Showing posts with label heat exchanger. Show all posts
Showing posts with label heat exchanger. Show all posts

Tuesday, 24 February 2015

Functions of Air cooled heat exchangers

Air cooled heat exchangers are only one of various kinds of heat exchanger. Heat exchangers are gadgets which are specially designed for aiding the transfer of heat from one fluid towards the other. For us to better understand, typical samples of devices that use heat exchangers include the air conditioners, refrigerators as well as space heaters.

But let us not dwell a lot of over the general heat exchanger rather let's now take a look at air cooled heat exchangers or ACHEs for short. It rejects heat from a hot fluid directly to fan-blowing ambient air. ACHEs are commonly utilized each time a procedure or set up creates heat that has to be removed and regrettably lacks local use. Your car's radiator is actually an example of ACHE device. The engine must be cooled to prevent overheating due to friction and combustion functions by the engine. The excess heat is taken away by the water or glycol coolant mix. Majority of the heat should be taken away, and the best way is as simple as supplying ambient air.

There are more functions for air cooled heat exchangers, including the upstream production, refineries and petrochemical facilities. It can also be used on conditions with high temperature, high pressure, corrosive fluids and environments. Moreover, air coolers is usually equipped and used in gas and oil refineries; compressor stations for oil pipelines; subsurface gas storage facilities; plants producing polychlorvinyl, polyethylene, glass fiber, biplastic; caustic soda plants; by-product coke plants and ammonia transportation and handling plants.


Besides learning the actual functions of ACHEs, we should have a view upon how it operates inside and its elements. Usually, air coolers for process application are composed of a finned-tube bundle with rectangular container headers on both ends of the tubes. Headers are boxers that dispense the fluid from the piping to the tubes. The other parts include one or more fans that give cooling air. The fans are generally powered by electric motors and are also accompanied by speed reduction devices. The fan drive assemblage is sustained by the metal mechanical drive support system. Generally, the air flows up-wards all the way through a horizontal tube bundle. The fans could be either forced or induced draft, dependant upon whether the air is pushed or pulled through the tube bundle. Forced draft unit enables a simple access for maintenance for the fans and the bundles. Furthermore, the fans stay in the cold ambient air. Whilst the induced draft unit provides a stable as well as strong thermal performance because of the protection of the finned surface against wind, rain, hail and snow by the plenum chamber. The induced draft also guarantees an improved air distribution, much less hot air recirculation, much less air-side fouling and lower noise levels at grade. Space in between the fans and the tube bundle is encircled by a plenum chamber, that directs the air. The full assembly is usually installed on legs or perhaps a pipe rack.

Understanding and knowing the inside and out of ACHEs is fairly difficult, especially for those who have no background in mechanical matters. And for this reason, let us once again move our attention on another subject matter, which is the "why" question. With regards to economy, air coolers are preferred due to the lower maintenance expenses. Some other benefits offered by air coolers are as follows: lack of the need for cooling water or other cooling media, no issue shall arise with regards to the thermal as well as chemical pollution of cooling fluids, and it quite fast to install by bolted assembly.

ACHEs are regarded as a "green" alternative because no chemical treatment methods are required to the water or fluid used by the assembly. And temperature is the only parameter that has to be considered whenever getting rid of the water used. Without a appropriate heat exchanger equipment, overheating will ruin your equipments and appliances, specially the parts subjected to heat. Out of all of the things that have been pointed out, if we are to consider the trend that the world is going, air cooled heat exchangers are the ideal choice for industrial plants and other plants if the environment is to be considered.

Friday, 20 February 2015

Explaining What is a Fin Fan Cooler in Simple Language

A fin fan cooler is a term used to refer to an aerial cooler. I believe at one time a specific manufacturer called their coolers "Fin-Fans" and the term later came to be a reference to any aerial cooler. Much the same was as electric refrigerators were all referred to as Frigidaire's or copies are referred to as XEROX's.


This type of aerial cooler is used a great deal in refinery and petro chemical plants. The construction usually consists of two metal rectangular boxes with drilled holes to accept hollow tubes that have aluminum fins attached to them.
For those familiar with a car radiator, the concept is the same. The difference is Fin Fan Cooler Manufacturer construction needs to be more robust because the pressure contained by the coolers is usually much higher than that of a car radiator.
The two boxes (called headers) with the interconnecting tubes are housed in a light metal plenum that directs air from one or more fans over the finned tubes to achieve the desired cooling.
This is a simplified description of an aerial cooler. There are many details regarding fabrication, configuration, materials, fan design etc. that I have left out.
Air coolers are twice as expensive to purchase and install as water coolers. The great advantage of an air cooler is that it does not need cooling water. The difficult aspect of air cooling arises from the flow of air across the tubes.
Most air coolers are either induced-draft or forced-draft, the more common arrangement being forced draft. The air is moved by rather large fans. The tubes are surrounded with foil-type fins, typically 1 in high. The surface area of the fins as compared to the surface area of the tubes is typically 12 to 1. That is why we call an air cooler an extended-surface heat exchanger.
The heat-transfer coefficient of an air cooler Aluminum Radiator (Btu, per hour, per square foot of finned area, per degree Fahrenheit) is not particularly good. It might be 3 to 4 for cooling a viscous liquid, or 10 to 12 for condensing a clean vapor. The low heat-transfer coefficients are offset by the large extended surface area.
In a forced-draft air cooler, cool air is blown through the underside of the fin tube bundle. In an induced-draft air cooler, cool air is drawn through the underside of the fin tubes. Either way, road dust, dead moths, catalyst fines, and greasy dirt accumulate along the lower row of tubes. As the tubes foul, they offer more resistance to the airflow. 

Sunday, 15 February 2015

Shell & Tube Heat Exchanger By Heatec Holdings

We design and manufacture Shell & Tube Heat Exchanger to meet any size and pressure constraints, while achieving maximum heat transfer with increased lifespan and efficiency. Our expertises include manufacturing and fabricating whole range of materials from Low Temp, Stainless Steel, Duplex, Super Duplex, CuNi to clad materials.

Our heat exchange’s are able to meet the stringent requirements of any certification party (e.g, BV, DNV, and ABS) and are able to comply with ASME, API 660 and TEMA standards. We are also a approved manufacturer for NKK Class.

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Principal Office
Heatec Jietong Pte. Ltd.
10 Tuas South Street 15,
Singapore 637076
Tel:  +65 6861 1433
Fax: +65 6861 1347
Email: admin@heatec.com.sg

Saturday, 14 February 2015

Structure characteristic of Fin Tube Heat Exchanger

This kind of cooler are bi-metal rolling compound fin tube type heat exchanger, it is composed of casing、tube bundle、tube box and separator and so on. The specific heat exchanging process is as follow:After heat air flow into gas inlet connect piping, and then swerve to cross outside of the fin, and exchange heat with cooling water in the pipe. Cooled air is separated into oil and gas through separator, and then it flow out to circle from gas outlet tube via turning, thereby complete two courses of heat exchanging and separation. Due to process air flow through tube bundle, its pressure lost will be smaller than traditional baffle plate heat exchanger.

   The casing of bi-metal rolling compound fin tube type heat exchanger is composed of front-end
plate、barrel、gas inlet connecting and flanges、gas outlet connecting and flanges、rear-end plate、saddle、seal plate、slide way and so on. Front-end plate is rotundity with square hole opened on it, where the tube bundle thrust into casing. It has advantage of strong capacity of bearing inner pressure and simple manufacturing. Gas inlet and outlet connecting are arranged separately at two sides of barrel. Connecting flange adopt loose flange,which can settle problems such as centering in course of piping installation. Rear-end plate often adopt rotundity slab, the heat exchanger with bigger diameter or bearing bigger pressure also can adopt ellipse head. The saddle adopted by this suites of inter-stage cooler is spring pedestal,which can remove temperature difference stress existing in the course of working of inter-stage cooler and portion axial\radial stress in piping.  Seal plate is divided into upper spacer、lower spacer、rear spacer. The material of seal bar is silicon rubber, due to seal bar is easy to damage, we make the connection between seal bar and spacer design into bolt connection. After seal bar meet the tube bundle, it separate casing into two portions that is gas inlet and outlet so that succeed to prevent gas is short circuit. The design of slide way by our company is replaceable type. It is better to settle the problem of replacing. Condensation water exhaust outlet is set at the end of casing, where the condensation water flow out from head exchanger.

   The tube bundle of bi-metal rolling compound fin tube type heat exchanger is composed of heat exchanging tube、tube sheet、upper and lower side plate and wheel assembly etc. heat exchanging tube adopted bi-metal rolling compound fin tube. Tube sheet adopted compound tube sheet material. For processing precision of tube hole, it should be according to GB151. Connection of tube sheet and heat exchanger adopt welding structure. Between tube sheet and upper & lower side plate adopt bolt connection. Upper & lower side plate can be taken out in course of checking and repair for the purpose of washing completely for tube bundle. Channel steel and reinforcement strip on upper & lower side plate are playing the strengthening rules. In additional, the surface of channel steel contact with seal bar of upper & lower spacer to come true seal structure. Sliding unit of this heat exchanger adopt structure of wheel and slide way for assembling easily, wheel assembly and lower side plate adopt bolt connection for replacing in time.

   Tube tank of bi-metal rolling compound fin tube type heat exchanger divided into fore-tube tank and rear-tube tank. Number of water-circle need to confirm according to the request of casing diameter and heat-exchanging. In general there are 2、4、6 water-circle number, and it rely on U type seal washer to detach the circle. Numbers of seal channel are made between two bolt holes, screw plug press the O ring tightly to make tube tank and fore-end tube plate connect together. Gas outlet and water discharge are set on fore-tube tank. Gas outlet can ensure that cooling water can be filled in all tube bundle in early operation of heat exchanger. Water discharge is used in checking and repair, it can remove cooling water in pipe.
   The separator of bi-metal rolling compound fin tube type heat exchanger is composed of separator frame and wire mesh demister etc.. The material of separator frame is stainless steel. In order to ensure separating effect, wire mesh demister always adopt high-efficiency type. When the length of heater is more than two meter, it adopt multi-separator, with the structure connected by bolt between separators or separator and casing for convenient checking and repair.


   Bi-metal rolling compound fin tube type heat exchanger is with advantage of low power consumption、small pressure lost、good proof-rust、high heat exchanging efficiency. Nowadays it has been widely used in air-separation industry. 

Thursday, 5 February 2015

Thermal Design specifications and properties of electronic components and materials (Part 2)



The modelling technics currently used have at least two different methods for creating real models for thermal design. One method uses direct geometrical/material analyses to make thermal model for components and the other method uses thermal resistor/capa-citor networks for example the DELPHI-project. Both of these methods should be possible in component level specifications.

The European co-operative project DELPHI /Rosten et al/ is an example of an activity where the responsibility of the thermal design has been attempted to be shared between the supplier of component and the end user.

The specification system for thermal specifications of electronic components and sub-systems and the applicable tests/measurement methods should cover following areas:

- Component specifications
- Interface specimens and materials (heat conducting specimens, thermally conductive insulators) and their specifications and models
- Subsystems (Printed circuit boards, units, rails)
- Heat sinks and fans.
- Material specifications (materials of components and other parts of electronics)

Some guidelines are needed for the thermal specification of PCB and subsystem level. It should be kept in mind that all relevant heat transfer mechanisms are treated, conduction, convection and radiation, when components are positioned on PCB. Monitoring the work of existing groups generating thermal models - DELPHI, SEED, JEDEC; SEMI, and standardising these different methods will be an important task for this research project and CENELEC.

REFERENCE

1. Rosten, H.I. et al. Final report to SEMITHERM XIII on the European-funded project DELPHI - the Development of libraries and physical models for an inte-grated design environment.
Thirteenth Annual IEEE Semiconductor Thermal Measurement and Management Symposium, Austin, TX, USA, 1997. Pp. 73 - 91.
2. Vinke, H. & Lasance, C.J.M. Recent achievements in the thermal characteriza¬tion of electronic devices by means of boundary condition independent compact models.
Thirteenth Annual IEEE Semiconductor-Thermal Measurement and Management Symposium, Austin, TX, USA, 1997. s. 32 - 39

1. ECONOMIC AND SOCIAL BENEFITS

A good thermal design of electronics is crucial on the reliable and safe operation of equip¬ment. The current situation makes it difficult to design electronics effectively because of the lack of standardised thermal specifications of electronic components and heat conducting materials. The ever increasing power density of electronics causes large difficulties for the designers who need more accurate and reliable information of thermal properties. The existence of standards could make it much more economical to make good thermal design.
 
2. SCIENTIFIC AND TECHNOLOGICAL OBJECTIVES

The RTD work-programme should contain the following tasks:

1. Definition of specifications of the thermal properties of electronic components

1.1 Parameters

Definition of the specific thermal parameters concerning thermal design of components, assembled printed wiring boards, materials and test methods.

1.2 Units

Units (and symbols) of the thermal parameters concerning thermal behavior and also design of components, assembled printed wiring boards and various materials shall be defined.

2. Thermal specifications of electronic components and interface parts

2.1 Evaluation of various package types of electronic components

Evaluation of package types used in electronic components shall cover such packages which probably have use also in the future. Evaluation concentrates on finding possibilities to use some simplified geometric thermal model for these package types. Therefore the project has to find and develop some principles how such simpilification should be done.

2.2. PBGA-package evaluation of simplification of detailed geometric models

The objective is to develop methodology for deciding what level of geometric simplification is practical in modelling thermal properties of Plastic ball grid array packages (PBGA). The project includes comparing the simplified models to accurate geometric model of this package type by using simulations and testing.

2.3 Resistor package geometric model

The effect of mounting method of resistors on temperature of the component itself. Developing description of some standardised mounting methods.

2.4 Description of heat sink thermal properties

Develop a method for describing thermal behaviour of heat sinks by using effective heat transfer surface area  for the component instead of using the thermal model of heat sink. This kind of scaling factor reduces the size of accurate thermal model considerably.

3. Thermal specifications of materials used in electronic components

3.1 Material types

Selection of basic material types, how to manage specification for
- construction materials
- interface materials, glues, adhesives, plates

Metals, plastics, ceramics, adhesives, glues, printed wiring board materials, other conductive materials, powder metals, composites

3.2 Basic properties of various materials

- Standard definition of various properties (use of other standards)
- Description of specification for various basic material types
- Effect of surface contact resistance on thermal properties
Thermal conductivity, thermal resistance, contact resistance at surface, thermal capacitance, specific heat, emissivity, density, coefficient of thermal expansion, surface properties (roughness), etc.

3.3. Test methods of thermal properties of materials

- Comparison and further development of test methods
- Selection of test methods to measure various material types

7. TIME SCALE

Although no rigid time scale requirements apply to this project, based on the described objectives, the whole project should be completed within three years maximum.

8. IMPORTANT ADDITIONAL INFORMATION

To get a reasonable amount of progress in this area, a minimum of three intrested parties is necessary.

Close connections with CENELEC should be demonstrated in the proposal, and ensured during the proposed workplan, in order to properly match the requirements of industry and the evolution of technology.


Solar energized Liquid Desiccant Air Conditioning – A review (Part I)

Abstract

A review on Liquid Desiccant based cooling technologies with special focus on advances in
liquid desiccant materials and configurations of heat and mass exchangers have been
discussed. Performance comparison and energy saving potential of a hybrid liquid desiccant
cooling system based on vapour compression based sensible cooling and liquid desiccant
based dehumidification in comparison to conventional vapour compression system has been
reviewed. Hybrid liquid desiccant cooling system has enormous energy and cost saving
potential especially in hot and humid regions like India. The ability of Liquid Desiccant
cooling technology to be energized by Solar thermal makes it an attractive alternative to high
electrical energy intensive conventional vapour compression based cooling for residential and
commercial HVAC applications.

Keywords: Liquid Desiccant, Dehumidification, Vapour Compression, Solar Thermal.

1. Introduction

India is a tropical country and more than 80% of Indian Sub continental area falls under
Warm humid or Composite Climatic zone [1]. These climatic zones are characterized by high
annual average temperatures and high humidity. With rapid urbanization and industrialization
in India, there is sharp rise in air conditioning load in Industrial, commercial as well as
residential buildings.

 The Air conditioning load could be broadly classified as sensible load and latent load.
Conventional vapour compression Air conditioners (VAC) meet the total air conditioning
load by cooling the air below the dew point temperature and thus condensing the moisture.
These systems require evaporator temperatures to be maintained much lower than required to
achieve sensible cooling alone. The dew point temperature is much below the set temperature
level and hence process air requires further heating to bring its temperature to set temperature
level. This requirement increases the capacity rating of the compressors and requires high
electricity and consequently operates at reduced coefficient of performance (COP) [2].

There is a necessity to separate the latent cooling load and sensible cooling load and handle
them separately so as to improve the COP of the air conditioners. The desiccant cycles can be
used to reduce the moisture content of air by partially converting latent cooling load to
sensible cooling load and then meeting the load by VAC’s. These systems with vapour
compression cycle for meeting sensible cooling load and liquid – desiccant cycle for latent
cooling load are called hybrid systems.

2. Liquid desiccant dehumidification and air conditioning

A desiccant material has a strong attraction for water vapour. Desiccants are commonly used
in industrial applications where low dew-point air is needed. The strength of a desiccant can
be measured by its equilibrium vapour pressure (i.e., pressure of water vapour that is in
equilibrium with the desiccant). This equilibrium vapour pressure increases roughly
exponentially with the temperature of the desiccant/water system. It also increases as the
desiccant absorbs water (a dilute liquid desiccant will have a higher equilibrium vapour
pressure than a concentrated liquid desiccant). When the absolute humidity of air that has
come into equilibrium with a liquid desiccant of fixed concentration is plotted on a
psychometric chart, the equilibrium line closely follows a line of constant relative humidity
and the Fig1. illustrates this behaviour for solutions of lithium chloride.


As shown in the Fig 2., the brine-bulb temperature for a 43% solution of lithium chloride and
air at 30.0/25.6°C dry-bulb/wet-bulb will be 47.8°C. With an ambient wet-bulb temperature of
25.6°C, a typical cooling tower might supply water at29.4°C. It’s impractical to cool the
ambient air using this cooling water in a conventional heat exchanger, because the cooling
water is only one degree below the air temperature. However, a strong cooling effect could be
achieved by wetting the surfaces of the heat exchanger with the 43% lithium chloride. Of
course, one does not get this enhanced cooling for free. If the cooling process is to be
continuous, energy must be expended to regenerate the desiccant back to its original
concentration. If ambient air from the preceding example is brought into equilibrium with
43% lithium chloride at 85°F (29.4°C), the air will have a dew point of 33.5°F (0.8°C), a wetbulb
of 57.8°F (14.3°C), and its enthalpy will be reduced from 41.5 Btu/lb (96.3 kJ/kg) to
24.9 Btu/lb (57.8 kJ/kg). This large cooling effect, both in terms of latent cooling and total
cooling, and low dew point—both of which are achieved without a compressor—demonstrate
the potential for liquid desiccants to become an important part of HVAC systems. Liquid
desiccants have been successfully used to produce dry air for a surprisingly long time. Dr.
Russell Bichowsky, working for the Frigidaire Division of General Motors, first used
solutions of lithium chloride to dry air in the 1930s. Also in the 1930s, the Niagara Blower
Company introduced a liquid desiccant technology that used glycol solutions to prevent frost
from forming on low-temperature evaporators. Both lithium chloride and glycol continue to
be used today in liquid-desiccant dehumidifiers, but their use is limited primarily to industrial
applications[3].

3. Hybrid configuration: desiccant de-humidification and vapour compression based
cooling

An example of desiccant cooling application is represented in fig. 3 [4].


Figure 3.Schematic of Hybrid Liquid Desiccant aided Vapour compression air conditioning

Here, the cool strong desiccant solution is sprayed onto the top of the dehumidifier through
spraying nozzles. By gravitation, it trickles through the structure of the dehumidifier where it
gets contact with the process air stream blown perpendicularly to its trickling flow direction.
Since, the cool and strong desiccant solution vapour pressure is less than that of the air vapour
pressure, water vapour migrates from the air stream to the desiccant solution and condenses
therein. Consequently, the heat of condensation and mixing are liberated causing an increase
in the solution’s temperature. The process air stream is slightly cooled down due to its contact
with the cold desiccant solution. The dehumidified and rather warm process air stream then
passes successively through the evaporative cooler and the evaporator of the traditional
refrigerant vapour compression air conditioner, before being delivered into the conditioned
space. The diluted desiccant solution, exited from dehumidifier, is circulated through the
regenerator where it is heated and the moisture absorbed in the dehumidifier is now lost to the
scavenger air stream. In order for the system to keep functioning continuously and effectively,
an equal amount of water vapour absorbed from the humid air and condensed to the desiccant
solution in dehumidifier must be evaporated from the desiccant solution in the regenerator.
The hot and strong desiccant solution is thereafter cooled down in the pre-cooler and then
cooled further in the heat exchanger (HX) before being ready again to dehumidify the
incoming process air.

The lowest limit temperature attainable by the evaporative cooler is the process air wet bulb
temperature which decreases with the decrease of the relative humidity and increases with the
elevation of the dry bulb temperature. The essential role of the desiccant solution in this example is to lower the relative humidity of the incoming air stream in order to enable the
evaporative cooler to function more effectively.
Here, the desiccant assisted evaporative cooling is associated with the traditional vapour
compression air conditioning to reduce its size and enhance its coefficient of performance.
Because the latent load is handled independently by the desiccant dehumidifier, the need of
cooling the ventilation air below its dew point is obviated. The temperature of evaporation can
thus be lifted up to 15 °C from its generally practiced level of 5 °C for the traditional vapour
compression system. The increase in evaporation temperature will entail the increase of the
system’s coefficient of performance (COP).

This assemblage can be useful in humid climates where the wet bulb temperature is fairly
high. In such climates, a significantly downsized vapour compression air conditioner can be
supplemented with a desiccant assisted evaporative cooler in order to reach the desired indoor
temperature, thus enabling costs and energy savings and improving the indoor air quality.

4. Liquid desiccant materials

Liquid desiccants such as Glycols and solutions of halide salts are routinely used in industrial
de-humidifiers. Commonly used liquid desiccant materials include lithium chloride, lithium
bromide, calcium chloride, triethylene glycol and mixture of salts etc. The choice of desiccant
will have a profound effect on the design of desiccant de-humidifiers.

The desirable properties of liquid desiccants include large saturation absorption capacity, low
regeneration temperature, Low Viscosity, Good heat transfer, non volatile, non – corrosive,
odourless, non toxic, non flammable, stable and inexpensive. Surface Tension of liquid
desiccants is an important parameter of liquid desiccants as it plays important role in static
hold up and wetting of the surface of heat and mass exchanger of Liquid desiccant system.
Halide salts such as lithium chloride and lithium bromide are very strong desiccants. A
saturated solution of lithium bromide can dry air to 6% relative humidity and lithium chloride
to 15% but halide salts are corrosive in nature. Lithium Chloride has good desiccant
characteristics and does not vapourize at ambient conditions but droplet filters are necessary
to prevent any mixing of the liquid droplets with process air. Cost of halide salts are relatively
high except calcium chloride whose cost is comparatively low compared to LiCl, LiBr and
TEG. Another advantage of Calcium chloride is its low viscosity which reduces the pumping
power. But the CaCl2 salt is highly corrosive in nature and can be used in non metallic
systems only [5].

The least expensive alternative to lithium chloride is calcium chloride. Unfortunately, calcium
chloride is a relatively weak desiccant. A 42% solution, which is about as strong as can be
used without encountering crystallization, will dry air to about 35% rh. (For comparison, a
43% lithium chloride solution can dry air to a 15% rh.).

Glycols are the second class of liquid desiccants now used in industrial equipment. Both
triethylene and propylene glycol have low toxicity, and their compatibility with most metals
has led several researchers to use them in LDACs designed for HVAC applications. However,
all glycols have one undesirable characteristic that they are volatile and any evaporation into
the supply air makes it unacceptable for air conditioning for occupied buildings [6]. Salts of weak organic acids, such as potassium or sodium formate and acetate, have been explored as less corrosive alternatives to halide salts that are also not volatile. Although it is a significantly weaker desiccant than lithium bromide or lithium chloride, the ability to dry air below 30% relative humidity could make potassium formate a good alternative desiccant in some applications. Another less expensive alternative is potassium acetate. While potassium acetate could dry air to about 25%, its viscosity becomes very high. At 70% concentration and 27°C, a potassium acetate solution has a viscosity of about 28 cp. This is almost twice has high as a 43% lithium chloride solution at the same temperature. Water at 27°C has a viscosity of close to 1.0. [3].

Studies were also conducted on mixtures of calcium chloride and lithium chloride solutions to
take the advantage of good desiccant properties of LiCl and low cost CaCl2 [7].

4.1 Advantages of using liquid desiccants include

1. Lower air pressure drop in process air stream.
2. Liquid desiccants are capable of providing equivalent dehumidification as solid desiccant
systems with lower regeneration temperature(mostly 70 - 80°C) due to the internal cooling
provided by cooling tower water or chilled water and allowing utilization of solar heat or
waste heat.
3. Pumping of liquid desiccants is possible makes it possible to connect several small
desiccant dehumidifiers to a larger regeneration unit which is especially beneficial for
large multi zonal commercial buildings.
4. Liquid desiccants have high COP’s as highly efficient liquid-liquid exchangers could be
employed.
5. Simultaneous air dehumidification and desiccant regeneration is not necessary as it is
possible to store dilute saturate liquid until regeneration heat is available.
6. Liquid desiccants are highly beneficial for their ability to filter microbial contamination,
bacteria, viruses, and moulds from process air stream.

To know more, please visit: http://www.heatecholdings.com/

Wednesday, 4 February 2015

The Purpose of Using a Fresh Water Generator


While sea water is not edible or can be consumed in any appropriate way, many generators out there are rather helpful in the process of converting sea water into fresh water in a short period of time. The fresh water generator has managed to achieve a huge amount of attention from countless people from all over the globe. This is due to the fact that generators come in handy for many reasons, all of which are unique and what all individuals require in the first place. These are mainly used for the purpose of the conversion of sea water to fresh water.

Easy Installation
When it comes to the important matter of installation, a fresh water generator hardly takes up a lot of time. This means that people can have it installed without having to struggle too much in the matter, making it a great choice for the conversion of sea water to fresh water within a little amount of time. Usually these generators are not as huge as one may expect them to be, making them rather portable and easy to install due to their compact size that is most unlikely for a generator.


Less Maintenance Required 
What makes a fresh water generator worth its cost is the fact that it requires very low maintenance. While many people think that it is not simply true, these generators require no extra cleaning or an addition of other machines and equipment in order to run the generator on a daily basis in the future. Any ship crew or an individual on ships and boats can actually use it daily and save time on the low maintenance for this particular generator. The generator offers very easy access to anyone who wishes to use it. It does not require a good amount of maintenance for long periods of time.

Production of Low Salinity Water
The production of low salinity water is the result of using these generators; thus, those who are looking for acquiring this particular feature should definitely go for these generators as they can surely bring out their desired results in the near future. These generators are usually equipped with electric motors as well as water pumps, which come in handy in the job the machine has to carry out. Some of these generators also have steam heating systems built in inside them. The usage of these generators these days has already helped a great deal of people in the process of converting sea water into fresh water; and those who have not yet brought it should really do so now.

Cost Efficient 
The operational costs are also rather low in comparison and this makes it cost efficient. This is due to the fact that less fuel is used in the process of converting sea water to the fresh one. A fresh water generator is usually the kind of machinery which is used for a long period of time and even in short, it lasts for more than ten years. Different brands offer generators which are unique in their own way; therefore, the choice is completely up to people and they can always decide according to whatever they prefer more.

User-Friendly
A fresh water generator is something that everyone needs, especially for people who travel a lot and spend a lot of time on ships. The process of converting sea water to fresh water can be simply impossible and had it not been for these generators, people would still be looking for various other ways to carry out the task. These generators are easy to use on a day to day basis. This means that everyone can use it without having to have any prior technical knowledge. On the other hand, there is nothing difficult about these generators also because they are made for general use.

People can go here to read the new information about fresh water generator.

Thermal specifications and properties of electronic components and materials (Part 1)

1. CONFORMITY WITH THE WORK PROGRAMME

This topic falls under the Competitive and Sustainable Growth Programme, generic activity Measurement and Testing.  Specifically, it is related to Objective GROW-2000-6.2.1 Methodologies to Support Standardisation and Community Policies for which expressions of interest have been called.

2. KEYWORDS

Thermal specification, thermal design, electronic component, modelling, thermal interface, properties of materials, design rule, test method, standardisation.

3. SUMMARY OF OBJECTIVES AND JUSTIFICATION

Controlled thermal design of electronic equipment is currently a very important area of electronic design. This is because the dissipated power densities of modern electronic chips have now reached such a high level that advanced heat transfer systems are needed. However there currently exists very little standardised information about the thermal properties of various electronic components and materials, or the test methods for verify¬ing these thermal properties.
With the new standardised specifications, models and test methods the users and designers of electronic equipment could get better, compatible and more realistic description of the thermal behavior of electronic equipment. Design time reduction and better accuracy can be achieved by using more effective and harmonized thermal models and specifications of electronic components and of heat conducting materials.

4. BACKGROUND

Controlled thermal design of electronic equipment is currently a very important area of electronic design. This is because the dissipated power densities of modern electronic chips have now reached such a high level that advanced heat transfer systems are needed.
However, there currently exists very little standardised information about the thermal properties of various electronic components and materials, or the test methods for verify¬ing these thermal properties. In CENELEC there are no standards for the thermal design of electronic equipment and components.
With regard to standardisation, the technical development of thermal models for compo-nents, and thermal simulation methods are advanced enough, to be used for better
thermal specifications for electronic components. Recent studies performed in Europe by DELPHI and SEED projects (DELPHI = Development of Libraries of Physical models for an Integrated design environment, SEED = Supplier Evaluation and Exploitation of DELPHI, SEED is European ESPRIT project) and the published documents by JEDEC and SEMI will help when starting specification work at CENELEC. In the International Electrotechnical Commission (IEC) there are not any activities on this area yet.
The information sources of thermal data for the manufacturer of electronic equipment are material suppliers and component suppliers. Using both of these channels the equipment designer should get reasonable thermal data. To improve this data flow from supplier to equipment manufacturer, some standardised specification system is needed. CENELEC is the most suitable organisation to co-ordinate this task.


On the following page there is a key figure illustrating ideas on how to manage the basic thermal specification parameters which should be addressed when specifying an elec-tronic component. In these specifications it is very important, to cover all the applicable heat transfer mechanisms: thermal conduction, convection and radiation.
It is also important to describe every component type by the actual feasible method (which is also measurable) to be used in verification of given parameter values in various models.


How to manage thermal properties of electronic components?



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Tuesday, 3 February 2015

Reasons for Investing in a Steam Condenser

For those who are not aware, a steam condenser is used for a many different reasons and one of the most important ones includes the condensation of steam to water. These are used for other reasons too but majorly, they come in handy for condensing steam to water in the long run. The process may take up a lot of time but it is exceptionally effective and efficient. These are used by many high end industries as well as plants in the present times. Therefore, investing in these surely is the best way for anyone to convert condensed steam into water without having to face any issue. There are a number of reasons why people should – and are – investing in steam condensers and here are a few of them.

High End Affordability 
While these condensers may seem rather high end, their prices are not as much and these days, individuals can purchase these at reasonable prices. However, prices are always linked to the kind of condensers and that means their quality. Therefore, it is highly essential to be aware of the fact that a steam condenser is most likely to have a variable price range, all of which depends solely on the type and kind of the condenser. High quality ones are more towards the costly side and the average quality ones should be attainable for a fairly less price. The fact that it is so affordable has led many enthusiastic people to the shops to purchase the product. Most customers are impressed with the fact that it costs so less and yet is able to perform to such high standards. Better quality combines with high end affordability has really helped the product.




Easy to Install & Use 
The best part about setting up a steam condenser is the fact that it enables people to do any kind of installation. While a lot of equipment requires fixed installation, these condensers can be installed in a number of different ways which are all beneficial on their own. It all depends on either the requirement or the type of installation which is required by a person in the first place. These condensers can be installed both vertically as well as horizontally – choosing from both of these truly does depend on the person who is setting up these condensers for major applications of various kinds. It does not require hard labor to install the product and it also does not require experts to teach people how to use it. It is quite customer and user friendly in all senses of the word. It makes work simpler and easier to do.

Vast Variety
The condensation tends to take place in containers, which are all unique in their own way. Mostly, the containers are either shell & tube shaped, for that matter. A steam condenser can have any of these containers or chambers for the matter of condensing steam to water. However, everyone’s requirements tend to vary, which is why choosing the right chamber for the process is exceptionally important and should be thoroughly considered by an individual who is about to go ahead with the overall process of condensing heat to water. By choosing the right container, the procedure is most likely to go smoothly and be successful later on. There are a number of different options and varieties to choose from. Really, the customers can simply go crazy over the choice. It can be made using a number of different materials to suit each individual’s style or requirement as well.

So there it is, these are all the reasons why steam condensers are considered to be such industry winners and are selling like hot cakes in the markets. Go and buy one now!

Thermal Design Objective for Spacecraft




The basic purpose of thermal design is to maintain the temperature of all spacecraft components within desired limits.  We also wish to minimize the temperature fluctuation (thermal cycling) that the spacecraft components are subjected to.  FalconSat-2’s internal components, which are the most thermally sensitive parts of the satellite, are fairly thermally decoupled from the external heat flux the satellite is subjected to.  This is due to the design with the inner column and outer structural shell.  This allows us to control the temperature with a passive thermal design approach.  We will modify the thermo-optical properties (absorptivity and emissivity values) of the external facets of the satellite so that the satellite and all components are maintained within the optimal temperature range.

On FalconSat-2, the operational temperatures are limited by the electronic components within the satellite, and specifically by the battery.  The battery is the most thermally sensitive of the satellite subsystems because it cannot be recharged below 0˚C.  As a result, the nominal temperature range targeted for the batteries and internal components of FalconSat-2 is +5 to +30 deg C.  The other commercial electronics within the satellite have temperature limits of –40 and +85 deg C.  The structural components and solar panels have much more relaxed temperature limits.  Table 1 lists the temperature limits for FalconSat-2.

Table 1 – Temperature limits for FalconSat-2 subsystems


To design the thermal subsystem and ensure that FalconSat-2 will meet these temperature limits, we had to first simulate the thermal behavior of the satellite.  This will allow us to see how the satellite will behave without any thermal control implemented, which will in turn show us what design we must implement to meet the temperature range requirements.  In order to simulate the satellite’s thermal behavior, a model had to be created.

We require a detailed thermal model of FalconSat-2 for several reasons.  Primarily, we need to simulate expected on-orbit thermal behavior of the satellite and ensure that no spacecraft components exceed their maximum or minimum temperature limits.  We also need to ensure that the temperature fluctuation (thermal cycling) of all spacecraft components is minimized.  By simulating varying on-orbit scenarios, including varying attitude modes and varying subsystem operation modes, we can also simulate worst-case hot and worst-case cold temperature scenarios.  Furthermore, we wish to use the thermal model to simulate testing environments that we will subject the satellite to at various phases throughout the development.  Furthermore, we wish to integrate the thermal model into an overall behavioral model of the satellite to assess the interaction of the thermal design with the rest of the satellite.

The inputs to the flux history calculation routine are the satellite’s epoch classical orbital elements, epoch date and Universal Time, the satellite’s attitude control method (Sun-tracking, velocity tracking, tumbling, or quaternions), and the time of flight taken from the simulation clock.  The outputs are insolation, Earth infrared, and albedo fluxes for each face with respect to time for an entire orbit.

The flux history calculation model is broken into five modules within MatLab.  These modules, along with their inputs and outputs, are discussed here:

COE Update--This module updates the classical orbital elements (COEs) from the epoch time to the current simulation time. Inputs are the epoch COEs, the epoch date and time, and the time of flight, taken from the MatLab simulation clock.  This module outputs updated COEs for the satellite and the current Julian date.

Light--This module calculates the sun position vector, the satellite position and velocity vectors, and whether or not the sun currently illuminates the satellite.  Inputs are the current COEs and Julian date.  Outputs are the satellite position vector (R), satellite velocity vector (V), sun position vector (Rsun), illumination flag (Vis) and satellite/sun Beta angle.

Surface Normals--This module calculates the surface normal vectors of each of the six faces of the satellite.  This routine is used if the satellite is sun-tracking, velocity-tracking, or randomly tumbling.  There is a switch where the user can choose which tracking mode to use.  Alternatively, the surface normal vectors can be calculated using quaternions from an interface with Satellite Tool Kit.  There is a switch that allows the user to choose which method of calculating the surface normal vectors they would like to use.  Inputs are the satellite position vector (R), satellite velocity vector (V), sun position vector (Rsun), illumination flag (Vis) and satellite/sun Beta angle.  Outputs from the module are the surface normal vectors for each face of the satellite, the angle from the +K axis to the satellite R vector (phi), and the angle from the +I axis to the satellite R vector (theta).

Insolation--This module calculates the insolation flux on each of the six faces of the.  Its inputs are the surface normal vectors, sun position vector, and illumination flag.  It outputs the insolation flux on each face in Wm-2 in both graphical and matrix form.

Earth Effects--This module calculates the Earth Infrared and Albedo flux on each of the six faces of the satellite.  This part of the model takes the longest time, as there is a double discrete summation to calculate the Earth IR and Albedo view factors for each face of the satellite.  Inputs are the surface normal vectors for each face of the satellite, the satellite position vector (R), the sun position vector (Rsun), the angle from the +K axis to the satellite R vector (phi), and the angle from the +I axis to the satellite R vector (theta).  It outputs the Earth infrared and Albedo flux on each face in Wm-2 in both graphical and matrix form.

You can read more about thermal design here.

The CFRP Primary Structure of the Space Telescope


ABSTRACT
The design of the Primary Structure of the Mid Infra – Red Instrument (MIRI) onboard the NASA/ESA James Webb Space Telescope will be presented. The main design driver is the energy flow from the 35 K “hot” satellite interface to the 7 K “cold” MIRI interface. Carbon fibre reinforced plastic (CFRP) was chosen for this application due to the low thermal conductivity at cryogenic temperatures, high strength and low density. Details of the qualification programme will be given.
INTRODUCTION
One of the European contribution to the James Webb Space Telescope is the Mid InfraRed Instrument (MIRI), which contains both a camera and a spectrograph. The Primary Structure is a hexapod connecting the MIRI and the ISIM (Integrated Science Instrument Module) structure of the telescope. This structure is supplied by Danish Space Research Institute (DSRI).


Fig. 1 The hexapod structure mounted to the MIRI Instrument

ENVIRONMENTS

The Primary Structure supporting MIRI must sustain the launch loads with a safety margin.  During operation the structure will serve as thermal isolation between MIRI, which is cooled down to 7 K, and the 35 K ‘hot’ ISIM structure of the James Webb Space Telescope. The goal for the total heat flow through the hexapod structure is less than 6 mW. The requirements for the Primary Structure are summarized in Table 1.
Table 1

 Summary of Primary Support Structure requirements

Weight of MIRI
103 Kg
Minimum Eigenfrequency
60 Hz
Max. g-load in any direction
20 g
Operational temperature
7K - 35K
Maximum heat flow through all 6 struts
6 mW
Max. Weight of hexapod
5 Kg

DESIGN

The Primary Structure has been designed to have high strength and high stiffness, and at the same time have a low heat flow at cryogenic temperatures. This structure is designed as a hexapod with 6 struts as legs and 3 brackets at the interface between the struts and the ISIM. A similar bracket configuration is used for the interface to MIRI (see Fig. 2)
Fig. 2  Primary support structure with 6 struts, 3 ISIM and 3 MIRI brackets.
The 3 apexes of the struts at the ISIM structure and the 3 apexes of the struts at the MIRI side lie on circles with diameters of 1200 mm and 600 mm, respectively. The angle between the struts at the MIRI interface is 110 degrees. This ensures that the stiffness of the structure has the same, minimum, value in all axes, which minimises the heat conducted along the truss legs. In a cryogenic truss structure the conducted heat load is directly proportional to the sum of the stiffnesses in three orthogonal axes.

Struts are assembled from a CFRP-tube and 2 Invar end fittings. The CFRP tubes have an inner diameter of 33 mm and a wall thickness of 1.3 mm. Using struts result in a good thermal design because they are long and the loads are transferred purely in tension or compression. As a result, the stresses across the section are uniform and all the material that is conducting heat is also doing its share of carrying the load. Since the length of the struts is already fixed, the cross section and the materials can be optimised.

To avoid moment loads on the struts, the brackets have flexures in two directions to avoid transferring the moments.

The struts are connected to the brackets with pins. The pins have two parts. A split bush with an inner conical bore and a conical pin, which is preloaded with a nut (see Fig.3). Play is taken out by preloading the pin. The struts and the brackets are locked in the same process.
Fig.3 Pin assembly of a bush with an inner conical pin preloaded with a nut.
CFRP-DESIGN
CFRP has been chosen for the tubes, since it has high strength, good stiffness, low Coefficient of Thermal Expansion (CTE), can operate at cryogenic temperatures and has a low density. CFRP with high strength fibres has a high Strength/Thermal conductivity ratio at these temperatures (1, see Fig. 4).
Fig. 4 Ratio of tensile strength/thermal conductivity for unidirectional (0 deg) fibre – reinforced laminates as a function of temperature (1).  It can be seen that HS carbon (High stress carbon) has a high ratio at low temperatures.
We have chosen to use T300 fibre because of its excellent ratio of strength to conductivity (Fig 4). Its characteristics are also very well documented and it is qualified for space use. Although the design of the struts is limited by stiffness and buckling considerations, using a high-modulus fibre would not help since there would be no advantage thermally and the high sensitivity of high-modulus fibre to microcracking is a real disadvantage. (See Table 2)
Table 2

Laminate Property

Fibre type

Low CTE
High modulus
Low CME
High modulus
Strength
High strength
High stiffness
High modulus
Resistance against microcracking
at cryogenic temperatures
Low modulus
(High strength)
Low thermal conductivity
High strength
Fibre volume content is a main parameter for characterizing the mechanical properties of a laminate. The properties improve with increasing fibre volume content. Due to the high viscosity of the L20/SG resin system used, the maximum fibre volume content achieved for these struts is about 56%.

The primary design driver for the struts is the stiffness requirement. The second important design driver is buckling. High stiffness and high buckling resistance is achieved by having a high Young’s modulus in the axial direction of the strut. This implies a lower cross section to achieve the same eigenfrequency . For our application, the laminate does not need to have isotropic properties. In Table 3, it can be seen that a laminate with (0°, 90°) fiber angles is preferred.
Table 3

Fibre lay up (relative to the tube direction)

Young’s-modulus of laminate

(45,-45)
14380 MPa
21,1 %
(0,90)
68070 MPa
100,0%
(0,60,-60)
48500 MPa
71,3 %
(0,45,90,-45)
48500 MPa
71,3 %
Manufacturing of a precise (0°,90°)  laminate is not possible, since in the filament winding process the 0° fibres cannot be well controlled. To get a laminate with better manufacturing quality it is necessary to rotate the layers through a small angle. This reduces the Young’s modulus but with an angle of 3° the reduction is very small (see Table 4).
Table 4 Comparison of inclined lay up

Fibre lay up (relative to tube direction)

Young’s-module of the laminate

(0,90)
68070 MPa
100,00 %
(1,91,-1,-91)
68040 MPa
99.96 %
(2,92,-2,-92)
67992 MPa
99,88 %
(3,93,-3,-93)
67730 MPa
99,50 %
(5,95,-5,-95)
67130 MPa
98,62 %
(10,100,-10,-100)
64280 MPa
94,43 %
To reduce the formation of the microcracks during the cool – down, it is important that the fibre layers have the same thickness. Microcracks occur in the resin parallel with the fibres (see Fig. 5). Cracks are formed because each layer has a high stiffness, high strength and a low CTE value in the fibre direction and a high CTE, low strength and a low stiffness in the direction normal to the fibres. During cool - down the layer contracts most in the normal direction adding strain to both directions. In a laminate with same layer thickness, stresses will build up to the same level in both directions, and thereby dividing the stresses in an optimal way. The strength of the fibre layer is low in the normal direction, and if  the critical strength is exceeded, microcracks will be formed.
Ffig. 5 Direction of fibre layer properties between a 0° degrees layer and a 90° degrees layer.
The CFRP-tube has endfittings bonded to the inner diameter. The first inner layer must be a (+ or -) 3° layer since this carries the axial loads better between the endfitting and the tube. The outer layer should be a (+ or -) 93° layer to keep the tube together. The lay up is shown in Table 5.
Table 5 Fibre lay up of CFRP-tubes.
Layer
Angle
thickness
1 (Inner tube)
+3°
0.15 mm
2
-3°
0.15 mm
3
+93°
0.15 mm
4
-93°
0.15 mm
5
+3°
0.15 mm
6
-3°
0.15 mm
7
+93°
0.15 mm
8 (Outer tube)
-93°
0.15 mm
Table 5. Fibre lay up of CFRP-tubes.
Calculations based on data provided by ESA in connection with the HERSCHEL and PLANCK missions indicates that this laminate will have  a thermal conductivity ~0.035 Wm-1K-1 at 7 K and ~0.218 Wm-1K-1 at 35 K. This is a change of more than a factor of 6 over the range, implying higher temperature gradients in the cool end of the tube. The heat flow for one strut is calculated to be 1mW. The temperature distribution can be seen on Fig. 6.
Fig.6 Temperature distribution through a CFRP strut –tube.  Note the high temperature gradient at the cool end.
TEST-PROGRAM
The struts have to go through a test program before they are ready for delivery for the structural test model (STM). This program includes measurements of strength, cryogenic cycling, thermal conductivity, CTE, CME and fibre volume. The test program is on-going.
Strength: This test has the purpose to verify the strength of the struts. This is a standard tension and compression load test where the struts are loaded with a test load 20% higher as the actual max load. The struts manufactured in phase 1 (the development phase) have been tested with a test load of 16500 N.
Cryogenic test:  The purpose of this test is to verify that the struts do not lose strength and to investigate if there is a change in stiffness after thermal cycling to cryogenic temperatures. Three struts will each be cooled down to 7 K 12 times. After 3, 6, 9 and 12 cycles the struts will be loaded in tension with the test load of 16500 N as used in the strength test (see Fig. 8).
The struts for these tests are only 200 mm long. The 3 struts have now been through the 3 first cycles and have been tested with tensile test load. The graph for the deformation force curves can be seen in Fig. 9.

Fig. 8 Short strut mounted in tension test machine.
Fig 9 Force and deformation curves for 3 struts before and after the 3 first cycles. The 3 struts show  increased deformations after 3 thermal cyclings 0 – 4 mm.
Thermal conductivity: Will be measured by the Rutherford Appleton Laboratory (UK) in the range from 7K to 35 K.
CTE is measured at Forschungszentrum Karlsruhe. The CTE is measured on samples which are 1.2 mm x 4 mm x 25 mm.  The measuring range is from RT to 20 Kelvin.
CME is measured from a complete dry tube to a  60% moisture content at RT.
Fiber volume has been measured for the first samples and the result is an average of 56.1 ± 1.1 % (rms).
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REFERENCES
  1. R.P Reed and M. Golda. Cryogenic properties of unidirectional composites. Cryogenics 1994 Volume 34, Number 11