A large selection of outlet positions, casing geometries, casing thicknesses and materials is available for the various impeller types. The following is a description of the standard product range; a very flexible production allows special requirements to be met as well.
|Inlet size||250 up to 2800 mm|
|Casing thickness||1,5 up to 16 mm|
|Impeller types||N, M, X, Y (adjustable pitch)|
|Motor frame size||63 up to 400|
|Drive type||Coupling-, belt- or direct drive|
|Position||A, AU, AD, B, BD, BU according to Eurovent|
|Casing form||Short/long casing, swing out with/without shaped inlet|
|Surface treatment||Primer, finish, hot-dip galvanized, on request|
|Corrosion resistant cast aluminium|
|-Casing||Steel, aluminium, special alloys|
|Special design||Flame-proof, high temperature, shock proof, according to requirements|
The specific design of a fan is mainly determined by the installation in which it will be used. Beside the physical properties such as pressure, volume flow rate and temperature, the operating conditions and the installation location are of major importance (Reference DIN 24 163 for a complete description of the input parameters for a fan specification). The actual fan dimensions are mainly determined by the motors and accessories used.
Our axial flow fan range is distinguished by a large number of different standard designs. The different impeller hub-diameter rations enable us to satisfy a very large range of volume flow rate/pressure combinations for most types of installations.
The quick selection charts/nomogramm sheets and our dimension sheets give an overview over the most commonly used axial flow fans. In addition to the shown standard fans, we also manufacture a large number of special designs, e. g. explosions proof, pump room fans, shock proof fans, smoke extract fans, jet fans etc. In case of demand for special fans please inquire.
The fan selection graphs make allow a quick selection of the axial flow fans normally used at 50 Hz. They providethe fan type, the size, number of poles of the motor, the shaft power and the sound power.
The following gives a brief description of our axial flow fan casing designs.
The design of an axial flow fan is described by the casing length, the fan diameter (inside dimension), casing thickness, motor/terminal box design and the accessories. All our axial flow fans can be supplied as a standard with 2 to 10 mm casing gadge and a diameter from 250 mm to 2800 mm.
The application and the location of the fan determines the gadge. For example 2 to 4 mm is used in normal industrial installations, 3 to 6 mm below deck on ships and 8 to 10 mm above deck or in heavy duty industrial applications.
The specifications of the installation determines the design. The following gives some guidelines.
For many applications (industrial or ship building) the designs A and G (GT for jet fans) are used. The designs have a long casing that fully encloses the motor, with an external terminal box. The design A has a service access to allow minor servicing. A special case of design G (GT for jet fans) is the design GD (GDT), which has an inlet cone instead of a flange for free inlet.
For many ventilation applications a small fan is mounted in a duct system. The designs D and W (DD and WD with inlet cone for free inlet) are used for that. They have a short fan casing with the motor partly outside the casing.
In some installations it is important to be able to often access the impeller or the motor without disassembling the whole system. For this kind of applications we recommend our design B or W, WD. By having the impeller /motor mounted on a swing out type access door, all type of service and maintenance can easily be done.
For free inlet operation fans withfree inlet as DD or E should be choosen.
In principle all fans can be reversed, but with much reduced performance data.
Fans with an R (f. i. GDR) are nearly 100 % reversible by using special impellers and other special features.
For installations where the motor can not be in the airflow, we offer the designs S or T. They are for example used for applications with highly flammable gases or for material transport fans. Both designs use a V-belt drive. In design S the motor is mounted on the fan casing itself, while in design T the motor is on a separate base frame.
Our impellers have all aerofoil blades with high efficiencies and favourable 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 corrosions resistant cast aluminium alloy. It's low weight gives good life expectancy for the motor bearings.
The quick selection tables/nomogramme is an aid for quickly selecting the most suitable impeller.
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.
This type with 6 or 8 blades has high efficiencies (up to 85 %) and good noise rating. The blue (red with guide vane) fan curves on the nomogramme sheets or quick selection chart show the normally most advantageous performance area.
To achieve higher pressure and volume flow rates with good efficiencies (up to 80 %) we normally use the impeller types M8 and X8 (black and blue curves on the nomogramme sheets/quick selection chart).
These impellers combined with 15 bladed guide vanes provide very high pressures for axial flow fans while still maintaining good overall efficiencies.
These impeller types allow an almost 100 % reversibility of the air flow without too much loss in performance.
In additon to the above standard types a limited range of steel impellers or elder types of axial flow impellers are available.
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 catalogue. If the need arises please send us an inquiry.
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.
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.
The fan casings are normally made of heavy gauge plates and structural steel, free from grease and oil and with negligable 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, 2h ¦ 300°C, 2h ¦ 400°C, 2h und 700°C, 90 minutes.
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.
Axial fans are quite sensitive against lopsided air supply to the impeller. When different velocities reign in parallel pathes of flow, turbulencies 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 turbulencies near the duct wall, fans should have a conical inlet or a bellmouth 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 turbulencies that lead to an important noise level increase.
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 extrea heavy start may be necessary.
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 antistall rings according to Prof. Eck. The fan curve will be stabilised to the dotted line with much reduced vibration levels.
In most cases the use of two- or three speed motors is sufficient, sometimes in connection with a damper. It is important that the eigenfrequencies 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.
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.
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 energised.
When star-delta start is employed the switching over must not be done too early in order to avoid large current pulses.
Selection, prediction and manufacturing tolerances cannot be avoided. The tolerances for fans are summarised 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, gastight 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.
|Tolerance class acc. to DIN 24 166||1||2||3|
|Volume flow rate||± 2,5 %||± 5 %||± 10 %|
|Total pressure increase pt||± 2,5 %||± 5 %||± 10 %|
|Shaft power pw||± 3 %||± 8 %||± 16 %|
|Efficiency||− 2 %||− 5 %||−−−|
|Sound values Lw,||+ 3 dB||+ 4 dB||+ 6 dB|
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.
The allowable tolerances of dimensions without given tolerance values on all drawings are according to DIN 8570 Part 1, tolerance class C.
|Rated dimension (mm)||2
|Tolerance (mm)||± 1||± 3||± 4||± 6||± 8||± 11||± 14|