Patent Grant
9714765
This application is a national stage filing under section 371 of International Application No. PCT/EP2013/058400, filed on Apr. 23, 2013, and published in English on Oct. 31, 2013, as WO 2013/160306, and claims priority to British Application No. 1207079.3 filed on Apr. 23, 2012. The entire disclosures of each of the prior applications are hereby incorporated herein by reference.
This invention relates to a burner apparatus. More particularly, the invention relates to a burner apparatus for use in conjunction with dryers such as a rotary dryer or kiln, for example a rotary dryer of the type used for the drying of aggregates.
Asphalt is the name used in the UK and Europe to denote the material, used in road building and other civil engineering applications, which comprises aggregates (e.g. crushed rock, gravel, shingle, sand and recycled broken up asphaltic road surface material) coated in bitumen. In the USA, this material is generally known as asphalt concrete.
The aggregates used in making asphalt typically contain substantial quantities of water, either because of the wet nature of the medium from which they have been extracted, or because they have been left out in the open and have therefore been exposed to atmospheric moisture. Consequently, the aggregates need to be dried before use. Moreover, in order to ensure efficient mixing of the aggregates and bitumen and maximise the binding of the bitumen to the aggregates, it is desirable that the aggregates should be heated prior to mixing with the bitumen. For these reasons, the aggregates used in making asphalt tend to be heated to temperatures in the range from 150 to 190° C. or higher. In some asphalt mixes such as hot rolled asphalt (HRA), temperatures as high as 220° C. to 230° C. are used.
A typical asphalt plant will therefore comprise a dryer for drying and heating the aggregates. A common form of dryer used in asphalt plants is a rotating drum dryer in which the heat for the drying process is provided by one or more combustion burners at one end of the drum. Air is drawn through the combustion burners and the heated gases from the burner pass along the interior of the rotating drum and out through a gas exhaust outlet at the far end of the drum. The stream of hot gases from the burner passing through the drum serves to dry the aggregates. In order to facilitate the drying and heating process, the internal side wall of the drying zone of the drum is provided with a series of scoops or blades which scoop up the aggregates from the floor of the drum, lift them to the high point of revolution of the drum and then drop them so that they fall back as a curtain of aggregates through the stream of hot gases to the floor of the drum. In most known types of drum dryer, a contra-flow arrangement is used in which the drum is inclined so that the drying aggregates gradually migrate from an inlet at the end of the drum opposite the combustion burner towards the end at which the burner is located. Once they have reached the burner end, the dried hot aggregates are discharged into a conveyor device, such as a bucket lift, which carries them to hot aggregate storage containers where they are stored prior to be mixed with hot bitumen to form asphalt.
A problem with many known dryers is that, for a variety of reasons, it has proved difficult to achieve efficient combustion. The short combustion zones found in many dryers and the interference caused by falling aggregates and airborne dust each contribute to inefficient combustion.
If combustion of the fuel is incomplete, the exhaust emissions vented into the atmosphere will contain large concentrations of pollutants such as carbon monoxide, sulphur and nitrogen oxides. In addition to being atmospheric pollutants, unburnt fuels will condense on the bag filters used in many aggregate drying plants shortening the useful life of the filters thereby increasing costs in replacement bags.
In order to prevent incomplete combustion, it is customary to set up a burner so that an amount of air in excess of the stoichiometric amount required for combustion is mixed with the fuel prior to or during combustion. However, if too much excess air is introduced into the burner, this will lead to inefficiency and in particular inefficient transfer of heat between the air passing through the drying drum and the aggregates in the drying drum. Ideally, therefore, a burner should be set up to use the lowest possible level of excess air needed for complete combustion.
Hitherto, it has proved very difficult to control the amount of excess air used in asphalt plant dryers and, typically, asphalt plant dryers tend to be “over-aired”. Thus, whereas the gas burners used in boilers may function well using as little as 5% excess air, asphalt dryer plants typically operate with excess air levels anywhere between 100% and 1000%. As a consequence, asphalt dryer plants are typically very inefficient in terms of their energy consumption.
One object of the present invention is to provide a more energy-efficient burner-dryer arrangement which requires less excess air.
Another object of the present invention is to provide a burner in modular form in which individual modules can readily be separated or removed to give access to confined areas of the burner for maintenance purposes.
A further object of the invention is to provide a burner which is capable of burning more than one fuel efficiently.
In one aspect, the invention provides a burner for use in an aggregates dryer, the burner being provided with means for controlling the excess air.
Accordingly, in a first aspect, the invention provides a burner configured for use with a dryer for drying aggregates, the burner comprising:
Preferably, the second airflow modifier device is fixed (i.e. is immovably mounted) relative to the opening at the upstream end of the combustion chamber. For example, the second airflow modifier device can be mounted in the combustion chamber on a wall separating the combustion chamber from the burner chamber so that it surrounds the said opening.
In one embodiment, the second airflow modifier device comprises a plurality of air twist blades mounted on an inner wall of the combustion chamber in close proximity to the air escape channel around the periphery of the first airflow modifier device. The air twist blades are typically angled so as to direct the air into a vortex. An advantage of this arrangement is that the air twist blades can easily be retrofitted into an existing burner combustion chamber.
The direction of twist imparted by the second airflow modifier device may be opposite to a direction of twist imparted by the first airflow modifier device.
The second airflow modifier device is typically provided with a plurality of angled blades (“air twist blades”) which impart helical motion to the airflow.
In a preferred embodiment, both the first airflow modifier device and the second airflow modifier device are arranged to twist airstreams passing therethrough in opposite directions.
The combination of the first and second airflow modifier devices provides much more effective mixing of the atomised fuel and air thereby facilitating more complete combustion and reducing emissions of partial combustion products such as carbon monoxide.
Preferably, means are provided for varying the size of the air escape channel around the periphery of the first airflow modifier so as to vary the flow of excess air into the combustion chamber.
For example, in one embodiment, the first airflow modifier device may be mounted so as to be movable forwards or backwards along an axial path so as to vary the size of the air escape channel.
In another embodiment, a movable baffle element is provided which can be moved (for example in an axial direction) to reduce or increase the size of the air escape channel.
The first airflow modifier device is typically configured to impart twist to a stream of air passing through it. Thus, for example, it can take the form of a swirl plate comprising a plurality of radially extending vanes arranged so as to twist the flow of air into a vortex.
The burner nozzle is conveniently mounted in a central opening in the swirl plate.
The first airflow modifier device may have a peripheral surface which is shaped so as to direct excess air through the air escape channel. For example, the peripheral edge or surface may be inclined at an angle of from 20° to 70°, typically 30° to 60° (more typically 40° to 50°, for example approximately 45°) with respect to the plane of the first airflow modifier device. The angle of inclination of the surface is such that air incident on the surface is directed outwardly and around the first airflow modifier device and into the combustion chamber.
Means may be provided for varying the gap around the periphery of the first airflow modifier device so as to vary the flow of excess air into the combustion chamber. Thus, the gap may be reduced to reduce the flow of excess air around the periphery of the first airflow modifier device, or it may be widened to increase the flow of excess air into the combustion chamber.
In one embodiment of the invention, the gap around the periphery of the first airflow modifier device is defined by the distance between an outer edge of the first airflow modifier device and an inner rim of the upstream opening of the combustion chamber. In this embodiment, the size of the gap can be controlled by moving the first airflow modifier device with respect to the inner rim of the said opening.
For example, movement of the first airflow modifier device backwards or forwards in an axial direction will result in the size of the gap changing.
In an alternative embodiment, the first airflow modifier device is immovable so that the distance between the outer edge of the air director element and an inner rim of the upstream opening of the combustion chamber is fixed, and a movable baffle element is provided which can be moved into or out of the gap to vary the size of the gap. The movable baffle element can be, for example, an annular element which is movable backwards and forwards in an axial direction.
In a further embodiment, the first airflow modifier device is movable with respect to the inner rim of the said opening so as to vary the size of the gap therebetween and a movable baffle element is provided which provides further control over the size of the gap.
The first airflow modifier device, when movable, may be mounted on a support frame or support rods which are movable, for example by virtue of being mounted on or linked to an actuator such as an electrical motor or solenoid-driven actuator or a pneumatic or hydraulic ram. The first airflow modifier device may be mounted in a plurality (e.g. three or four) of support rods, each of which is mounted on an actuator. Thus, for example, there may be three or four such actuators which move the support rods.
The first airflow modifier device and the fuel-atomising burner nozzle can be mounted on a movable support frame which is connected to one or more actuators such as electrical motor or solenoid-driven actuators or pneumatic or hydraulic rams. The support frame may advantageously be movable along a track provided by one or more stationary support rails. In one embodiment, the support frame is suspended from a stationary support rail.
An ignition device such as an ignition lance is typically provided for igniting the atomised fuel when the burner is started up. The ignition device (e.g. lance) can, for example, be mounted on the movable support frame, when present.
The burner is preferably provided with diagnostic means for measuring at least one characteristic of a flame produced by the burner and/or at least one characteristic of the combustion gases produced by the burner. For example, the diagnostic means may provide information on the colour or shape of the flame and may therefore provide information about the extent of combustion of the fuel.
In one embodiment, the diagnostic means comprises a photocell.
Alternatively, or additionally, the diagnostic means may comprise one or more instruments at a location downstream of the burner for monitoring the composition of the combustion gases (e.g. carbon monoxide content) produced by the burner.
Information provided by the diagnostic means enables an operator of the burner to assess whether combustion is taking place efficiently and hence whether more or less excess air is required. The size of the air escape channel (e.g. the gap around the periphery of the first airflow modifier device) can be varied in response to information provided by the diagnostic means. This can be done manually, automatically or semi-automatically. An electronic controller (e.g. a computer) can be used to process information received from the diagnostic means and then send appropriate signals to the actuators for increasing or reducing the size of the air escape channel.
The combustion chamber can be constructed so as to be adjustable in length. For example, the combustion chamber may be formed from two or more telescopic components which can be moved together to reduce the length of the combustion chamber or moved apart to increase the length of the combustion chamber.
For example, one component of the combustion chamber may be fixed and another component may be movable with respect to the one component. The movable component of the combustion chamber may be mounted on one or more movable support rods or a movable support frame.
An advantage of having a combustion chamber of adjustable length is that when installing or commissioning the burner, the length of the combustion box can be adjusted to produce a desired shape of the flame to suit the particular dimensions and circumstances of use of the dryer in which the burner is mounted.
For example, the combustion box can be shortened to accommodate or form a shorter wider flame or can be lengthened to accommodate or form a longer narrower flame.
In a second aspect, the invention provides a burner configured for use with a dryer for drying aggregates, the burner comprising:
Unless the context requires otherwise, each of the optional features, preferences and embodiments set out above in relation to the first aspect of the invention apply also to the above second aspect of the invention.
In each of the foregoing aspects and embodiments of the invention, the burner comprises means providing a flow of air through the burner chamber and into the combustion chamber.
The means providing a flow of air through the burner chamber typically comprises an air intake, a fan and a motor for driving the fan.
The fan can be contained within a fan chamber, the fan chamber being provided with an air inlet and an air outlet.
The fan, fan chamber, air inlet and air outlet and motor for driving the fan can together constitute a blower module.
The blower module can be mounted on an underlying support structure.
The underlying support structure can have one or more air inlets communicating with the air inlet of the fan chamber. The one or more inlets of the support structure and an air inlet of the fan chamber may together constitute a main (or sole) air intake of the burner. An advantage of having the main (or only) air intake located beneath the blower module is that it reduces the overall length of the burner.
The interior of the support structure is preferably insulated with acoustic foam to reduce noise associated with the intake of air.
The blower module can be constructed so that it can be separated from the burner chamber to allow access to the burner chamber for maintenance purposes.
In one embodiment, the blower module is movably mounted on the support structure so that it can be moved away from the burner chamber to give access to the burner chamber.
The support structure and the blower module can be provide with mutually engaging wheels, rollers and a track to enable the blower module to be moved away from the burner chamber.
In a third aspect, the invention provides a burner configured for use with a dryer for drying aggregates, the burner comprising:
Unless the context requires otherwise, the burner chamber, blower module, support structure and combustion chamber may be provided with any one of more of the features set out above in relation to the first and second aspects of the invention.
For example, the burner may be provided with a first and optionally a second airflow modifier device as hereinbefore defined, and means may be provided as defined herein for varying the size of an air escape channel at the periphery of the first airflow modifier device so as to vary the flow of excess air into the combustion chamber.
Furthermore, the combustion chamber may be variable in length as hereinbefore defined.
In each of the foregoing aspects and embodiments of the invention, there is provided a means for conveying fuel to the burner nozzle.
The means for conveying fuel to the burner nozzle will typically comprise one or more pipes or tubes and a valve for controlling the supply of fuel to the burner nozzle.
In one preferred embodiment of the invention, the valve for controlling the supply of fuel to the burner is capable of controlling fuel flow from several different fuel sources.
A fuel valve capable of controlling the supply of fuel from several different fuel sources represents a further aspect of the invention.
Accordingly, in a fourth aspect, the invention provides a fuel valve for connecting a burner to two separate fuel supplies, the fuel valve comprising:
In the dual fuel valve of the invention, a rotatable valve member is mounted in a main throughbore passing through the valve body. The rotatable valve member has a pair of transverse channels passing through it. The valve member can be rotated so that the transverse channels move into or out of alignment with the passageways through the valve body, thereby to allow or prevent flow of fuel through the valve. The term “transverse” as used herein means that the channels extend in a sideways direction relative to the rotational axis of the valve member. The transverse channels may be oriented perpendicularly with the respect to the rotational axis of the valve member or they may be oriented at an angle of less than 90° with respect to the axis. Preferably the transverse channels extend in a straight line from one side of the valve member to the other.
The rotatable valve provides a means of turning the fuel flow on and off. The transverse channels may be arranged so that both flow paths are opened at the same time or they can be arranged so that only one flow path is opened at a time. One or more additional transverse channels may be present in the valve member to provide the option of opening both flow paths simultaneously or one at a time.
Each obturator element is typically provided with a window which can be moved into or out of alignment with the transverse channels of the valve member and adjacent passageways of the valve body so as to regulate flow of fuel through the valve. The valve is preferably provided with means for controlling the extent of overlap between the window in each obturator element with the transverse channels thereby controlling the size of the aperture through which the fuel can pass. Although the obturator elements could in principle be used for fine control of fuel flow when the burner is in use, in practice the size of the aperture is typically set prior to use of the burner depending on the size and rate of fuel consumption of the burner and the type of fuel being burnt. Thus, for example, a light gas oil will typically require a smaller aperture than a more viscous waste oil and the valve will be set up before use accordingly.
In a preferred embodiment, the obturator elements are cylindrical in form and have a central throughbore in which the valve member sits. The cylindrical obturator elements may be located in enlarged bore regions at either end of the main throughbore of the valve body.
The obturator elements are movable in an axial direction along the main throughbore. Preferably means are provided for being about incremental axial movement of the obturator elements. For example, the obturator elements may be provided at an outer end thereof with a thread which engages a correspondingly threaded rotatable element, rotation of which is converted into axial movement of the obturator element.
The positions of the obturator elements may be adjusted manually, or one or more actuators may be provided to bring about controlled axial movement of the obturator elements. For example, when the obturator element is provided with a thread which engages a correspondingly threaded rotatable element, the rotatable element may be connected to an actuator which imparts controlled rotation to the rotatable element.
The valve body may be formed as a solid body, e.g. a block which has a plurality of passages passing through it. The passages can be formed by machining, casting, moulding or a combination thereof. In one embodiment, the block is formed from a metal material.
The term “throughbore” as used herein is used in a general sense to refer to a passageway or channel which passes through the valve body from one side of the body to another and is not intended to imply any particular means (e.g. drilling) of forming the channel or passageway.
The transverse channels of the valve member and the plurality of passageways through the valve body together form a pair of separate flow paths, one for each fuel supply. In general, the two flow paths are isolated from one another so that different fuels passing through the valve do not mix.
Each flow path may be connected to a secondary flow path which bypasses the valve member. The secondary flow path is provided with one or more valves for controlling flow of fuel therethrough. The secondary flow path is typically of smaller bore than each main flow path.
The secondary flow path can be used to allow a limited amount of fuel to pass through the valve when the valve member is in the closed position. For example, the secondary flow path can be connected to an igniter or pilot flame nozzle so that a pilot flame can be lit before the burner is turned on fully. Once the burner has been fully turned on, the secondary flow path can be closed.
A meter for measuring fuel flow can advantageously be mounted in the secondary flow path.
Typically, an on-off valve will be provided in a fuel upstream of the inlets for each flow path. The on-off valve can be a solenoid valve, for example.
The fuel valve of the fourth aspect of the invention can be used with the burners of each of the first, second and third aspects of the invention.
The burners of the invention are intended for use as part of an apparatus for drying materials such as aggregates. The combustion chamber of the burner in use is typically mounted adjacent or at least partially within a drying chamber of a dryer.
For example, when the dryer is a rotating drum dryer of the type described in the introductory part of this application, the combustion chamber of the burner can be mounted in an end wall of the rotating drum.
In a further aspect, the invention provides a dryer apparatus (e.g. a rotating drum dryer apparatus) comprising a burner as hereinbefore defined.
The invention also provides a method of drying aggregates, which method comprises passing the aggregates through a dryer apparatus (e.g. a rotating drum dryer apparatus) comprising a burner as hereinbefore defined.
The invention will now be described in more detail, but not limited, by reference to the specific embodiments illustrated in the accompanying drawings
Referring to the drawings,
The burner apparatus comprises a support structure 1, a blower module 2, a burner chamber 3 and a combustion chamber 4.
The burner apparatus in use is mounted at one end of a rotary dryer 5 (see
The support structure 1 serves not only to take the weight of the blower module 2 but also serves as an air intake for the blower module. Typically, in use, the support structure 1 is mounted on a platform at one end of the rotary dryer. The platform may have ventilation openings so that air may pass through the platform and up through the support structure and into the fan chamber. Preferably, however, the support structure 1 is provided with feet (not shown) at each corner which elevate the support structure so that there is a gap of about 10 centimeters between the underlying surface and the support structure through which air can pass en route to the fan chamber. The support structure is configured such that at least 50% of the air required by the burner passes up through the support structure. An advantage of this arrangement is that the overall length of the burner can be reduced.
In order to reduce the noise associated with the burner, the support structure 1 contains acoustic foam to give noise reduction insulation so that the structure functions as a silencer as well as a support for the blower module.
On its upper surface, the blower module is provided with a hinged inlet 2.2 which is fitted with acoustic foam to assist noise reduction. The inlet 2.2 can be lifted up on its hinges to allow access to the interior workings of the blower section.
The blower module is provided with locating pins 2.10 which locate in the pin locators 3.14 on the combustion chamber module 3 to provide correct alignment between the blower module and the combustion chamber module.
Also mounted on the outer surface of the burner chamber is a dual fuel valve 3.2, the construction of which is illustrated in more detail in
A photocell holder 3.3 containing a photocell device for flame diagnostics purposes is also attached to the outer surface of the burner chamber.
The interior workings of the burner chamber are shown in
A swirl plate 3.11 (which constitutes a first airflow modifier device) is secured to the lance 3.16 and also to the swirl plate support rods 3.7. At the periphery of the swirl plate 3.11 is an air is an inclined surface 3.12 which is inclined at an angle of about 45° with respect to the plane of the swirl plate 3.11.
The end wall 3.19 of the burner chamber has a circular hole in which the swirl plate 3.11 sits. In the rest position, there is a relatively small annular gap 3.13 between the outer surface 3.12 and the rim of the hole in the end wall 3.19. The size of the air gap 3.13 can be increased by actuating the pneumatic rams 3.1 so that the swirl plate 3.11 is moved in a forward direction.
The configuration of the swirl plate 3.11 can be seen more clearly in
The support spider 3.8, lance 3.16, ignition lance 3.32 and swirl plate 3.11 can all be removed from the burner chamber 3 by removing the two bolts on the ram bracing bar 3.61 and the bolt on the pneumatic ram top support 3.6. As shown in
The combustion chamber 4 can be of fixed length or it can be of adjustable length as shown in
The fuel feed to the lance 3.16 is shown in more detail in
Referring to
The obturator elements 3.24 each have threaded ends 3.48. A threaded end of one obturator element is attached by means of a thread on the radially inner surface 3.50 of span adjuster 3.21 whereas the threaded end 3.48 of the other obturator element 3.24 is attached by means of a thread on the radially inner surface 3.52 to the other span adjuster 3.22. The span adjuster 3.22 is configured to fit over the end 3.23a of the fuel adjustment stem 3.23 whereas the span adjuster 3.21 has a reduced diameter opening 3.21B through which the end 3.23B of the rotatable valve member adjustment stem 3.23 can be inserted.
The span adjusters 3.21 and 3.22 are each provided with external threads 3.21C and 3.22C respectively which engage threads in the surface of the enlarged bore portions 3.40C of the main throughbore 3.40.
In order to open the valve to fuel to flow through it to the burner, the valve member 3.23 is rotated until the transverse channels 3.42 in the valve member come into alignment with the windows 3.46 in the obturator elements and the inlet 3.27 and outlet 3.28 of the fuel valve thereby creating a free flow path through the valve. In order to turn off the flow of fuel to the burner, the valve member 3.23 is rotated so that the transverse channels 3.42 are moved out of alignment with the windows 3.46 and the fuel inlet 3.27 and fuel outlet 3.28.
The rate of flow of fuel through the passages 3.42 and 3.46 can be varied by rotating the span adjuster 3.21 so that it rides along the threaded region 3.48 of the valve insert 3.24 thereby causing the obturator element 3.24 to move along the main throughbore towards the midpoint. As the valve insert 3.24 moves, the area of overlap of the channels 3.42 and windows 3.46 is progressively reduced thereby reducing the amount of fuel that can pass through the transverse channels. In general, the area of overlap of the channels 3.42 and windows 3.46, and hence the fuel flow rate through the valve, is set prior to use of the burner according to the size and nature of the burner and the type of fuel that is to be used. Thus, for example, more viscous waste oils may require a larger aperture (i.e. larger area of overlap) whereas lighter gas oils may typically require a smaller aperture. It will be appreciated also that a larger burner will require more fuel and hence the valve will be set so as to give a larger area of overlap between the channels 3.42 and windows 3.46.
The inlet 3.27 and outlet 3.28 passages are linked by a bypass passage 3.26 which forms a secondary flow path through the block. A fuel pressure gauge 3.29 is mounted in a threaded aperture in the wall of the fuel valve block so that the inner end of the fuel gauge is in fluid communication with the bypass channel 3.26. Also disposed in the bypass channel is a bypass needle valve 3.25 which has a passageway 3.25C of reduced diameter extending through part of its length.
A stop bolt 3.30 is mounted in a threaded passageway and this can be tightened to prevent rotational movement of the obturator element 3.24.
The rotatable valve member 3.23 is connected to an electronic actuator device 3.31 which can rotate the valve member to allow the passage of fuel through the valve.
When setting up the burner, the fuel to be used is selected by actuating the appropriate solenoid valve 3.30A or 3.30B with the rotatable valve member 3.23 in the closed position, i.e. wherein the transverse channel 3.42 is not aligned with the transverse channel or window 3.46 through the obturator element 3.24. The fuel is therefore diverted along the bypass channel 3.26 past the fuel pressure gauge 3.29 which senses the fuel pressure being delivered. The bypass needle valve 3.25 is set to the minimum aperture required to produce a flame and fuel passes through the valve 3.25 and on towards the lance where it is atomised and ejected into the turbulent air stream. The gas ignition lance 3.32 is used initially to initiate combustion of the atomised fuel. Once the fuel has been ignited, the rotatable valve member 3.23 can be rotated into an open position to allow fuel to pass directly from inlet 3.27 to the outlet 3.28 and on to the lance 3.16.
In use, atomised fuel ejected from the lance 3.16 is mixed with turbulent air passing through the swirl plate 3.11 and the air twist plate 4.31. Excess air is directed through the gap 3.13.
In order to increase the temperature of the burner, more fuel is delivered to the lance 3.16 through the fuel valve 3.2. At the same time, the airflow rate is increased proportionately in order to keep the fuel to air ratio at the correct level. However, increasing airflow through the combustion chamber would lead to the build-up of back pressure behind the swirl plate as only a proportion of the excess air would be able to escape through the gap 3.13. Therefore, in order to avoid the back pressure build-up, the swirl plate is moved forwardly (i.e. towards the combustion chamber 4) thereby increasing the gap 3.13 and allowing more excess air to pass through the gap. By enabling more air to be delivered to the combustion chamber, the fuel is burnt more efficiently and concentrations of carbon monoxide are substantially reduced.
The efficiency of combustion is further enhanced by the presence of the fixed air twist plate 4.3 which rotates the air in the opposite direction to the swirl plate 3.11, thereby increasing turbulence in the air and ensuring mixing of the air and atomised fuel.
In the burner apparatus of
The burners of the invention have greatly improved efficiency of combustion compared to known fuel oil burners typically used in asphalt manufacturing plants.
The improved combustion efficiency is demonstrated by the greatly reduced carbon monoxide concentrations produced by burners of the present invention compared with known commercially available fuel oil burners used in asphalt plants. For example, when burning 100% recycled fuel oil, carbon monoxide emissions were comparable to those produced by natural gas burners and were less than a third (and in three out of four cases less than a quarter) of the carbon monoxide emissions produced by commercially available fuel oil burners.
It will readily be apparent that numerous modifications and alterations may be made to the specific embodiments of the invention described above without departing from the principles underlying the invention. All such modifications and alterations are intended to be embraced by this application.
| Number | Date | Country | Kind |
|---|---|---|---|
| 1207079.3 | Apr 2012 | GB | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/EP2013/058400 | 4/23/2013 | WO | 00 |
| Publishing Document | Publishing Date | Country | Kind |
|---|---|---|---|
| WO2013/160306 | 10/31/2013 | WO | A |
| Number | Name | Date | Kind |
|---|---|---|---|
| 5573396 | Swanson | Nov 1996 | A |
| 6575734 | Brashears et al. | Jun 2003 | B1 |
| 6652268 | Irwin et al. | Nov 2003 | B1 |
| 8505302 | Uhm et al. | Aug 2013 | B2 |
| 20040219466 | Marino et al. | Nov 2004 | A1 |
| 20080280243 | Swanson et al. | Nov 2008 | A1 |
| Number | Date | Country |
|---|---|---|
| 2533352 | Jan 2003 | CN |
| 101725985 | Jun 2010 | CN |
| 2406674 | Aug 1975 | DE |
| H01203811 | Aug 1989 | JP |
| 2000193127 | Jul 2000 | JP |
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| International Search Report for PCT/EP2013/058400 dated Nov. 15, 2013. |
| English Translation of Chinese Search Report for counterpart Chinese Application No. 2013800332161 dated Feb. 2, 2016. |
| Number | Date | Country | |
|---|---|---|---|
| 20150140499 A1 | May 2015 | US |
