EP3776529B1 - Vorrichtung zur erzeugung von druckwellen hoher amplitude - Google Patents

Vorrichtung zur erzeugung von druckwellen hoher amplitude Download PDF

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Publication number
EP3776529B1
EP3776529B1 EP19712237.7A EP19712237A EP3776529B1 EP 3776529 B1 EP3776529 B1 EP 3776529B1 EP 19712237 A EP19712237 A EP 19712237A EP 3776529 B1 EP3776529 B1 EP 3776529B1
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EP
European Patent Office
Prior art keywords
piston
gas spring
pressure
gas
discharge opening
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP19712237.7A
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German (de)
English (en)
French (fr)
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EP3776529A1 (de
EP3776529C0 (de
Inventor
Paul Müller
Harald HERZ
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hitachi Zosen Innova AG
Explo Engineering AG
Martin GmbH fuer Umwelt und Energietechnik
Original Assignee
Hitachi Zosen Innova AG
Explo Engineering AG
Martin GmbH fuer Umwelt und Energietechnik
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Application filed by Hitachi Zosen Innova AG, Explo Engineering AG, Martin GmbH fuer Umwelt und Energietechnik filed Critical Hitachi Zosen Innova AG
Publication of EP3776529A1 publication Critical patent/EP3776529A1/de
Application granted granted Critical
Publication of EP3776529B1 publication Critical patent/EP3776529B1/de
Publication of EP3776529C0 publication Critical patent/EP3776529C0/de
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Classifications

    • G—PHYSICS
    • G10—MUSICAL INSTRUMENTS; ACOUSTICS
    • G10K—SOUND-PRODUCING DEVICES; METHODS OR DEVICES FOR PROTECTING AGAINST, OR FOR DAMPING, NOISE OR OTHER ACOUSTIC WAVES IN GENERAL; ACOUSTICS NOT OTHERWISE PROVIDED FOR
    • G10K15/00—Acoustics not otherwise provided for
    • G10K15/04—Sound-producing devices
    • G10K15/043—Sound-producing devices producing shock waves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23C—METHODS OR APPARATUS FOR COMBUSTION USING FLUID FUEL OR SOLID FUEL SUSPENDED IN  A CARRIER GAS OR AIR 
    • F23C15/00—Apparatus in which combustion takes place in pulses influenced by acoustic resonance in a gas mass
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23J—REMOVAL OR TREATMENT OF COMBUSTION PRODUCTS OR COMBUSTION RESIDUES; FLUES 
    • F23J3/00—Removing solid residues from passages or chambers beyond the fire, e.g. from flues by soot blowers
    • F23J3/02—Cleaning furnace tubes; Cleaning flues or chimneys
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28G—CLEANING OF INTERNAL OR EXTERNAL SURFACES OF HEAT-EXCHANGE OR HEAT-TRANSFER CONDUITS, e.g. WATER TUBES OR BOILERS
    • F28G7/00—Cleaning by vibration or pressure waves
    • F28G7/005—Cleaning by vibration or pressure waves by explosions or detonations; by pressure waves generated by combustion processes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23J—REMOVAL OR TREATMENT OF COMBUSTION PRODUCTS OR COMBUSTION RESIDUES; FLUES 
    • F23J3/00—Removing solid residues from passages or chambers beyond the fire, e.g. from flues by soot blowers
    • F23J3/02—Cleaning furnace tubes; Cleaning flues or chimneys
    • F23J3/023—Cleaning furnace tubes; Cleaning flues or chimneys cleaning the fireside of watertubes in boilers

Definitions

  • the present invention relates to a device and a method for generating high-amplitude pressure waves, in particular for cleaning boilers.
  • Such a device for generating high-amplitude pressure waves is from U.S. 5,864,517 known.
  • acoustic vibrations are generated that are significantly stronger than those that can be generated by loudspeakers. They can be used in particular for cleaning boilers, since these pressure waves cause particles to detach.
  • two different pulsed burns are discussed.
  • Detonative combustion has extremely fast flame velocities of 2,000 to 4,000 m/s, while deflagrative combustion has much slower flame velocities, such as less than 200 m/s, and the pressure waves are of significantly lower amplitude.
  • the EP 2 319 036 relates to a method and a device for generating explosions, in particular high-intensity pressure pulses.
  • a pressure-resistant container with a main explosion chamber as in the above-mentioned US patent, with an outlet opening for the pressure pulses and a piston closing the outlet opening.
  • the position of the piston is shifted by an auxiliary explosion in an auxiliary explosion chamber in such a way that it releases the outlet opening.
  • This procedure requires precise time coordination between the triggering of the main explosion and the preceding auxiliary explosion.
  • the device then also has a gas spring chamber which brakes the pushed-back piston and, after the gases have been blown out of the main explosion chamber, pushes said piston back to its original position.
  • FIG. 1 shows another method and apparatus for generating explosions in which the gas spring mechanism includes a relief mechanism disclosed as an over-centre spring mechanism.
  • the FR 2,938,623 an explosion cylinder having a piston movable between an open and a closed position for cyclically generating explosions of pressurized gas or air for cleaning purposes.
  • the invention is based on the object of specifying an improved device which can be ignited more simply and reliably.
  • an object of the invention is to provide the device with a longer maintenance interval, since the wear and tear of the moving parts in the pressure-resistant container due to the explosions is considerable and, in the prior art, only allows a limited number of repetitions of the cleaning ignitions before the plant needs maintenance. Since the processes in power plant technology, the basic industry and in technical chemistry are usually carried out in complex chemical plants, a number of such devices for generating high-amplitude pressure waves are usually provided for cleaning the various containers, which then have to be serviced accordingly.
  • the device is preferred for cleaning boilers in large technical Plants such as waste incinerators, coal-fired power plants, silos, etc. used to remove slag or deposits.
  • the main advantage there is that the individual cleaning cycles can be repeated very quickly and several times.
  • the use of gases as cleaning material for generating the sequence of pressure waves and associated pressure pulses is relatively cheap and high pressures can be generated.
  • the delivery of two chemical fluids, which do not inherently burn up or explode, at a time just before the blast is triggered increases safety. It also enables cleaning of systems that are still warm and possibly in operation, since the reacting substances are exposed to the hot environment for a long time.
  • the pressure wave generated can be conducted via a pipe over long distances into a boiler at the point to be cleaned.
  • the tube can be permanently installed on the system to be cleaned, but can also be inserted from the outside, for example pushed telescopically into a system or a boiler. Due to the pressure pulse generated during the burn-up, deposits and dirt are blown away from the inner pipes in the boiler and its walls and at the same time the pipes and walls vibrate. Both actions result in efficient cleaning of the systems to be cleaned.
  • a device for generating high-amplitude pressure waves has a pressure-resistant container.
  • This can be in several parts. It has at least one combustion chamber incorporated therein. Several combustion chambers can be connected to each other. At least one ignition device reaching into the combustion chamber(s) is provided. There is at least one feed line for feeding a flowable combustible material into the combustion chamber, preferably separately a fuel and an oxidant, such as natural gas and air or methane and oxygen. Various other liquid or gaseous fuels can also be used.
  • the pressure-resistant container has a discharge opening for the directed release of gas pressure generated by the ignition of the combustible material in the combustion chamber.
  • closure means that closes the discharge opening, which is designed to release the discharge opening for the directed discharge, and which can then be pushed into the starting position by a spring device after the burnout.
  • the closure means is a piston that can be displaced in its longitudinal direction and has a rear section that is oriented in the direction of the spring device and a front section that is oriented in the direction of the discharge opening.
  • the seat of the piston has a piston surface that is inclined obliquely to the discharge opening, which is arranged opposite a housing surface that is also inclined obliquely to the discharge opening, with the housing surface being oriented relative to the piston surface at an angle towards the discharge opening from one perpendicular to the piston direction Closing line opens starting.
  • the angle can be between 0.5 and 5 degrees, preferably between 1 and 3 degrees, in particular 2 degrees.
  • the seal line perpendicular to the direction of the piston may be located within the piston wall of the lower portion such that there is a rounded static pressure opening area between the seal line and the piston wall.
  • a flange surface perpendicular to the piston axis, which is connected to the combustion chamber or belongs to it, can have a surface area that is between 50 and 200 percent of a surface area that is given by the surface area of the piston surface.
  • a transition area can be provided between these two sections.
  • the front section is arranged in the area of the combustion chamber when the piston is in a position that closes the discharge opening.
  • the front section In relation to the longitudinal direction of the piston the front section is tapered compared to the rear section, so that the transition region forms an effective surface aligned transversely to the longitudinal direction of the piston, on which a pressure driving the piston back is exerted when the combustible material is ignited, so that the front section of the piston uncovers the discharge opening . This makes cleaning easier, since the pressure build-up can also be achieved by burning off and is then itself responsible for opening the path to the discharge funnel.
  • the transition area can be an area that tapers continuously in the longitudinal direction of the piston of the gas spring from a larger piston diameter to a smaller piston diameter, which is arranged in the area of the combustion chambers.
  • the transition area can also be formed by a flange-like tapering of the piston.
  • a hollow central guide line can be provided in the pressure-tight container, which guides the piston in the front area in its interior. This has advantages when the piston guide wears out, since it allows for guidance over sections of the piston that are further apart. At least one connecting gap is then provided between the combustion chambers and an auxiliary pressure chamber in the area of the flange-like taper of the piston.
  • the combustion chamber can be arranged in a ring around the piston around its longitudinal axis.
  • the ring-shaped walls of the combustion chamber can then be stacked and sealed ring segments which are advantageously closed off at the top and bottom by a cover plate and a base plate.
  • the height and the volume of the cylindrical combustion chamber can thus be scaled in a simple manner, since no special chambers of different sizes have to be provided.
  • the only thing that belongs to such a scaled combustion chamber is the piston, which is adjusted accordingly in terms of length, as the closure unit.
  • At least two combustion chambers can be arranged in one plane at an angular distance from one another radially to a central axis.
  • two combustion chambers can be diametrically opposed. Then either the longitudinal axis of the gas spring together with the central axis; three combustion chambers could then be 120 degrees apart in the common plane. Or the longitudinal axis of the gas spring also lies in the said plane of the at least two combustion chambers, so that with three combustion chambers an angular distance of 90 degrees between the individual elements is possible.
  • the discharge opening has a tube with a tube longitudinal direction.
  • the longitudinal direction of the discharge opening can then either coincide with the central axis, i.e. the discharge opening can lie in the extension of the piston, or the longitudinal axis of the gas spring can lie in said plane of the at least two combustion chambers. Then, for example with two combustion chambers, an angular distance of less than 120 degrees can be provided between the two combustion chambers, so that they are more aligned with the discharge opening.
  • the gas spring can have a front gas spring chamber space opposite the piston and a rear gas spring chamber space separated from this by a partition wall, with a first connection as a return flow connection and a second connection with a check valve being provided between the front gas spring chamber space and the rear gas spring chamber space, the check valve being so is arranged to permit unrestricted flow of media from the front to the rear gas spring chamber but substantially block the reverse flow out of the rear gas spring chamber.
  • the first and the second connection can be provided in the partition wall.
  • the second connection can have at least two partial connections which, on the one hand, open out laterally one above the other in the longitudinal direction of the piston movement in the wall of the gas spring in the front gas spring chamber space and, on the other hand, end in the rear gas spring chamber space, so that the openings occur one after the other when the piston penetrates into the front gas spring chamber space are covered, said sub-connections each having their own check valve.
  • the individual non-return valves are switched off successively, so that the media flow from the front to the rear gas spring chamber slows down, i.e. the braking effect due to the gas pressure build-up in the front gas spring chamber decreases.
  • the second connection can have a controllable check valve, which can optionally have a control valve connected in series and a check valve, which controllable check valve is connected to a control unit, with which the ignition can be triggered, the control unit being designed to switch the controllable check valve in a first predetermined time interval after ignition of the flowable combustible material. This can ensure that the burnup in the burnup chamber is complete before the piston is allowed to retreat any further.
  • the first connection can have a controllable backflow valve, which can optionally have a control valve connected in series and a backflow guide, which controllable backflow valve is connected to the control unit, with which the ignition can be triggered, the control unit being designed to combine the controllable backflow valve in one to open second predetermined time interval after the opening of the controllable check valve.
  • Two separate gas spring gas connections can also be provided for the front and rear gas spring chambers, with the control unit having a gas filling control unit with which the gas filling pressure in the front and rear gas spring chambers can be set to a predetermined value before ignition, the Gas filling pressure in the front gas spring chamber can be set higher than in the rear gas spring chamber.
  • the gas filling pressure in the front gas spring chamber can be set at least 2 times, preferably at least 3 times or 5 times higher than in the rear gas spring chamber, so that on the one hand the front gas spring pressure chamber does not recede or only recedes insignificantly during ignition , since the pressure prevailing in it upon ignition opposes the pressure building up in the combustion chamber, and the retreat only occurs completely and quickly when the check valve is opened, since a gas pressure difference was set.
  • the rear chamber can be at atmospheric pressure while only the front gas spring pressure chamber has been pressurized with the inert gas.
  • a device for generating pressure waves of high amplitude, in particular for cleaning boilers, with a pressure-resistant container with a combustion chamber installed therein and at least an ignition device reaching into the combustion chamber, with at least one supply line for supplying a free-flowing combustible material into the combustion chamber, the pressure-resistant container having a discharge opening for the directed release of gas pressure generated in the combustion chamber by the ignition of the combustible material and a closure means closing the discharge opening, which is designed to release the discharge opening for directed discharge, and which can be displaced into the starting position by a spring device, the closure means being a piston which can be displaced in its longitudinal direction and which has a rear section oriented in the direction of the spring device and a front section in the direction of the The front section is arranged in the region of the combustion chamber when the piston is in a position that closes the discharge opening, the seat of the piston
  • this angle is advantageously between 0.5 and 3, in particular 1 degree.
  • the closure line oriented perpendicular to the direction of the piston is advantageously arranged within the piston wall of the lower section, so that there is a rounded static pressure opening area between the closure line and the piston wall.
  • the front section is tapered in relation to the rear section.
  • the taper relates to the inner piston seat wall and then preferably has an opposite outer housing valve seat wall which opens inwards towards the outlet at a small angle.
  • the figure 1 shows a perspective view of a device for generating high-amplitude pressure waves according to an embodiment of the invention.
  • a first pressure-resistant container 21 and a second pressure-resistant container 22 are arranged to the left and right of a central body 30 .
  • these containers 21 and 22 run essentially parallel to the boiler wall 5, a detail of which is shown.
  • a drain funnel 61 with a downstream drain pipe 62 is also flanged to the central body 30 , which protrudes through the boiler wall 5 and ends in a drain opening 63 in the boiler interior 15 .
  • the discharge opening 63 can also be arranged directly on the boiler wall and the discharge pipe 62 can be made shorter than the discharge funnel 61 or can be omitted entirely.
  • the gas spring pressure body 40 is flanged to the central body 30 opposite the discharge funnel 61 .
  • a first gas reservoir 51 and opposite a second gas reservoir 52 are provided on the left and right.
  • the construction of the containers 21 and 22 may be longer, i.e. an aspect ratio for the internal volume 121 and 122 of between 5:1 and 20:1.
  • the functioning of the device for generating pressure waves will now be explained in conjunction with the schematic representation of the device 1 with the 2 described.
  • the two left and right pressure-resistant containers 21 and 22 are arranged on the central body 30 and have a first combustion chamber 121 and a second combustion chamber 122, respectively.
  • the pressure-resistant containers 21 and 22 are cylindrical with an interior space that is larger in diameter in the rear area, ie the passage tapers towards the central body 30 .
  • a piston 70 is arranged in the central body 30, which will be shown in more detail in the further drawings, which in the closed state shown separates the chambers 121 and 122 from one another and closes the outlet in the direction of the discharge funnel 61 with its front end 72 of the piston 70.
  • the piston 70 protrudes with its upper part 71 in the gas spring pressure body 40 as shown in FIG 3 is shown in more detail.
  • the valve seat itself is identified by reference number 300 . This can in particular after the 14 and the detailed views of the Figures 15A, 15B, 15C be designed in order to then unfold the effect as shown in 16 is shown.
  • the object of the high-amplitude pressure wave generating device is to generate the same in the first and second pressure chambers 121 and 122 by burning a fluid fuel or explosive.
  • This fuel is preferably formed by the mixing of components that are not combustible or explosive per se and that are stored in the first and second gas storage tanks 51 and 52 .
  • These gas reservoirs 51 and 52 are fed via external gas supply lines 53 and 54 from corresponding gas connections 57 and 58 which are regulated via external gas supply line valves 55 and 56 .
  • the first gas reservoir 51 is connected to the combustion chambers 121 and 122 via a first gas filling line 151 and an interposed first gas filling valve 153 .
  • the representation of 2 with the connection to only one combustion chamber 121 is also possible if corresponding compensating lines are provided between the first and second combustion chambers 121 and 122.
  • the second gas connection 58 that the second Gas reservoir 52 is directly or indirectly connected to the combustion chambers 121 and 122 via the second gas filling line 152 and the second gas filling valve 154 .
  • the embodiment shown corresponds to filling of the combustion chambers 121 and 122 via two dosing tanks with subsequent inflow into the device. Otherwise it is also possible to fill the device directly via panels.
  • a gas spring gas connection 47 is provided, with a gas spring supply valve 48 and a gas spring supply line 49, the gas for the gas spring 40 in the gas spring interior 41 and 42, as in FIG 3 to see is initiated.
  • first and a second gas in the present exemplary embodiment, reference is made to a first and a second gas.
  • the first gas can be methane or natural gas, for example, while the second gas can be oxygen or air or an oxygen-containing air mixture.
  • the flowable combustible material may be an explosive mixture; in addition to gaseous material, it may also be liquid, powdery material or a mixture of such materials.
  • the combustion chambers 121 and 122 are additionally connected to an ignition device which triggers an ignition of the combustible material in the combustion chambers 121 and 122 at the same time. If, as in the embodiment of 6 an annular gap is provided, in short a volumetric connection of the two combustion chambers 121 and 122, then only one ignition device is necessary. Glow plugs or spark plugs, among others, can be used as the ignition device. An intensified ignition by means of a spark plug, which has a higher ignition energy than a glow plug, the speed of the reaction can be increased. A more rapid pressure build-up in the combustion chambers 121 and 122 thus takes place.
  • the outlet opening of the pressure-tight container is kept closed beforehand by the piston 70 as the closing means.
  • the gas spring allows the closure to be kept closed even against the filling pressure of the combustible elements in the combustion chambers 121 and 122. Only through the pressure increase when the flowable mixture is ignited is the pressure on the intermediate area 75 increased so that the piston 70 is pushed back accordingly. Then, as in connection with the 3 will be described, the gas spring element then also brings about a return of the piston 70 as a closing means after burning off and allows the process to be directly repeated by refilling the chambers 121 and 122. At the same time, substances in the boiler are reliably prevented from flowing back into the device.
  • the piston 70 is opened so quickly that the pressurized mixture in the combustion chambers 121 and 122 is still not completely burned when escaping, so that the gas mixture in the discharge funnel continues to burn, so that a pressure pulse with a high pressure peak is generated. If air is used as one of the two media in addition to CH 4 or natural gas, the chemical reaction will take place within the combustion chambers 121 and 122 and all of the energy will be converted in the device. The gas is then released to the outside by a subsequent, ie time-delayed, rapid opening of the piston 70 after the initial pressure build-up.
  • the 3 shows a lateral sectional view in a schematic representation of a device for generating pressure waves with its components essential to the invention.
  • the first and second pressure-resistant containers 21 and 22 border on the discharge funnel 61 inserted in them, which has a rounded valve seat contact 65 at its inner end.
  • the front end 72 of the piston 70 adjoins this valve seat contact 65, which is designed as a horizontal, essentially circular contact line running perpendicularly and concentrically to the longitudinal axis 90 of the piston, to which the tapered piston region 73 is connected.
  • a piston transition area 75 follows, in which the diameter of the piston is increased in order to have a larger diameter at the rear end of the piston 71 .
  • the rear piston diameter 171 is thus designed to be larger than the front piston diameter 172; in particular, the piston 70 has a surface 91 as seen in its longitudinal direction (as in 4 designated) with a size that is sufficient to move the piston in the direction of the gas spring 40 upon ignition.
  • the diameter and height of the cavities of the gas spring 40 can be selected to be larger in relation to the combustion chambers 121 and 122.
  • the piston 70 is sealed between the walls of the left and right pressure-resistant vessels 21 and 22 by a series of seals 81 and 82 in its longitudinal direction, the three seals 81 being bronze seals, while the seal 82 sandwiched between them is an O ring is. These seals 81 and 82 are embedded in grooves in the piston 70; they could also be provided in the opposite walls.
  • the piston 70 which is thus passed through the central body 30 with the pressure-tight containers 21 and 22 in a sealing manner, then protrudes in a sealing manner against the front gas spring chamber space 41 in the gas spring pressure body 40, which is separated from the rear gas spring chamber space 42 by a gas spring partition 43.
  • a check valve 44 and a gas return flow opening 45 are provided in the gas spring partition.
  • the function of the gas spring is as follows.
  • the two components of the combustible gas mixtures are fed into the chambers 121 and 122 through the gas filling lines 151 and 152 .
  • these gases are ignited.
  • pressure is exerted on the transition area 75 , which overcomes the gas spring pressure holding against it and moves the piston 70 into the area of the front gas spring chamber space 41 .
  • the non-return valve 44 is provided in the intermediate wall 43, which opens immediately and quickly equalizes the gas pressure between the front gas spring chamber space 41 and the rear gas spring space 42, so that after an initially strong movement of the piston 70, this then increased resistance from the combined gas spring chamber 41 and 42 is braked.
  • the combustible gases escape from the discharge funnel 61 in burnt or still burning form and reduce the pressure in the combustion chambers 121 and 122. Since the valve in the gas spring partition 43 is a non-return valve 44, the combination of the gas spring chambers 41, 42 is then only connected through the gas return flow opening 45, which is much smaller in diameter, with the then pushes back the gas of the gas spring from the rear gas spring chamber 42 into the front gas spring chamber 41 and pushes the piston 70 into its initial position, as shown in FIG figure 3 is shown pushes. Any gas losses are compensated for by the gas spring feed line 49 .
  • the gas of the gas spring 40 can be air or an inert gas such as N 2 .
  • the 4 shows in three superimposed cross sections Figures 4a, 4b and 4c three cross sections through the device 3 along the intersection lines IVa, IVb and IVc.
  • the piston 70 advantageously has a round cross-section.
  • FIG. 8 shows a cross-section along the line IVa through the top wall 21, 22 of the pressure-tight containers, showing a bronze seal 81 surrounding the rear portion 71 of the piston 70.
  • FIG. 4b a parallel sectional plane in the combustion chamber 121, 122 and through the combustion chamber 121, 122 is shown, which is a section along the line IVb in the upper area of the space of the combustion chambers 121 and 122, in which the piston 70 has the diameter of the rear area 71 has.
  • the Figure 4c shows another section along the line IVc, parallel to the section of the Figure 4b in the lower area of the cavity, where it can be seen directly that the width of the piston 70 in the central chamber area 30 butts against the walls of the pressure-resistant container 21, 22 and thus has a width that remains constant over the length of the piston; on the other hand, the depth in the direction of longitudinal alignment of the inner spaces 121, 122 is made smaller. It can thus be seen directly here that there is a difference between the front piston diameter 172 and the rear piston diameter 171, the term piston diameter here corresponding to the width in the longitudinal direction of the combustion chambers 121, 122 lying opposite one another.
  • the vent opening 61 is here in all three drawings Figures 4a, 4b and 4c below the Character level shown. It is just as possible as it is in the 3 of the state of the art WO 2010/025574 It is shown that the discharge funnel 61 is connected to a combustion chamber 121 in the longitudinal direction of the extension on the other side of the central body 30 and the closure element as a piston 70 is perpendicular to it, so that the gas mixture escapes straight ahead in the longitudinal direction of the entire device when the piston 70 is pushed back can.
  • combustion chambers which are in the plane of the combustion chambers 121 and 122 of FIG 1 , 2 or 6 are arranged corresponding to the cutting plane 92 in 7 , since in all cases here the piston 70 is perpendicular to said plane of arrangement of the combustion chambers and the discharge funnel 61.
  • the discharge funnel 61 would be in the same plane as all the combustion chambers and could then, for example, be equiangularly spaced from all of them. With three combustion chambers then 90 degrees to each other.
  • the combustion chambers opposite the discharge funnel 61 can also be arranged closer together, so that the outflow direction does not have to be changed as much.
  • the figure 5 shows an enlarged section of the transition area 75 of the piston 70.
  • first diameter 121 from the longitudinal axis 90 of the piston which is designed to be smaller than the rear piston diameter 171 .
  • the transition region 75 thus forms two rectangular strips 91 in a section in the projection of the longitudinal axis 90, which serve as pressure transmission strips.
  • the combustible chambers have a volume of between one and two liters, with the gas filling pressure being between 10 and 30, for example between 15 and 25 bar.
  • the diameter of the annular opening closed by the piston is between 40 and 15 mm, in particular between 60 and 100 mm, in particular 80 mm.
  • Ignition can be performed in a manner similar to the prior art WO 2010/025574 be configured and thus happen, for example, electrically or by light ignition.
  • the 6 12 shows a schematic perspective view of another device for generating high-amplitude pressure waves according to an embodiment of the invention.
  • Two pressure-resistant containers 21 and 22 are also arranged here on the central body 30 and the gas spring pressure body 40 is provided perpendicular to these.
  • the gas filling lines 151 and 152 lead into the central body 30 and the supply line of the ignition device 50 is shown in the middle of the central body 30 .
  • FIG. 12 now shows a schematic cross-sectional view of the device 6 with a vertical cutting axis.
  • the longitudinal axis 90 of the piston which corresponds to the longitudinal axis of the gas spring pressure body 40, crosses the horizontal central section plane 92 of the pressure bodies 21 and 22. Elements of the central body 30 are shown in FIG 7 been omitted from the drawing for the sake of simplicity.
  • the pressure-resistant containers 21 and 22 reach the discharge funnel 61 , the inner end of which forms the valve seat contact 65 for the piston 70 .
  • the sealing line is a circular ring on the valve seat 300.
  • the piston 70 has a tapered lower area 73, which is adjoined by the transition area 75, which increases in diameter and leads into the rear piston area 71.
  • the piston 70 is hollow here. It may be in two parts, the lower end being insertable into the hollow piston 70 for contact with the valve seat 65 .
  • the valve seat 300 can again as in FIG 14 shown, be executed.
  • the rear area of the piston 70 has a sufficient height from the transition area 75 to its upper flat end surface, which delimits the lower gas spring chamber space 41, so that even if the piston is pushed back into this front gas spring chamber space 41, the piston 70 still rests against the inner walls of the Gas spring 40 rests essentially sealingly through the following sealing elements.
  • the bronze guides 81 which are arranged with a greater distance from one another, also have a sealing function and they, like the O-ring 82, are in corresponding circumferential grooves stored in the piston 70.
  • the check valve 44 and the gas return flow opening 45 are provided in the gas spring partition 43, which runs essentially perpendicular to the longitudinal axis 90 of the piston.
  • the gas return flow opening 45 can also be referred to as an orifice.
  • the gas spring supply line 47 is led to the rear end of the gas spring chamber space 42 , with which an inert gas such as nitrogen, CO2 or argon can be refilled externally via the gas spring gas connection 49 . If the spring chamber spaces 41 and 42 are sufficiently sealed, the gas can also be air.
  • the 8 shows the embodiment of 6 in section plane 92. It can be seen that the piston 70 is arranged at a constant distance in this central area from the inner wall of the central body 30 and that there is an annular gap 123 that extends in the piston longitudinal axis direction 90, which is used to equalize the pressure between the two combustion chambers 121 and 122 are designed. Thus, in the present exemplary embodiment, a gas supply line 151 and 152 arranged next to one another is sufficient for the two gases or fluids to be mixed for combustion. Centrally in the annular gap 123 between the combustion chambers 121 and 122, preferably also in the middle of the central body, the glow plug or spark plug 59 is arranged reaching into the annular gap 123, which is connected to the line 50 of the ignition device. Screens or metering valves 153 and 154 are provided here, so that the combustion chambers 121 and 122 are filled directly.
  • Such an annular gap 123 can also be guided on one side, ie only on the side of the spark plug 59, and it can also be used in other exemplary embodiments with two or more other combustion chambers.
  • the 9 shows a schematic perspective view of a further device for generating pressure waves of high amplitude according to an embodiment of the invention.
  • An arrangement that is symmetrical about the longitudinal axis 90 of the piston has been provided here.
  • an annular pressure-resistant container 25 is provided in which the gas supply lines 151 and 152 lead.
  • This pressure-resistant container 25 is arranged below the gas spring pressure body 40 in its extension, and the ignition device supply line 50 is guided into the interior of the device through the section of the pressure-resistant container 25 that protrudes beyond the gas spring body.
  • the pressure-resistant container 25 is made up of a cover plate, a base plate and here a ring, which are placed against one another in a sealing manner. Several rings can also be arranged one above the other.
  • FIG. 12 shows a schematic cross-sectional view with a vertical section axis of the device 9 .
  • the gas spring 40 is formed analogously to the other exemplary embodiments. There are two significant structural differences from these other embodiments which have been used together here. In other exemplary embodiments not shown in the figures, however, it is also possible to combine only one of the two differences described below with the other exemplary embodiments.
  • the first difference from the other embodiments is that there is an annular combustion chamber 125 that completely surrounds the piston 70 .
  • annular combustion chamber 125 that completely surrounds the piston 70 .
  • the spark plug 59 of the igniter 50 is sealed into the annular combustion chamber 125 through the top wall plate.
  • the two gas supply lines 151 and 152 are introduced directly. In other words, there are no gas reservoirs 51 and 52 as dosing elements. This is controlled by the orifices 153 and 154 during filling.
  • the second difference between the other embodiments and the embodiment of figs 9 and 10 lies in the design of the piston 70.
  • the projection of the pressure surface 91 of the other exemplary embodiments is formed here by an underside 191 of the piston 70, which underside and inside of the piston delimit an auxiliary pressure chamber 95. On its underside, this borders on a down tapering deflection profile strand 96.
  • the strand 96 which is hollow here, has a uniform inner diameter, into which the lower section with the tapered piston region 173 runs, which is guided opposite the strand 96 via two bronze seals 81 here.
  • the pressure in the annular combustion chamber 125 increases as in the previous examples, with the pressure having the opportunity here to expand via a connecting gap 126 into the auxiliary pressure chamber 95 .
  • gaps 126 can also be provided, preferably at regular angular distances from one another, so that the deflection profile strand 96 is fastened to the plate or the gas spring pressure body through the connecting gaps 126, except for these interruptions.
  • the internal pressure of the annular combustion chamber 125 acts on the underside of the rear end 71 of the piston 70 with its surface 191 projecting beyond the core in the auxiliary pressure chamber 95.
  • the pressure exerted on this surface 191 which corresponds to the pressure on the projection corresponds to the pressure surface 91 from the other exemplary embodiment
  • the piston 70 in its line 96 is pushed backwards into the front gas spring chamber space 41 by the enlarging auxiliary pressure space 95, with a bronze seal 81 and an O-ring 82 are provided.
  • FIG. 9 shows a schematic cross-sectional view with vertical section axis 90 of a device with features which partially correspond to the device 6 correspond and in part to those of 9 or 10.
  • the walls surrounding the rear section of the piston 70 have extensions 196 which protrude into the interior of the combustion chamber 125 .
  • These extensions 196 which are ring-shaped here, correspond to the strand 96 from the 10 and are used for further guidance of the piston 70. They can also correspond to bronze rings 81 opposite, which are embedded in the piston 70. In other words, it is advantageous to guide the piston 70 over a greater length, and this can be realized by a line guided in the middle or by extensions 96 in the form of rings or ring segments.
  • the piston 70 itself can be designed hollow to save weight, whereby it can be open to the front in the longitudinal direction 90 on the inside, or it can also be made of a solid material, in particular steel, or it can be hollow and have a front-inserted, in particular have screwed-in plugs. This can also form the sealing surface for the valve seat 65 .
  • the 12 shows a schematic cross-sectional view with vertical section axis 90 of another embodiment of a gas spring 140, wherein the further area of the device with the piston 70 and the spark plug 59 and the combustion chambers and discharge funnels, not shown here, can be configured similarly or identically.
  • the essential difference to the gas spring 40 consists in an external bypass of the check valve 44 outside the pressure body as well as the external bypass of the gas return flow opening 45 outside of the pressure body. So both will not be inside of the gas spring partition 43 between the two spaces 41 and 42 but have external valves 144 and 145. These diaphragms or control valves 144 and 145 are connected to the control line labeled 150, which is also connected to the ignition device.
  • the line 150 does not indicate a direct electrical or otherwise directly electrically activating line, but symbolizes that a control unit, not shown in the drawings, transmits control signals to the spark plug 59 and to the valves 144 and 145, so that they switch with a corresponding time delay .
  • the non-return valve 44 is first switched continuously by the valve 144, optionally with a slight delay, in order to initially brake the movement of the piston by means of a rapid pressure build-up in the front gas spring chamber 41 and, after opening, to quickly equalize the pressure with the rear gas spring chamber 42 to reach.
  • the valve 145 for the return flow opening 45 is closed. It can also open in advance, as it only lets a small amount of gas through in the opposite direction.
  • FIG. 13 a further schematic cross-sectional view with a vertical section axis 90 shows another exemplary embodiment of a gas spring 240, which can also be used in a device, for example according to FIG 1 , 6 , 10 or 11 can be used.
  • the non-return valve 244 is fourfold, while the gas return flow opening 45 is arranged in the gas spring intermediate wall 43 as in the other exemplary embodiments.
  • the individual openings 246 of the four check valves 244 are arranged one above the other at intervals along the Piston longitudinal axis 90 is provided (not necessarily directly above one another, but also possible laterally offset at an angular distance from one another), so that the receding piston 70, gradually moving from below, breaks the orifices 246 one after the other and thus the connection to the check valves 244 from the connection between the front gas spring chamber 41 and the rear gas spring space 42 interrupts.
  • the gas pressure equalization between the front and rear spring chambers 41 and 42 via the check valves 244 is gradually reduced, which leads to a softer braking of the piston 70 in the front gas spring chamber 41. without the need for more complicated controls of valves.
  • the check valves 244 are closed purely mechanically.
  • the 14 shows a sectional view of an outer wall 172 of a piston 70 of an exemplary embodiment of a valve seat 300 with further features.
  • the outer wall is in the 14 on the opposite wall of the gas spring pressure body 40; however, it can also be in contact with the guide strand 96 .
  • the valve seat 300 is supported downward by mating surfaces of the exhaust gas funnel 61 . Between the exhaust gas funnel 61 and the gas spring pressure body 40 there is an opening which leads into the first combustion chamber 121 . Instead of the upper section of the exhaust gas funnel 61, a defined opposing surface can also be present, which is assigned to the pressure-resistant containers 21, 22, for example.
  • the view of 14 is closed off at the upper piston end by the piston surface 170, which is perpendicular to the side wall of the front piston diameter 172 and above which the (front) gas spring chamber space 41 is provided.
  • This configuration is in the embodiments of 2 , 3 , 7 , 10 , 11 usable.
  • an auxiliary pressure chamber 95 is provided, in which a flange surface 191 is a pressure surface for moving the piston 70.
  • a line 301 is drawn on the valve seat 300 which indicates a distance from the side wall of the piston diameter 172 .
  • This is a distance from a bend R2 belongs, which belongs to the inner piston seat wall 302 from the side wall 172, which is better seen in the detailed views of FIGS Figures 15A to 15C can be seen.
  • This inner piston seat wall 302 is opposite the outer or housing-side valve seat wall 303.
  • the two walls 203 and 303 which essentially form an angle of about 45 degrees, in other exemplary embodiments that are not shown, between 30 and 60 degrees, relative to the axis of piston movement 305 have, are not parallel to each other, but have an angle 304, which in the embodiment of FIG 14 is specified as 1 degree, but can also be formed between 0.5 and 5 degrees, in particular between 1 and 3 degrees.
  • the peak of the opening angle 304 is located at the intersection of the line 301, which indicates the end of the curvature of the piston 70, with the opposite outer housing-side wall 303 and closes there in a circular ring the outer discharge funnel space 306 of the (here shown) first combustion chamber 121, but naturally also in relation to the second combustion chamber 122 .
  • valve seat 300 is in the course of time in the explosive opening of the piston path in the Figure 15A (beginning 0.5 mm), Figure 15B (opening 1mm), Figure 15C (Clear passage 2mm) shown, with reference to the power relationships will be pointed out in the 16 are shown.
  • arrows 311, 312, 313, 314 and 315 are drawn. These stand for the entire surfaces on which they stand. If present, these are the optional antechamber surface 311, the static auxiliary surface 312, the dynamic auxiliary surface 313, the piston inner surface 314 and the gas spring surface 315 diametrically opposed to all of these.
  • the optional antechamber surface 311 is the flange widening in the auxiliary chamber pressure space 95.
  • the static auxiliary surface 312 is the curved surface that is defined by the distance 301 and the radius R2 corresponding to it at the front end of the piston in 14 results, which then, in the mathematical sense, continuously merges into the inner piston seat wall 302.
  • the dynamic auxiliary surface 313 is so called because the angle 304 causes the two walls 302 and 303 to diverge in the direction of the discharge funnel space 306 and the surface thus develops dynamically.
  • the arrows would be 313 in a sequence from the inside edge to near the arrow 312.
  • the piston inner surface 314 is shown here in the depression of the hollow piston, but it could also exist at the lower end of the piston.
  • the gas spring surface 315 is provided diametrically opposite.
  • the 16 shows the force on the piston 70 on the Y-axis versus time on the X-axis.
  • the basic effect of the auxiliary pressure chamber 95 and its area 311 is characterized by the line 411.
  • the area 511 between the 0 line and the line 411 is therefore a key figure for the antechamber effective area.
  • Line 412 shows the additional force resulting from the rounded area at arrow 312 and identified by area 512 between line 411 and line 412 .
  • boost ends at a point in time with a reversal of the boost curve 413 at a somewhat later point in time 521, at which the diverging gap after Figures 15A to 15C to a culvert as in Figure 15C has widened.
  • This does not mean that there is a slot with a width of 2 millimeters, it depends on the depth of the valve seat, i.e. the distance from the curve R2 (described by the line / arrow 301) to the start of the discharge funnel space 306
  • line 414 separates from line 413 in the downswing area.
  • the geometry of the valve seat has a positive effect on the opening behavior of the piston.
  • the narrowest shifts Cross-section radially from the outside to the inside, resulting in the advantages of small projected areas when closed, which prevents unwanted opening.
  • the antechamber 95 ensures the initial opening at the desired time.
  • it is possible to use this auxiliary chamber by arranging the surfaces 191 in the main chamber space 121 (i.e. without separate ignition, similar to the exemplary embodiment in figure 10 ) so that area 511 corresponds to incipient ignition of the main chamber.

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  • Engineering & Computer Science (AREA)
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EP19712237.7A 2018-03-29 2019-03-27 Vorrichtung zur erzeugung von druckwellen hoher amplitude Active EP3776529B1 (de)

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EP18165013 2018-03-29
PCT/EP2019/057752 WO2019185736A1 (de) 2018-03-29 2019-03-27 Vorrichtung und verfahren zur erzeugung von druckwellen hoher amplitude

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JP7432359B2 (ja) * 2019-12-26 2024-02-16 川崎重工業株式会社 衝撃波式スートブロワおよびその運転方法
CA3236318A1 (en) * 2021-11-02 2023-05-11 Explo Engineering Ag Protection device for a boiler access point
WO2023111195A1 (de) 2021-12-17 2023-06-22 Explo Engineering Ag Befestigungsvorrichtung für eine reinigungseinrichtung basierend auf der einleitung von druckwellen hoher amplitude
JP7153824B1 (ja) 2022-07-22 2022-10-14 三菱重工パワーインダストリー株式会社 圧力波発生装置

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KR20210020870A (ko) 2021-02-24
CN112074897A (zh) 2020-12-11
JP7401516B2 (ja) 2023-12-19
AU2019241452B2 (en) 2024-05-30
AU2019241452A1 (en) 2020-10-15
RU2020131058A (ru) 2022-04-29
BR112020019905A2 (pt) 2021-01-05
US20210199284A1 (en) 2021-07-01
TW201941839A (zh) 2019-11-01
CA3094256A1 (en) 2019-10-03
EP3776529A1 (de) 2021-02-17
RU2020131058A3 (zh) 2022-04-29
TWI803607B (zh) 2023-06-01
EP3776529C0 (de) 2023-06-07
JP2021519409A (ja) 2021-08-10
WO2019185736A1 (de) 2019-10-03

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