Apparatus and method for generating high amplitude pressure waves

Abstract

A device for generating high-amplitude pressure waves, in particular for cleaning boilers, comprising: a pressure-resistant container (21, 40) having a combustion chamber (121) inserted therein, which can be filled with a combustible flowable material via a supply line. The pressure-resistant container has a discharge opening (306) for the directed discharge of the gas pressure generated by the ignition of the combustible material. A piston (70) closes the discharge opening, which can open the discharge opening for directed discharge and return to the starting position by a spring device. With respect to the longitudinal direction (305) of the piston, the seat of the piston (70) has a piston face (302), which is inclined in an inclined manner relative to the discharge opening (306) and is arranged opposite to a housing face (303), which is also inclined in an inclined manner relative to the discharge opening (306), wherein the housing face (303) is open at an angle (304) relative to the piston face (302), which angle is oriented toward the discharge opening (306) starting from a closing line (65) oriented perpendicular to the piston direction (90).

Description

Technical Field

[0001] The present invention relates to an apparatus and a method for generating high amplitude pressure waves, and in particular to an apparatus and a method for cleaning boilers. Background Art

[0002] Such a device for generating high-amplitude pressure waves is known from US 5,864,517. The acoustic oscillations generated by the device are significantly stronger than those generated by a loudspeaker. The acoustic oscillations can be used in particular for boiler cleaning, since these pressure waves can cause adhering particles to detach. In the case of US 5,864,517, two different impulse combustions are discussed, namely detonation and deflagration. Detonation combustion has a very fast flame speed of 2,000 m / s to 4,000 m / s, while deflagration combustion has a much slower flame speed of, for example, less than 200 m / s, and the amplitude of the pressure wave is significantly lower.

[0003] EP 2 319 036 relates to a method and a device for generating an explosion, in particular a high-intensity pressure pulse. The device comprises a pressure-resistant container having a main explosion chamber as described in the above-mentioned US patent, which has an outlet for the pressure pulse and a piston that closes the outlet. The piston is displaced in the position of the piston by an auxiliary explosion in an auxiliary explosion chamber so that the piston opens the outlet opening. The process 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 already pushed back piston and pushes the piston back to its initial position after the gas has been blown out of the main explosion chamber.

[0004] Another method and device for generating an explosion is shown in EP 1 922 568. The gas spring mechanism has a pressure relief mechanism which is shown as a spring mechanism.

[0005] A method and device for generating explosions for cleaning by means of acoustic emission are also disclosed in Tibor Horst Füle's article “Cleaning technologies with sonic horns and gas explosions at the waste-fired power plant in Offenbach (Germany), cleaning with sonichorns and gas explosions at the waste-fired power plant Offenbach”, VGB Powertech, Vol. 93, No. 8, August 1, 2013, pages 67 to 72, ISSN; 1435-3199.

[0006] Furthermore, FR 2,938,623 shows an explosion cylinder having a piston which is movable between an open position and a closed position to cause periodic explosions of gas or air under pressure for cleaning purposes. Summary of the invention

[0007] Based on this prior art, the object of the present invention is to specify an improved device and method which can be ignited more easily and more safely.

[0008] Furthermore, it is an object of the invention that the device provides long maintenance intervals, since explosions lead to considerable wear of movable parts in pressure vessels and in the prior art only a limited number of cleaning ignitions can be repeated before the device has to be maintained. Since in power plant engineering, primary industry and process chemistry these processes are often carried out in complex chemical plants, a large number of such devices for generating high-amplitude pressure waves are usually provided for cleaning various vessels, which then have to be maintained accordingly.

[0009] The device is preferably used for cleaning boilers in large technical plants such as waste incineration plants, coal-fired power stations, silos, for removing slag or sediments, etc. The main advantage is that each cleaning cycle can be repeated very quickly and performed several times. In addition, it is relatively cheap to use gas as a cleaning material to produce a certain order of pressure waves and associated pressure pulses, and high pressure can be generated. At the time point just before the pressure wave is triggered, adding two chemical fluids that do not burn or explode themselves can also improve safety. Since the reaction material is exposed to a hot environment for a long time, it can also be cleaned when the device is still hot and may still be in operation.

[0010] The pressure waves generated can be guided into the boiler via a longer-distance tube to the location to be cleaned. The tube can be fixed to the equipment to be cleaned, but it can also be inserted from the outside, for example in a telescopic manner, into the equipment or boiler. The pressure pulses generated during burnout blow away deposits and dirt from the inner tubes in the boiler and the boiler wall and at the same time cause the tubes or walls to vibrate. Both actions allow the equipment to be cleaned to be effectively cleaned.

[0011] Various other uses are conceivable where high, rapid force pulses, pressure pulses or pressure waves with high intensity and / or (fast) repeatability are required. Examples are pressure generators for sheet metal forming or drives for firearms, where the pressure pulses are used to accelerate projectiles. Such systems can also be used in the field of controlled avalanche-like triggering.

[0012] The device for generating high amplitude pressure wave, in particular the device for cleaning boiler, has a pressure vessel. The pressure vessel can be multi-piece. The pressure vessel has at least one combustion chamber arranged inside it. Several combustion chambers can be connected to each other. At least one ignition device extending into one or more combustion chambers is provided. At least one supply line for supplying a flowable combustible material to the combustion chamber should be provided, and the at least one supply line preferably supplies fuel and oxidant separately, such as natural gas and air or methane and oxygen. Various other liquid or gaseous fuels can also be used here. In this case, the pressure vessel should have a discharge opening for directional opening of the gas pressure generated by the ignition of the combustible material in the combustion chamber. Before and during ignition, there is a closing mechanism for closing the discharge opening, which is designed to open the discharge opening for directional discharge, and then after combustion, the closing mechanism can be moved to the initial position by a spring device. The closing mechanism is a piston, which can be displaced in the longitudinal direction of the piston, and the piston has a rear section aligned in the direction of the spring device and a front section aligned in the direction of the discharge opening.

[0013] Relative to the longitudinal direction of the piston, the seat of the piston has a piston face which is inclined in a manner inclined relative to the discharge opening, and the piston face is arranged opposite to a housing face which is also inclined in a manner inclined relative to the discharge opening, so that the housing face is open at a certain angle relative to the piston face, which is oriented from a closing line oriented perpendicular to the piston direction toward the discharge opening.

[0014] The angle may be between 0.5 and 5 degrees, preferably between 1 and 3 degrees, in particular 2 degrees.

[0015] A closure line oriented perpendicularly to the piston direction can be located in the piston wall of the lower section, so that a rounded static pressure opening surface is present between the closure line and the piston wall.

[0016] The flange surface perpendicular to the piston axis, connected to the combustion chamber or belonging to the combustion chamber, can have a surface dimension that is between 50 and 200 percent of the surface dimension given by the surface dimension of the piston surface.

[0017] A transition region can be provided between the two sections. The front section is located in the region of the combustion chamber in the case of a piston position that closes the discharge opening. With respect to the longitudinal direction of the piston, the front section tapers relative to the rear section, so that the transition region forms an active surface oriented transversely to the longitudinal direction of the piston, on which the pressure driving the piston back is applied when the combustible material ignites, so that the front section of the piston opens the discharge opening. This makes cleaning simpler, since a pressure buildup can also be achieved by combustion, and the pressure itself is then responsible for opening the passage to the discharge funnel.

[0018] The transition region can be a region that tapers continuously from a larger piston diameter to a smaller piston diameter in the longitudinal direction of the piston of the gas spring, which region is located in the region of the combustion chamber. On the other hand, the transition region can also be formed by a flange-like taper of the piston.

[0019] In particular, a hollow central guide column can be arranged in the pressure-resistant container, which guides the piston in its interior in the front region. This has advantages with regard to wear of the piston guide, since it enables guidance on a more distant section of the piston. In this case, at least one connecting gap is provided between the combustion chamber and the auxiliary pressure chamber, and the at least one connecting gap is provided in the region of the flange-like taper of the piston.

[0020] The combustion chamber can be arranged annularly around the piston and around the longitudinal axis of the piston. In particular, the annular wall of the combustion chamber can then be stacked annular segments connected in a sealed manner, which are advantageously closed at the top and bottom by a cover plate and a base plate. The height and volume of the cylindrical combustion chamber can thus be scaled in a simple manner, since it is not necessary to provide special combustion chambers of different sizes. A single piston, which is correspondingly adjusted in length, then belongs as a closed unit to this scaled combustion chamber.

[0021] At least two combustion chambers can be arranged radially with respect to the central axis in a plane at an angular distance from one another. In particular, the two combustion chambers can be arranged diametrically opposite one another. The longitudinal axis of the gas spring then coincides with the central axis; the three combustion chambers can then have an angular distance of 120 degrees in a common plane. Alternatively, the longitudinal axis of the gas spring also lies in the plane with the at least two combustion chambers, so that for the three combustion chambers an angular distance of 90 degrees between the individual elements is possible.

[0022] The discharge opening usually has a tube with a tube longitudinal direction. In this case, the tube longitudinal direction can coincide with the central axis, i.e. the discharge opening is in the extension of the piston or the longitudinal axis of the gas spring is located in the plane of at least two combustion chambers. In this case, for example in the case of two combustion chambers, an angular distance of less than 120 degrees can also be provided between the two combustion chambers, so that the two combustion chambers are more aligned with the outlet opening.

[0023] The gas spring can have a front gas spring chamber space opposite to the piston and a rear gas spring chamber space separated from the front gas spring chamber space by a partition wall, wherein a first connection piece serving as a return connection piece and a second connection piece having a check valve are present between the front gas spring chamber space and the rear gas spring chamber space, wherein the check valve is arranged so as to allow the medium to flow unimpeded from the front gas spring chamber into the rear gas spring chamber, but substantially blocks the medium from flowing out of the rear gas spring chamber in the opposite direction.

[0024] A first connection piece and a second connection piece can be arranged in the partition wall. On the other hand, the second connection piece can have at least two sub-connectors, which on the one hand open laterally to each other in the wall of the gas spring in the front gas spring chamber space in the longitudinal direction of the piston movement and on the other hand terminate in the rear gas spring chamber space so that the openings are covered sequentially in time when the piston enters the front gas spring chamber space, and each of the sub-connectors has its own non-return valve. As a result, the individual non-return valves are closed sequentially, so that the medium flow from the front gas spring chamber to the rear gas spring chamber is slowed down, i.e., the braking effect is reduced due to the increased gas pressure in the front gas spring chamber.

[0025] The second connection piece may have a controllable non-return valve, which may optionally have a control valve and a non-return valve connected in series, which controllable non-return valve is connected to a control unit, by which the ignition can be triggered, wherein the control unit is designed to open the controllable non-return valve at a first predetermined time interval after the ignition of the flowable combustible material. This ensures that the combustion in the combustion chamber is completed before the piston is allowed to move back further.

[0026] The first connection element may include a controllable return valve, which may optionally have a control valve and a return flow guide connected in series, which controllable return valve is connected to a control unit, by which the ignition can be triggered, wherein the control unit is designed to open the controllable return valve at a second predetermined time interval after the opening of the controllable non-return valve. As a result, the return flow can be activated with a delay in time after the opening of the controllable non-return valve and thus after the pressure balance between the front gas spring pressure chamber and the rear gas spring pressure chamber has been achieved, i.e., the closing movement of the piston can be triggered with a delay in time, so that the combustion gases still under pressure completely leave the combustion chamber.

[0027] It is also possible to provide two gas spring gas connections separately for the front gas spring chamber and the rear gas spring chamber, wherein the control unit has a gas filling control unit, by which the gas filling pressure in the front gas spring chamber and the rear gas spring chamber can be set to a predetermined value before ignition, wherein the gas filling pressure in the front gas spring chamber can be set higher than the gas filling pressure in the rear gas spring chamber. In particular, 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 the gas filling pressure in the rear gas spring chamber, so that on the one hand the front gas spring pressure chamber does not recede or only recedes slightly during ignition, because the prevailing pressure in the front gas spring pressure chamber during ignition is opposite to the pressure established in the combustion chamber, and the receding only occurs completely and quickly when the non-return valve opens, because the gas pressure difference has already been set. In particular, in the rear chamber, the atmospheric pressure can prevail, while only the front gas spring pressure chamber is pressurized with inert gas.

[0028] In order to solve the above-mentioned problems, an improved device and method that can ignite more simply and safely are described, specifying a device for generating high-amplitude pressure waves, in particular for cleaning boilers, which device has: a pressure-resistant container, the pressure-resistant container having a combustion chamber placed in the pressure-resistant container and at least one ignition device extending into the combustion chamber; at least one supply pipeline for supplying flowable combustible material to the combustion chamber, wherein the pressure-resistant container has a discharge opening for directed discharge of gas pressure generated by ignition of the combustible material in the combustion chamber and a closing mechanism for closing the discharge opening, the closing mechanism is designed to open the discharge opening for directed discharge, and the closing mechanism can be moved to In the initial position, it is characterized in that the closing mechanism is a piston that can be displaced in the longitudinal direction of the closing mechanism, and the piston has a rear section oriented in the direction of the spring device and a front section oriented in the direction of the discharge opening, the front section being arranged in the region of the combustion chamber when the piston is in a position that closes the discharge opening, and the seat of the piston has a piston face relative to the longitudinal direction of the piston, which is inclined in an inclined manner relative to the discharge opening, and a housing face is arranged relative to the piston face, which is also inclined in an inclined manner relative to the discharge opening, wherein the housing face is open at a certain angle relative to the piston face, which angle is oriented from a closing line oriented perpendicularly to the piston direction toward the discharge opening. Here, the angle is advantageously between 0.5 degrees and 3 degrees, in particular 1 degree. The closing line oriented perpendicularly to the piston direction is advantageously located in the piston wall of the lower section, so that there is a rounded static pressure opening face between the closing line and the piston wall. The device also has the following characteristics: relative to the rear section, the front section tapers relative to the longitudinal direction of the piston. The taper relates to the inner piston seat wall and then preferably has an opposite outer housing valve seat wall which opens inwardly at a small angle towards the outlet.

[0029] Further embodiments are given in the dependent claims. BRIEF DESCRIPTION OF THE DRAWINGS

[0030] The preferred embodiments of the present invention are described below according to the accompanying drawings, which are only for illustrative purposes and should not be interpreted restrictively. The accompanying drawings show:

[0031] Figure 1 A schematic perspective view showing an apparatus for generating high-amplitude pressure waves according to an embodiment of the present invention;

[0032] Figure 2 Show according to Figure 1 A schematic diagram of the device;

[0033] Figure 3 A lateral, not-to-scale, cross-sectional view of a device for generating pressure waves with its components which are essential to the invention;

[0034] Figure 4A , Figure 4B & Figure 4C Three superimposed cross sections are shown through the Figure 3 Three horizontal sections of the equipment;

[0035] Figure 5 Show according to Figure 3 A schematic detailed view of the piston between lines IVb and IVc;

[0036] Figure 6 is a schematic perspective view of another apparatus for generating high-amplitude pressure waves according to an embodiment of the present invention;

[0037] Figure 7 Is based on Figure 6 A schematic cross-sectional view of a vertical cross-sectional axis of a device;

[0038] Figure 8 Is based on Figure 6 A schematic cross-sectional view of a device with a horizontal cross-sectional axis;

[0039] Fig. 9 is a schematic perspective view of another apparatus for generating high-amplitude pressure waves according to an embodiment of the present invention;

[0040] Fig.10 Is based on Fig. 9 A schematic cross-sectional view of a vertical cross-sectional axis of a device;

[0041] Fig.11 is a schematic cross-sectional view with a vertical cross-sectional axis according to the device, the device having a portion according to Figure 6 and according to Fig. 9 Features;

[0042] Fig.12 It can be used according to Figure 1 , Figure 6 , Fig.10 or Fig.11 A schematic cross-sectional view of a vertical cross-sectional axis of an embodiment of a gas spring in a device of FIG. 1 ;

[0043] Fig.13 is to be used according to Figure 1 , Figure 6 , Fig.10 or Fig.11 A schematic cross-sectional view of a vertical section axis of another embodiment of a gas spring in a device of FIG. 1 ;

[0044] Fig.14is a schematic partial view of a middleware of a device according to another embodiment of the present invention, which middleware can also be used for Figure 2 , Figure 3 , Figure 7 , Fig.10 and Fig.11 middle;

[0045] Fig.15A , Fig. 15B and Fig. 15C yes Fig.14 A detailed view of the different open cycle times; and

[0046] Fig.16 is a graph of force versus time for an embodiment of a valve seat of an apparatus for generating high amplitude pressure waves. DETAILED DESCRIPTION

[0047] Figure 1 A perspective view of a device for generating high-amplitude pressure waves according to an embodiment of the invention is shown. 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. In this embodiment, these containers 21 and 22 extend substantially parallel to the boiler wall 5 shown partially. In addition, a discharge funnel 61 with a downstream discharge pipe 62 is connected to the central body 30 in a flanged manner, the discharge pipe protruding through the boiler wall 5 and terminating in a discharge opening 63 located in the boiler interior space 15. In other embodiments, the discharge opening 63 can also be located directly on the boiler wall, and the discharge pipe 62 can be designed to be shorter than the discharge funnel 61 or completely omitted. On the opposite side of the discharge funnel 61, the gas spring pressure body 40 is connected to the central body 30 in a flanged manner. In the lower region of the lower central body 30, a first gas supply container 51 and a second gas supply container 52 located on the opposite side are arranged on the left and right sides. In other embodiments, the configuration of containers 21 and 22 may be longer, ie, the aspect ratio of the internal volume 121 and the internal volume 122 is between 5:1 and 20:1.

[0048] Now combine Figure 1 and Figure 2 A schematic diagram of the device is shown to describe the function of the device for generating pressure waves. Figure 2 The schematic diagram shows Figure 1 The left and right pressure vessels 21 and 22 are arranged on the central body 30, and the pressure vessels 21 and 22 respectively have a first combustion chamber 121 and a second combustion chamber 122. In this embodiment, the pressure tanks 21 and 22 are cylindrical, and the pressure tanks 21 and 22 have an inner space with a larger diameter in a cylindrical shape in the rear area, that is, there is a channel taper toward the central body 30.

[0049] In the central body 30, a piston 70 is arranged, which will be shown in more detail in the following figures, and which in the closed state shown separates the chambers 121 and 122 in front of each other and closes the outlet by its front end 72 facing the discharge funnel 61. The piston 70 protrudes into the gas spring pressure body 40 with its upper part 71, as shown in FIG. Figure 3 The valve seat itself is marked with reference numeral 300. This can be particularly Fig.14 as well as Fig.15A , Fig. 15B , Fig. 15C to design the detailed view in order to subsequently produce Fig.16 The effect shown in .

[0050] The purpose of the device for generating high-amplitude pressure waves is to generate high-amplitude pressure waves in the first pressure chamber 121 and the second pressure chamber 122 by burning a fluid fuel or an explosive. The fuel is preferably formed by mixing components which are themselves non-flammable or non-explosive and which are stored in a first gas storage container 51 and a second gas storage container 52. These gas reservoirs 51 and 52 are supplied from corresponding gas interfaces 57 and 58 via external gas supply lines 53 and 54, which are controlled via external gas supply valves 55 and 56. The first gas storage container 51 is connected to the combustion chamber 121 and the combustion chamber 122 via a first gas filling line 151 and a first gas filling valve 153 connected in the middle. If a corresponding compensation line is provided between the first combustion chamber 121 and the second combustion chamber 122, then Figure 2 The illustration of being connected to only one combustion chamber 121 is also possible. Correspondingly, for the second gas interface 58, the second gas storage container 52 is directly or indirectly connected to the combustion chamber 121 and the combustion chamber 122 via the second gas filling pipeline 152 and the second gas filling valve 154. The design shown corresponds to filling the combustion chamber 121 and the combustion chamber 122 via two metering tanks, which then flow into the device. Otherwise, the device can also be filled directly via the orifice.

[0051] Furthermore, a gas spring gas interface 47 is provided, wherein the gas for the gas spring 40 is introduced into the gas spring interior 41 or the gas spring interior 42 via a gas spring supply valve 48 and a gas spring supply line 49, such as Figure 3 As shown in .

[0052] In this embodiment, a first gas and a second gas are mentioned. The first gas may be, for example, methane or natural gas, and the second gas may be oxygen or air or an air mixture containing oxygen. In other embodiments, the flowable combustible material may be an explosive mixture, which may be gaseous, liquid, powder, or a mixture of these materials.

[0053] In addition, the combustion chamber 121 and the combustion chamber 122 are connected to an ignition device, which triggers the ignition of the combustible materials in the combustion chamber 121 and the combustion chamber 122 at the same time. Figure 6 If an annular gap is provided as in the embodiment of the present invention, i.e. if two volume connections of the combustion chamber 121 and the combustion chamber 122 are provided, only one ignition device is required. Furthermore, a glow plug or a spark plug can be used as the ignition device. By strengthening the ignition with the aid of a spark plug, the reaction speed can be increased, and a spark plug has a higher ignition energy than a glow plug. As a result, a faster pressure increase occurs in the combustion chamber 121 and the combustion chamber 122.

[0054] When ignition is triggered, a controlled combustion or controlled explosion of the combustible or explosive mixture components occurs in the combustion chambers 121 and 122, which exerts pressure on the piston 70 and there in particular on the intermediate region 75, as will be combined Figure 3 This results in a movement of the piston 70 in the longitudinal direction of the piston 70 against the pressure of the gas spring 40 , while this movement causes the connection between the combustion chambers 121 and 122 and the exhaust funnel 61 to open quickly.

[0055] Prior to this, the outlet opening of the pressure-resistant container is kept closed by the piston 70 as a closing mechanism. The gas spring allows the closure to remain closed even against the filling pressure of the combustible elements in the combustion chambers 121 and 122. Only when the pressure increases in the event of ignition of the flowable mixture does the pressure on the intermediate region 75 increase so that the piston 70 is pushed back accordingly. Subsequently, as will be combined Figure 3 As described, then, after burnout, the gas spring element also causes the piston 70 to be pushed back as a closing mechanism and allows the process to be repeated directly by refilling chambers 121 and 122. At the same time, the contents of the boiler are reliably prevented from flowing back into the device.

[0056] The piston 70 opens so quickly that the pressurized mixture in the combustion chamber 121 and the combustion chamber 122 is not yet completely burned when it escapes, so that the gas mixture in the discharge funnel continues to burn, thereby generating a pressure pulse with a high pressure peak. When air is used as one of the two media other than CH4 or natural gas, a chemical reaction occurs inside the combustion chamber 121 and the combustion chamber 122, and all energy is converted in the device. Then, after the initial pressure increase, the gas is released into the atmosphere by the subsequent, i.e. time-delayed, rapid opening of the piston 70.

[0057] Figure 3 A schematic illustration of a device for generating pressure waves is shown in a lateral section with its components which are essential to the present invention.

[0058] The first pressure-resistant container 21 and the second pressure-resistant container 22 are adjacent to a discharge funnel 61 inserted therein, the discharge funnel 61 having a rounded valve seat contact portion 65 at its inner end. The front end 72 of the piston 70 adjoins the valve seat contact portion 65, the valve seat contact portion 65 being designed as a horizontal, substantially circular contact line extending perpendicularly and concentrically to the piston longitudinal axis 90, the front end 72 being followed by a tapered piston region 73. The tapered piston region 73 is adjoined by a piston transition region 75, at which the diameter of the piston increases so as to have a larger diameter at the rear end of the piston 71. Therefore, the rear piston diameter 171 is designed larger relative to the front piston diameter 172, in particular, the piston 70 has a surface 91 in its longitudinal direction (as shown in FIG. 4), which has a size sufficient to move the piston in the direction of the gas spring 40 during ignition. The diameter and height of the cavity of the gas spring 40 can be selected to be larger relative to the combustion chambers 121 and 122. The piston 70 is sealed between the wall of the left pressure-resistant container 21 and the wall of the right pressure-resistant container 22 along the longitudinal direction of the piston 70 by a series of seals 81 and seals 82, wherein three seals 81 may be bronze seals, and the seals 82 disposed between the three seals 81 are O-rings. These seals 81 and 82 are embedded in grooves in the piston 70; these seals 81 and seals 82 may also be disposed in opposite walls.

[0059] The piston thus passes through the central body 30 in a sealed manner together with the pressure-resistant containers 21 and 22, and the piston 70 then protrudes in a sealed 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 wall 43. A non-return valve 44 and a gas return opening 45 are arranged in the gas spring partition wall.

[0060] The function of the gas spring is as follows. The two components of the combustible gas mixture are supplied to chambers 121 and 122 through gas filling lines 151 and 152. These gases are Figure 3 The ignition device (not shown in the illustration) ignites. As a result, a pressure is exerted on the transition region 75, which overcomes the gas spring pressure held against it and moves the piston 70 into the region of the front gas spring chamber 41. In order to ensure that this movement is sufficiently fast, a non-return valve 44 is arranged in the partition wall 43, which opens immediately and quickly equalizes the gas pressure between the front gas spring chamber 41 and the rear gas spring chamber 42, so that after the initial strong movement of the piston 70, this movement is braked by the increased resistance from the combined gas spring chamber 41 and gas spring chamber 42. After the piston 70 is pushed back in the direction of the partition wall 43, the combustible gas escapes from the exhaust funnel 61 in a burning or still burning form and reduces the pressure in the combustion chambers 121 and 122. Since the valve in the gas spring partition wall 43 is a non-return valve 44, the gas spring chambers 41, 42 are only connected via the gas return opening 45, which has a much smaller diameter. This then forces the gas of the gas spring to squeeze from the rear gas spring chamber 42 back into the front gas spring chamber 41 and pushes the piston 70 into its initial position, as shown in FIG. Figure 3 Any gas loss is compensated by the gas spring supply line 49. The gas in the gas spring 40 can be air or an inert gas such as N2.

[0061] FIG. 4 shows three cross-sectional views, FIG. 4a, FIG. 4b and FIG. 4c, stacked one on top of the other, respectively along the intersection lines IVa, IVb and IVc through the Figure 3 The piston 70 advantageously has a circular cross section.

[0062] FIG. 4 a shows a cross section through the upper wall 21 , 22 of the pressure vessel along the line IVa, wherein the bronze seal 81 around the rear region 71 of the piston 70 is shown.

[0063] 4 b shows parallel sectional planes in and through the combustion chambers 121 , 122 , wherein the sectional planes are sections taken along line IVb in the upper part of the space of the combustion chambers 121 and 122 , wherein the piston 70 has a diameter of the rear region 71 .

[0064] FIG4c then shows another section along line IVc, which is parallel to the section of FIG4b in the lower region of the cavity, wherein it can be directly observed that, although the width of the piston 70 in the central chamber region 30 abuts against the wall of the pressure-resistant container 21, 22 and therefore has a constant width over the piston length, the depth in the direction of the longitudinal orientation of the inner chamber 121, 122 is designed to be smaller. Thus, it can be directly observed here that there is a difference between the front piston diameter 172 and the rear piston diameter 171, wherein the term piston diameter here corresponds to the width in the longitudinal direction of the opposite combustion chambers 121, 122.

[0065] Here in all three figures 4a, 4b and 4c the discharge opening 61 is shown below the plane of the drawing. Figure 3 As shown in the figure, the discharge funnel 61 is connected to the combustion chamber 121 as far as possible in the longitudinal direction of the extension on the other side of the central body 30, and as a closing element of the piston 70, it is perpendicular to the combustion chamber 121, so that when the piston 70 is pushed back, the gas mixture can escape directly and straight forward along the longitudinal direction of the entire device.

[0066] It can also be arranged in Figure 1 , Figure 2 or Figure 6 Two, three, four or more combustion chambers in the plane of the combustion chambers 121 and 122, the plane corresponding to Figure 7 The cross-sectional plane 92 of the embodiment of the present invention is 90 degrees from the discharge funnel 61, because in all cases the piston 70 is perpendicular to the mentioned arrangement plane of the combustion chambers and the discharge funnel 61. In the device according to WO 2010 / 025574, the discharge funnel 61 is in the same plane as all the combustion chambers and the discharge funnel 61 can, for example, have the same angular distance to all the combustion chambers. In the case of three combustion chambers, at 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 significantly.

[0067] Figure 5 An enlarged section through a transition region 75 of a piston 70 is shown.

[0068] It can be observed here that, starting from the longitudinal axis 90 of the piston, there is a first diameter 121 which is smaller than the rear piston diameter 171. Thus, the transition region 75 forms two rectangular strips 91 in a cross section projected along the longitudinal axis 90, which serve as pressure transmission strips. When filling the combustion chambers 121 and 122, the pressure applied to these strips 91 is not enough to push the piston 70 back against the gas spring pressure. This changes suddenly after the gas mixture is ignited, because a pressure difference of up to 25 to 30 times the filling pressure may occur here, which is then sufficient to push the piston 70 back under the correspondingly adjusted gas spring tension. In an exemplary embodiment, the combustible chamber has a volume between one liter and two liters, where the gas filling pressure can be between 10 bar and 30 bar, for example between 15 bar and 25 bar. The diameter of the annular opening closed by the piston is between 40 mm and 15 mm, in particular between 60 mm and 100 mm, more particularly 80 mm.

[0069] The ignition can be designed in a similar manner to the prior art document WO 2010 / 025574 and can therefore be carried out, for example, electrically or by light ignition.

[0070] Figure 6 A schematic perspective view of another device for generating high-amplitude pressure waves according to an embodiment of the present invention is shown. Throughout the specification, the same features are marked with the same reference numerals. Two pressure vessels 21 and 22 are also arranged on the central body 30, and a gas spring pressure body 40 is arranged perpendicular to the pressure vessels. Gas filling pipelines 151 and 152 lead to the central body 30, and the supply pipeline of the ignition device 50 is shown in the center of the central body 30.

[0071] Now, Figure 7 Shows a cross section with vertical axes according to Figure 6 Schematic cross-sectional view of the device. The piston longitudinal axis 90, which corresponds to the longitudinal axis of the gas spring pressure body 40, intersects the horizontal mid-section plane 92 of the pressure bodies 21 and 22. For simplicity, Figure 7 , the elements of the central body 30 are omitted from the drawing. The pressure-resistant containers 21 and 22 reach the discharge funnel 61 in the lower region, wherein the inner end of the discharge funnel 61 forms a 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, followed by a transition region 75 with an increased diameter, which leads to the rear piston region 71. Here, the piston 70 is hollow. The piston 70 can be two-piece, wherein the lower end can be inserted into the hollow piston 70 to contact the valve seat 65. The valve seat 300 can again be as Fig.14 Designed as shown.

[0072] The rear region of the piston 70 has a sufficient height from the transition region 75 to the upper flat end face of the piston 70 which delimits the lower gas spring chamber space 41, so that even if the piston is pushed back into the front gas spring chamber space 41, the piston 70 will always be in essentially sealing contact with the inner wall of the gas spring 40 via the lower sealing element. Figure 7 In the embodiment of the invention, two bronze guides 81 are provided around the piston 70 and a sealing O-ring 82 is arranged between the guides 81. The guides 81 arranged at a large distance from each other also have a sealing function and, like the O-rings 82, are mounted in corresponding circumferential grooves in the piston 70. In the gas spring partition wall 43, which is substantially perpendicular to the piston longitudinal axis 90, a non-return valve 44 and a gas return opening 45 are provided. The gas return opening 45 can also be referred to as an orifice. A gas spring supply line 47 leads to the rear end of the gas spring chamber 42, with which an inert gas such as nitrogen, CO2 or argon can be filled externally via a gas spring gas interface 49. The gas can also be air if the spring chamber 42 and the spring chamber 42 are sufficiently sealed.

[0073] Figure 8 The cross-sectional plane 92 shows Figure 6 . Here, it can be observed that the piston 70 is arranged at a constant distance from the inner wall of the central body 30 in this middle region and that there is an annular gap 123 extending in the direction 90 of the piston longitudinal axis, the annular gap 123 being designed to balance the pressure between the two combustion chambers 121 and 122. Therefore, in the present embodiment, the gas supply lines 151 and 152 arranged adjacent to each other are sufficient to mix the two gases or fluids for combustion. The glow plug or spark plug 59 is arranged to extend into the annular gap 123, centrally located in the annular gap 123 between the combustion chambers 121 and 122, preferably also at the middle height of the central body, the annular gap 123 being connected to the pipeline 50 of the ignition device. Orifices or metering valves 153 and 154 are provided here for direct filling of the combustion chambers 121 and 122.

[0074] Such an annular gap 123 may also be guided on one side, ie only on one side of spark plug 59 , and such annular gap 123 may also be used in other embodiments having two or more other combustion chambers.

[0075] Fig. 9A schematic stereogram of another device for generating high-amplitude pressure waves according to an embodiment of the invention is shown. Here, a symmetrical arrangement about the longitudinal axis 90 of the piston has been provided. In particular, an annular pressure vessel 25 is provided, to which gas supply lines 151 and 152 lead. The pressure vessel 25 is arranged below the gas spring pressure body 40 via its extension, and the ignition device supply line 50 leads to the interior of the device via a section of the pressure vessel 25 that protrudes beyond the gas spring body. Here, the pressure vessel 25 comprises a cover plate, a bottom plate and a ring here, which are arranged together in a sealed manner. Several rings stacked on top of each other can also be arranged.

[0076] Fig.10 Shows that according to Fig. 9 Schematic cross-sectional view of the vertical cross-sectional axis of the device.

[0077] The gas spring 40 is formed in the same manner as the other embodiments. Compared to these other embodiments that have been used together here, there are two main structural differences. However, in other embodiments not shown in the drawings, only one of the two differences described in the following example can also be combined with other embodiments.

[0078] A first difference from the other embodiments is that an annular combustion chamber 125 is provided which completely surrounds the piston 70. Thus, an annular element of the pressure vessel 25 is provided, in this case three rings, which are arranged in Fig. 9 The spark plug 59 of the ignition device 50 is inserted into the annular combustion chamber 125 in a sealed manner through the upper wall. Fig.10 At another location below the two gas supply lines 151 and 152 are introduced directly. In other words, there are no gas storage containers 51 and 52 as dosing elements. This is controlled by orifices 153 and 154 during filling.

[0079] Other implementations and Fig. 9 and Fig.10The second difference between the embodiments in the embodiment of the invention lies in the design of the piston 70. Here, the projection of the pressure surface 91 of the other embodiments is formed by the lower side 191 of the piston 70, which lower side and the piston inner side delimit an auxiliary pressure space 95. This auxiliary pressure space is adjoined on its lower side by a deflection profiled column 96 which tapers downwards and has a uniform inner diameter, into which the lower section extends by a tapered piston area 173 which is guided relative to the column 96 by two bronze seals 81. When the combustible gas mixture supplied from the pipelines 151 and 152 is ignited by the spark plug 59, the pressure in the annular combustion chamber 125 increases as in the previous examples, wherein here the pressure can expand into the auxiliary pressure chamber 95 via the connecting gaps 126. It is also possible to provide several such gaps 126, preferably at regular angular intervals from one another, so that the deflection profile 96 is fixed to the plate or the gas spring pressure body except for these interruptions realized by the connecting gaps 126.

[0080] Thus, shortly after ignition, the internal pressure of the annular combustion chamber 125 acts on the underside of the rear end 71 of the piston 70 via the face 191 of the piston protruding beyond the core in the auxiliary pressure chamber 95. The pressure exerted on this face 191, which corresponds to the pressure on the projection of the pressure face 91 from the other embodiment, thus moves the piston 70 backwards along its column 96 into the front gas spring chamber 41 via the enlarged auxiliary pressure chamber 95, wherein here also a bronze seal 81 and an O-ring 82 are arranged between the rear end of the piston 71 and the inner wall of the gas spring 40.

[0081] When the piston 70 moves backward, the connection between the annular combustion chamber 125 and the exhaust funnel 61 (not shown here) opens, which is characterized by the distance between the column 96 and the valve seat 65. In this case, the pressure of the combustion or explosion of the medium present in the annular combustion chamber space 125 acts on the retreating piston 70.

[0082] Fig.11 A schematic cross-sectional view of a vertical section axis 90 of a device having the following features is shown: the device partially corresponds to the device according to Figure 6 The device and partly corresponds to Fig. 9 and Fig.10 Those devices.

[0083] Involving basis Figure 1 and Figure 6 The piston 70 of the embodiment is surrounded by an annular combustion chamber 125, such as Fig. 9 and Fig.10. Thus, here the annular gap 123 widens into the annular chamber space 125 and, instead of two opposing combustion chambers 121 and 122, there is only one cylindrical combustion chamber with the piston 70 as the core. Otherwise, the function of pushing back the piston 70 is solved in exactly the same way by the pressure of the combustion gas mixture exerted on the transition region 75. Fig.11 In the diagram, the gas spring pressure body is shown as a one-piece element with a cover of the combustion chamber 125, which is annular (if the inserted piston 70 is regarded as the central element) or in other cases cylindrical. Of course, this can also be several elements connected together in the form of flanges. It is important for the illustration here that the wall surrounding the rear section of the piston 70 has extensions 196 that protrude into the interior space of the combustion chamber 125. These extensions 196, which are designed here as annular, correspond to the extensions from Fig.10 The extension 196 can also be opposite to a corresponding bronze ring 81 embedded in the piston 70. In other words, it is advantageous to guide the piston 70 over a longer length, and this can be achieved by a centrally guided column or by an annular or ring segment-shaped extension 96.

[0084] The piston 70 itself can be designed to be hollow to reduce weight, wherein it is open toward the front in the longitudinal direction 90, or it can also be made of solid material, in particular steel, or it can be hollow and have a plug inserted from the front, in particular a plug screwed in. The piston 70 can also form a sealing surface for the valve seat 65.

[0085] Fig.12A schematic cross-sectional view of a vertical section axis 90 of another embodiment of a gas spring 140 is shown, wherein the wider area of ​​the device with piston 70 and spark plug 59 as well as the combustion chamber and exhaust funnel not shown here can be designed similarly or identically. The main difference from the gas spring 40 is the external bypass of the non-return valve 44 outside the pressure body and the external bypass of the gas return opening 45 outside the pressure body. Therefore, both are not guided inside the gas spring partition wall 43 between the two chambers 41 and 42, but have external valves 144 and external valves 145. These openings or control valves 144 and 145 are connected to a control line marked with 150, which is also connected to the ignition device. Here, the pipeline 150 does not represent a direct electric line or other direct electrical control line, but rather schematically represents the transmission of control signals from a control unit not shown in the figure to the spark plug 59 and valves 144 and valves 145, so that these switching elements have a corresponding time delay. After ignition, 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 the rapidly increasing pressure in the front gas spring chamber 41 and to quickly achieve pressure balance with the rear gas spring chamber 42 after opening. Here, the valve 145 for the return opening 45 is closed. The valve 145 can also be opened in advance, since the valve 145 only allows a small amount of gas to pass in the opposite direction. Thereafter, when all the gas has burned out and the pressure from the chambers 41 and 42 should therefore drive the piston back, the orifice 145 is opened and the valve 144 is closed. With such a controlled valve, it is also no longer necessary to design the elements 44 and 45 as non-return valves or orifice plates; the elements 44 and 45 can also be simple pipelines.

[0086] at last, Fig.13 A further schematic cross-sectional view with a vertical section axis 90 of a further embodiment of a gas spring 240 is shown, which can likewise be inserted, for example, according to Figure 1 , Figure 6 , Fig.10 or Fig.11In the device. Here, the non-return valve 244 is quadruple, and the gas return opening 45 is located in the gas spring intermediate wall 43, as in other embodiments. The arrangement of the four non-return valves 244 connected to the rear gas spring chamber space 42 via corresponding separate pipelines 243 creates an additional function of cooperating with the retracting piston 70. The arrangement of the separate openings 246 of the four non-return valves 244 is arranged at a certain interval along the piston longitudinal axis 90 to overlap each other (not necessarily directly overlap each other, but can also be laterally offset from each other at a certain angular distance), so that the retracting piston 70, which gradually moves from below, interrupts the openings 246 one by one, and thus interrupts the connection from the connecting piece between the front gas spring chamber 41 and the rear gas spring chamber 42 to the non-return valve 244. Therefore, as the piston stroke increases, that is, as the piston 70 moves back into the gas spring 240, the gas pressure compensation between the front spring chamber 41 and the rear spring chamber 42 via the check valve 244 gradually decreases, resulting in a softer braking of the piston 70 in the front gas spring chamber 41 without the need for more complex valve control. The closing of the check valve 244 is purely mechanical.

[0087] Combined with the above Figures 1 to 13 All embodiments shown in the embodiments may additionally or exclusively be designed with a combination of Fig.14 The valve seat 300 described herein has the function of passing through FIG. 15A to FIG. 15C is illustrated in a detailed view of a cross section of the valve seat 300, and Fig.16 Measured results of the force curve acting on the piston 70 over time are shown in FIG.

[0088] Fig.14 A cross-sectional view of the outer wall 172 of the piston 70 is shown with an embodiment of the valve seat 300 having other features. Fig.14 The outer wall of the exhaust funnel 61 abuts against the opposite wall of the gas spring pressure body 40; the outer wall may also abut against the guide column 96. In this case, the valve seat 300 is supported downward by the mating surface of the exhaust funnel 61. Between the exhaust funnel 61 and the gas spring pressure body 40 is an opening to the first combustion chamber 121. Instead of the upper part of the exhaust funnel 61, there may also be a defined mating surface, which is assigned to the pressure vessels 21, 22, for example. Fig.14 The upper piston end is closed by a 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 arranged. This design can be used for Figure 2 , Figure 3 , Figure 7 , Fig.10 , Fig.11 Here is shown an embodiment similar to Fig.10 of an embodiment of an embodiment, in Fig.10 In the embodiment, an auxiliary pressure chamber 95 is provided, wherein the flange surface 191 is a pressure surface for moving the piston 70 .

[0089] A line 301 is drawn on the valve seat 300 indicating the distance from the side wall of the piston diameter 172. This is the distance belonging to the bend R2, which is the distance from the side wall 172 to the inner piston seat wall 302, which can be FIG. 15A to FIG. 15C This inner piston seat wall 302 is opposite to the outer or housing-side valve seat wall 303. It is important here that the two walls 203 and 303 are substantially at an angle of about 45 degrees to the piston movement axis 305, in other embodiments not shown, at an angle of between 30 and 60 degrees, and that the two walls 203 and 303 are not parallel to each other but at an angle 304, which is at an angle of about 45 degrees to the piston movement axis 305. Fig.14 In the embodiment of the present invention, 1 degree is specified, but it can also be formed between 0.5 degrees and 5 degrees, especially between 1 degree and 3 degrees.

[0090] The apex 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 and at which the external exhaust funnel chamber 306 is closed in the form of a ring from the first combustion chamber 121 (shown here), but of course also relative to the second combustion chamber 122, with the opposite outer shell-side wall 303.

[0091] This design of valve seat 300 is based on the piston Fig.15A (starting at 0.5mm), Fig. 15B (Open 1mm), Fig. 15C The time sequence of the explosive opening in the (2 mm clear channel) is shown, where reference Fig.16 Arrows 311, 312, 313, 314 and 315 are Fig.14 and Fig. 15C (Due to space conditions, only Fig. 15C ). These arrows represent the entire surface on which they are located. If present, these arrows are the optional pre-chamber surface 311, the static auxiliary surface 312, the dynamic auxiliary surface 313, the piston inner surface 314 and the gas spring surface 315 which is completely opposite to all these surfaces.

[0092] The optional pre-chamber surface 311 is an extension of the flange in the auxiliary chamber pressure cavity 95. The static auxiliary surface 312 is formed by Fig.14The curved surface formed by the distance 301 in the hollow piston and the radius R2 corresponding thereto at the front piston end, then in a mathematical sense, the curved surface smoothly transitions into the inner piston seat wall 302. The dynamic auxiliary surface 313 is so specified because the two walls 302 and 303 are deviated from each other in the direction of the discharge funnel cavity 306 by the angle 304, and therefore the surface develops dynamically. Here, the arrows 313 should be drawn in the order starting from the inner edge to close to the arrow 312. Finally, the inner surface 314 is drawn in the recess of the hollow piston, but it can also be drawn at the lower end of the piston. The gas spring surface 315 is arranged to be exactly opposite to the inner surface 314.

[0093] Fig.16 The force acting on the piston 70 is shown on the Y axis relative to the time on the X axis. The basic effect of the auxiliary pressure chamber 95 and its surface 311 is marked by line 411. Therefore, the surface 511 between the 0 line and the line 411 is a key indicator of the pre-chamber effect surface. The line 412 shows the additional force effect, which is generated by the rounded surface at the arrow 312 and is marked by the surface 512 between the line 411 and the line 412.

[0094] This force increases until the piston 70 lifts off the valve seat at time 520. Then, the dynamic surface 313 comes into play and generates a boost marked by line 413, wherein this effect is marked as an increase in force by the surface 513 located between lines 412 and 413. A moment later and with a slight delay, the reaction of the gas spring 40 comes into play, the force effect of the gas spring 40 being marked by line 415.

[0095] When Figures 15A to 15C The offset gap shown in has been widened to Fig. 15C , the increase in force, referred to as the boost, ends at the point in time when the boost curve 413 reverses at a slightly later point in time 521. This does not mean that there is a 2 mm wide groove here, which depends on the depth of the valve seat, i.e. on the distance from the rounding R2 (described by the line / arrow 301) to the start of the discharge funnel space 306. At the point in time 521, the line 414 separates from the line 413 in the downward region.

[0096] With the corresponding force effects in line 414 and area 415, the emptying of the piston chamber is added in the downward region, wherein in sum the characteristic line 419 is then formed as a bus and oscillates in a rhythm opposite to that of the gas spring line. In summary, the geometry of the valve seat has a positive influence on the opening behavior of the piston. During opening, the narrowest cross section is radially displaced from the outside to the inside, so that a small projected surface is advantageous in the closed state, which prevents accidental opening. In the embodiment shown, the pre-chamber 95 ensures the initial opening at the desired time. However, this can be achieved by arranging the surface 191 in the main chamber space 121 (i.e. without a separate ignition, similar to Fig.10 The auxiliary chamber is replaced by the embodiment in the figure, so that the surface 511 corresponds to the initial ignition of the main chamber.

[0097] Since the narrowest cross section is radially displaced from the outside to the inside, the enlargement of the active surface after the initial opening directly leads to a boosting effect on the piston movement, which is FIG. 15A to FIG. 15C The initial opening movement is shown in FIG.

[0098] Reference numerals list

[0099] 5 Boiler wall 59 Spark plug

[0100] 10 Equipment 61 Discharge funnel

[0101] 15 Boiler internal space 62 Discharge pipe

[0102] 21 Right pressure container 63 Discharge opening

[0103] 22 Left pressure vessel 65 Valve seat contact part

[0104] 25 Annular pressure vessel 70 Piston

[0105] 30 Central body 71 Rear end of piston

[0106] 40 Gas spring pressure body 72 Front end of piston

[0107] 41 Front gas spring chamber 73 Tapered piston area

[0108] 42 Rear gas spring chamber 75 Piston transition area

[0109] 43 Gas spring partition 81 Bronze seal

[0110] 44 Check valve 82 O-ring

[0111] 45 Gas return opening 90 Longitudinal axis of piston

[0112] 47 Gas spring gas connection 91 Projection of the pressure surface

[0113] 48 Gas spring supply valve 92 Horizontal plane

[0114] 49 Gas spring supply line 95 Auxiliary pressure chamber

[0115] 50 Ignition equipment 96 Guide column

[0116] 51 first gas storage container 121 first combustion chamber

[0117] 52 Second gas storage container 122 Second combustion chamber

[0118] 53 First external gas supply line 123 Combustion chamber annular gap

[0119] 54 Second external gas supply line 125 Annular combustion chamber

[0120] 55 First gas supply valve 126 Tapered column

[0121] 56 Second gas supply valve 140 Gas spring

[0122] 57 First gas interface 144 Check valve

[0123] 58 Second gas interface 145 Backflow control valve

[0124] 151 First gas filling pipeline 305 Piston movement axis (open)

[0125] 152 Second gas filling pipeline 306 Exhaust funnel cavity

[0126] 153 First gas filling valve 311 Pre-combustion chamber surface

[0127] 154 Second gas filling valve 312 Static auxiliary surface

[0128] 170 Piston surface 313 Dynamic auxiliary surface

[0129] 171 Rear piston diameter 314 Piston inner surface

[0130] 172 Front piston diameter 315 Gas spring surface

[0131] 173 Tapered piston area 411 Pre-chamber action line

[0132] 175 Piston flange transition section 412 Static surface effect line

[0133] 191 flange surface 413 power assistance line

[0134] 196 Ring guide extension 414 Piston exhaust line

[0135] 240 Gas spring 415 Gas spring action line

[0136] 243 connection pipeline 419 bus

[0137] 246 pipeline port 511 pre-combustion chamber action surface

[0138] 300 Valve seat 512 Static surface

[0139] 301 Line indicating the end of the bend 513 Assisting surface

[0140] 302 Internal piston seat wall 514 Piston exhaust surface

[0141] 303 Valve seat wall on the outer shell side 520 Piston opening time

[0142] 304 Angle 521 between 302 and 303 Passage when the piston seat is open

Claims

1. A device for generating high-amplitude pressure waves for boiler cleaning, the device comprising: a pressure-resistant container having a combustion chamber inserted therein and at least one ignition device extending into the combustion chamber; at least one supply line for supplying a flowable combustible material into the combustion chamber, wherein the pressure-resistant container has a discharge opening for directional discharge of gas pressure caused by ignition of the combustible material in the combustion chamber, and a closing mechanism, the closing mechanism closing the discharge opening, the closing mechanism being designed to open the discharge opening for directional discharge, and the closing mechanism being displaceable to a starting position by a gas spring, It is characterized in that The closing mechanism is a piston that can be displaced in its longitudinal direction, and has a rear section oriented in the longitudinal direction of the gas spring and a front section oriented in the longitudinal direction of the discharge opening, wherein the front section is arranged in the area of ​​the combustion chamber when the piston is in a position to close the discharge opening, and with respect to the longitudinal direction of the piston, the seat of the piston has a piston face that is inclined in an inclined manner relative to the discharge opening, and a housing face is arranged opposite to the piston face, and the housing face is also inclined in an inclined manner relative to the discharge opening, wherein the housing face is open at an angle relative to the piston face, and the angle is oriented toward the discharge opening starting from a closing line oriented perpendicularly to the longitudinal direction of the piston.

2. The device according to claim 1, wherein The angle is between 0.5 degrees and 5 degrees.

3. The device according to claim 2, wherein: The angle is between 1 degree and 3 degrees.

4. The device according to claim 1 or 2, wherein: The closure line, which is oriented perpendicularly to the longitudinal direction of the piston, is arranged in the piston wall of the lower section, so that a rounded static pressure opening surface is present between the closure line and the piston wall.

5. The device according to claim 1 or 2, wherein: A flange surface perpendicular to the piston axis, connected to the combustion chamber or belonging to the combustion chamber, has a surface dimension that is between 50 and 200 percent of the surface dimension given by the surface dimension of the piston surface.

6. The device according to claim 1 or 2, wherein: The combustion chamber is arranged annularly or cylindrically around the piston and around the longitudinal axis of the piston.

7. The device according to claim 6, wherein: The annular wall of the combustion chamber is a series of tightly connected annular segments which are stacked and closed at the top by a cover plate and at the bottom by a base plate.

8. The device according to claim 1 or 2, characterized in that A transition area is arranged between the rear section and the front section, and the front section is arranged in the area of ​​the combustion chamber when the piston is in a position to close the discharge opening. With respect to the longitudinal direction of the piston, the front section is designed to be tapered relative to the rear section, so that the transition area forms an active surface, which is transversely aligned with respect to the longitudinal direction of the piston, and when the combustible material is ignited, the pressure driving the piston back is applied to the active surface, so that the front section of the piston opens the discharge opening.

9. The device according to claim 8, wherein: The transition region is a region which tapers continuously in the longitudinal direction of the piston from a larger piston diameter to a smaller piston diameter and is arranged in the region of the combustion chamber.

10. The device according to claim 8, wherein: The transition region is formed by a flange-like taper of the piston.

11. The device according to claim 10, wherein: A hollow central guide column is arranged in the pressure-resistant container, or an annular guide extension is arranged on the pressure-resistant container leading to the combustion chamber, wherein the hollow central guide column or the annular guide extension guides the piston in the front area inside thereof, and establishes an auxiliary pressure chamber in the rear area of ​​the piston, wherein at least one connecting gap is arranged between the combustion chamber and the auxiliary pressure chamber, and the at least one connecting gap is arranged in the area of ​​the flange-shaped tapered portion of the piston.

12. The device according to claim 8, wherein: At least two combustion chambers are arranged in a plane and have a main longitudinal direction, wherein the main longitudinal directions of two adjacent combustion chambers are arranged radially at a certain angular distance from each other with respect to the central axis of the device, wherein the longitudinal axis of the gas spring coincides with the central axis of the device, or the longitudinal axis of the gas spring is located in the plane of the at least two combustion chambers and has an angular distance from adjacent combustion chambers.

13. The device according to claim 12, wherein: The outlet opening has a tube with a tube longitudinal direction, wherein the tube longitudinal direction of the outlet opening coincides with the center axis or the longitudinal axis of the gas spring lies in the plane of the at least two combustion chambers.

14. The device according to claim 1 or 2, wherein: The gas spring comprises a front gas spring chamber space opposite to the piston and a rear gas spring chamber space separated from the front gas spring chamber space by a partition wall, and a first connection piece as a return connection piece and a second connection piece having a check valve are arranged between the front gas spring chamber space and the rear gas spring chamber space.

15. The device according to claim 14, wherein: The first connection member and the second connection member are disposed in the partition wall.

16. The apparatus according to claim 14, wherein: The second connecting piece has at least two sub-connecting pieces, which on the one hand are stacked one on top of the other and open laterally in the longitudinal direction of the piston movement in the wall of the gas spring in the front gas spring chamber space with orifices, and on the other hand terminate in the rear gas spring chamber space so that the orifices are covered in sequence when the piston enters the front gas spring chamber space, wherein the sub-connecting pieces each have a check valve.

17. The apparatus according to claim 14, wherein: The second connecting member includes a second controllable check valve, which includes a second control valve and a check valve connected in series. The second controllable check valve is connected to a control unit, and the ignition device can be triggered by the control unit, wherein the control unit is designed to open the second controllable check valve at a first predetermined time interval after igniting the flowable combustible material.

18. The apparatus according to claim 17, wherein: The first connecting member includes a first controllable check valve, which has a first control valve and a return guide connected in series. The first controllable check valve is connected to the control unit, and the ignition device can be triggered by the control unit, wherein the control unit is designed to open the first controllable check valve at a second predetermined time interval after opening the second controllable check valve.

19. The apparatus according to claim 17, wherein: Two gas spring gas ports are provided for the front gas spring chamber space and the rear gas spring chamber space, wherein the control unit includes a gas filling control unit, which can be used to adjust the gas filling pressures in the front gas spring chamber space and the rear gas spring chamber space to predetermined values ​​before ignition, respectively, wherein the gas filling pressure in the front gas spring chamber space can be set to be higher than the gas filling pressure in the rear gas spring chamber space.

20. A method for generating high amplitude pressure waves by means of the device for generating high amplitude pressure waves for boiler cleaning according to claim 14, the method comprising the steps in the following order: - filling the front gas spring chamber space and the rear gas spring chamber space with an inert gas, - filling at least one combustion chamber with a flowable combustible material, - igniting said flowable combustible material in at least one combustion chamber, in, After ignition, the piston opens the discharge opening by means of the pressure increased by the combustion of the flowable combustible material and, after the burnt gases have escaped, drives the piston back into the closed initial position.

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