This diploma thesis covers the influence of fouling in heat exchangers and heat transfer coefficient. In the first part of the thesis are covered the characteristics of fouling and its formation, process, and effects on heat transfer surfaces in exchangers. In the next part of the thesis, chemical analysis of cooling water is performed on an extracted sample and the potential of fouling is determined based on the analysis. In the conclusion part, computational models of fouling in the tube side of the heat exchanger are presented; fouling of an actual heat exchanger is calculated and compared with data captured during the operation of the heat exchanger.

Regenerative heat exchangers are used in a wide range of industries and in the technical equipment of buildings. These heat exchangers play an important role in saving thermal energy and removing volatile organic compounds from flue gases. The theoretical part of the work deals with the division of regenerative exchangers into rotary and switching exchangers and the possibilities of their use. These types of heat exchangers are used in many applications, e.g. as a heat exchanger using waste heat to preheat the process gas (regeneration layer), or as catalysts to accelerate the reaction required to remove volatile organic compounds (catalytic layer), or as integrated equipment where both the regeneration layer and the catalytic layer. The aim of the diploma thesis is experimental support in the development of a computer program for the design of a specific integrated device. The program allows the calculation of the regeneration and catalytic bed, or both beds simultaneously, i.e. integrated equipment. The diploma thesis deals with the support of a mathematical model for the calculation of the regeneration bed. Pressure loss and heat transfer play an important role in the selection and subsequent calculation of a suitable bed. To calculate them, it is possible to find more available computational relationships that differ significantly in their accuracy. It is therefore necessary to select the most suitable ones for the computational model. The practical part of the work then deals with research, analysis, and assessment of the suitability of methods used to calculate pressure losses based on a comparison with the values measured on experimental equipment. Subsequently, the work deals with computational methods for determining the heat transfer coefficient of the packed bed. A significant part of the practical part deals with the modification of the experimental equipment for the verification of computational relations for the determination of heat transfer with measured data.

Thermal processing of wastes is a metod, when during combustion occur reduction of wastes till 10% previous volume. The main advantage of this method is possibility to heat utilization for heat and electric production. Through thermic process develops range of pollutants (NOx, CO, SO2, HCl, HF, PCDD/F) that had to be remove from off-gas or reduced to enviromental values in agreement with laws in force [16]. For this purpose are combustion units equip with range of devices for removing this pollutans. The main task of this diploma thesis is selectoin of ctirical device in term of pressure drops. The value of pressure drop stands significant part in proposition of efficiecy off-gas fan. In increase or decrease total pressure drop consumption of electrical energy of off-gas fan is rising or going down. Change of consumption in total classification is projecting in energy utilization rate of waste where is determinate if it stands of energy utilizatoin or just incineration. In first part of diploma thesis are described in detail availability methods of off-gas cleaning where is described their principle, advanteges, disadvatages and comparison of effectivity. In second part of diploma thesis is made example model about influnce technology on value of total pressure drop. There were chosen two technologies for removing dioxins (technology of catalytic filtration REMEDIA and DeNox/DeDiox). For both technologies were made detailed analysis of pressure drops single components of these technologies. Attainment results were compared and rated with one another. For analysis these two methods were designed mathematical process in software Maple 9.5.

The main task of thesis is to find optimum geometry of the heat exchanger. The biggest emphases is placed to finding the most optimum of streaming liquid in the heat exchanger and to minimisation pressure losses. There is a effort to regulate the streaming liquids in heat exchangers so that in multitube and on the shell side don´t create dead areas, it means to avoid sedimentation of particle in these places. Dead areas cause rising resistance against heat transfer and necessity of frequently cleaning the heat exchanger. For these reasons is necessary to do analyse of flowing and to looking for the optimal geometry of the heat exchanger.

The topic of this master thesis is upgrading of biogas. As a mixture of gases produced during anaerobic digestion, contains methane which is highly energy valuable gas. But also other substances that we want to remove. We will present the motivation for upgrading biogas and the possibility of separation, generally the pressure swing adsorption method. The key parameter of this technique is the choice of a suitable adsorbent. This is possible based on the knowledge of adsorption processes, therefore, is also described below. The objective of this thesis is to determine the parameters of the pressure swing adsorption metod. To do this it is necessary to determine the adsorption capacity of the adsorbent, measure breakthrough curves of carbon dioxide and methane, and determine the pressure drop of solid bed, etc. As a result we can finally make a balance and evaluate the applicability in practice.

Thesis solves problems using the nanotechnology for air filtration in HVAC systems. Main specialization work is air filtration for clean spaces with high classes of purity. For example Hospitals, sophisticated technology service, pharmacy etc. Thesis is devide for three parts. First part contains foundation infromations about theory and making fabrics by nanotechnology. Next I described laws of physics, That were using during the solving filtration´s issues. Goal for second part was making the experiments, which should show abilities and properties nanofilters during the air filtration in real environment HVAC systems. In the end measure part is compare nanofilters with common filters. There is describe nanofiltres behavior and their possibilies during the filtration as well as. In last part I expressed own opinions on air filtration by nanofibers. Opinions were making throught informations, That I found out in the process working on thesis and my experiences in HVAC field. By this facts I did compare for get a better idea. Additionally last part contains summary infomations from previously parts and own vision to development in the future. Goal work isn´t promotion and advertising sorts technologies. Ask is just summary and describe discovered knowledges, considered opinions ensue from measuring, information from the Net and people Who work in nanotechnology field.

Die thermodynamischen Eigenschaften von Flüssighelium erfordern einen hohen technischen Aufwand zu dessen Lagerung und Transfer. Aufgrund der extrem niedrigen Normalsiedetemperatur von 4,2 K ist die Verflüssigung des unter Normbedingungen gasförmigen Heliums sehr energieintensiv. Darüber hinaus besitzt Helium eine sehr niedrige Verdampfungsenthalpie, weshalb bereits geringe Wärmeeinträge signifikante Verdampfungsverluste verursachen. Infolge der räumlichen Trennung von Heliumverflüssigungsanlagen und Verbrauchern ist ein Flüssigheliumtransfer in der Regel unvermeidlich. Beim Transfervorgang durch Wärmeeintrag und Druckverluste generiertes Heliumkaltgas muss erneut dem energieaufwändigen Verflüssigungsprozess zugeführt werden, bevor es als Kältemittel verwendet werden kann. Zur Etablierung eines verlustarmen Flüssigheliumtransfers mit einflutigen flexiblen Transferleitungen sind daher die Verdampfungsverluste im Rahmen der thermohydraulischen Optimierung zu reduzieren. Die Optimierung erfolgt dabei durch die Kopplung von systematischen Messungen mit thermohydraulischen Berechnungen. Untersuchungen mit instrumentierten Versuchstransferleitungen erfolgen an einem an der Heliumverflüssigungsanlage der Technischen Universität Dresden neu eingerichteten Versuchsstand. Dabei stellt sich heraus, dass der Gesamtdruckverlust vorwiegend durch das im flexiblen Abschnitt eingesetzte Wellrohr verursacht wird. Mittels eines gesonderten Messaufbaus werden verschiedene Wellrohrtypen hinsichtlich der resultierenden Reibungsdruckverluste untersucht und eine verlustarme Wellrohrgeometrie identifiziert. Neben den Druckverlusten wird auch der Wärmeeintrag durch Modifikationen des Isolationsaufbaus reduziert. Im Zuge der thermohydraulischen Optimierung vermindern sich die Verdampfungsverluste, wodurch die pro Zeiteinheit in der Transportkanne deponierte Flüssigheliummenge zunimmt. Zusätzliche Messungen während des Stillstands der Transferleitung liefern Rückschlüsse auf das Verhalten der Transferleitung, wenn kein Flüssighelium transferiert wird. Im Stillstand neigen die betrachteten Transferleitungsgeometrien zu thermisch angetriebenen Druckschwingungen, sogenannten thermoakustischen Oszillationen. Diese beeinflussen die Betriebssicherheit und die Lagergüte des stationären Speichers negativ, weshalb geeignete Methoden zur Dämpfung der thermoakustischen Oszillationen vorgeschlagen werden.:1 Einleitung 1 1.1 Motivation . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 1 1.2 Stand der Wissenschaft . . . . . . . . . . . . . . . . . . . . . . . . . . . 2 1.3 Gegenstand und Aufbau der Arbeit . . . . . . . . . . . . . . . . . . . . . 3 2 Helium als Kälteträger 6 2.1 Grundlegende Stoffeigenschaften von Helium . . . . . . . . . . . . . . . . 6 2.2 Vorkommen, Gewinnung und Verwendung von Helium . . . . . . . . . . . 7 2.3 Bereitstellung von Flüssighelium . . . . . . . . . . . . . . . . . . . . . . . 10 2.4 Aufbau einer flexiblen Transferleitung für Flüssighelium . . . . . . . . . . . 12 3 Berechnungsgrundlagen 14 3.1 Druckverlust . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 14 3.1.1 Gesamtdruckverlust . . . . . . . . . . . . . . . . . . . . . . . . . 14 3.1.2 Reibungsdruckverlust im Glattrohr . . . . . . . . . . . . . . . . . . 14 3.1.3 Reibungsdruckverlust im Rohr mit parallelen Wellen . . . . . . . . 15 3.1.4 Zweiphasenmultiplikator . . . . . . . . . . . . . . . . . . . . . . . 17 3.1.5 Druckverlust durch Höhenänderung . . . . . . . . . . . . . . . . . 19 3.1.6 Beschleunigungsdruckverlust . . . . . . . . . . . . . . . . . . . . . 19 3.1.7 Druckverlust durch Einzelwiderstände . . . . . . . . . . . . . . . . 19 3.2 Gesamtwärmeeintrag der Transferleitung . . . . . . . . . . . . . . . . . . 20 3.3 Lokaler Wärmestrom . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 22 3.3.1 Strahlungswärmestrom . . . . . . . . . . . . . . . . . . . . . . . . 22 3.3.2 Wärmetransport durch die MLI . . . . . . . . . . . . . . . . . . . 23 3.3.3 Wärmetransport durch die Rohrwand . . . . . . . . . . . . . . . . 24 3.3.4 Wärmetransport entlang der Konstruktionselemente . . . . . . . . 25 3.3.5 Konvektiver Wärmeübergang bei einphasiger Strömung . . . . . . . 25 3.3.6 Wärmeübergang beim Sieden einer erzwungenen Strömung . . . . 26 3.4 Thermoakustische Oszillation . . . . . . . . . . . . . . . . . . . . . . . . 28 3.4.1 Definition und Entstehung einer thermoakustischen Oszillation . . . 28 3.4.2 Abschätzung von Amplitude und Frequenz . . . . . . . . . . . . . 31 4 Messaufbau und Versuchsdurchführung 34 4.1 Charakterisierung der Transferleitung . . . . . . . . . . . . . . . . . . . . 34 4.1.1 Messaufbau . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 34 4.1.2 Versuchsdurchführung . . . . . . . . . . . . . . . . . . . . . . . . 36 4.1.3 Untersuchte Transferleitungskonfigurationen . . . . . . . . . . . . 37 4.2 Druckverlust in parallel gewellten Rohren . . . . . . . . . . . . . . . . . . 38 4.2.1 Messaufbau . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 38 4.2.2 Versuchsdurchführung . . . . . . . . . . . . . . . . . . . . . . . . 40 4.2.3 Untersuchte Wellrohrgeometrien . . . . . . . . . . . . . . . . . . . 40 4.3 Messmittel . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 41 4.3.1 Druckmessung . . . . . . . . . . . . . . . . . . . . . . . . . . . . 41 4.3.2 Temperaturmessung . . . . . . . . . . . . . . . . . . . . . . . . . 42 4.3.3 Volumenstrommessung . . . . . . . . . . . . . . . . . . . . . . . . 42 4.3.4 Wägeeinrichtung . . . . . . . . . . . . . . . . . . . . . . . . . . . 42 4.3.5 Supraleitende Füllstandssonde . . . . . . . . . . . . . . . . . . . . 43 4.3.6 Datenaufnahme . . . . . . . . . . . . . . . . . . . . . . . . . . . 43 5 Thermohydraulisches Berechnungsmodell 44 5.1 Aufbau . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 44 5.2 Validierung . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 50 5.3 Ergebnisse . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 53 5.3.1 Wärmeeintrag . . . . . . . . . . . . . . . . . . . . . . . . . . . . 53 5.3.2 Druckverlust . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 55 5.3.3 Transferrate . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 56 6 Ergebnisse der messtechnischen Untersuchung 59 6.1 Wärmeeintrag . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 59 6.2 Druckverlust . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 60 6.3 Austrittsdampfgehalt . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 62 6.4 Transferrate . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 67 6.5 Einkühl- und Aufwärmverhalten . . . . . . . . . . . . . . . . . . . . . . . 70 6.6 Schwingungsneigung der Transferleitung im Stillstand . . . . . . . . . .72 6.6.1 Auftreten thermoakustischer Oszillationen . . . . . . . . . . . . . . 72 6.6.2 Ermittlung des Temperaturprofils . . . . . . . . . . . . . . . . . . 74 6.6.3 Berechnung von Druckamplitude und Frequenz . . . . . . . . . . . 76 6.6.4 Resultierender Wärmeeintrag in den Heliumspeicher . . . . . . . . 79 6.6.5 Dämpfung thermoakustischer Oszillationen . . . . . . . . . . . . . 79 6.7 Reibungsdruckverlust in parallel gewellten Rohren . . . . . . . . . . . . 81 7 Design- und Anwendungsempfehlungen 87 8 Zusammenfassung 91 Literatur 94 Anhang 100 A Messwerte von Druck, Volumenstrom und Massenänderung für HeTra 1 . . 100 B Messwerte von Druck, Volumenstrom und Massenänderung für HeTra 2 . . 101 C Messwerte von Druck, Volumenstrom und Massenänderung für HeTra 3 . . 103 D Messwerte des Kannendrucks für alle untersuchten Transferleitungen . . . 105 E Reibungsbeiwerte der Wellrohre . . . . . . . . . . . . . . . . . . . . . . . 106 F Berechnung des Wärmeeintrags durch thermoakustische Oszillationen . . . 107

Regarding the great importance of a good working environment, in this research, ventilation systems installed in kitchens of restaurants were studied in order to avoid problems and to understand the key factors that can influence on the performance of the system. The results obtained were taken into account to provide some recommendations to a real ventilation system of a restaurant called Pastaria in Gävle (Sweden). This concrete ventilation system was not performing good, and some calculations based on the kitchen design were made trying to offset the problem. A large number of scientific studies related to restaurant kitchen hoods and ventilation systems were used to get the findings. These articles were obtained from scholar web databases. The main problem found in kitchen hoods is the inadequate exhaust airflow. The minimum required airflow varies depending on the size and shape of the hood. Keil et al. (2004) found in their research that only 39% and 24% of the studied hoods met the minimum recommended airflow from ACGIH and ASHRAE guidelines, respectively. Other key factors found are related to the kitchen design. The kitchen hood is recommended to have incorporated a capture hood covering all the burners. Side panels can be employed to increase the capture and containment. High efficiency filters and rigid ducts are also recommended. The cleaning of the ventilation ducts is also an important factor, they are recommended to be cleaned between 1 to 9 years depending on the activity of the kitchen. Thus, key factors such as disturbing airflows and the presence/movement of the cooks can disturb the kitchen hood performance. A very effective solution, isolating the fumes below the hood, that is getting developed is the installation of an inclined air curtain from the cooking surface. Related to the kitchen hood and the ventilation system of the Pastaria restaurant. Some measurements and information were obtained in a visit to the restaurant. After calculations, it was obtained based on the kitchen design that is required a minimum airflow of 4 140 m3/hour. In order to do that, the heat exchanger Swegon Silver C RX, installed in the system, requires a minimum size of 11/12. The distribution of the kitchen appliances in this restaurant seems to be correct. However, a future study in order to see if there are disturbing airflows affecting the kitchen hood performance must be carried out. If after checking all recommendations the performance of the kitchen hood is not good enough yet, an inclined air curtain may be installed due to their great effectiveness against problems of hoods. In conclusion, it was clearly obtained that a correct kitchen distribution design and calculations must be done for each restaurant in order to install the most adequate kitchen hood with the best characteristics. This way, fumes, odors, moisture and particles will be easily exhausted allowing a better environment out of risks to the establishment and customers health.

In this thesis, an innovative coarse grid CFD approach is developed that aims toexploit the capabilities of sub-channel codes and CFD methods while overcoming theirlimitations. In the approach, a very coarse mesh is implemented in the CFD softwareOpenFOAM and a new wall treatment, based on the traditional concept of the wallfunction, is applied to the wall boundary conditions of the domain to take into accountthe low resolution of the grid which does not allow to effectively capture the effect of thesolid walls on the thermo-hydraulics of the flow. To investigate the performance of thenew approach, the method is implemented first in three simple test cases for whichthe sub-channel codes are the state-of-the-art thermo-hydraulic analysis since theyare single-phase flow problems in which there are no prevailing 3D flow conditions.An additional test case representing a 2x2 fuel bundle with three full-length rods andone half-length rod is investigated to verify the behavior of the new approach in caseswhere secondary flows are present. The results for the pressure fields are comparedwith the analytical pressure profiles for the four test cases that well represent the onesthat would be obtained with sub-channel code analysis, while the results for the wallshear stresses obtained in the four test cases are compared with the ones obtained witha more refined mesh in which the traditional wall function approach is implementedsince they should be the best estimation of the actual wall shear stresses at the walldomain. For the first two cases, the developed approach produces reasonable resultswith a good agreement to the analytical pressure profiles while the other two testcases show that the methodology has a limited applicability and, before proceedingwith the extension of the new approach to single-phase problems with 3D prevailingphenomena and two-phase problems, it is necessary to solve the issues that emerge forsome types of cases. / I denna avhandling utvecklas en innovativ CFD-metod med grovt rutnät som syftar till att utnyttja kapaciteten hos underkanalskoder och CFD-metoder och samtidigt övervinna deras begränsningar. I metoden implementeras ett mycket grovt nät i CFD-programvaran OpenFOAM och en ny väggbehandling, baserad på det traditionella konceptet med vägg väggfunktion, tillämpas på domänens vägggränsvillkor för att ta hänsyn till den låga upplösningen av nätet som inte tillåter att effektivt fånga effekten av de solida väggar på flödets termo-hydraulik. För att undersöka prestandan hos den nya tillvägagångssättet implementeras metoden först i tre enkla testfall för vilka subkanalskoderna är den senaste termo-hydrauliska analysen eftersom de är enfasflödesproblem där det inte finns några rådande 3D-flödesförhållanden.Ett ytterligare testfall som representerar ett 2x2 bränsleknippe med tre fullängdsstavar och en halvlång stav undersöks för att verifiera beteendet hos den nya metoden i fall där sekundära flöden förekommer. Resultaten för tryckfälten jämförs med de analytiska tryckprofilerna för de fyra testfall som väl representerar de som som skulle erhållas med kodanalys av underkanalen, medan resultaten för väggskjuvspänningarna skjuvspänningar som erhållits i de fyra testfallen jämförs med de som erhållits med ett mer förfinat nät i vilket den traditionella väggfunktionsmetoden är implementerad eftersom de bör vara den bästa uppskattningen av de faktiska väggskjuvspänningarna vid väggens domän. För de två första fallen ger den utvecklade metoden rimliga resultat med en god överensstämmelse med de analytiska tryckprofilerna medan de andra två visar att metoden har en begränsad tillämplighet och, innan man går vidare med utvidgningen av den nya metoden till enfasproblem med 3D-fenomen och två fenomen och tvåfasproblem, är det nödvändigt att lösa de problem som uppstår för vissa vissa typer av fall.

Fjärrvärmen utgör omkring hälften av all uppvärmning som sker i Sverige idag och har utöver det en viktig roll då den tar vara på mycket energi som annars hade gått till spillo. Att kunna vara ekonomiskt konkurrenskraftig gentemot andra uppvärmningsalternativ är en viktig del för fjärrvärmens fortsatta utveckling. Det finns flera alternativ och möjligheter att göra detta, ett av dem är att hålla nere driftkostnaderna. Det kan bland annat göras genom att minska tryckfallen i näten, som även kan ge en ökad expansionsmöjlighet. Idag används främst avstängningsventiler med reducerande genomlopp i näten, främst på grund av den billigare investeringen. Trots detta saknas en kunskap om hur dessa ventiler påverkar näten sett till tryckfall, drift- och investeringskostnader jämfört med ventiler med fullt genomlopp. För att undersöka detta har två metoder använts för att komplettera varandra och öka förståelsen för ventilerna. Den första metoden beräknade det generella fallet teoretiskt för att se vid vilka flöden som ventiler med fullt genomlopp är mer gynnsamma. Den andra metoden beräknade ett specifikt fall med simuleringar i ett verkligt nät med de olika ventilerna och beräkna vilken som är den mest ekonomiskt gynnsamma. Resultaten av det generella fallet visar att ventiler med fullt genomlopp blir mer gynnsamma när flödeshastigheten överstiger omkring 1 m/s, oavsett dimension, beräknat på under 30 år med ett elpris på 1,50 kr/kWh. Vid dimensionering av nät är det vanligt att använda 1,5 - 2,0 m/s, detta utgör ofta en liten del av nätets drifttid och är ofta lägre. Beräkning av det specifika fallet visade att ventiler med reducerande genomlopp är det ekonomiska alternativet då återbetalningstiden för ventiler med fullt genomlopp var över 600 år vid 1,50 kr/kWh. Utifrån detta kan slutsatsen dras att ventiler med fullt genomlopp inte bör ersätta reducerande genomlopp, utan att det i stället handlar om att identifiera de delar i nätet som utgör, eller kan komma att utgöra, en strypning eller förträngning i nätet där höga flödeshastigheter kan förekomma och möjligtvis byta till fullt genomlopp. / District heating makes up about half of all heating that takes place in Sweden today and, in addition to that, has an important role as it makes use of a lot of energy that would otherwise have been wasted. Being able to be economically competitive against other heating alternatives is an important part of the continued development of district heating. There are several options to do this, one of which is to keep operating costs down. This can be done by reducing the pressure drops in the networks, which can also provide an increased possibility of expansion. Today, shut-off valves with reducing throughput are mainly used in networks, often because of the cheaper investment. Despite this, there is a lack of knowledge about how these valves affect the networks, which is attributed to pressure drop, operating and investment costs compared to valves with full flow. To investigate this, two methods have been used to complement each other and increase the understanding of the valves. In the first method, the general case is calculated theoretically to see at which flows valves with full flow are advantageous. The second method calculates a specific case with simulations in a real network with the different valves and calculates which one is the most economically advantageous. The results of the general case show that valves with full flow become more advantageous when the flow rate exceeds about 1 m/s, regardless of dimension, calculated over 30 years with an electricity price of SEK 1.50 /kWh. When dimensioning networks, 1.5 - 2.0 m/s is a common value, this often constitutes a small part of the network's operating time and is often lower. Calculation of the specific case showed that valves with reducing throughput are the economic alternative as the payback period for valves with full throughput was over 600 years at SEK 1.50/kWh. Based on this, the conclusion can be drawn that valves with full throughput should not replace reducing throughput, but that it is instead a question of identifying the parts of the network that constitute a throttling or constriction in the network where high flow rates can occur and possibly switch to valves with full throughput.