsible for water entrainment mechanism through the pump. The geometrical parameter S/D_th has a vital effect on the performance of the jet pump, where as it decreases the water to air mass ratio increased at constant driving pressure. Also, increasing suction head improves the entrained water. At certain value of the driving pressure, the

driving air is increased dramatically and consequently the water to mass ratio starts to decreases as shown from Figure 5.

Figures 6(a)-(c) shows the variations of water to air mass ratio, against the driving pressure at H_s = 10, 20, and 30 cm, respectively for different values of (S/D_th = 0.5, 1.5, and 3.0). The results depict that, increasing the driving pressure is the more power consumed to entrain

the water, and consequently additional cost of the pumping process. Hence, increasing the suction head and decreasing the geometrical parameter (S/D_th) will recover the performance of the jet pump at the same driving pressure. Consequently, no additional cost is required anymore and the efficiency is conserved.

Increasing H_s leads to increase in ṁ_w for the same ṁ_a.

But the optimum performance is at S/D_th = 0.5 The driving air pressure P_a leads to proportional increase in M up to the optimum region, and then increasing P_a will lead to decreases in M. This means that driving air pressure must be limited otherwise it causes a reverse effect.

A: Cross sectional area (m²)

A_t: Total flow area (m²)

An: Nozzle (jet) cross sectional area (m²)

A_MC: Mixing chamber cross sectional area (m²)

C_d: Calibration coefficient from the orifice calibration curve (−)

d_o: Orifice diameter (m²)

D_th: Driving nozzle exit diameter (m²)

D: Tube diameter (m²)

D_oi: Orifice inside diameter (m)

D_oo: Orifice outside diameter (m)

D_mix: Mixing chamber diameter (m)

H: Static suction head (m)

H_s: Suction head is the net vertical distance between the water level in the feeding water tank and the center line of the suction tubes (m)

K: Constant (−)

K_en: Friction loss coefficient, throat entrance (−)

L_th: Throat length (m)

(ṁ_a): Air mass flow rate (m³/s)

(ṁ_w): Water mass flow rate (m³/s)

M: Water to air mass ratio (ṁ_w/ṁ_a) (−)

N: Efficiency % P_a: The driving air pressure “pressure of the jet of air coming from the nozzle (Pa)

P_US: Up-stream pressure (Pa)

P_dS: Down-stream pressure (Pa)

P_v: Vapor pressure (Pa)

R: Area ratio (A_n/A_MC) (−)

S: The distance between throat interface and driving nozzle interface (m)

Z: High of water in the upper tank (Connected to the discharge line) (m)

Α: Divergent or convergent angle (˚)