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Anexo Proyecto fin de carrera completo en inglés Master thesis Author: Ricard Terés Duaso Matr.Num.: 528090 HTW Berlin 6/1/2011 Title: Director: Prof. Dr.-Ing. Stefan Frank Area of Mechanical engineering HTW Berlin Experimental investigation on the influence of the scroll housing on the performance of Sirocco type fan Experimental investigation on the influence of the scroll housing on the performance of Sirocco fans Abstract The aim of this work was to perform an experimental investigation on the influence of the scroll housing on the performance of Sirocco type fan (i.e. Radial fans with forward curved blades). It was developed under the Research funding of “Numerical Calculations and Designing of Sirocco Fans” in German “Numerische Berechnung und Auslegung von Trommelläufer-Ventilatoren” (NUBAT) at the University of Applied Sciences Berlin (HTW Berlin). The main goal of this work was to evaluate the behavior of the Sirocco type fan for different configurations regarding on the parameters of the scroll housing and the relative position of the rotor inside it. It was expected to find a better performance of the fan and achieve a higher static efficiency. Common Sirocco fans are about 30-55%. To achieve this goal, three main tasks were necessary. The first task was the development and manufacturing of appropriate test models of Sirocco type fan. The second was the design, organization and implementation of a measurement campaign based on an existing test rig. The final task was the compilation and evaluation of the results. After a deep review of the literature and by using the advices of the members of the team, six new models of the fan were designed by using appropriate 3D software. The sketches of these designs were sent to an external workshop in order to be manufactured. After receiving the new pieces it was necessary to assembly them and to polish them to ensure a good surface finish. A measurement campaign was organized in order to evaluate the models. The whole measurement matrix regarded the amount of 144 different variations in the configuration of the fan to be checked. By using technologically-advanced equipment i.e. high-accuracy chamber test rig, contactless torque sensor and multifunctional fan test rig, the measurements were recorded. All the data was compiled and evaluated. The measurements were converted in graphs to easy appreciate the behavior of the fan. The characteristic curves for the pressure rise, torque on shaft and static efficiency were drawn. An extensive static efficiency study was developed to find the configuration with the best static efficiency. The influences of the parameters of design were evaluated. Interesting information on the behavior of the new model of Sirocco type fan has been found. The best static efficiency recorded rises to 69% for a rotational speed of 1000 rpm. Moreover some influences and trends were found while evaluating the characteristic curves and were included in this work. Acknowledgement I would like to express my sincere gratitude to Prof. Dr.-Ing. Stepan Frank who brought me the chance to develop my Master thesis in the team of research of mechanical engineering in HTW Berlin. I appreciate specially his support and guidance during all the development of my work there. I am grateful to Adam Stuchlik for his constant advices and assistance, to all the members of the team for their helping hand in difficult moments and to my tutor in Spain, Mr Guillermo Hauke. I am grateful also to my family which in the distance always expressed me the love and support that I needed. Sincerely Ricard Terés Duaso Berlin, June 2011 Contents 1 Introduction 1.1 Description of the problem ............................................................................ 1 1.2 Objectives of this work .................................................................................. 2 1.3 Previous projects ............................................................................................ 3 1.4 State-of-the-art ............................................................................................... 3 1.4.1 Chamber test rig .................................................................................. 3 1.4.2 Torque sensor ...................................................................................... 5 2 Designed pieces for the development of this work 2.1 Parameters of design on Sirocco type fan...................................................... 7 2.1.1 Fixed parameters for the geometry of the rotor................................... 8 2.1.2 Variable parameters for the geometry of the scroll housing ............... 9 2.2 Positioning pieces for the scroll housing ..................................................... 11 2.3 Components for calibrating the torque sensor ............................................. 11 2.4 Manufacturing the models ........................................................................... 12 3 Test rig 3.1 Specifications ............................................................................................... 15 3.2 Fan test rig ................................................................................................... 16 3.2.1 Body structure ................................................................................... 16 3.2.2 Fan unit .............................................................................................. 17 3.2.3 Movement of the fan unit through the rail guides ............................. 17 3.2.4 Scroll housing integration ................................................................. 18 3.3 Integration into the chamber test rig ............................................................ 19 4 Mathematical foundations 4.1 Introduction.................................................................................................. 21 4.2 Determination of the characteristics of the fan ............................................ 22 5 Uncertainty of measurement 5.1 Resume of the sources of uncertainty in the test rig .................................... 25 6 Measurement campaign 6.1 Measurement matrix .................................................................................... 27 6.2 Procedure for measuring .............................................................................. 29 6.3 Methodology of measuring .......................................................................... 30 1.4 State-of-the-art 4 Chamber test rigs for small fans are usually designed according to the DIN 24163 and have a testing capacity starting at a flow rate of 11 m³/h up to 1600 m³/h, utill an increment of pressure of 2500 Pa. The main components of a test chamber stand are the volume measuring equipment associated to inlet and outlet sections, a support fan, a hermetically sealed housing with flow conditioner, a cabinet for measuring and the Control technology. The determination of volume flow will be done by the volume measuring equipment according to DIN EN ISO 5167. To cover the entire range of flow rates, different pipe inlets with different sections can be switch. The pressure loss in the inlet pipe will be compensated by the support fan and it will not affect to the measurement. To set the desired pressure or the desired flow rate on the suction side of the DUT (Device under Test), the required air flow generated through the support fan and the DUT, is guided into the measuring chamber through a motorized throttle valve and a diffuser. A flow conditioner is located in the hermetically sealed chamber which ensures that the airflow moves evenly to the outlet. In the outlet is positioned the Test fan. The sensors are connected to the main panel by using the appropriated data bus. The detailed measurements are recorded by a computer and appropriate software. The chamber test rig provided by ILK Dresden ensures high-accuracy data to determinate the performance curves on test. With precise and well adapted sensors is providing a uncertainty for the flow rate less than 1% and for pressure differences less than 0,5%. A scheme of the parts of the test chamber stand is shown in Figure 1.2. Figure 1.2: Scheme of the Test chamber rig by ILK Dresden 1.4 State-of-the-art 5 1.4.2 Torque sensor A torque sensor is used for monitoring the torque that is contributing on the shaft. The applications of torque sensors are diverse: They are used in assemblies to monitor a maximum torque such as engines, crankshafts, gearboxes and transmissions, or in quality control in measuring the power output of a machine. In general, torque sensors are combined with others type of sensors at the same time, for example to determine the rotational speed or the rotation angles. That allows to record certain angle positions that could be useful in the case of Sirocco type fans or to save rotational speeds in order to check out the performance of this kind of fans. Torque sensors of the latest generation effectuate the required readings by using non-contact technology, so that losses and uncertainties are reduced. These torque sensors operate on the principle of strain gage technology. The torque signal is transmitted from the rotating shaft via frequency modulation and is processed as an analog signal. These torque sensors also give the rotation angle signal as a transistor-transistor logic signal levels (TTL) from which allows the transmitted square wave frequency as a function of other devices to control the angle of rotation signal. This signal is read twice during the 360 degrees. So that means that the sensors provide two signals for every degree arranged from 1 to 360. The angle of positioning is determined by the amount offset of the two tracks. Common torque sensors start at a range of 0,35 Nm and depending on size, can reach 30 kNm. The accuracy classes are between 0,2% and 0,01% (accuracy relative to full scale). Thus, an absolute measurement uncertainty is less than 0,005 Nm. The ranges of these torque sensors reach up to 30,000 rpm. A picture of the torque sensor used in this project can be appreciated in Figure 1.3: Figure 1.3: Rotational torque sensor (source: http://www.kistler.com) 2 Designed pieces for the development of this work To achieve the objectives of this work, new mechanical pieces need to be design. We need six new scroll housings, their own positioning pieces to center them, and some auxiliary pieces to calibrate the torque sensor. In this chapter all the details of these new pieces can be found. 2.1 Parameters of design on Sirocco type fan By collecting the inheritance from Werner Roth in his comprehensive study of Sirocco type fan (Roth, 1980) we can use his description of the variables involved in the design of that kind of fans. Refer to Figure 2.1. Geometry of the scroll housing: αs: Opening angle of spiral curve αt: Angle of positioning of the tongue Se: Minimum gap between rotor and scroll housing Rt: Radius of the tongue B: Width of the scroll housing Geometry of the rotor: D 1 : Inner diameter D 2 : Outer diameter b: Width of the rotor Rb: Radius of the blade βs 1 : Inlet blade angle βs 2 : Outlet blade angle Figure 2.1: Design parameters for Sirocco type fan given by Roth 2.1 Parameters of design on Sirocco type fan 8 As this investigation is focused on the influence of the scroll housing on the performance of Sirocco type fan, we work with fix parameters on the rotor design. We will check out the influence of the parameters of the scroll housing. In addition, we evaluate how a slightly decenter from the origin position of the rotor affects on the performance of the fan. In resume: • Fixed parameters for the geometry of the rotor • Variable parameters for the geometry of the scroll housing • Once built the scroll housing, by using decentering the rotor (runout), check out the influence on the performance of the fan. 2.1.1 Fixed parameters for the geometry of the rotor The rotor used for this work is coming from the company Punker 1 . We work with this rotor because we assume that has already an optimized design and because this work is focused on the influence of the scroll housing on the performance of Sirocco type fan. The model used for the investigation has these properties: Geometry of the rotor: D 1 = 130 mm D 2 = 160 mm b = 62 mm Rb = 15 mm βs 1 = 77,3 º βs 2 = 165,4º These parameters will never change during the measurement campaign therefore there is no need to design for the rotor. 1 Punker: Blower wheels and Fan Technology (www.punker.de) Figure 2.2: Fixed parameters of design for the rotor 2.1 Parameters of design on Sirocco type fan 9 2.1.2 Variable parameters for the geometry of the scroll housing This section is one of the most important points on the design of new pieces. To perform these designs we use for one hand, again the references provided by Roth on his study, and from the other hand the knowledge provided by a previous work from a member of the team (Lückemann, 2009). Roth has experimented with Sirocco type fan and he arrived to the conclusions that for the best performance, these relations are needed: αs = 5º B/b = 1,08 Se/D 2 = 0,08 Rt/D 2 = 0,05 αt = 65º Lückemann experimented with the same type of fan on his work with good results following the next criteria: αs = 7º B/b = 1,08 Se/D 2 = 0,075 Rt/D 2 = 0,05 αt = 67º As we see the relations for obtaining high efficiencies are practically the same ones. The interest of this work is born in the fact that Roth did an exhaustive experimentation in all the aspects of the Sirocco fan: rotor, blades, housing, nozzles, tongue, etc. But with that amount of experimentation he could not practice as much detailed as to arrive a definitive conclusions. He is expressing this fact on his own words besides empathizing the lack of experimentation in this kind of fans. For instance, when he is checking the influence of the opening angle of spiral curve (αs), he uses on his measurements different angles for this purpose. These angles are αs = 3º, 5º, 7º, 9º and 11º, that is every 2 degrees. The opening angle that is giving the best efficiency for him is 5º. But could happen that the real maximum is for another angle near this one for example for 4,5º or 5,5º. That is why in this work we experiment with short divisions around that maximum. For the new investigation we experiment with divisions in every 0,5 degree in the range from 3º to 5,5º. More precisely the opening angles of spiral curves involved in the new study are: αs: 3,0º; 3,5º; 4,0º; 4,5º; 5,0º; 5,5º. We check as well two values for the width of housing that is for 67 mm and 87 mm. By using the dimensionless parameter B/b = 67/62; 87/62 = 1,08; 1,4. According 2.1 Parameters of design on Sirocco type fan 10 to Roth, the relation B/b = 1,08 should be better, but we want to repeat the experiment and check out this results for ourselves. About the value of the gap between rotor and housing we design by using the criteria of Se/D 2 = 0,075. As the outer diameter of the rotor is D 2 = 160 mm, this gap should be Se = 0,075·160 = 12 mm. The radius of the tongue is fixed according the relation Rt/D 2 = 0,05. As long as we know the D 2 , the value of this radius is Rt = 0,05·160 = 8 mm For the angle of positioning of the tongue we use the criteria of αt = 67º As a resume of the design of the new scroll housings, a final scheme is shown in Figure 2.3: Geometry of the scroll housing: Stays constant Variable αt: 67º αs: 3,0º; 3,5º; 4,0º; 4,5º; 5,0º; 5,5º Se: 12 mm B: 67; 87 mm Rt: 8 mm Figure 2.3: Parameters of design for the scroll housing For obtaining the points to drawn the logarithmic spiral contour with the different values of αs, we created a sheet tool that allows exporting these points to 3D-design software. We have a view of this tool in Appendix A. Tool for obtaining the points of the spiral curve. 2.2 Positioning pieces for the scroll housing 11 2.2 Positioning pieces for the scroll housing This piece is used to align the scroll housing in the origin position on the desk from the fan test rig in order to proceed with the measurement. As we built six scroll housings we need six positioning pieces as well. The design of this piece is easy to obtain after having the corresponding design of the housing. This part has to match inside the cavity of the housing. In addition, it is needed a hole with the diameter of the shaft of the rotor in the central point of the spiral curve that is 10 mm. Figure 2.4: Positioning piece for 5º housing An example of a positioning piece for the scroll housing of 5 degree is shown in Figure 2.4. 2.3 Components for calibrating the torque sensor The torque sensor allows to record the torque present in the shaft and afterwards to calculate the efficiency of the fan. Before mounting the torque sensor in his placement in the fan test rig, we execute a manual verification of the accuracy of the values given by this sensor although we have a regulatory certificate of calibration of it. We need a new part for this pre-calibration that has to stop the shaft in order to record the static moment created when a mass is hanging on the bar opposite side of the shaft. Refer to Figure 2.5. 2.4 Manufacturing the models 12 Figure 2.5: Pre-calibration set for the torque sensor This new piece that we need has to be able to fix or free the shaft as own necessity. 2.4 Manufacturing the models The piece to calibrate the torque sensor was manufactured in the workshop of the HTW Berlin. For manufacturing this piece, used in the calibration of the torque sensor, we created and sketch 2-d by hand. Then we wrote the regulatory sheet to send to the Workshop of the HTW Berlin. For manufacturing the scroll housings, these were sent to an extern workshop. We decided to cut it from an external company specialized in wood material. In order to cut the housing we send a file with the sketches drawn with software for designing and subsequently we create and sketch 2-d with the profile of each housing. In total are six sketches: for the housing of 3,0º-3,5º-4,0º-4,5º-5,0º and 5,5º. Additionally another six sketches for manufacturing the six positioning pieces for the housings. The restrictions for the design of the housings were to cut the piece in a block of wood of 300 x 300 mm. All the designs are adapted to this geometry. As an example, we can appreciate the sketch for the housing of 5 degree in Figure 2.6. 2.4 Manufacturing the models 13 Figure 2.6: Scroll housing of 5 degrees For more details about the final geometry of the scroll housings and the positioning pieces please refer to Appendix G. Specifications of the components. To conclude this chapter, we have a picture of the all pieces manufactured for the measurement campaign. In Figure 2.7 we can appreciate the full set of manufactured pieces for this work. In foreground there are the six positioning pieces for the housings. In middle view the complementary pieces to increase the width of housing to 87mm. Finally, in the background of the picture, the six housings of 67 millimeter width. 3.3 Integration into the chamber test rig 20 Figure 3.8: Alignment of the shaft of the fan test rig to the chamber outlet To proceed with the alignment to the test chamber we have to place manually the fan test rig. The shaft of the fan test rig has to be coincident in direction to the hole of the green centering piece of the chamber. Afterwards the test rig is ready to develop the measurements. 4 Mathematical foundations In this chapter we describe all the mathematical equations and relations that we use to process and to compare the data of this work. 4.1 Introduction To compare flow machines of different sizes and different operating conditions, it is necessary to normalize the measured data. For this purpose, are used the similarity laws of mechanical models and the dimensionless ratios. Examples are the similarity fan laws: the relation between flow rate, pressure rise and power consumption. Also the dimensionless ratios like: Number of Reynolds, dimensionless ratio of pressure, dimensionless ratio of flow rate, or dimensionless ratio of performance. The results of the measurements made (see Chapter 7 Collected data) are comparable to other flow machines by using these relations. Can be also classified entering for example in the Cordier 2 diagram. Figure 4.1: Cordier diagram (source: Carolus, 2003) In the Cordier diagram, the best points of efficiency for different flow machines are registered by using the dimensionless ratio of rotational speed σ and the dimensionless ratio of diameter δ. For the registration of the performance of Sirocco 2 Otto Cordier, German engineer 4.2 Determination of the characteristics of the fan 22 type fans are necessary to be saved e.g. the flow rate, the increase of static pressure, torque on shaft and the static efficiency. Afterwards is possible to determine dimensionless ratios such as dimensionless ratio of flow rate (f), dimensionless ratio of pressure rise (ψ) and the efficiency η (See Roth, 1980). 4.2 Determination of the characteristics of the fan In this section we specify the equations for determining the characteristics and sizes of the investigated fan that will be needed for the evaluation and registration of this fan. Using the chamber test rig it is possible to obtain for each operating point the following data: • The flow rate in m³/ h (Q) • The increase of static pressure or pressure rise in Pa (∆p st ) • The torque on shaft in Nm (M) • The rotational speed in rpm (n) In addition, the following data are recorded by the chamber test rig: • Density of the air in the chamber in kg / m³ • Pressure of the barometer in Pa • Temperature in the chamber in ° C • Relative humidity of the air in% • Mass flow in kg / h • Absolute humidity of the air g/m3 • Temperature of the room in ° C • Reynolds number Flow rate (Q) and increase of static pressure (∆p st ) of the Sirocco type fan are determined by the test chamber in m³/h and in Pa and can be used unchanged. The static efficiency (η st ) of the fan is calculated as the ratio between the delivered power on the shaft (Pmec) by the motor and the hydraulic useful hydraulic power provided by the fan (Phyd):        2 (4-1) P  ∆   (4-2)     ⁄ 100 (4-3) To determine the dimensionless ratios commented above, the following metrics and connections are necessary: 4.2 Determination of the characteristics of the fan 23 To calculate the dimensionless ratio of flow rate (f r ) 3 is necessary to use the flow rate (Q), the geometry of the rotor (D 2 ) and the rotational speed (n). There are different philosophies, such as the geometry of the flow machine is respected. Cordier has entered the turbo-machines in the chart named after him only with the diameters. Since the width of the rotor plays a critical size, the width is included in the geometry:   !" # $ % $ & ' (4-4)   " # $ % $ $ (' (4-5 ) To calculate the dimensionless ratio of static pressure rise (ψ st ) is necessary the increase of static pressure (∆P st ), the density of the medium (ρ), the geometry of the fan (D 2 ) and the rotational speed (n), as follows: )   *+, -# $ % $ $ ' $ (4-6) Finally, if we want to enter our data in Cordier diagram we need also to evaluate two more parameters: dimensionless ratio of the speed of the fan (σ) and dimensionless ratio of the geometry of the fan (δ): .  / 0/$ 2 &/3 (4-7) 4  2 0/3 / 0/$ (4-8) 3 Sub index “r” refers to radial fans 5 Uncertainty of measurement The uncertainty in the measurement of a physical value delimits a range of values within which the true value of the parameter is assumed to be. In this chapter, the uncertainty of the measurements is determined. Here we review the deviations from the flow rate, the increase of pressure of the chamber test rig, the deviations from the torque and from the speed of the torque sensor. 5.1 Resume of the sources of uncertainty in the test rig By ILK Dresden the following deviations in the chamber test rig are known: Table 5-1: Uncertainty in the chamber test rig Chamber test rig Sensors Measurement range Relative uncertainty Flow rate 11…1600 m3/h 1% from reading Pressure rise +2500 Pa 0,5% from reading Temperature ± 0,3 ºC Relative air humidity ± 1% By the specifications of the torque sensor we know: Table 5-2: Uncertainty of the torque sensor Torque sensor Sensors Measurement range Relative uncertainty Torque 0…2 Nm 0,2% full scale Rotational speed 0…7000 min - 1 0,2% full scale Finally the combined uncertainties are resumed subsequently: 5.1 Resume of the sources of uncertainty in the test rig 26 Table 5-3: Combined uncertainties for the measurements Combined uncertainty Measurement Relative uncertainty (Q, ∆Pst) 1,1% from reading (Q, η st) 7,6% from reading For more details about the quantification of the uncertainty in the test rig please refer to the literature: [10] FRANK, S. STUCHLIK, A.: Numerical analysis and design of sirocco fans with ideal and disturbed inflow and outflow. 2011. 6 Measurement campaign The aim of the measurement campaign is to record the performance of the new designed scroll housings. After this campaign we have the necessary data to develop a precise study about the designs and we will be able to analyze the data searching for the best static efficiencies and influence of the parameters of design on Sirocco type fan. 6.1 Measurement matrix This measurement campaign regards on one hand the evaluation of the new scroll housings and on the other hand the evaluation of effects on the performance of the fan when the rotor is slightly decentered from the design position. All this variations are consolidated in this measurement campaign. We detail its parts below. We have six scroll housings according to the values of the opening angle of spiral curve that we want to check out. Table 6-1: Values for evaluating the opening angle of spiral curve α s: Opening angle of spiral curve 3,0º 3,5º 4,0º 4,5º 5,0º 5,5º We have six complementary parts for the scroll housings for increasing their width from 67 mm to 87 mm which is the same than increase B/b from 1,08 to 1,4. Table 6-2: Values for evaluating the dimensionless ratio of housing width B/b: Dimensionless ratio of housing width 1,08 1,4 To decenter the rotor from the design position, we use as a reference the minimum gap between rotor and housing (Se). The original design is according to the relation Se/D 2 = 0,075. We want to decenter the rotor to the positions Se/D 2 = 0,025; 0,050; 0,010 and 0,015. That means to move the rotor to have the minimum gap of Se = 4; 8; 16 and 20 mm. Table 6-3: Values for evaluating the dimensionless ratio of the gap Se/D 2 : Dimensionless ratio of the gap between rotor and housing 0,025 0,050 0,075 0,010 0,015 6.1 Measurement matrix 28 In addition we want to set these five positions of minimum gap in two additional angles. A part from the original position (23º), we want to set the minimum gap at 0º and -23º according to general angles. In order not to confuse with the angle of positioning of the tongue (αt), we create a new variable named αe (angle of eccentricity) to define the position of the minimum gap between rotor-housing (Se). In Figure 6.1 we can appreciate more clearly in which way we want to decenter the rotor position for the measurement campaign. Figure 6.1: Decentering the rotor position according to the parameters Se and αe Although this way of decenter the rotor it has polar coordinate definition (Se, αe = 4 mm, 0º, for instance), we have to set the positions in Cartesian coordinates in Y-X- axes according to the software that controls the servomechanism. For detailed values about the positioning on X-Y-axes, please refer to Appendix B. Values for decentering the rotor. Table 6-4: Values for evaluating the angle of eccentricity of the gap αe: angle of eccentricity of the minimum gap rotor-housing 23º 0º -23º Grouping all these parameters, we can summarize all the measurement campaign as it follows. Configurations of sirocco type fan to measure: 1) αs= 3,0º; 3,5º; 4,0º; 4,5º; 5,0º; 5,5º 6 configurations 2) B/b = 1,08; 1,4 2 configurations 3) Se/D 2 = 0,025; 0,050; 0,075; 0,100; 0,150 5 configurations 4) αe = 23º; 0º; -23º 3 configurations Total 144 configurations In resume, we have 144 different configurations to evaluate. 6.2 Procedure for measuring 29 6.2 Procedure for measuring All the configurations of the Sirocco type fan are evaluated at a rotational speed of 1000 rpm. The procedure for measuring is explained subsequently: Firstly is needed a warm up for the whole test rig. The first thing to proceed is to warm up the motor. The nominal rotational speed is 1000 rpm, as said above. The criteria used to warm up this device are to switch on the motor at a rotational speed of 20% from the nominal, which is 200 rpm during 20 minutes. This warm up is requested for providing to all the assembly parts a right temperature before to start the measurement action. The parts involved in this process are the motor itself, the right angle gear, the shaft, the torque sensor, the couplings and the bearings. The chamber test rig has a process of warm up at the same time. Again by using with the same criteria of 20%, the flow rate is set to 100 m 3 /h during 20 minutes. This is necessary to raise the temperature of the internal parts of the chamber such as auxiliary support fan, internal conducts through which the air stream flows, etc. Once the system reaches the operating temperature, the next step is to locate the scroll housing into the fan test rig. When the scroll housing is assembled to the servo arms, it is needed to find the origin position. The servomechanism is digitally controlled and uses two servo arms to move the scroll housing both in X and Y axis. But the initial position has to be set manually. For this purpose the positioning pieces are used. Firstly, the positioning piece is introduced into the scroll housing of the corresponding opening angle, as we see in Figure 6.2: Figure 6.2: Setting the scroll housing of 5º to the reference position 7.1 Most relevant data grouped by housing families 36 7.1 Most relevant data grouped by housing families 7.1.1 Scroll housing with opening angle of spiral curve of αs = 3,0° Figure 7.1: Increase of static pressure vs. flow rate curves of the Sirocco type fan D160x62mm at 1000rpm, scroll housing with an opening angle of 3º. Figure 7.2: Torque on shaft vs. flow rate curves of the Sirocco type fan D160x62mm at 1000rpm, scroll housing with an opening angle of 3º. 0 20 40 60 80 100 120 0 50 100 150 200 250 300 350 400 450 Increase of static pressure in Pa Flow rate in m 3 /h Q-∆p characteristic curves B/b=1,08; Se/D2=0,075; αe=23° B/b=1,08; Se/D2=0,025; αe=0 ° B/b=1,4; Se/D2=0,075; αe=23 ° B/b=1,4; Se/D2=0,025; αe=0° 160x62 mm Rotor ; Reference air density ρ=1,2 Kg/m3 Housing: αs=3°; B/b=variable, Rotor position: Se/D 2 =variable; αe=variable Manual measurement: steps of 25 m 3 /h; Rotational speed: 1000 rpm 0 0,05 0,1 0,15 0,2 0,25 0 50 100 150 200 250 300 350 400 450 Torque on shaft in Nm Flow rate in m 3 /h Q-M characteristic curves B/b=1,08; Se/D2=0,075; αe=23° B/b=1,08; Se/D2=0,025; αe=0 ° B/b=1,4; Se/D2=0,075; αe=23° B/b=1,4; Se/D2=0,025; αe=0 ° 160x62 mm Rotor ; Reference air density ρ=1,2 Kg/m3 Housing: αs=3°; B/b=variable, Rotor position: Se/D 2 =variable; αe=variable Manual measurement: steps of 25 m 3 /h; Rotational speed: 1000 rpm 7.1 Most relevant data grouped by housing families 37 Figure 7.3: Static efficiency curves of the Sirocco type fan D160x62mm at 1000rpm, scroll housing with an opening angle of 3º. Spiral opening angle: αs = 3° B/b = 1,08 B/b = 1,4 Se/D 2 = 0,075; αe = 23° Se/D 2 = 0,025; αe = 0° 0 10 20 30 40 50 60 70 80 0 50 100 150 200 250 300 350 400 450 Static efficiency in % Flow rate in m 3 /h Q-η characteristic curves B/b=1,08; Se/D2=0,075; αe=23° B/b=1,08; Se/D2=0,025; αe=0° B/b=1,4; Se/D2=0,075; αe=23 ° B/b=1,4; Se/D2=0,025; αe=0 ° 160x62 mm Rotor ; Reference air density ρ=1,2 Kg/m3 Housing: αs=3°; B/b=variable, Rotor position: Se/D 2 =variable; αe=variable Manual measurement: steps of 25 m 3 /h; Rotational speed: 1000 rpm 7.1 Most relevant data grouped by housing families 38 7.1.2 Scroll housing with opening angle of spiral curve of αs = 3,5° Figure 7.4: Increase of static pressure vs. flow rate curves of the Sirocco type fan D160x62mm at 1000rpm, scroll housing with an opening angle of 3,5º. Figure 7.5: Torque on shaft vs. flow rate curves of the Sirocco type fan D160x62mm at 1000rpm, scroll housing with an opening angle of 3,5º. 0 20 40 60 80 100 120 0 50 100 150 200 250 300 350 400 450 Increase of static pressure in Pa Flow rate in m 3 /h Q-∆p characteristic curves B/b=1,08; Se/D2=0,075; αe=23° B/b=1,08; Se/D2=0,025; αe=0° B/b=1,4; Se/D2=0,075; αe=23 ° B/b=1,4; Se/D2=0,025; αe=0 ° 160x62 mm Rotor ; Reference air density ρ=1,2 Kg/m3 Housing: αs=3,5°; B/b=variable, Rotor position: Se/D 2 =variable; αe=variable Manual measurement: steps of 25 m 3 /h; Rotational speed: 1000 rpm 0 0,05 0,1 0,15 0,2 0,25 0 50 100 150 200 250 300 350 400 450 Torque on shaft in Nm Flow rate in m 3 /h Q-M characteristic curves B/b=1,08; Se/D2=0,075; αe=23 ° B/b=1,08; Se/D2=0,025; αe=0° B/b=1,4; Se/D2=0,075; αe=23° B/b=1,4; Se/D2=0,025; αe=0° 160x62 mm Rotor ; Reference air density ρ=1,2 Kg/m3 Housing: αs=3,5°; B/b=variable, Rotor position: Se/D 2 =variable; αe=variable Manual measurement: steps of 25 m 3 /h; Rotational speed: 1000 rpm 7.1 Most relevant data grouped by housing families 39 Figure 7.6: Static efficiency curves of the Sirocco type fan D160x62mm at 1000rpm, scroll housing with an opening angle of 3,5º. Spiral opening angle: αs = 3,5° B/b = 1,08 B/b = 1,4 Se/D 2 = 0,075; αe = 23° Se/D 2 = 0,025; αe = 0° 0 10 20 30 40 50 60 70 80 0 50 100 150 200 250 300 350 400 450 Static efficiency in % Flow rate in m 3 /h Q-η characteristic curves B/b=1,08; Se/D2=0,075; αe=23° B/b=1,08; Se/D2=0,025; αe=0° B/b=1,4; Se/D2=0,075; αe=23° B/b=1,4; Se/D2=0,025; αe=0° 160x62 mm Rotor ; Reference air density ρ=1,2 Kg/m3 Housing: αs=3,5°; B/b=variable, Rotor position: Se/D 2 =variable; αe=variable Manual measurement: steps of 25 m 3 /h; Rotational speed: 1000 rpm 7.1 Most relevant data grouped by housing families 40 7.1.3 Scroll housing with opening angle of spiral curve of αs = 4,0° Figure 7.7: Increase of static pressure vs. flow rate curves of the Sirocco type fan D160x62mm at 1000rpm, scroll housing with an opening angle of 4º. Figure 7.8: Torque on shaft vs. flow rate curves of the Sirocco type fan D160x62mm at 1000rpm, scroll housing with an opening angle of 4º. 0 20 40 60 80 100 120 0 50 100 150 200 250 300 350 400 450 Increase of static pressure in Pa Flow rate in m 3 /h Q-∆p characteristic curves B/b=1,08; Se/D2=0,075; αe=23° B/b=1,08; Se/D2=0,025; αe=0° B/b=1,4; Se/D2=0,075; αe=23° B/b=1,4; Se/D2=0,025; αe=0 ° 160x62 mm Rotor ; Reference air density ρ=1,2 Kg/m3 Housing: αs=4°; B/b=variable, Rotor position: Se/D 2 =variable; αe=variable Manual measurement: steps of 25 m 3 /h; Rotational speed: 1000 rpm 0 0,05 0,1 0,15 0,2 0,25 0 50 100 150 200 250 300 350 400 450 Torque on shaft in Nm Flow rate in m 3 /h Q-M characteristic curves B/b=1,08; Se/D2=0,075; αe=23° B/b=1,08; Se/D2=0,025; αe=0° B/b=1,4; Se/D2=0,075; αe=23° B/b=1,4; Se/D2=0,025; αe=0 ° 160x62 mm Rotor ; Reference air density ρ=1,2 Kg/m3 Housing: αs=4°; B/b=variable, Rotor position: Se/D 2 =variable; αe=variable Manual measurement: steps of 25 m 3 /h; Rotational speed: 1000 rpm 7.1 Most relevant data grouped by housing families 41 Figure 7.9: Static efficiency curves of the Sirocco type fan D160x62mm at 1000rpm, scroll housing with an opening angle of 4º. Spiral opening angle: αs = 4° B/b = 1,08 B/b = 1,4 Se/D 2 = 0,075; αe = 23° Se/D 2 = 0,025; αe = 0° 0 10 20 30 40 50 60 70 80 0 50 100 150 200 250 300 350 400 450 Static efficiency in % Flow rate in m 3 /h Q-η characteristic curves B/b=1,08; Se/D2=0,075; αe=23° B/b=1,08; Se/D2=0,025; αe=0 ° B/b=1,4; Se/D2=0,075; αe=23 ° B/b=1,4; Se/D2=0,025; αe=0 ° 160x62 mm Rotor ; Reference air density ρ=1,2 Kg/m3 Housing: αs=4°; B/b=variable, Rotor position: Se/D 2 =variable; αe=variable Manual measurement: steps of 25 m 3 /h; Rotational speed: 1000 rpm 7.1 Most relevant data grouped by housing families 42 7.1.4 Scroll housing with opening angle of spiral curve of αs = 4,5° Figure 7.10: Increase of static pressure vs. flow rate curves of the Sirocco type fan D160x62mm at 1000rpm, scroll housing with an opening angle of 4,5º. Figure 7.11: Torque on shaft vs. flow rate curves of the Sirocco type fan D160x62mm at 1000rpm, scroll housing with an opening angle of 4,5º. 0 20 40 60 80 100 120 0 50 100 150 200 250 300 350 400 450 Increase of static pressure in Pa Flow rate in m 3 /h Q-ΔP characteristic curves B/b=1,08; Se/D2=0,05; αe=23° B/b=1,08; Se/D2=0,075; αe=23° B/b=1,08; Se/D2=0,025; αe=0° B/b=1,08; Se/D2=0,05; αe=0 ° B/b=1,08; Se/D2=0,05; αe=-23° B/b=1,4; Se/D2=0,075; αe=23° B/b=1,4; Se/D2=0,025; αe=0 ° 160x62 mm Rotor ; Reference air density ρ=1,2 Kg/m3 Housing: αs=4,5°; B/b=variable, Rotor position: Se/D 2 =variable; αe=variable Manual measurement: steps of 25 m 3 /h; Rotational speed: 1000 rpm 0 0,05 0,1 0,15 0,2 0,25 0 50 100 150 200 250 300 350 400 450 Torque on shaft in Nm Flow rate in m 3 /h Q-M characteristic curves B/b=1,08; Se/D2=0,05; αe=23° B/b=1,08; Se/D2=0,075; αe=23 ° B/b=1,08; Se/D2=0,025; αe=0° B/b=1,08; Se/D2=0,05; αe=0° B/b=1,08; Se/D2=0,05; αe= - 23 ° B/b=1,4; Se/D2=0,075; αe=23° B/b=1,4; Se/D2=0,025; αe=0° 160x62 mm Rotor ; Reference air density ρ=1,2 Kg/m3 Rotor position: D 2 /Sz=variable; αe=variable, Housing: B/b=variable; αs=4,5º Manual measurement: steps of 25 m 3 /h; Rotational speed: 1000 rpm 160x62 mm Rotor ; Reference air density ρ=1,2 Kg/m3 Housing: αs=4,5°; B/b=variable, Rotor position: Se/D 2 =variable; αe=variable Manual measurement: steps of 25 m 3 /h; Rotational speed: 1000 rpm 7.1 Most relevant data grouped by housing families 43 Figure 7.12: Static efficiency curves of the Sirocco type fan D160x62mm at 1000rpm, scroll housing with an opening angle of 4,5º. Spiral opening angle: αs = 4,5° B/b = 1,08 B/b = 1,4 Se/D 2 = 0,05; αe = 23° Se/D 2 = 0,075; αe = 23° Se/D 2 = 0,025; αe = 0° Se/D 2 = 0,05; αe = 0° Se/D 2 = 0,075; αe = -23° 0 10 20 30 40 50 60 70 80 0 50 100 150 200 250 300 350 400 450 Static efficiency in % Flow rate in m 3 /h Q-η characteristic curves B/b=1,08; Se/D2=0,05; αe=23° B/b=1,08; Se/D2=0,075; αe=23° B/b=1,08; Se/D2=0,025; αe=0 ° B/b=1,08; Se/D2=0,05; αe=0° B/b=1,08; Se/D2=0,05; αe=-23° B/b=1,4; Se/D2=0,075; αe=23° B/b=1,4; Se/D2=0,025; αe=0 ° 160x62 mm Rotor ; Reference air density ρ=1,2 Kg/m3 Housing: αs=4,5°; B/b=variable, Rotor position: Se/D 2 =variable; αe=variable Manual measurement: steps of 25 m 3 /h; Rotational speed: 1000 rpm 7.1 Most relevant data grouped by housing families 44 7.1.5 Scroll housing with opening angle of spiral curve of αs = 5,0° Figure 7.13: Increase of static pressure vs. flow rate curves of the Sirocco type fan D160x62mm at 1000rpm, scroll housing with an opening angle of 5º, width of housing B/b=1,08 and angle of eccentricity of gap rotor-housing of 23º. Figure 7.14: Torque on shaft vs. flow rate curves of the Sirocco type fan D160x62mm at 1000rpm, scroll housing with an opening angle of 5º, width of housing B/b=1,08 and angle of eccentricity of gap rotor-housing of 23º. 0 20 40 60 80 100 120 0 50 100 150 200 250 300 350 400 450 Increase of static pressure in Pa Flow rate in m 3 /h Q-ΔP characteristic curves Se/D2=0,025 Se/D2=0,05 Se/D2=0,075 Se/D2=0,1 Se/D2=0,125 160x62 mm Rotor ; Reference air density ρ=1,2 Kg/m3 Housing: αs=5°; B/b=1,08 , Rotor position: Se/D 2 =variable; αe=23° Manual measurement: steps of 25 m 3 /h; Rotational speed: 1000 rpm 0 0,05 0,1 0,15 0,2 0,25 0 50 100 150 200 250 300 350 400 450 Torque on shaft in Nm Flow rate in m 3 /h Q-M characteristic curves Se/D2=0,025 Se/D2=0,05 Se/D2=0,075 Se/D2=0,1 Se/D2=0,125 160x62 mm Rotor ; Reference air density ρ=1,2 Kg/m3 Housing: αs=5°; B/b=1,08 , Rotor position: Se/D 2 =variable; αe=23° Manual measurement: steps of 25 m 3 /h; Rotational speed: 1000 rpm 7.1 Most relevant data grouped by housing families 45 Figure 7.15: Static efficiency vs. flow rate curves of the Sirocco type fan D160x62mm at 1000rpm, scroll housing with an opening angle of 5º, width of housing B/b=1,08 and angle of eccentricity of gap rotor-housing of 23º. Spiral opening angle: αs = 5° B/b = 1,08 Se/D 2 = 0,025; αe = 23° Se/D 2 = 0,05; αe = 23° Se/D 2 = 0,075; αe = 23° Se/D 2 = 0,1; αe = 23° Se/D 2 = 0,125; αe = 23° 0 10 20 30 40 50 60 70 80 0 50 100 150 200 250 300 350 400 450 Static efficiency in % Flow rate in m 3 /h Q-η characteristic curves Se/D2=0,025 Se/D2=0,05 Se/D2=0,075 Se/D2=0,1 Se/D2=0,125 160x62 mm Rotor ; Reference air density ρ=1,2 Kg/m3 Housing: αs=5°; B/b=1,08 , Rotor position: Se/D 2 =variable; αe=23° Manual measurement: steps of 25 m 3 /h; Rotational speed: 1000 rpm 7.1 Most relevant data grouped by housing families 52 7.1.6 Scroll housing with opening angle of spiral curve of αs = 5,5° Figure 7.25: Increase of static pressure vs. flow rate curves of the Sirocco type fan D160x62mm at 1000rpm, scroll housing with an opening angle of 5,5º. Figure 7.26: Increase of static pressure vs. flow rate curves of the Sirocco type fan D160x62mm at 1000rpm, scroll housing with an opening angle of 5,5º. 0 20 40 60 80 100 120 0 50 100 150 200 250 300 350 400 450 Increase of static pressure in Pa Flow rate in m 3 /h Q-ΔP characteristic curves B/b=1,08; Se/D2=0,05; αe=23° B/b=1,08; Se/D2=0,075; αe=23 ° B/b=1,08; Se/D2=0,025; αe=0° B/b=1,08; Se/D2=0,05; αe=0° B/b=1,08; Se/D2=0,05; αe= - 23 ° B/b=1,4; Se/D2=0,075; αe=23° B/b=1,4; Se/D2=0,025; αe=0° 160x62 mm Rotor ; Reference air density ρ=1,2 Kg/m3 Housing: αs=5,5°; B/b=variable, Rotor position: Se/D 2 =variable; αe=variable Manual measurement: steps of 25 m 3 /h; Rotational speed: 1000 rpm 0 0,05 0,1 0,15 0,2 0,25 0 50 100 150 200 250 300 350 400 450 Torque on shaft in Nm Flow rate in m 3 /h Q-M characteristic curves B/b=1,08; Se/D2=0,05; αe=23° B/b=1,08; Se/D2=0,075; αe=23 ° B/b=1,08; Se/D2=0,025; αe=0° B/b=1,08; Se/D2=0,05; αe=0° B/b=1,08; Se/D2=0,05; αe= - 23 ° B/b=1,4; Se/D2=0,075; αe=23° B/b=1,4; Se/D2=0,025; αe=0° 160x62 mm Rotor ; Reference air density ρ=1,2 Kg/m3 Housing: αs=5,5°; B/b=variable, Rotor position: Se/D 2 =variable; αe=variable Manual measurement: steps of 25 m 3 /h; Rotational speed: 1000 rpm 7.1 Most relevant data grouped by housing families 53 Figure 7.27: Static efficiency curves of the Sirocco type fan D160x62mm at 1000rpm, scroll housing with an opening angle of 5,5º. Spiral opening angle: αs = 5,5° B/b = 1,08 B/b = 1,4 Se/D 2 = 0,05; αe = 23° Se/D 2 = 0,075; αe = 23° Se/D 2 = 0,025; αe = 0° Se/D 2 = 0,05; αe = 0° Se/D 2 = 0,075; αe = -23° 0 10 20 30 40 50 60 70 80 0 50 100 150 200 250 300 350 400 450 Static efficiency in % Flow rate in m 3 /h Q-η characteristic curves B/b=1,08; Se/D2=0,05; αe=23° B/b=1,08; Se/D2=0,075; αe=23° B/b=1,08; Se/D2=0,025; αe=0 ° B/b=1,08; Se/D2=0,05; αe=0 ° B/b=1,08; Se/D2=0,05; αe=-23° B/b=1,4; Se/D2=0,075; αe=23° B/b=1,4; Se/D2=0,025; αe=0 ° 160x62 mm Rotor ; Reference air density ρ=1,2 Kg/m3 Housing: αs=5,5°; B/b=variable, Rotor position: Se/D 2 =variable; αe=variable Manual measurement: steps of 25 m 3 /h; Rotational speed: 1000 rpm 8 Evaluation of the results In this chapter, we analyze all the curves registered in the measurement campaign searching for the best performances on the Sirocco type fan. The most interesting data for us, in this investigation, is the static efficiency. That is one of the objectives of this work. Therefore, we execute a detailed analysis looking for the highest values. An important issue as well, is to observe which values of the parameters of design are allowing these maximums. We try to find out the most favorable mix of the parameters of design to reach the maximum static efficiencies. As we have four different parameters of design (αs, B/b, Se/D 2 , αe) interacting with each other, this section has four subsections, one per each, in which one we search for their own maximums. Additionally, there are another two more ones. An initial subsection shows the highest efficiency of the whole measurement campaign. A final subsection shows the highest values for static efficiency depending on flow rate points. Finally, in the last part of this chapter we reveal some influences and trends found concerning the parameters of design on Sirocco type fan. 8.1 Maximum efficiencies found 8.1.1 Maximum static efficiency of the whole measurement campaign According to the experimental data, the highest static efficiency found is 69,1%. The configuration that provides this maximum is detailed in Table 8-1: Table 8-1: Maximum static efficiency of the whole measurement campaign. η max Configuration αs η max B/b Se/D 2 αe data file ° % - - ° - 5 69,1 1,08 0,075 -23 110126_67_5_160x62_-23_12_1000 8.1 Maximum efficiencies found 56 Figure 8.1: Performance curves of the Sirocco type fan D160x62mm at 1000rpm, configuration with maximum static efficiency. In Figure 8.1, we can appreciate the performance of the configuration of Sirocco type fan with the highest static efficiency of the whole measurement campaign. In the graph, we can see three curves on the behavior of the fan: increase of static pressure, torque on shaft and finally, static efficiency. Both the curve of increase of static pressure and torque on shaft have a smooth behavior lines. The efficiency curve is more dentate line which presents its maximum for flow rate of 75 m 3 /h. This value of 69,1% represents a step forward on the study of Sirocco fans type in the department of Fluid dynamics in HTW Berlin. As a reference, the last old highest value for the same type of fan at 1000 rpm found was 50%. That was registered by a student working in the department one year ago. So that means that we have increased the last old static efficiency in 38,2%, so from 50% to 69,1% according to the experimental measurements. For more detailed information about the performance of this configuration please refer to Appendix E. Details of the configuration with highest static efficiency. 8.1.2 Maximum static efficiencies by opening angle families We can also have a look on the fluctuation on the static efficiency due to the opening angle of spiral curve αs. As we know, we have built six different scroll housings depending on this parameter. We have housings for αs = 3º; 3,5º; 4º; 4,5º; 5º; 5,5º. In this subsection, we 0,00 0,05 0,10 0,15 0,20 0,25 0 20 40 60 80 100 120 0 50 100 150 200 250 300 350 400 450 Torque on shaft in Nm Increase of static pressure in Pa Static efficiency in % Flow rate in m 3 /h Q-∆P-M-η characteristic curves Configuration with highest efficiency point η max =69,1% 160x62 mm Rotor ; Reference air density ρ=1,2 Kg/m3 Housing: αs=5°; B/b=1,08, Rotor position: Se/D 2 =0,075 αe=-23° Manual measurement: steps of 25 m 3 /h; Rotational speed: 1000 rpm η max =69,1% 8.1 Maximum efficiencies found 57 notice which are the values of opening angle of spiral curve that are more desirable to obtain higher efficiencies. We can appreciate as well, which are the configurations that provide the highest efficiencies for each housing. Figure 8.2: Static efficiency vs. flow rate curves of the Sirocco type fan D160x62mm at 1000rpm, maximum static efficiency configuration by opening angle of families. In Figure 8.2, we can see six different curves of static efficiency vs. flow rate in different colors, each color corresponding to one of the housings. The highest efficiency of each housing is highlighted by using a red circle in the main point accompanied by a small text annotation with each maximum value. Complementing this information, there is a legend on the right side where we can appreciate the configurations that provide these maximums. The maximum static efficiencies each scroll housing reach, are resume below: Table 8-2: Maximum static efficiencies by open angle families. η max by families of αs Configuration αs η max B/b Se/D2 αe data file ° % - - ° - 3 56,5 1,08 0,025 0 110125_67_3_160x62_0_4_1000 3,5 60,0 1,08 0,075 23 110125_67_35_160x62_23_12_1000 4 65,0 1,08 0,075 23 110125_67_4_160x62_23_12_1000 4,5 65,7 1,08 0,075 23 110125_67_45_160x62_23_12_1000 5 69,1 1,08 0,075 -23 110126_67_5_160x62_-23_12_1000 5,5 60,2 1,08 0,05 23 110127_67_55_160x62_23_8_1000 0 10 20 30 40 50 60 70 80 90 0 50 100 150 200 250 300 350 400 450 Static efficiency in % Flow rate in m 3 /h Q-η characteristic curves αs=3°; B/b=1,08; Se/D2=0,025; αe=0° αs=3,5°; B/b=1,08; Se/D2=0,075; αe=23° αs=4°; B/b=1,08; Se/D2=0,075; αe=23° αs=4,5 ° ; B/b=1,08; Se/D2=0,075; αe=23 ° αs=5°; B/b=1,08; Se/D2=0,075; αe=-23° αs=5,5°; B/b=1,08; Se/D2=0,05; αe=23° Configurations with highest efficiency point by opening angle families 160x62 mm Rotor ; Reference air density ρ=1,2 Kg/m3 Manual measurement: steps of 25 m 3 /h; Rotational speed: 1000 rpm η 5 =69,1% η 3 =56,5% η 35 =60,0% η 4 =65,0% η 45 =65,7% η 55 =60,2% 8.1 Maximum efficiencies found 58 As we see in Table 8-2, the maximum efficiency is rising from the opening angle of 3º since it reaches the upper point. This maximum is for 5º opening angle. Afterwards, it continues falling for next values. The most favorable value on the opening angle parameter is αs = 5º providing an static efficiency of 69,1%. Obviously, this configuration matches with the highest static efficiency of the whole measurement campaign, mentioned in the previous subsection. It is important to notice that all the maximums are reached by the value of width of scroll housing B/b = 1,08. About the parameter of the gap rotor-housing, we can say that the most repeated configuration on the table is Se/D 2 = 0,075. Moreover this value is always moving between the range from 0,025 to 0,075 and never takes higher position. There is nothing clear to say about the angle of eccentricity because the values are moving in all the range. We can only say that αe = 23º is the most repeated configuration on Table 8-2. In addition, to have a full view of these configurations, their curves of increase of static pressure and torque on a shaft vs. flow rate are added. Refer to Figure 8.3 and Figure 8.4. Figure 8.3: Increase of static pressure vs. flow rate curves of the Sirocco type fan D160x62mm at 1000rpm, maximum static efficiency configuration by opening angle of families. In Figure 8.3 we have the increase of static pressure for the best configurations grouped by angles. We can see on it that in general we can say: the bigger opening angle the larger flow rate, as well, the bigger opening angle the higher initial increase of static pressure. These questions are analyzed with more detail in a further Section 8.2 0 20 40 60 80 100 120 0 50 100 150 200 250 300 350 400 450 Increase of static pressure in Pa Flow rate in m 3 /h Q-∆P characteristic curves αs=3°; B/b=1,08; Se/D2=0,025; αe=0° αs=3,5°; B/b=1,08; Se/D2=0,075; αe=23° αs=4°; B/b=1,08; Se/D2=0,075; αe=23° αs=4,5 ° ; B/b=1,08; Se/D2=0,075; αe=23 ° αs=5 ° ; B/b=1,08; Se/D2=0,075; αe= - 23 ° αs=5,5 ° ; B/b=1,08; Se/D2=0,05; αe=23 ° Configurations with highest efficiency point by opening angle families 160x62 mm Rotor ; Reference air density ρ=1,2 Kg/m3 Manual measurement: steps of 25 m 3 /h; Rotational speed: 1000 rpm 8.1 Maximum efficiencies found 59 Resume of trends and influences found. We can appreciate in the same figure, that the configurations according to Se/D 2 =0,075 and αe = 23º, present a downfall of pressure in the range between 50 – 100 m 3 /h. In the case of figure, that is for the opening angles of 3,5º;4º;4,5º. Finally the curves for the torque on shaft are shown in Figure 8.4. Figure 8.4: Torque on shaft vs. flow rate curves of the Sirocco type fan D160x62mm at 1000rpm, maximum static efficiency configuration by opening angle of families. As a conclusion of this subsection, we can say that the most favorable value to obtain highest efficiencies for the opening angle of spiral curve is 5º. Additionally experimental data shows that and opening angle of 4,5º is better than 5,5º. That could mean that if there is a maximum point for the efficiency is more plausible that this will be between 4,5º-5º than 5º-5,5º. 8.1.3 Maximum static efficiencies by width families Another parameter of study is the dimensionless ratio for the width of housing B/b. We have two values: B/b = 1,08; 1,4. In the next Figure 8.5, we can appreciate the best configurations for these two values. 0 0,05 0,1 0,15 0,2 0,25 0 50 100 150 200 250 300 350 400 450 Torque on shaft in Nm Flow rate in m 3 /h Q-M characteristic curves αs=3 ° ; B/b=1,08; Se/D2=0,025; αe=0 ° αs=3,5 ° ; B/b=1,08; Se/D2=0,075; αe=23 ° αs=4 ° ; B/b=1,08; Se/D2=0,075; αe=23 ° αs=4,5°; B/b=1,08; Se/D2=0,075; αe=23° αs=5°; B/b=1,08; Se/D2=0,075; αe=-23° αs=5,5°; B/b=1,08; Se/D2=0,05; αe=23° Configurations with highest efficiency point by opening angle families 160x62 mm Rotor ; Reference air density ρ=1,2 Kg/m3 Manual measurement: steps of 25 m 3 /h; Rotational speed: 1000 rpm 8.1 Maximum efficiencies found 60 Figure 8.5: Performance curves of the Sirocco type fan D160x62mm at 1000rpm, maximum static efficiency configuration by width of housing families. As we see in the picture, the maximum static efficiency for the thick housing is 60,3% and for the thin one is 69,1%. That means that the most properly value for B/b parameter is 1,08. In Table 8-3, we can see the details. Table 8-3: Maximum static efficiencies by width of housing families. η max by families of B/b Configuration B/b η max αs Se/D2 αe data file - % ° - ° - 1,08 69,1 5 0,075 -23 110126_67_5_160x62_-23_12_1000 1,4 60,3 4,5 0,075 23 110127_87_45_160x62_23_12_1000 About the behavior of the increase of pressure, they are complementary. Before the flow rate point of 150 cubic meters, the increase of pressure for the thick housing undergoes the thin one. After that point, we have the opposite behavior. This is also happening with the efficiency curves. As a conclusion of subsection, we say that a width for housing of B/b = 1,08 give better efficiencies. 8.1.4 Maximum static efficiencies by gap rotor-housing families 0,00 0,05 0,10 0,15 0,20 0,25 0 20 40 60 80 100 120 0 50 100 150 200 250 300 350 400 450 Torque on shaft in Nm Increase of static pressure in Pa Static efficiency in % Flow rate in m 3 /h Q-∆P-M-η characteristic curves αs=5°; B/b=1,08; Se/D2=0,075; αe=-23° αs=4,5°; B/b=1,4; Se/D2=0,075; αe=23° Configurations with most efficient point by width families: B/b=1,08, 1,4 160x62 mm Rotor ; Reference air density ρ=1,2 Kg/m3 Manual measurement: steps of 25 m 3 /h; Rotational speed: 1000 rpm η 1,08 =69,1% η 1,4 =60,3% 8.1 Maximum efficiencies found 61 The gap rotor-hosing is also an important parameter on the Sirocco type fans. In this study we have arranged 5 values for this parameter: Se/D 2 = 0,025; 0,05; 0,075; 0,1; 0,125. Figure 8.6: Static efficiency vs. flow rate curves of the Sirocco type fan D160x62mm at 1000rpm, maximum static efficiency configuration by gap rotor-housing families. In Figure 8.6 are shown the efficiency curves by this grouping family. The highest efficiency is for the value of Se/D 2 = 0,075. We can observe that the three higher points are for curves with 5º opening angle and the last two one for 4,5º. So we can attend to the same considerations than the previous part: if there is a maximum point for the efficiency is more plausible that this will be between 4,5º-5º. All of them belongs to the thin housing B/b = 1,08. As said before, this relation is providing always the best values for static efficiency. About the parameter αe, we can’t give a clear recommendation because as we see in Table 8-4., it is fluctuating all over the range. Table 8-4: Maximum static efficiencies by gap rotor-housing families. η max by families of Se/D 2 Configuration Se/D2 ηmax αs B/b αe data file - % ° - ° - 0,025 62,1 4,5 1,08 0 110125_67_45_160x62_0_4_1000 0,05 63,3 4,5 1,08 23 110125_67_45_160x62_23_8_1000 0,075 69,1 5 1,08 -23 110126_67_5_160x62_-23_12_1000 0,1 66,6 5 1,08 -23 110126_67_5_160x62_-23_16_1000 0,125 63,0 5 1,08 23 110126_67_5_160x62_23_20_1000 0 10 20 30 40 50 60 70 80 90 0 50 100 150 200 250 300 350 400 450 Static efficiency in % Flow rate in m 3 /h Q-η characteristic curves αs=4,5°; B/b=1,08; Se/D2=0,025; αe=0° αs=4,5°; B/b=1,08; Se/D2=0,05; αe=23° αs=5°; B/b=1,08; Se/D2=0,075; αe=-23° αs=5°; B/b=1,08; Se/D2=0,1; αe=-23° αs=5 ° ; B/b=1,08; Se/D2=0,125; αe=23 ° Configurations with highest efficiency point by gap rotor-housing families 160x62 mm Rotor ; Reference air density ρ=1,2 Kg/m3 Manual measurement: steps of 25 m 3 /h; Rotational speed: 1000 rpm η 0,075 =69,1% η 0,1= 66,6% η 0,025 =62,1% η 0,125 =63,0% η 0,05 =63,3% 8.2 Resume of trends and influences found 68 curve trend. That means that there is a maximum value of static efficiency that depending on the opening angle. This fact is explained more clearly in the next point. Figure 8.13: Location of the best static efficiency points for Sirocco type fan 2) The best static efficiency points for each value of opening angle present an approximate parabolic distribution with a maximum around 5º. In Figure 8.13, we can appreciate the static efficiency curves for the entire opening angle values recorded in the measurements (3,0 to 5,5 degree). The best efficiency point is highlighted with a dot according the same color. A trend curve has been drawn to collect the distribution of these points. The maximum efficiency is rising from the opening angle of 3º since it reaches the upper point. This maximum is for 5º opening angle. Afterwards, there is a drop, as we see for the angle of 5,5º. The flow rate responsible of each point is increasing according the influence that we explain in the previous point. The location of the best static efficiency points means that there is an optimum in the design according the parameter of opening angle. In our measurement the best value for this parameter is 5 degree. But according on the trend line drawn in the figure, it is probable that the real maximum could be located between 4,5 and 5,0 degree. 30 40 50 60 70 0 50 100 150 200 250 300 350 Static efficiency in % Flow rate in m3/h Q-η characteristic curves (influence of opening angle, 2) 3º Housing 3,5º Housing 4º Housing 4,5º Housing 5º Housing 5,5º Housing 160x62 mm Rotor ; Reference air density ρ=1,2 Kg/m3 Housing: αs=variable; B/b=1,08 , Rotor position: Se/D 2 =0,075; αe=23° Interpolated curves from experimental data; Rotational speed: 1000 rpm 8.2 Resume of trends and influences found 69 8.2.2 Influence of the width of housing We have observed a clear influence of the width of housing (B/b) on the performance of the fan that is explained below. Figure 8.14: Influence of the width of housing on the performance of Sirocco type fan 3) Maximal static efficiencies on Sirocco type fan can only be expected by designing scroll housings as thinner as possible in relation to the width of the rotor. The positive effect of increasing the width of housing is the bigger flow rate achieved and a rise of the static pressure provided by the fan, as we see in Figure 8.14. On the other hand this fact produces a decrease of the maximum static efficiency for smaller flow rates where the maximum is located. The increase of the maximum flow rate provided by the fan displaces the best efficiency point to the right as it occurs when increasing the value of opening angle. When a housing much broader than the rotor is requested, the best performance is achieved by placing the rotor as much closer as possible from the inlet of the fan. Proceeding this way, the distribution of the air stream is the most homogeneous according to the measurements. 0 20 40 60 80 100 120 0 50 100 150 200 250 300 350 400 450 Increase of static pressure in Pa Static efficiency in % Flow rate in m 3 /h Q-ΔP-η characteristic curves (influence of housing width) B/b=1,08 B/b=1,4 160x62 mm Rotor ; Reference air density ρ=1,2 Kg/m3 Housing: αs=4,5°; B/b=variable, Rotor position: Se/D 2 =variable; αe=variable Manual measurement: steps of 25 m 3 /h; Rotational speed: 1000 rpm 160x62 mm Rotor ; Reference air density ρ=1,2 Kg/m3 Housing: αs=4,5°; B/b=variable, Rotor position: Se/D 2 =0,025; αe=0° Interpolated curves from experimental data; Rotational speed: 1000 rpm 8.2 Resume of trends and influences found 70 8.2.3 Influence of decentering the rotor Decentering the rotor from the original position was one of the parts included in the measurements. It had an important influence on the results for instance because the maximum static efficiency was found with this procedure. Apart of this fact, we observed some influences on the performance of the fan that are explained subsequently. Figure 8.15: Influence of the gap rotor-housing on the pressure curve on Sirocco type fan 4) The smaller gap between rotor-housing, the bigger pressure rise values for initial flow rate. In Figure 8.15 we can observe the curves of pressure rise and efficiency for three configurations where the only change from each other is the gap between rotor-housing. The initial pressure rise becomes higher when the gap decreases from 0,125 (green curve) to 0,025 (red curve) in about 35 Pa. That represents an increase of 35%. 0 20 40 60 80 100 120 0 50 100 150 200 250 300 350 400 Increase of static pressure in Pa Static efficiency in % Flow rate in m 3 /h Q-ΔP-η characteristic curves (influence of gap rotor-housing) Se/D2=0,025 Se/D2=0,075 Se/D2=0,125 160x62 mm Rotor ; Reference air density ρ=1,2 Kg/m3 Housing: αs=5°; B/b=1,08 , Rotor position: Se/D 2 =variable; αe=0° Interpolated curves from measurements; Rotational speed: 1000 rpm 8.2 Resume of trends and influences found 71 Figure 8.16: Influence of the angle of eccentricity in Sirocco type fan 5) The parameter of angle of eccentricity αe, can be used to avoid the pressure oscillations that appear for flow rates around 75 m3/h in some configurations of Sirocco type fan. According to the measurements, some configurations of sirocco type fan present big oscillations in the pressure rise curves at a flow rate at about 75 m3/h, as we can appreciate in Figure 8.16. Particularly the configurations with the relations Se/D2 = 0,075 and αe = 23º. By setting a smaller angle of eccentricity for this configuration the oscillations can be corrected obtaining smooth curves as we see in the figure above. The last trend observed during the measurements is explained below. 0 20 40 60 80 100 120 0 50 100 150 200 250 300 350 400 Increase of static pressure in Pa Static efficiency in % Flow rate in m 3 /h Q-∆P-η characteristic curves (influence of angle of eccentricity) Se/D2=0,075; αe=23° Se/D2=0,075; αe=0° Se/D2=0,075; αe=23° Se/D2=0,075; αe=0° 160x62 mm Rotor ; Reference air density ρ=1,2 Kg/m3 Housing: αs=5°; B/b=1,08 , Rotor position: Se/D 2 =0,075; αe=variable Manual measurement: steps of 25 m 3 /h; Rotational speed: 1000 rpm 8.2 Resume of trends and influences found 72 Figure 8.17: Common point in the configuration of Sirocco type fan. 6) All the configurations of the fan concerning the same opening angle and same width of housing have a common point in the pressure rise curves. In figure Figure 8.17 we can appreciate that all the pressure rise curves have a point in common. The curves are drawn for opening angle of 5 degree and width of housing of 1,08. This fact could mean that decentering the rotor have some effects on the performance of the fan related with the pressure rise, as the two ones explained above but is not as such difference as changing a principal parameter of design, for instance the opening angle or the width of housing. 0 20 40 60 80 100 120 0 50 100 150 200 250 300 350 400 Increase of static pressure in Pa Flow rate in m 3 /h Q-ΔP characteristic curves (influence of decentering the rotor) Se/D2=0,025; αe=23 ° Se/D2=0,1; αe=0 ° Se/D2=0,05; αe=23 ° Se/D2=0,125; αe=0 ° Se/D2=0,075; αe=23° Se/D2=0,025; αe=-23° Se/D2=0,1; αe=23° Se/D2=0,05; αe=-23° Se/D2=0,125; αe=23 ° Se/D2=0,075; αe= - 23 ° Se/D2=0,025; αe=0° Se/D2=0,1; αe=-23° Se/D2=0,05; αe=0° Se/D2=0,125; αe=-23° Se/D2=0,075; αe=0° 160x62 mm Rotor ; Reference air density ρ=1,2 Kg/m3 Housing: αs=5°; B/b=1,08 , Rotor position: Se/D 2 =variable; αe=variable Manual measurement: steps of 25 m 3 /h; Rotational speed: 1000 rpm 9 Comparison of the results So far we recorded our measurements by using one high-accuracy chamber test rig with known and accurate uncertainties (see Chapter 5 Uncertainty of measurement), we can compare the results obtained in this work with another sources of information. We have mainly two references for comparing our results. The first one is to compare with the results of CDF simulations provided by a member of the team. The other is to compare with the figures that Roth obtained on his study of sirocco fans (Roth, 1980). We detail each one in the following parts. 9.1 Comparison with CFD’s results Computational fluid dynamics (CFD) is a branch of fluid mechanics that uses numerical methods and algorithms to solve and analyze problems that involve fluid flows. Computers are used to perform the calculations required to simulate the interaction of liquids and gases with surfaces defined by boundary conditions. Experiments are used, in general, in order to validate CFD calculations and to provide starting values and boundary conditions. In addition, CFD allows obtaining details in the whole flow field: stream lines, shear stress, velocity and pressure distribution, particle tracks, etc. Figure 9.1: Sample illustration of velocity magnitude on Sirocco type fan α=7º (source: Darvish, 2010) An example of CFD simulation applied on Sirocco type fan is shown in Figure 9.1. We can see the velocity magnitude in m/s over the geometry of the fan. 9.1 Comparison with CFD’s results 74 We can obtain the necessary information from the simulations to establish a comparison. We applied CFD on one configuration of the Sirocco type fan evaluated in the measurement campaign: αs = 5º ; B/b = 1,08 ; Se/D 2 = 0,075 ; αe = 23º The results are shown in Figure 9.2 by using graphs. In this graph we present the habitual characteristic curves of pressure rise, torque on shaft and static efficiency vs. flow rate. In red-colored lines we have the curves for the experimental data and in bluecolored lines we have the curves provided by the CFD simulation. Figure 9.2: Comparison between Experimental data and CFD simulations for 5º housing The data is qualitatively and quantitatively in good accordance with each other. The deviation amount is less than 5 to 10 %. The pressure curve matches with high-accuracy in the range of flow rate from 175 to 275 m3/h. For higher values of flow rate, the differences are growing, as well for the initial point. The average deviation considering the pressure rise is 4,0 %. The torque is the curve with the highest affinity. The deviation starts at the initial point with a deviation of 1,5 % but is slightly increasing with the flow rate to rise 5 %. The experimental torque is always slightly smaller than the simulated. The average deviation considering the full range of the torque is 3,4 %. The static efficiency has the highest deviation from all three characteristic curves. This can be assumed by considering the differences in pressure rise and torque. In fact, we calculate the static efficiency by using both the pressure rise and torque in the 0 0,05 0,1 0,15 0,2 0,25 0,3 0,35 0,4 0 10 20 30 40 50 60 70 80 90 0 50 100 150 200 250 300 350 400 Torque on shaft in Nm Increase of static pressure in Pa Static efficiency in % Flow rate in m3/h Comparison CFD-Experiment CFD simulation Experimental data 9.2 Comparison with Roth’s results 75 calculations. When there are deviations in these two values it have repercussions on the finally value of static pressure. The deviation for the static efficiency in the range of flow rate from 175 to 275 m3/h is contained around 6 %. This one is increasing for further flow rate values and for the first point, where the differences are higher than 15 %. Considering the full range, the average of the deviation of static efficiency is 8,7 %. For more detailed info about the deviations in each point, refer to Table 9-1. Table 9-1: Deviation between Experimental and CFD simulations for 5º housing To finish this comparison between our experimental results and the data obtained from the CFD simulations, we conclude that the concordance between each other is very good, both qualitatively and quantitatively. 9.2 Comparison with Roth’s results Roth obtained, after his extensive study on sirocco fans, a big amount of tables where he reflected the influence of the different variables on the performance of the fan. The most interesting for us in our study are shown in Figure 9.3. Figure 9.3: Graphs given by Roth on his study 9.2 Comparison with Roth’s results 76 In these two graphs we have the characteristics curves for Sirocco type fan for different opening angles of spiral curve (3º, 5º, 7º, 9º, 11º) all of them according to dimensionless ratio of width of housing B/b = 1,08. The characteristic curve that we could use for the comparison is the one with 5º. Due to the difficulty to compare both results coming from different graphs, we merge them in a single one. To achieve this objective, the points from the curves of Roth have been read carefully by hand and a table has been created. For the details of this table of points please refer to Appendix F. Data collected from Roth’s graphs. Afterwards this list of points was inserted in a sheet to merge all the curves in the same graph. We apply the comparison with this experimental configuration (same as previous comparison with CFD): αs = 5º ; B/b = 1,08 ; Se/D 2 = 0,075 ; αe = 23º Figure 9.4: Comparison between experimental and Roth’s curves for Sirocco type fan In Figure 9.4, we can appreciate the pressure rise curves together in the same graph. The values to draw the characteristic curves are according fr (flow rate dimensionless ratio) and ψf (static pressure rise dimensionless ratio). We use the same parameters that Roth used to show his curves. For more details about these parameters, please refer to Chapter 4 Mathematical foundations. These two curves are in good qualitative accordance. The experimental curve measured in this work presents the same trend as the one from Roth besides better performance due to the fact that higher flow rate is achieved. 0 0,5 1 1,5 2 2,5 3 0 0,05 0,1 0,15 0,2 0,25 0,3 0,35 0,4 ψf f r Experimental vs. Roth's characteristic curves 5 ° Roth 5 ° Experiment 5° Experiment: Housing: αs=5°; B/b=1,08 , Rotor position: Se/D 2 =0,075; αe=23° 9.2 Comparison with Roth’s results 77 To have a more accurate comparison we have built the next table that contains the deviation between each measured point. Table 9-2: Deviation between Experimental and Roth’s data for 5º housing As we can appreciate in Table 9-2, the average deviation between our experimental results and the Roth’s data is substantial for the initial and the final points defined. The average deviation for these points is about 25 %. The deviation concerning the full range is 15,1 % From Roth’s curve for 5º opening angle, we know exactly the values of two parameters that he used to obtain this curve. The opening angle is αs = 5º and the width ratio is B/b = 1,08. But it is not written on his work all the details of this curve. One of the most important is the value of the length of the outlet. (See Figure 2.1) On the other hand, the affinity of the experimental curve for the opening angle of 5 degree is in good accordance for the middle points, that is in the range of flow ratio (fr) from 0,1 to 0,2. The average deviation for these points is about 6 %. As a conclusion of this chapter, we can say, after comparing the deviations with CFD simulations and Roth’s data, that we have: -Good agreement of CFD with experiments -Good agreement of Roth with this the measurements of this work for middle points of the characteristic curve. Appendices Appendices II Appendix A. Tool for obtaining the points of the spiral curve Figure 12.1: Sheet tool created for obtaining the points of the logarithmic spiral curve Appendices III Appendix B. Values for decentering the rotor Figure 12.2: Displacements in X-Y axes from the origin position for all the configurations Appendices IV Figure 12.3: Values of the displacements in X-Y axes translated into code for RSTerm software Appendices V Appendix C. Data provided by the chamber test rig Figure 12.4: Example of data table provided by the chamber test rig for a measurement on the scroll housing of 5º Appendices VI Appendix D. Study of maximal static efficiencies Table 12-1: Summary of the best static efficiencies found by different criteria 0. Max static efficiency found ηmax Configuration αs η max B/b Se/D 2 αe data file ° % - - ° 5 69,1 1,08 0,075 -23 110126_67_5_160x62_-23_12_1000 1. Max static efficiencies by opening angle families ηmax by families of αs Configuration αs η max B/b Se/D 2 αe data file ° % - - ° 3 56,5 1,08 0,025 0 110125_67_3_160x62_0_4_1000 3,5 60,0 1,08 0,075 23 110125_67_35_160x62_23_12_1000 4 65,0 1,08 0,075 23 110125_67_4_160x62_23_12_1000 4,5 65,7 1,08 0,075 23 110125_67_45_160x62_23_12_1000 5 69,1 1,08 0,075 -23 110126_67_5_160x62_-23_12_1000 5,5 60,2 1,08 0,05 23 110127_67_55_160x62_23_8_1000 2. Max static efficiencies by width families ηmax by families of B/b Configuration B/b η max αs Se/D 2 αe data file - % ° - ° 1,08 69,1 5 0,075 -23 110126_67_5_160x62_-23_12_1000 1,4 60,3 4,5 0,075 23 110127_87_45_160x62_23_12_1000 3. Max static efficiencies by gap rotor-housing families ηmax by families of Se/D 2 Configuration Se/D 2 η max αs B/b αe data file - % ° - ° 0,025 62,1 4,5 1,08 0 110125_67_45_160x62_0_4_1000 0,05 63,3 4,5 1,08 23 110125_67_45_160x62_23_8_1000 0,075 69,1 5 1,08 -23 110126_67_5_160x62_-23_12_1000 0,1 66,6 5 1,08 -23 110126_67_5_160x62_-23_16_1000 0,125 63,0 5 1,08 23 110126_67_5_160x62_23_20_1000 Appendices VII 4. Max static efficiencies by angle of eccentricity families ηmax by families of αe Configuration αe η max αs B/b Se/D 2 data file ° % ° - - 23 65,7 4,5 1,08 0,075 110125_67_45_160x62_23_12_1000 0 65,4 5 1,08 0,075 110126_67_5_160x62_0_12_1000 -23 69,1 5 1,08 0,075 110126_67_5_160x62_-23_12_1000 5. Max static efficiencies by each point of flow rate η max by each point of flow rate Configuration Flow rate Max efficiency B/b Se/D 2 αe data file m3/h % - - ° 0 0,0 - 25 48,7 1,08 0,125 -23 110126_67_5_160x62_-23_20_1000 50 62,6 1,08 0,125 23 110126_67_5_160x62_23_20_1000 75 69,1 1,08 0,075 -23 110126_67_5_160x62_-23_12_1000 100 65,4 1,08 0,075 0 110126_67_5_160x62_0_12_1000 125 65,4 1,08 0,075 23 110125_67_45_160x62_23_12_1000 150 63,3 1,08 0,075 23 110126_67_5_160x62_23_12_1000 175 59,3 1,4 0,075 23 110127_87_45_160x62_23_12_1000 200 59,8 1,4 0,075 23 110128_87_55_160x62_23_12_1000 225 57,3 1,4 0,075 23 110128_87_55_160x62_23_12_1000 250 55,3 1,4 0,075 23 110128_87_55_160x62_23_12_1000 275 52,7 1,4 0,075 23 110128_87_55_160x62_23_12_1000 300 46,0 1,4 0,075 23 110128_87_55_160x62_23_12_1000 325 40,6 1,4 0,075 23 110128_87_55_160x62_23_12_1000 350 34,9 1,4 0,075 23 110128_87_55_160x62_23_12_1000 375 20,3 1,4 0,05 0 110128_87_5_160x62_0_8_1000 400 14,9 1,4 0,05 0 110128_87_5_160x62_0_8_1000 425 6,9 1,4 0,05 0 110128_87_5_160x62_0_8_1000 450 0,7 1,4 0,05 0 110128_87_5_160x62_0_8_1000 Appendices VIII Appendix E. Details of the configuration with highest static efficiency Figure 12.5: Performance details for the configuration with highest static efficiency Appendices IX Appendix F. Data collected from Roth’s graphs Figure 12.6: Tables created after reading manually the points of Roth’s curves Appendices XVI Figure 12.13: Specifications of the couplings by R+W Appendices XVII Figure 12.14: Specifications of the bearings by SNR Appendices XVIII Drehstrommotor DFT80K2/TF Motor-Drehzahl [R/min] 2700 Bauform IM B5 Motor-Moment [Nm]/ED [%] S1 Motor-Spannung [V] 230/400 Motor-Leistung [kW] 0,75 LS-Anzahl (Satz je Antrieb) 1 Sprache D/LNI Sachnummer 1 Typenschild 01818686 Motor-Frequenz [Hz] 50 Motor-Spannung [V]/Schaltart 230/400 Dreieck/Stern Nennstrom [A] 3,50/2,00 cos PHI 0,86 wärmeklasse/Schutzart [IP] F/54 Nettogewicht [kg] 9,087 [Fabrikationsnummer 01.1259527401.0001X08] Figure 12.15: Specifications for the motor by SEW-EURODRIVE Appendices XIX Figure 12.16: Specifications of the frequency inverter Movitrac by SEW-EURODRIVE