EP3776529A1 - Device and method for producing pressure waves of high amplitude - Google Patents
Device and method for producing pressure waves of high amplitudeInfo
- Publication number
- EP3776529A1 EP3776529A1 EP19712237.7A EP19712237A EP3776529A1 EP 3776529 A1 EP3776529 A1 EP 3776529A1 EP 19712237 A EP19712237 A EP 19712237A EP 3776529 A1 EP3776529 A1 EP 3776529A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- piston
- gas spring
- pressure
- gas
- chamber
- 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.)
- Granted
Links
- 238000004519 manufacturing process Methods 0.000 title 1
- 239000000463 material Substances 0.000 claims abstract description 17
- 238000004140 cleaning Methods 0.000 claims abstract description 16
- 230000009969 flowable effect Effects 0.000 claims abstract description 11
- 239000007789 gas Substances 0.000 claims description 216
- 238000002485 combustion reaction Methods 0.000 claims description 49
- 230000007704 transition Effects 0.000 claims description 17
- 238000000034 method Methods 0.000 claims description 11
- 238000005192 partition Methods 0.000 claims description 8
- 230000003068 static effect Effects 0.000 claims description 8
- 230000001960 triggered effect Effects 0.000 claims description 5
- 239000011261 inert gas Substances 0.000 claims description 4
- 238000010304 firing Methods 0.000 claims 1
- 230000000630 rising effect Effects 0.000 claims 1
- 238000004880 explosion Methods 0.000 description 15
- 239000000203 mixture Substances 0.000 description 11
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 description 10
- KUNSUQLRTQLHQQ-UHFFFAOYSA-N copper tin Chemical compound [Cu].[Sn] KUNSUQLRTQLHQQ-UHFFFAOYSA-N 0.000 description 8
- 230000000694 effects Effects 0.000 description 8
- 229910000906 Bronze Inorganic materials 0.000 description 7
- 239000010974 bronze Substances 0.000 description 7
- 230000009471 action Effects 0.000 description 6
- 238000007789 sealing Methods 0.000 description 6
- 239000002360 explosive Substances 0.000 description 5
- 239000000126 substance Substances 0.000 description 5
- 239000000446 fuel Substances 0.000 description 4
- QVGXLLKOCUKJST-UHFFFAOYSA-N atomic oxygen Chemical compound [O] QVGXLLKOCUKJST-UHFFFAOYSA-N 0.000 description 3
- 230000008901 benefit Effects 0.000 description 3
- 239000012530 fluid Substances 0.000 description 3
- 230000007246 mechanism Effects 0.000 description 3
- 239000003345 natural gas Substances 0.000 description 3
- 239000001301 oxygen Substances 0.000 description 3
- 229910052760 oxygen Inorganic materials 0.000 description 3
- XKRFYHLGVUSROY-UHFFFAOYSA-N Argon Chemical compound [Ar] XKRFYHLGVUSROY-UHFFFAOYSA-N 0.000 description 2
- IJGRMHOSHXDMSA-UHFFFAOYSA-N Atomic nitrogen Chemical compound N#N IJGRMHOSHXDMSA-UHFFFAOYSA-N 0.000 description 2
- 238000006243 chemical reaction Methods 0.000 description 2
- 238000004200 deflagration Methods 0.000 description 2
- 238000013461 design Methods 0.000 description 2
- 238000005474 detonation Methods 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 1
- 229910052786 argon Inorganic materials 0.000 description 1
- 238000000418 atomic force spectrum Methods 0.000 description 1
- 238000007664 blowing Methods 0.000 description 1
- 239000011538 cleaning material Substances 0.000 description 1
- 239000003245 coal Substances 0.000 description 1
- 239000000567 combustion gas Substances 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 239000002131 composite material Substances 0.000 description 1
- 150000001875 compounds Chemical class 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
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- 230000007423 decrease Effects 0.000 description 1
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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
- 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
-
- 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
Definitions
- the present invention relates to an apparatus and a method for generating high-amplitude pressure waves, in particular for boiler cleaning.
- Such a device for generating high amplitude pressure waves is known from US 5,864,517.
- acoustic vibrations are generated, which are significantly stronger than those that can be generated by loudspeakers. They can be used in particular for boiler cleaning, as these pressure waves leads to a detachment of attached particles.
- US 5,864,517 two different pulsed burns are discussed. The detonation and the deflagration.
- the detonative combustion has an extremely fast flame speed of 2,000 to 4,000 m / s, while the deflagration combustion has much slower flame speeds of less than 200 m / s and the pressure waves are of significantly lower amplitude.
- 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 piston is displaced in position by an auxiliary explosion in an auxiliary explosion chamber such that it releases the outlet.
- This procedure requires precise temporal coordination between the triggering of the main explosion and the previous auxiliary explosion.
- the device then further has a gas spring chamber, which decelerates the retracted piston and pushes back the said piston to its original position after blowing out the gases from the main explosion chamber.
- EP 1 922 568 shows another method and apparatus for generating explosions in which the gas spring mechanism has a release mechanism disclosed as a spring-loaded mechanism.
- FR 2,938,623 shows an explosion cylinder having a piston movable between open and closed positions for cyclically generating explosions of pressurized gas or air for cleaning purposes.
- the present invention seeks to provide an improved device and method which is easier and safer to ignite.
- an object of the invention is to provide the device with a longer maintenance interval, since the wear of the moving parts in the pressure-resistant container by the explosions is significant and in the prior art allows only a limited number of repetitions of the cleaning ignitions before the installation must be serviced. Since in power plant technology, the basic industry and in the technical chemistry, the processes are usually carried out in complex chemical plants, a number of such devices for generating high-amplitude pressure waves for the purification of the various containers are usually provided, which then have to be maintained accordingly.
- the device is preferred for cleaning boilers in large technical Equipment such as waste incinerators, coal power plants, silos, used to remove slags or deposits etc.
- the main advantage is that the individual cleaning cycles can be repeated very quickly and repeatedly.
- the use of gases as a cleaning material to generate the sequence of pressure waves and associated pressure pulses is relatively inexpensive and high pressures can be generated.
- the addition of two chemical fluids that do not burn or explode at a time just prior to the release of the shock wave also increases safety. It also makes it possible to clean plants that are still warm and possibly in operation, since the reacting substances are exposed to the hot environment for a long time.
- the generated pressure wave can be conducted via a pipe over longer distances in a boiler to the point to be cleaned.
- the pipe can be firmly installed on the system to be cleaned, but also be introduced from the outside, for example, slidably telescopically pushed into a plant or a boiler. Due to the pressure pulse generated during the burnup, deposits and contaminants are blown away from inner tubes in the boiler and its walls and at the same time the tubes or walls are vibrated. Both actions cause an efficient cleaning of the plants to be cleaned.
- a device for generating high-amplitude pressure waves, in particular for boiler cleaning, has a pressure-resistant container.
- This can be multi-part. He has at least one introduced therein combustion chamber. Several Abbrennkammem can be interconnected. At least one ignition device extending into the braking chamber (s) is provided. There is at least one supply line for supplying a flowable combustible material into the combustion chamber, preferably separated a fuel and an oxidizer such as natural gas and air, or methane and oxygen. There are also various other liquid or gaseous fuels used.
- the pressure-resistant container has a discharge opening for the directed discharge of gas pressure generated by the ignition of the combustible material in the combustion chamber.
- a closing means closing the discharge opening is present, which is designed to release the discharge opening for the directed deflation, and which is then displaced after burning by a spring means in the starting position.
- the closure means is a displaceable piston in its longitudinal direction, which has a rear aligned in the direction of the spring device portion and a front in the direction of the discharge opening aligned portion.
- the seat of the piston has with respect to its longitudinal direction via an inclined obliquely to the discharge opening piston surface, which is opposite to a tilted obliquely to the discharge opening housing surface, wherein the housing surface relative to the piston surface with an outlet opening directed towards the angle of a perpendicular to the piston direction opening directed closure line.
- the angle can be between 0.5 and 5 degrees, preferably between 1 and 3 degrees, in particular 2 degrees.
- the closure line oriented perpendicular to the piston direction may be arranged inside 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.
- a flange surface which is perpendicular to the piston axis and which is connected to or belongs to the combustion chamber can have a surface area of between 50 and 200 percent of a surface area given by the surface area of the piston surface.
- a transition region may be provided.
- the front section is arranged at a position closing the discharge opening of the piston in the region of the combustion chamber.
- the front portion With respect to the longitudinal direction of the piston the front portion is tapered with respect to the rear portion such that the transition region forms an active surface oriented transversely of the longitudinal direction of the piston to which a pressure driving back the piston is applied upon ignition of the burnable material such that the forward portion of the piston releases the discharge port ,
- a simpler cleaning is possible, since the pressure build-up can also be achieved by burning and then responsible even for the opening of the way to the discharge funnel.
- the transition region may be a continuously tapering region 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 region of the combustion chambers.
- the transition region may also be formed by a flange-like taper of the piston.
- a hollow central guide strand may be provided in the pressure-resistant container, which guides the piston in the front region in its interior. This has advantages in the wear of the piston guide, since such a guide over further apart portions of the piston are possible. Then at least one connecting gap between the Abbrennkammem and a Flilfsdruckraum in the region of the flange-like taper of the piston is provided.
- the combustion chamber may be arranged annularly around the piston about its longitudinal axis.
- the annular walls of the combustion chamber can be stacked sealingly connected ring segments, which are advantageously completed by a top plate and a bottom plate top or bottom.
- At least two Abbrennkammem can be arranged in a plane at an angular distance from each other radially to a central axis.
- two Abbrennkammem diametrically opposite. Then either the longitudinal axis of the falls Gas spring with the central axis together; three Abbrennkammem could then have an angular distance of 120 degrees in the common plane.
- the longitudinal axis of the gas spring is also located in said plane of at least two Abbrennkammem, so that in three Abbrennkammem an angular distance of 90 degrees of the individual elements to each other is possible.
- the discharge opening usually has a pipe with a tube longitudinal direction.
- the tube longitudinal direction of the discharge opening coincide with the central axis, ie the discharge opening lie in the extension of the piston, or the longitudinal axis of the gas spring lies in said plane of the at least two Abbrennkammem.
- an angular distance of less than 120 degrees between the two combustion chambers are provided so that they are more aligned with the discharge opening.
- the gas spring may have a front gas spring chamber space opposite the piston and a rear gas spring chamber space separated therefrom by a first connection as a backflow connection and a second connection with a check valve between the front gas spring chamber space and the rear gas spring chamber space is arranged to allow unimpeded media flow from the front to the rear gas spring chamber, but substantially block the opposite direction from the rear gas spring chamber.
- the first and the second connection may be provided in the partition wall.
- the second connection may have at least two partial connections, which on the one hand open laterally 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 end in the rear gas spring chamber space, so that the mouths in succession in an ingress of the piston in the front gas spring chamber space be covered, said part compounds each have their own check valve.
- the individual check valves are successively switched off, so that the media flow slows down from the front to the rear gas spring chamber, that is, the braking effect by the gas pressure build-up in the front gas spring chamber decreases.
- the second connection may have a controllable check valve, which may optionally have a series-connected control valve and a check valve, which controllable check valve is connected to a control unit with which the ignition can be triggered, wherein the control unit is configured to the controllable check valve in a first predetermined time interval after the ignition of the flowable combustible material to open. This can be used to ensure that the burning in the combustion chamber is completed before the piston is allowed to retreat further.
- the first connection may comprise a controllable backflow valve, which may optionally have a series-connected control valve and a return flow guide, which controllable backflow valve is connected to the control unit with which the ignition is triggered, wherein the control unit is configured to the controllable backflow valve in a second predetermined time interval after the opening of the controllable check valve to open.
- control unit has a Gas Schollbeckmatitician with the gas filling pressure in the front and in the rear gas spring chamber is adjustable to a predetermined value prior to ignition, wherein the Gas filling pressure in the front gas spring chamber is higher than in the rear gas spring chamber is adjustable.
- the gas full pressure in the front gas spring chamber can be set higher than in the rear gas spring chamber by at least 2 times, preferably at least 3 times or 5 times, so that, on the one hand, the front gas spring pressure chamber does not recede or ignites only insignificantly upon ignition , Since the pressure prevailing in her on ignition opposes the pressure building up in the combustion chamber, and the retreat occurs only when opening the check valve then completely and quickly, as already Gas pressure difference was set.
- atmospheric pressure may prevail in the rear chamber, while only the front gas spring pressure chamber has been pressurized with the inert gas.
- a device for generating high amplitude pressure waves in particular for boiler cleaning, with a pressure-resistant container with a combustion chamber introduced therein and at least one reaching into the combustion chamber ignition device , with at least one supply line for supplying a flowable combustible material into the combustion chamber, the pressure-resistant container having a discharge opening for directionally discharging gas pressure generated by the ignition of the burnable material in the combustion chamber and a closure means closing the discharge opening, which is designed, the discharge opening to release for directional release, and which is displaceable by a spring device into the starting position, characterized in that the closure means is a displaceable in its longitudinal direction piston, which has a rear portion oriented toward the spring device and a front portion oriented in the direction of the discharge opening, that the front portion is arranged in the region of the combustion chamber at a position of the piston closing off the discharge opening, with respect to the longitudinal direction of the piston of the piston has an inclined obliquely to
- this angle is advantageously between 0.5 and 3, in particular 1 degree.
- the closure line oriented perpendicular to the piston direction is advantageously arranged inside 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 portion is tapered with respect to the rear portion.
- the taper relates to the inner piston seat wall and then preferably has an opposite outer housing valve seat wall which opens inwardly toward the outlet at a small angle.
- FIG. 1 is a schematic perspective view of an apparatus for generating high amplitude pressure waves according to an embodiment of the invention
- Fig. 2 is a schematic view of the device of Fig. 1;
- Fig. 3 is a side not-scale sectional view of a device for
- Fig. 5 is a schematic detail view of the piston of Fig. 3 between the lines
- Fig. 6 is a schematic perspective view of another device for
- Fig. 7 is a schematic cross-sectional view with a vertical sectional axis of
- Fig. 8 is a schematic cross-sectional view with horizontal section axis of
- FIG. 9 is a schematic perspective view of another device for
- FIG. 11 is a schematic cross-sectional view with a vertical sectional axis of a
- Fig. 12 is a schematic cross-sectional view with a vertical sectional axis of a
- FIGS. 1, 6, 10 or 11 shows a schematic cross-sectional view with a vertical sectional axis of another embodiment of a gas spring insertable in a device, for example according to FIGS. 1, 6, 10 or 11;
- FIGS. 2, 3, 7, 10 and 11 show a schematic partial view of a center piece of a device according to a further exemplary embodiment of the invention, which can also be used in FIGS. 2, 3, 7, 10 and 11:
- Figs. 15A, 15B and 15C are detail views of Fig. 14 at various times of an opening cycle.
- FIG. 16 is a graph of force versus time for the embodiment of FIG. 16
- Valve seat for a device for generating high-amplitude pressure waves.
- FIG. 1 shows a perspective view of a device for generating high-amplitude pressure waves according to one exemplary embodiment of the invention.
- a central body 30 a first pressure-resistant container 21 and a second pressure-resistant container 22 are arranged. These containers 21 and 22 extend in the present embodiment substantially parallel to the boiler wall 5, which is shown in fragmentary form.
- a discharge hopper 61 is flanged with a subsequent discharge pipe 62 which projects through the boiler wall 5 and ends in a discharge opening 63 in the boiler interior 15.
- the drain opening 63 may also be located directly on the boiler wall, and the drain pipe 62 may be made shorter than the drain throat 61 or may be omitted altogether.
- the gas spring pressure body 40 is flanged to the central body 30.
- 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, that is, an aspect ratio for the internal volumes 121 and 122 of between 5: 1 and 20: 1.
- the two left and right pressure-resistant containers 21 and 22 are arranged, which have a first combustion chamber 121 and a second Abbrennsch 122.
- the pressure-resistant container 21 and 22 are cylindrical in the embodiment with a larger interior diameter in the rear area, ie to the central body 30 out there is a taper of the passage.
- a piston 70 is arranged, which will be shown in more detail in the further drawings, the chambers 121 and 122 separated in the illustrated closed state from each other and closes with its front end 72 of the piston 70, the outlet in the direction of Ablasstrichters 61st
- the piston 70 protrudes with its upper part 71 into the gas spring pressure member 40 as shown in more detail in FIG.
- Reference numeral 300 designates the valve seat itself. This can be configured, in particular, according to FIG. 14 and the detail views of FIGS. 15A, 15B, 15C, in order then to develop the effect as illustrated in FIG. 16.
- the object of the high amplitude pressure wave generating apparatus is to generate the same in the first and second pressure chambers 121 and 122 by burning off a fluid fuel or explosive.
- This fuel is preferably formed by the mixing of per se non-combustible or explosive components stored in the first and second gas reservoirs 51 and 52.
- These gas reservoirs 51 and 52 are fed via external gas supply lines 53 and 54 from respective gas ports 57 and 58, which are controlled by external gas supply valves 55 and 56.
- the first gas reservoir 51 is connected to the Abbrennkammem 121 and 122 via a first gas filling line 151 and an interposed first Gasföllventil 153.
- a gas spring gas connection 47 is provided, via a gas spring feed valve 48 and a gas spring feed line 49, the gas for the gas spring 40 in the gas spring interior 41 and 42, as shown in Fig. 3, is introduced.
- the first gas may be, for example, methane or natural gas, where the second gas may be oxygen or air or an oxygen-containing air mixture.
- the flowable combustible material may be an explosive mixture, it may be in addition to gaseous liquid, powdery or a mixture of such substances.
- Combustion chambers 121 and 122 are additionally connected to an ignition device which simultaneously initiates ignition of the burnable material in the combustion chambers 121 and 122. If, as in the embodiment of FIG. 6, an annular gap is provided, in short, a volumetric connection of the two Abbrennkammem 121 and 122, then only one ignition device is necessary. As ignition device, among other glow plugs or spark plugs can be used. 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. Thus, a faster pressure build-up takes place in the combustion chambers 121 and 122.
- the outlet opening of the pressure-resistant container is kept closed by the piston 70 as a closure means.
- the gas spring allows the closure to be kept closed even against the filling pressure of the burnable elements in the burn-off chambers 121 and 122. Only by increasing the pressure during the ignition of the flowable mixture is the pressure on the intermediate region 75 increased so that the piston 70 is pushed back accordingly. Subsequently, as will be described in connection with Fig. 3, the gas spring element then causes a return of the piston 70 as a closure means after burning and allows a direct repeatability of the process by refilling the chambers 121 and 122. At the same time, a backflow of avoided in the boiler substances in the device.
- the piston 70 is opened so quickly that the pressurized mixture in the combustion chambers 121 and 122 during the escape is still not completely burned, so that the gas mixture continues to burn in the discharge funnel, so that a pressure pulse is generated with high pressure peak.
- air as one of the two media besides CEl 4 or natural gas, the chemical reaction within the flash chambers 121 and 122 will expire and all the energy will be converted in the apparatus.
- the gas is released into the open air.
- FIG. 3 shows a sectional side view in a schematic representation of a device for generating pressure waves with their components essential to the invention.
- the first and second pressure-resistant containers 21 and 22 adjoin the discharge hopper 61 inserted in them, which has a rounded valve seat contact 65 at its inner end.
- valve seat contact 65 which is designed as a horizontal substantially circular contact line which is perpendicular and concentric to the piston longitudinal axis 90, adjoins the front end 72 of the piston 70, to which the tapered piston portion 73 adjoins.
- this tapered piston portion 73rd joins a piston transition region 75, in which the diameter of the piston is increased to have a larger diameter at the rear end of the piston 71.
- the rear piston diameter 171 is thus made larger than the front piston diameter 172, in particular, the piston 70 seen in its longitudinal direction, a surface 91 (as in Fig.
- the piston 70 is sealed between the walls of the left and right pressure-resistant containers 21 and 22 by a series of seals 81 and 82 in its longitudinal direction, where the three seals 81 can be bronze seals, while the interposed seal 82 is an O Ring is. These seals 81 and 82 are recessed in grooves in the piston 70; they could also be provided in the opposite walls.
- the function of the gas spring is as follows. Through the gas filling lines 151 and 152, the two components of the combustible gas mixtures in the chambers 121 and 122 are passed. By not shown in the drawing of FIG. 3 igniter these gases are ignited. As a result, a pressure is exerted on the transition region 75, which overcomes the gas spring pressure that holds against it and moves the piston 70 into the area of the front gas spring chamber space 41. For this movement to take place sufficiently quickly, the check valve 44 is provided in the intermediate wall 43, which opens immediately and the gas pressure between the front gas spring chamber 41 and the rear gas spring chamber 42 quickly compensates, so that after an initial strong movement of the piston 70, this then at increased resistance from the combined gas spring chamber 41 and 42 is braked.
- the combustible gases escape from the outlet hopper 61 in burnt or still burning form and reduce the pressure in the Abbrennkammem 121 and 122. Since it is the valve in the gas spring partition wall 43 is a check valve 44, then the composite of the gas spring chamber 41, 42 connected only by the diameter in the much lower gas return flow opening 45, with then the gas of the gas spring from the rear gas spring chamber 42 pushes back into the front gas spring chamber 41 and the piston 70 in its initial position, as shown in Figure 3, pushes. Any gas losses are compensated by the gas spring feed line 49.
- the gas of the gas spring 40 may be air or an inert gas such as N 2 .
- FIG. 4 shows, in three superimposed cross-sections FIG. 4 a, 4b and 4c, three cross-sections through the device according to FIG. 3 along the intersection lines IVa, IVb and IVc.
- the piston 70 advantageously has a round cross-section.
- FIG 4a shows a cross section along the line IVa through the upper wall 21, 22 of the pressure-resistant container, wherein a bronze seal 81 is shown, which surrounds the rear portion 71 of the piston 70.
- 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 region of the chamber of the combustion chambers 121 and 122, in which the Piston 70 has the diameter of the rear portion 71.
- the discharge opening 61 is here in all three drawings Fig. 4a, 4b and 4c below the Drawing plane shown. It is also possible, as shown in Fig. 3 of the prior art WO 2010/025574, that the discharge hopper 61 in the longitudinal direction of the extension on the other side of the central body 30 with a Abbrennhunt 121 is in communication and the closure element as a piston 70 is perpendicular thereto, so that the gas mixture with pushed back piston 70 can escape directly straight ahead in the longitudinal direction of the entire device.
- FIG. 5 shows an enlarged section of the transition region 75 of the piston 70.
- first diameter 121 which is smaller than the rear piston diameter 171.
- transition region 75 forms in a section in the projection of the longitudinal axis 90, two rectangular strips 91, which serve as pressure transfer strip.
- the combustible chambers have a volume between one and two liters, wherein the gas filling pressure may be between 10 and 30, for example between 15 and 25 bar.
- the diameter of the closed by the piston, the annular opening is between 40 and 15 mm, in particular between 60 and 100 mm, in particular 80 mm.
- the ignition can be configured in a similar manner as in the prior art WO 2010/025574 and thus, for example, done electrically or by light ignition.
- FIG. 6 shows a schematic perspective view of another device for generating high amplitude pressure waves according to an embodiment of the invention. Identical features are provided with the same reference numbers throughout the description.
- the gas spring pressure member 40 is provided at the central body 30, two pressure-resistant container 21 and 22 are arranged here and perpendicular to these, the gas spring pressure member 40 is provided at the central body 30, and 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 center of the central body 30.
- FIG. 7 now shows a schematic cross-sectional view of the device according to FIG. 6 with a vertical cutting axis.
- the piston longitudinal axis 90 which corresponds to the longitudinal axis of the gas spring pressure member 40, crosses the horizontal central section plane 92 of the pressure bodies 21 and 22. Elements of the central body 30 have been omitted here in Fig. 7 for simplicity of drawing.
- the pressure-resistant containers 21 and 22 extend to the outlet funnel 61, with its inner end forming 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 region 73, adjoined by the diameter-enlarging transition region 75, which leads into the rearward piston region 71.
- the piston 70 is made hollow here. It may be in two parts, wherein the lower end for contact with the valve seat 65 can be introduced into the hollow piston 70.
- the valve seat 300 can again be designed as shown in FIG. 14.
- the rear portion of the piston 70 has a sufficient height from the transition region 75 to its upper flat end surface, which limits the lower gas spring chamber space 41, so that even with a pushing back of the piston in this front gas spring chamber space 41, the piston 70 still on the inner walls of the Gas spring 40 is substantially sealingly applied by the following sealing elements.
- the check valve 44 and the gas return flow opening 45 are provided in the gas spring separating wall 43, which runs essentially perpendicular to the piston longitudinal axis 90.
- the Gas Wegströmö réelle 45 can also be referred to as a diaphragm.
- an inert gas such as nitrogen, CO 2 or argon can be refilled. With sufficient sealing of the spring chamber spaces 41 and 42, the gas may also be air.
- the piston 70 is arranged at a constant distance in this central region of the inner wall of the central body 30 and there extending in the Kolbenlijnsachseraum 90 Annular gap 123, which is designed to compensate for the pressure between the two Abbrennhuntn 121 and 122.
- a gas supply line 151 and 152 arranged next to one another is sufficient for the two gases or fluids to be mixed for burning off.
- 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.
- shutters or metering valves 153 and 154 are provided, so that a direct filling of the Abbrennkammem 121 and 122 is made.
- Such an annular gap 123 can also be guided on one side, that is, 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.
- FIG. 9 shows a schematic perspective view of a further device for generating high-amplitude pressure waves according to one exemplary embodiment of the invention.
- a symmetrical about the piston longitudinal axis 90 arrangement has been provided here.
- an annular pressure-resistant container 25 is provided, into which the gas supply lines 151 and 152 lead.
- This pressure-resistant container 25 is disposed below the gas spring pressure member 40 in its extension and the Zündvoriquesszutechnisch 50 is guided by the projecting beyond the gas spring body portion of the pressure-resistant container 25 into the interior of the device.
- the pressure-resistant container 25 of a cover plate, a bottom plate and here a ring constructed, which are sealingly juxtaposed. It can also be arranged on top of each other several rings.
- FIG. 10 shows a schematic cross-sectional view with a vertical sectional axis of the device according to FIG. 9.
- the gas spring 40 is formed analogously to the other embodiments. There are two major structural differences from these other embodiments that have been used here together. However, it is also possible in other embodiments, not shown in the figures, to connect only one of the two differences described below with the other exemplary embodiments.
- the first difference with the other embodiments is that there is an annular burn-off chamber 125 that completely surrounds the piston 70.
- annular elements of a pressure-resistant container 25 there are three rings that have been drawn because of the smooth flush outer surfaces in Fig. 9 as a ring.
- the spark plug 59 of the ignition device 50 is sealingly inserted into the annular Abbrennhunt 125.
- the two gas supply lines 151 and 152 are brought in directly. In other words, there are no gas reservoirs 51 and 52 as metering elements. This is controlled by the orifices 153 and 154 in the 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 embodiments is formed here by a bottom 191 of the piston 70, which underside and piston inside an auxiliary pressure chamber 95 limits. This bordered on its underside at a down tapered Ablenkprofilstrang 96.
- the hollow strand 96 here has a uniform inner diameter, in which the lower portion extends with the tapered piston portion 173, which is guided over two bronze seals 81 relative to the strand 96 here.
- the pressure in the annular Abbrennhunt 125 increases as in the previous examples, in which case the pressure has the opportunity to expand over a connecting gap 126 in the auxiliary pressure chamber 95 , It is also possible for a plurality of such gaps 126 to be provided, preferably at a regular angular distance from each other, so that the deflecting profile strand 96 is fastened to the plate or the gas spring pressure body through these gaps by the connection gap 126.
- the internal pressure of the annular burn-off chamber 125 pressurizes the underside of the rear end 71 of the piston 70 with its over-the-core surface 191 in the auxiliary pressure space 95.
- the pressure on the projection corresponds to the pressure surface 91 of the other embodiment, the piston 70 is displaced in its strand 96 by the increasing auxiliary pressure chamber 95 to the rear in the front gas spring chamber space 41, wherein also between the rear end of the piston 71 and the inner wall of the gas spring 40, a bronze seal 81st and an O-ring 82 are provided.
- FIG. 11 shows a schematic cross-sectional view with a vertical sectional axis 90 of a device with features which partially correspond to the device according to FIG. 6 and partly those of FIGS. 9 and 10, respectively.
- It is a piston 70 according to the embodiment of FIGS. 1 and 6, which is surrounded by an annular Abbrennhuntraum 125, as shown in the embodiment of FIGS. 9 and 10.
- the annular gap 123 is widened to the annular chamber space 125 and instead of two opposite Abbrennkammem 121 and 122, there is only one cylindrical with a piston 70 as the core. Otherwise, the function of pushing back the piston 70 is exactly the same solved by the force exerted on the transition region 75 pressure of the burning gas mixture.
- the gas spring pressure body is shown as a one-piece element with the lid of the annular (considering the piston 70 used as a central element) or otherwise cylindrical Abbrennhunt 125. Of course, this can also be several flanged elements. It is essential in the representation here that the walls comprising the rear portion of the piston 70 have extensions 196 which protrude into the interior of the combustion chamber 125. These extensions 196, which are configured here in a ring shape, correspond to the strand 96 from FIG. 10 and serve for the further guidance of the piston 70. They can also be opposite to bronze rings 81, 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 guided into the middle strand or by ring or ring segment-shaped extensions 96.
- the piston 70 itself may be hollow to save weight while being open inwardly in the longitudinal direction 90, or it may also be made of a solid material, in particular steel, or it may be hollow and may be hollowed from above, in particular screwed plug have. This can also form the sealing surface to the valve seat 65.
- FIG. 12 shows a schematic cross-sectional view with a vertical sectional axis 90 of another embodiment of a gas spring 140, wherein the further region of the device with the piston 70 and the spark plug 59 and the Abbrennkammem and Ablasstrichtem not shown here can be made similar or the same.
- the essential difference to the gas spring 40 is in an external deflection of the check valve 44 outside the pressure hull as well as the external bypass of the gas return port 45 outside the pressure hull. So both will not be within the gas spring partition wall 43 between the two chambers 41 and 42 out but have external valves 144 and 145. These orifices or control valves 144 and 145 are connected to the designated control line 150, which is also connected to the ignition device.
- the line 150 does not indicate a direct electrical or otherwise directly electrically driving line, but symbolizes schematically that control signals are transmitted to the spark plug 59 and to the valves 144 and 145 of a control unit, not shown in the drawings, so that they switch according to time delay .
- the check valve 44 is continuously switched by the valve 144, optionally delayed slightly to slow the movement of the piston initially by a rapid pressure build-up in the front gas spring chamber 41 and after opening quickly a pressure equalization with the rear gas spring chamber 42 to reach.
- the valve 145 for the return flow 45 to. It can also open in advance in advance, since it allows only a small amount of gas in the opposite direction.
- the shutter 145 opens and closes the valve 144.
- the elements 44 and 45 it is no longer necessary, the elements 44 and 45 than To design a check valve or diaphragm; they can also be simple lines.
- FIG. 13 shows a further schematic cross-sectional view with a vertical sectional axis 90 of another embodiment of a gas spring 240, which can likewise be inserted into a device, for example according to FIGS. 1, 6, 10 or 11.
- the check valve 244 is executed four times, while the gas return port 45 is arranged in the gas spring intermediate wall 43 as in the other embodiments.
- the arrangement of four check valves 244 which is connected via corresponding individual lines 243 with the rear gas spring chamber space 42, an additional function in conjunction with the receding piston 70 results.
- the arrangement of the individual orifices 246 of the four check valves 244 are one above the other at intervals along the Piston longitudinal axis 90 is provided (not necessarily directly above each other, but also laterally offset at an angular distance from each other), so that the receding piston 70, gradually moving from below moving, one after the other the orifices 246 and thus the connection to the check valves 244 of the connection between the front gas spring chamber 41 and the rear gas spring chamber 42 interrupts.
- FIG. 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 in FIG. 14 bears against the opposite wall of the gas spring pressure element 40; but it can also rest on the guide strand 96.
- the valve seat 300 is supported downwardly by counter surfaces of the exhaust funnel 61. Between exhaust funnel 61 and gas spring pressure element 40 is an opening which leads into the first combustion chamber 121.
- the upper portion of the exhaust funnel 61 may also be a defined counter surface may be present, for example, the pressure-resistant container 21, 22 is assigned.
- FIG. 14 is terminated at the upper end of the piston 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 embodiment can be used in the embodiments of FIGS. 2, 3, 7, 10, 11.
- an auxiliary pressure space 95 is provided, in which a flange 191 is a pressure surface for moving the piston 70.
- a line 301 is indicated, which indicates a distance from the side wall of the piston diameter 172. This is a distance from a curvature R2 heard from the side wall 172 to the inner piston seat wall 302, which can be better seen in the detail views of FIGS. 15A to 15C.
- This inner piston seat wall 302 is located opposite the outer or housing-side valve seat wall 303.
- the two walls 203 and 303 which is substantially an angle of approximately 45 degrees, in other not shown exemplary embodiments between 30 and 60 degrees, relative to the piston movement axis
- the apex of the opening angle 304 is located at the intersection of the line 301 indicative of the end of curvature of the piston 70 with the opposite outer housing-side wall 303 and closes there in an annulus the outer discharge hopper 306 of the first combustion chamber 121 (here shown) Of course, from the second combustion chamber 122 from.
- FIG. 15A start 0.5 mm
- Fig. 15B opening lmm
- Fig. 15C clear passage 2mm
- arrows 311, 312, 313, 314 and 315 stand for the entire surfaces on which they stand. These are, if present, the optional prechamber surface 311, the static auxiliary surface 312, the dynamic auxiliary surface 313, the piston inner surface 314, and the gas spring surface diametrically opposed thereto 315.
- the optional pre-chamber surface 311 is the flange widening in the auxiliary chamber pressure space 95.
- the auxiliary static surface 312 is the curved surface resulting from the distance 301 and its corresponding radius R2 at the front end of the piston in Fig. 14, which then becomes mathematically continuous into the inner Piston seat wall 302 merges.
- the dynamic auxiliary surface 313 is so designated because by the angle 304, the two walls 302 and 303 diverge toward the discharge hopper chamber 306, thereby dynamically developing the surface.
- the arrows 313 in a sequence from the inner edge to draw close to the arrow 312.
- the piston inner surface 314 is shown here in the recess of the hollow piston, but could also exist at the lower end of the piston.
- the diametrically opposite the gas spring surface 315 is provided.
- Fig. 16 shows on the Y-axis, the force acting on the piston 70 against the time on the X-axis.
- the basic effect of the auxiliary pressure chamber 95 and its surface 311 is indicated by the line 411.
- the area 511 between the 0-line and the line 411 is a measure of the pre-chamber effective area.
- Line 412 shows the additional force exerted by the rounded area at arrow 312 and is indicated by area 512 between line 411 and line 412.
- boost ends at a time with a reversal of the boost curve 413 to a somewhat later time 521, in which the diverging gap of FIGS. 15A to 15C has expanded to a passage as in FIG. 15C.
- This does not mean that it is a slot of width 2 millimeters, which depends on the depth of the valve seat, so the distance from the rounding R2 (described by the line / arrow 301) to the beginning of Ablastrichterraumes 306. Zu
- 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 moves Cross-section radially from the outside inwards, so that the advantages are small projected areas in the closed state, which avoids that an unwanted opening happens.
- the pre-chamber 95 provides for the initial opening at the desired time.
- it is possible to replace this auxiliary chamber by arranging the surfaces 191 in the main chamber space 121 (ie without separate ignition, similar to the exemplary embodiment in FIG. 10), so that the surface 511 corresponds to an incipient ignition of the main chamber.
- annular pressure vessel 90 piston longitudinal axis
- Ignition device 144 Checkback control valve first gas reservoir 145 Backflow control valve 1 second gas reservoir 151 first gas fill line first external gas supply 152 second gas fill line second external gas supply 153 first gas fill valve first gas supply valve 154 second gas fill valve second gas supply valve 170 piston surface first gas port 171 rear piston diameter second gas port 172 front piston diameter spark plug 173 tapered piston region discharge port 175 Piston flange transition Drain tube 191 Flange surface
- Valve seat 411 Pre-chamber line of action Line the end of curvature 412 Indicating the static surface line of action 413 Boost action line Inner piston seat 414 Piston discharge line Outside of the housing 415 Gas spring action line Valve seat wall 419 Sum line
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EP18165013 | 2018-03-29 | ||
PCT/EP2019/057752 WO2019185736A1 (en) | 2018-03-29 | 2019-03-27 | Device and method for producing pressure waves of high amplitude |
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EP3776529A1 true EP3776529A1 (en) | 2021-02-17 |
EP3776529C0 EP3776529C0 (en) | 2023-06-07 |
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EP19712237.7A Active EP3776529B1 (en) | 2018-03-29 | 2019-03-27 | Device for the production of high-amplitude pressure waves |
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US (1) | US20210199284A1 (en) |
EP (1) | EP3776529B1 (en) |
JP (1) | JP7401516B2 (en) |
KR (1) | KR20210020870A (en) |
CN (1) | CN112074897A (en) |
AU (1) | AU2019241452B2 (en) |
BR (1) | BR112020019905A2 (en) |
CA (1) | CA3094256A1 (en) |
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JP7458180B2 (en) * | 2019-12-23 | 2024-03-29 | 川崎重工業株式会社 | Shock wave soot blower system and its operating method |
JP7432359B2 (en) * | 2019-12-26 | 2024-02-16 | 川崎重工業株式会社 | Shock wave soot blower and its operating method |
KR20240101822A (en) * | 2021-11-02 | 2024-07-02 | 엑스플로 엔지니어링 아게 | Protective devices for boiler access points |
CA3241121A1 (en) | 2021-12-17 | 2023-06-22 | Marc Peter HANGARTNER | Fastening apparatus for a cleaning device based on introducing high-amplitude pressure waves |
JP7153824B1 (en) | 2022-07-22 | 2022-10-14 | 三菱重工パワーインダストリー株式会社 | pressure wave generator |
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FR2003488A1 (en) * | 1968-03-08 | 1969-11-07 | Messer Griesheim Gmbh | |
FR2278408A1 (en) * | 1974-05-31 | 1976-02-13 | Aquitaine Petrole | MECHANICAL WAVES EMISSION DEVICE |
DE3828112A1 (en) * | 1988-08-18 | 1990-02-22 | Hekatron Gmbh | Device for the testing of the functioning of a thermostatic detector in a region at risk of explosion |
US5864517A (en) | 1997-03-21 | 1999-01-26 | Adroit Systems, Inc. | Pulsed combustion acoustic wave generator |
FI118756B (en) * | 2004-04-02 | 2008-03-14 | Nirafon Oy | Process for generating gas pressure pulses in a particulate precipitation purifier and particulate precipitation purifier |
US7146916B2 (en) * | 2004-05-14 | 2006-12-12 | Eco/Technologies, Llc | Starved air inclined hearth combustor |
MX2007004484A (en) * | 2004-10-13 | 2007-06-25 | Ptc Therapeutics Inc | Pyrazole or triazole compounds and their use for the manufacture of a medicament for treating somatic mutation-related diseases. |
WO2007028264A2 (en) | 2005-09-05 | 2007-03-15 | Explo Engineering Gmbh | Method and device for generating compression waves |
CN102057422B (en) * | 2008-04-14 | 2013-09-25 | 阿夫纳·斯佩科特 | Automatic adjustable voltage to stabilize pressure for shockwave medical therapy device |
CH699486A2 (en) | 2008-09-04 | 2010-03-15 | Explo Engineering Gmbh | Device and method for generating explosions. |
FR2938623B1 (en) | 2008-11-18 | 2013-02-22 | Soc Detudes Et De Recherches De Lecole Nationale Superieure Darts Et Metiers Seram | DEFLAGRATOR CANON COMPRISING A MOBILE PISTON |
GB0921660D0 (en) * | 2009-12-10 | 2010-01-27 | Zettner Michael | Method for increasing the efficiency of a heat exchanger |
CH703104A2 (en) * | 2010-05-04 | 2011-11-15 | Explo Engineering Gmbh | Seal and method for producing a durchzündsperre for druckwelle generators. |
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RU173934U1 (en) * | 2016-08-16 | 2017-09-19 | Федеральное государственное казённое военное учреждение высшего профессионального образования "Военная академия материально-технического обеспечения имени генерала армии А.В. Хрулева" Министерства обороны Российской Федерации | A device for checking thermometers at a point of 1000C in boiling water vapor |
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-
2019
- 2019-03-27 WO PCT/EP2019/057752 patent/WO2019185736A1/en active Application Filing
- 2019-03-27 EP EP19712237.7A patent/EP3776529B1/en active Active
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- 2019-03-27 AU AU2019241452A patent/AU2019241452B2/en active Active
- 2019-03-27 US US17/042,684 patent/US20210199284A1/en active Pending
- 2019-03-27 BR BR112020019905-2A patent/BR112020019905A2/en active Search and Examination
- 2019-03-27 CN CN201980022861.0A patent/CN112074897A/en active Pending
- 2019-03-27 CA CA3094256A patent/CA3094256A1/en active Pending
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CA3094256A1 (en) | 2019-10-03 |
JP2021519409A (en) | 2021-08-10 |
US20210199284A1 (en) | 2021-07-01 |
RU2020131058A3 (en) | 2022-04-29 |
JP7401516B2 (en) | 2023-12-19 |
TW201941839A (en) | 2019-11-01 |
TWI803607B (en) | 2023-06-01 |
AU2019241452A1 (en) | 2020-10-15 |
EP3776529C0 (en) | 2023-06-07 |
CN112074897A (en) | 2020-12-11 |
WO2019185736A1 (en) | 2019-10-03 |
KR20210020870A (en) | 2021-02-24 |
AU2019241452B2 (en) | 2024-05-30 |
RU2020131058A (en) | 2022-04-29 |
BR112020019905A2 (en) | 2021-01-05 |
EP3776529B1 (en) | 2023-06-07 |
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