Our impellers have all aerofoil blades with high efficiency and favorable noise ratings. Of course electric motors are normally supported symmetrically, without feet disturbing the flow.

The blade angle can be adjusted at standstill, a big advantage when for example the duct system is modified. The aerodynamically shaped impellers are made of corrosion resistant cast aluminium alloy. It's low weight gives good life expectancy for the motor bearings.

The quick selection tables/nomogrammed is an aid for quickly selecting the most suitable impeller.

Description of single stage impellers

The standard impeller programme has four main types, N. M, X and Y with 6, 8 or 12 blades. By using guide vanes with 5 or 15 blades a high efficiency at high pressure is obtained.

1.Low pressure impeller N6 and N8

This type with 6 or 8 blades has high efficiency (up to 85 %) and good noise rating. The blue (red with guide vane) fan curves on the nomogrammed sheets or quick selection chart show the normally most advantageous performance area.

2.Medium pressure impellers M8 and X8

To achieve higher pressure and volume flow rates with good efficiency (up to 80 %) we normally use the impeller types M8 and X8 (black and blue curves on the nomogrammed sheets/quick selection chart).

3.High pressure impellers Y8 and Y12

These impellers combined with 15 bladed guide vanes provide very high pressures for axial flow fans while still maintaining good overall efficiency.

4.Reversible impellers NR8 and MR8

These impeller types allow an almost 100 % reversibility of the air flow without too much loss in performance. In addition to the above standard types a limited range of steel impellers or elder types of axial flow impellers are available.

Multistage axial flow fans

Axial flow fans can also be build in multistage versions to increase to total pressure achieved. Our various impellers with guide vanes can be installed in series. The fans are made by using motors with two shaft ends or two separate motors. The pressures can be added with a subtraction of approximately 15 % for the second stage.

The number of possible curves is so waste that they have not been included in this catalog. If the need arises please send us an inquiry.

Definition of Pitch

The pitch of the adjustable blades is defined as the distance of the trailing edge of the blade from the rim of the hub. This distance is specified in percent of the impeller diameter. Furthermore the letter "V" indicates that the trailing edge of the blades is prominent. The letter "Z" indicates that the trailing edge stands back. The indication "O" means that the distance between the trailing edge of the blade and the rim of the hub is zero, i. e. they lie in the same plane.

Example:

Impeller type: N8/V1,0/800

On this impeller having the diameter 800 mm, the trailing edge of the blade stands 1,0% of 800 mm = 8 mm out over the rim of the hub.

Materials and Surface Treatments

The fan casings are normally made of heavy gauge plates and structural steel, free from grease and oil and with negligible surface oxidation. They are painted with an epoxy resin iron oxide ground coat. All screws and nuts are galvanised. For seagoing vessels the screw connections of the service access are made of stainless steel or brass.

On request, the casings can be hot dip galvanised or receive a special coating.

The installed motors are usually designed for a temperature range of minus 25 to plus 40 degrees Celsius according to the rules VDE 0530.

Impellers are cast of GAlSi10Mg and guiding vanes are welded of rolled steel.

The impellers can withstand proofed temperatures 200°C, 2 hrs ¦ 300°C, 2 hrs ¦ 400°C, 2 hrs and 700°C, 90 minutes.

Explosion Proof

The casing of our explosion proof designs is lined with a spark protection plate of naval brass, which will cause no sparking due to friction or impact with the aluminium impeller. The motor will of course comply with pertinent rules.

Installation Guidelines

Axial fans are quite sensitive against lopsided air supply to the impeller. When different velocities reign in parallel paths of flow, turbulence may occur close to the impeller with important output losses as a consequence. Sharp bends at a short distance from the impeller should be avoided.In order to avoid a contraction of the air flow with turbulence near the duct wall, fans should have a conical inlet or a bell mouth whenever they have no duct system on their inlet side. Changes in the cross section of ducts shortly before the fan should, if possible, be carried out in such a way that no flow separations occur.

The fan output may be seriously diminished by cross section reductions shortly after the impeller. This is especially the case for axial fans with an important swirl in absence of guiding vanes. Upstream flow obstacles should be avoided, as they may create turbulence that lead to an important noise level increase.

Starting Times

The starting time is determined by both the accelerating torque, being equal to the difference between the motor torque and counter torque of the load and by the inertia of the impeller. The motor torque curve may vary considerably from case to case, in spite of existing rules. For the guaranteed starting torque, for instance, VDE 0530 rules allow a tolerance form −15 % to +25 %.For motors having the rotor class 16 the starting time is roughly:

where n is the fan speed in rpm, N the rated motor power in kW, M die mass of the fan in kg and D the impeller diameter.

For belt drive fans

n2 is to be substituted by nvent · nmot the product of the blower and motor speeds. If motor with lower starting torque's are employed, the calculated time is to be multiplied by 1,2 for rotor class 13 and 1,9 for class 10, where n is the number of fan rotations per minute, N the motor power in kW, M the impeller mass in kg and D the impeller diameter in m.

Long starting times should be expected for all axial fans having a lower speed than that of the motor, f. e. by means of a belt drive. In this and also in other cases the installation of relays for extra heavy start may be necessary.

Instability Range

The performance curves of axial fans have a more or less pronounced instability range, because of its shape often called saddle. In the range B − C (Fig. 1.6) a small increase of the flow resistance coefficient will cause a considerable decrease of the flow combined with a simultaneous decrease of the pressure produced by the fan. The working point of a fan should, if possible, be placed in its normal working range A − B, where it has the highest efficiency.

The effect of the saddle may be illustrated by means of Fig. 1.6 showing three working points of a fan. They are determined as intersection points of its performance curve with three different air flow resistance curves. These often follow the rule:

where C1, C2, C3 are the flow resistance coefficients. The necessary pressure increases with the square of the flow through a system.

Fig. 1.6 - Determination of the working point of an axial fan is intersection of its characteristic with three different resistance parables.

If we start from curve I and increase the coefficient by 20 %, we obtain curve II. The output in the new working point, defined as product of flow and total pressure, is 10 % lower than before. If the coefficient is increased once more by 20 %, we obtain curve III. The working point now falls into the saddle and the reduction of output is in the example shown 37 %.

Whenever fans work to the left of point B flow separation on the blades may cause these to vibrate considerably, eventually leading to fatigue. Especially for fans working between the points B and C the so called pumping may occur, where the working point on the curve is subject o travel continuously along the curve. This may aggravate the vibrations.

In order to prevent flow separation and pumping, our fans can on request be fitted with anti stall rings according to Prof. Eck. The fan curve will be stabilized to the dotted line with much reduced vibration levels.

Output Control/Vane controls

In most cases the use of two- or three speed motors is sufficient, sometimes in connection with a damper. It is important that the eigen frequencies of fan (especially when using frequency control) is avoided.

We also produce inlet vane controls from size 400 and upwards, allowing an economical control. Please ask for details.

Frequency converter control

When an axial fan is controlled by a frequency converter care has to be taken, that the fan is not for any length of time in one of it's resonance frequencies. The vibration amplitude must be measured on the motor itself and not on the casing. The resonance frequencies must be blocked, so that they are passed quickly.

At low rotational speeds, i. e. at low motor torque care must be taken, that the fan can not be stopped by a reverse air current, otherwise the motor may be overheated.

Electric current pulses

Especially sudden reversion of the direction of rotation as well as wind milling of axial impellers may cause large current pulses. This may cause disturbances in the electric supply net and unacceptable wear of the electric contacts. The high torque pulses may also harm impellers and electric motors.

Before the direction of rotation is reversed a sufficient run-out period must be allowed for. Wind milling may become so pronounced, that the installation of a motor brake may be recommendable, which only is released briefly before the motor is energized. When star-delta start is employed the switching over must not be done too early in order to avoid large current pulses.

Tolerances

Selection, prediction and manufacturing tolerances cannot be avoided. The tolerances for fans are summarized in the DIN 24 166. For fans the tolerance class 2 is normally applicable unless otherwise specifically agreed upon.

For special fans (e. g. rubber coated fans, special one-off impellers, gas tight design, explosion proof fans etc.) the tolerance class 3 is applicable. In case of doubt please consult one of our sales engineers.

Inlet/outlet disturbances are not included and have to be included separately.

Other tolerance levels than those given in DIN 24 166 must be agreed upon separately in writing.

Tolerances for various tolerances classes Operating conditions

The tolerances are only valid in the specified working point which is defined by the fan speed, volume flow rate, pressure increase, density and gas composition.Manufacturing tolerances

The allowable tolerances of dimensions without given tolerance values on all drawings are according to DIN 8570 Part 1, tolerance class C.