EP4042209A1 - Générateur d'ondes de pression et procédé de fonctionnement d'un générateur d'ondes de pression - Google Patents

Générateur d'ondes de pression et procédé de fonctionnement d'un générateur d'ondes de pression

Info

Publication number
EP4042209A1
EP4042209A1 EP20790036.6A EP20790036A EP4042209A1 EP 4042209 A1 EP4042209 A1 EP 4042209A1 EP 20790036 A EP20790036 A EP 20790036A EP 4042209 A1 EP4042209 A1 EP 4042209A1
Authority
EP
European Patent Office
Prior art keywords
pressure chamber
volume
pressure
opening
outlet
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.)
Pending
Application number
EP20790036.6A
Other languages
German (de)
English (en)
Inventor
Hans Rüegg
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
P Wave Ag
Original Assignee
Explotechnik AG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Explotechnik AG filed Critical Explotechnik AG
Publication of EP4042209A1 publication Critical patent/EP4042209A1/fr
Pending legal-status Critical Current

Links

Classifications

    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01V—GEOPHYSICS; GRAVITATIONAL MEASUREMENTS; DETECTING MASSES OR OBJECTS; TAGS
    • G01V1/00—Seismology; Seismic or acoustic prospecting or detecting
    • G01V1/02—Generating seismic energy
    • G01V1/133—Generating seismic energy using fluidic driving means, e.g. highly pressurised fluids; using implosion
    • G01V1/137—Generating seismic energy using fluidic driving means, e.g. highly pressurised fluids; using implosion which fluid escapes from the generator in a pulsating manner, e.g. for generating bursts, airguns
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B19/00—Machines or pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B1/00 - F04B17/00
    • F04B19/04—Pumps for special use
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/08—Cooling; Heating; Preventing freezing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B7/00—Piston machines or pumps characterised by having positively-driven valving
    • F04B7/02—Piston machines or pumps characterised by having positively-driven valving the valving being fluid-actuated
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01V—GEOPHYSICS; GRAVITATIONAL MEASUREMENTS; DETECTING MASSES OR OBJECTS; TAGS
    • G01V1/00—Seismology; Seismic or acoustic prospecting or detecting
    • G01V1/02—Generating seismic energy
    • G01V1/104—Generating seismic energy using explosive charges
    • 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

Definitions

  • the invention relates to a device and a method for generating high-intensity pressure pulses. It relates in particular to a pressure wave generator and a method for operating a pressure wave generator according to the preamble of the independent claims.
  • auxiliary and a main explosion are ignited in separate chambers.
  • the auxiliary explosion serves to release a closure of the main explosion chamber directly or via other locking mechanisms, so that a subsequent main explosion does not act with full force on the closure and impair or destroy it accordingly.
  • there is an explosion delay between the auxiliary and main explosion takes place, for example, by means of a delay line in which an explosion from an auxiliary to an Main chamber is performed or by means of delayed ignition in the two chambers via separate ignition devices present in the chambers.
  • At least one of these objects is achieved by a pressure wave generator and a method for operating a pressure wave generator according to the claims.
  • the method is used to operate a pressure wave generator with a pressure chamber, the pressure wave generator having
  • a closure element which closes the pressure chamber with respect to an outlet in a closed position and which closes it in an open position
  • An actuator by means of which the closure element can be brought from the closed position into the open position and, in particular, can also be brought from the open position into the closed position; the method comprising repetitively performing the following steps:
  • a volume of the pressure chamber is more than three liters, in particular more than four liters, in particular more than five liters.
  • the area at the narrowest point of the outlet is more than twenty square centimeters, in particular more than eighty square centimeters, in particular more than one hundred and eighty square centimeters.
  • the stated values for the area at the narrowest point correspond to the diameter being more than five centimeters, in particular more than ten centimeters, in particular more than fifteen centimeters.
  • an opening speed of the closure element is more than ten meters / second, in particular more than twenty meters / second, in particular at least thirty meters / second.
  • a stroke of the closure element during the opening and closing movement is between thirty and one hundred and fifty millimeters, in particular between forty and one hundred millimeters, in particular between fifty and eighty millimeters.
  • the pressure chamber is filled with the working medium at a pressure of more than one hundred and fifty bar, in particular of more than two hundred bar.
  • the discharge period is less than ten milliseconds, in particular less than five milliseconds, in particular less than three milliseconds.
  • the working medium is one of air, nitrogen and steam, in particular superheated steam or saturated steam.
  • the method has the following step carried out after the filling and before the opening of the pressure chamber:
  • the method has the following step carried out during the filling of the pressure chamber:
  • the working medium is heated to a temperature of 150 degrees Celsius to 250 degrees Celsius, in particular 230 degrees Celsius, or to a temperature of 200 degrees Celsius to 450 degrees Celsius, in particular 250 degrees Celsius.
  • the heating can take place, for example, by a temperature difference of more than 100 degrees Celsius, in particular more than 200 degrees Celsius, in particular more than 300 degrees Celsius, and possibly more than 400 degrees Celsius.
  • the heating can be done, for example, with a electric heating element happen.
  • the outflow speed and thus an impulse of the outflowing working medium increase with the square root of the temperature. Another effect of heating the working medium is that it can be prevented that the working medium cools down too much when it flows out of the pressure chamber.
  • the working medium When flowing out, the working medium expands to the ambient pressure and can thereby - depending on the circumstances and depending on which working medium is present - cool down to a temperature below its liquefaction temperature. As a result, the beam spreads at the speed of sound at the most after its exit, which limits the effectiveness of the device.
  • a heater which is arranged to heat the working medium located in the pressure chamber, in particular an electrical heater.
  • the heater is a heat exchanger, in particular with heat exchanger elements, in particular with electrically heated heat exchanger elements
  • the method occurs using a pneumatic actuator which has
  • a first piston surface which acts against a gaseous control medium in a first volume, a pressure in the first volume on the first piston surface causing an actuator force in a first direction;
  • the closure element can be brought from the closed position into the open position by the pneumatic actuator and in particular can also be brought from the open position into the closed position; wherein the method for opening the pressure chamber comprises the following steps:
  • the method is carried out using a pneumatic actuator which has:
  • a first piston surface which acts against a gaseous control medium in a first volume, a pressure in the first volume on the first piston surface causing an actuator force in a first direction;
  • a second piston surface which acts against the control medium in a second volume, a pressure in the second volume on the second piston surface causing an actuator force in a second direction opposite to the first.
  • the closure element can be brought from the closed position into the open position by the pneumatic actuator and, in particular, can also be brought from the open position into the closed position.
  • the procedure includes repeating the following steps: a) filling the first volume with a pressurized gaseous control medium, in particular by means of a filling valve, for example a compressed air valve; b) pressure equalization between the first volume and the second volume by means of a throttle and thereby, due to an area difference of the first piston surface and the second piston surface, moving the actuator in the first direction and thereby moving a closure element in a closing direction and closing the pressure chamber; c) filling the pressure chamber with a gaseous working medium; d) draining at least part of the control medium from the first volume, in particular by opening an inlet / outlet opening of the first volume, and thereby opening the pressure chamber; e) by a more rapid pressure drop in the first volume than in the second volume, moving the actuator in the second direction and thereby moving the closure element in the opening direction to open the pressure chamber with respect to an outlet, and releasing the working medium from the pressure chamber through the outlet.
  • a filling valve for example a compressed air valve
  • Steps a), b) and c) can be carried out simultaneously or overlapping in time.
  • Step d) is typically carried out after steps a), b) and c).
  • step d) the opening of the pressure chamber, triggered by the opening of the inlet / outlet opening, goes directly to step e).
  • a period of time between the triggering of the opening movement of the closure element, for example by actuating a drain solenoid valve, and the maximum opening of the closure element is in the range from 20 milliseconds to 120 milliseconds, in particular between 40 milliseconds and 60 milliseconds.
  • the time to open the closure element is less than ten milliseconds, in particular less than five milliseconds, in particular less than three milliseconds. It can be substantially equal to the drain time.
  • the pressure wave generator according to a first aspect is used to carry out the method described above. He has a pressure chamber, as well
  • a closure element which, in a closed position, closes the pressure chamber with respect to an outlet and, in an open position, enables the working medium to flow out of the pressure chamber into the outlet;
  • An actuator by means of which the closure element can be brought from the closed position into the open position and can be brought from the open position into the closed position;
  • a volume of the pressure chamber is more than three liters, in particular more than four liters, in particular more than five liters;
  • the area at the narrowest point of the outlet being more than twenty square centimeters, in particular more than eighty square centimeters, in particular more than one hundred and eighty square centimeters;
  • a stroke of the closure element during the opening and closing movement is between thirty and one hundred and fifty millimeters, in particular between forty and one hundred millimeters, in particular between fifty and eighty millimeters.
  • the Pressure wave generator generated mass flow made as large as possible.
  • the mass flow is proportional to the density and exit speed of the working medium as well as to the area of the exit opening.
  • a closure area of a closure opening which is closed and opened by the closure element, is at least as large as the area at the narrowest point of the outlet, in particular at least ten percent larger than the area at the narrowest point of the outlet.
  • the closure element is hollow-cylindrical and is arranged to close or open a closure opening corresponding to a cylindrical surface.
  • the hollow-cylindrical configuration allows the mass of the closure element to be reduced.
  • the annular surface of the piston which surrounds the hollow cylindrical recess, determines a recoil force with which the escaping gases drive the piston back.
  • the area of the hollow cylindrical recess is more than twenty-five, in particular more than fifty percent of the area of the locking element.
  • the cylindrical closure surface allows a large change in the surface area of the closure surface as a function of the movement of the closure.
  • a sum of areas on the closure element on which the pressurized working medium exerts a force acting on the closure element in the closing direction is less than ten percent of the cross-sectional area of the outlet at the point where the outlet is closed by the closure element.
  • an area of the inlet / outlet opening of the first volume is between two hundred square millimeters and five hundred square millimeters, or a maximum of one thousand five hundred square millimeters. In the case of a round cross-section of the opening, this corresponds to a diameter, rounded, between sixteen millimeters and twenty-five millimeters, or a maximum of forty-four millimeters. This enables the first volume to be emptied sufficiently quickly and, in turn, a correspondingly quick opening movement. The result is that this diameter is by and large independent of the first piston area, that is to say the area of the piston in the first volume.
  • the closure element upon an opening movement of the closure element, starting from an end position in which the closure element closes the closure opening, the closure element opens the closure opening only after having covered a minimal distance.
  • This path is different from zero. In particular, this path is more than five millimeters or more than eight millimeters.
  • a pressure wave generator according to a second aspect is used to carry out the method described above. He has a pressure chamber, as well A closure element which, in a closed position, closes the pressure chamber with respect to an outlet and, in an open position, enables the working medium to flow out of the pressure chamber into the outlet;
  • An actuator by means of which the closure element can be brought from the closed position into the open position and can be brought from the open position into the closed position;
  • a heater which is arranged to heat a working medium that is fed to the pressure chamber or a working medium present in the pressure chamber, in particular wherein the heater is an electrical heater.
  • a pneumatic actuator in particular for use in a pressure wave generator, has:
  • a first piston surface which acts against a gaseous control medium in a first volume, a pressure in the first volume on the first piston surface causing an actuator force in a first direction;
  • a second piston surface which acts against the control medium in a second volume, a pressure in the second volume on the second piston surface causing an actuator force in a second direction opposite to the first;
  • An inlet / outlet opening of the first volume for introducing and discharging the control medium into or out of the first volume
  • the pneumatic actuator has end position damping, in particular by closing the inlet / outlet opening.
  • the inlet / outlet opening is thus closed with respect to the first volume.
  • a piston closure element is arranged for closing the inlet / outlet opening.
  • the end position damping can thus be implemented in a simple manner by means of an element of the piston itself. In one method of operating the pneumatic actuator, the following steps are performed:
  • the inlet / outlet opening can be made relatively large in order to bring about the rapid pressure drop in the first volume.
  • the piston closure element is also arranged to separate a control medium filling line with respect to the first volume. This avoids high pressure surges in the filling line.
  • the two volumes are implemented as parts of a common working space of a cylinder in which a single piston is arranged, on which the two piston surfaces are formed. This makes the sealing of the pistons against the (now common) cylinder uncritical. There may even be a gap between the piston and cylinder. This acts as a throttle between the two volumes. The pressure equalization therefore takes place through this gap. This enables a further simplification of the construction. In this embodiment, the throttle is thus formed by the gap between the cylinder and the piston. There is no need for an otherwise customary piston seal.
  • the two volumes and piston surfaces lie on separate pistons in separate cylinders, and the two separate pistons are mechanically coupled and their movements are also coupled.
  • the first piston surface and a piston closure element for closing the inlet / outlet opening are formed on the same piston. This enables a particularly simple and reliable construction.
  • the pneumatic actuator has a cylinder discharge valve for quickly discharging the control medium from the first volume by opening the inlet / outlet opening.
  • the cylinder discharge valve has a piston surface on which a force for closing the cylinder discharge valve is generated when the control medium is applied, and a valve surface on which a force in the opening direction of the cylinder discharge valve is generated when the control medium is applied, the valve surface being smaller than the piston area. In this way, by applying the same pressure to both surfaces, the cylinder discharge valve can be brought into the closed position and held.
  • the pneumatic actuator has a discharge pilot valve for discharging control medium from a discharge valve volume in which the control medium acts on the piston surface. This can create a brief, temporary imbalance in the pressure on the two surfaces, which opens the cylinder drain valve.
  • a control medium filling line for filling both the discharge valve volume and the first volume with control medium is arranged under the same pressure. In this way, on the one hand, the same pressure can be achieved in the two volumes and, on the other hand, by virtue of the filling line acting as a throttle between the two volumes, the temporary imbalance can be achieved.
  • the pressure in the control medium is, for example, between 50 and 140 bar, in particular between 80 bar and 100 bar.
  • a section of the control medium filling line, through which the first volume is supplied with the control medium runs through the cylinder discharge valve, in particular a shut-off body of the valve.
  • this section is a passage in the shut-off body, which allows a small flow through the valve even when the valve is in the closed position.
  • a section of the control medium filling line, through which the first volume is supplied with the control medium runs through a housing of the pressure wave generator.
  • a linear guide of the piston is formed in that the piston encloses a rear closure guide and is linearly movable along the rear closure guide in a direction of movement, and a hollow cylindrical piston connecting element extending away from the piston in the direction of movement encloses a bearing element which is attached to the rear Lock guide is attached.
  • the second volume is formed between the piston, an inside of the piston connecting element, the bearing element and the rear locking guide.
  • the rear lock guide is fixedly connected to the housing.
  • a hollow cylindrical element can be driven as an extension of the hollow cylindrical piston connecting element, which is advantageous in certain applications.
  • this is the case with the pressure wave generator described here with a hollow cylindrical closure element.
  • the pressure wave generator can have a controller which is set up to control the pressure wave generator for carrying out the method according to at least one of the method claims.
  • the activation takes place by activating at least the valves of the pressure wave generator.
  • FIG. 1 shows a longitudinal section through a pressure wave generator
  • FIG. 2 shows a longitudinal section through another embodiment
  • FIGS. 3-4 embodiments with a heater for heating the working medium.
  • FIGS. 1 and 2 each show a pressure wave generator 1 with a pressure chamber 2.
  • a closure element 9 is arranged opposite an outlet 15 for closing the pressure chamber 2.
  • the closure element 9 is guided on a bearing element 14, which allows a linear opening and closing movement of the closure element 9.
  • the closure element 9 is hollow-cylindrical and has a piston which is guided through the bearing element 14, which is firmly connected to a housing 16.
  • the closure element 9 is shaped as a hollow cylinder and surrounds the bearing element 14, which is firmly connected to a housing 16.
  • FIGS. 1 and 2 show the closure element 9 in a closed position, ie the pressure chamber 2 is closed with respect to the outlet 15.
  • the outlet 15 is used for the directed discharge or discharge of the working medium. A pressure wave can thus be generated.
  • the closure element 9 In an open position, the closure element 9 exposes a closure surface of a closure opening. In the closed position, the closure opening is closed by the closure element 9. Here the locking surface is a cylinder surface.
  • the pressure chamber 2 is annular.
  • the pressure chamber 2 encloses the closure element 9.
  • the closure opening leads, starting from the pressure chamber 2, in the radial direction - with respect to the annular pressure chamber 2 - inwards. Working medium exiting through the closure opening flows inward in the radial direction and then in the axial direction - again with respect to the annular pressure chamber 2 - through the outlet 15. In the closed state, the closure element 9 rests against a valve seat of the housing 16.
  • the valve seat can be designed with a collar, which means that when the closure element is moved in the opening direction, starting from an end position in the closed position, the closure opening is only opened and the working medium can flow out after the closure element 9 has covered a certain distance. This path is shown as collar width 77. This makes it possible to accelerate the movement of the closure element 9 before the closure opening is opened, which in turn enables the closure opening to be opened sufficiently quickly to allow the working medium to flow out suddenly.
  • the size of the closure area is larger than the area of the outlet or outlet area, i.e. the cross-sectional area at which the outlet merges into the free space.
  • the outlet 15 corresponds to the narrowest point along the path of the working medium out of the pressure chamber 2. This has the consequence that the speed of the outflowing working medium is highest in the outlet 15 or shortly thereafter. In particular, the outflowing working medium only reaches the speed of sound shortly after the narrowest point, that is to say after the outlet 15. This is advantageous for the operation of the device.
  • a first filling line or working medium filling line 12 is arranged for filling the pressure chamber 2 with a working medium. It is fed valve 10 by a working medium.
  • the pressure chamber 2 is closed by the closure element 9 with respect to the outlet 15;
  • the pressure chamber 2 is filled with the working medium under high pressure, ie with a pressure of more than one hundred bar, in particular more than one hundred and fifty bar, in particular of more than two hundred bar;
  • the pressure chamber 2 opens suddenly so that the energy stored in the working medium is converted into kinetic energy over the shortest possible period of time. The shorter the period, the higher the speed and the impulse of the outflowing working medium and thus the effect of the pressure wave.
  • Opening speed 15 m / s to 40 m / s
  • Outlet area 80 cm 2 (corresponds to a diameter of approx. 100 mm)
  • Opening speed more than 15 m / s stroke: 60 mm
  • Pressure 250 bar to 300 bar, in particular 280 bar
  • Opening speed more than 25 m / s Stroke: 60 mm to 90 mm, in particular 75 mm
  • Pressure 250 bar to 300 bar, in particular 280 bar
  • Volume 4 liters to 6 liters, especially 5 liters
  • Stroke 50 mm to 70 mm, especially 60 mm
  • the working medium can be heated to a temperature of 150 degrees Celsius to 250 degrees Celsius, in particular 230 degrees Celsius, or to a temperature of 200 degrees Celsius to 450 degrees Celsius, in particular 250 degrees Celsius.
  • the opening movement of the closure element 9 is brought about by an active gas spring or pneumatic actuator 4b.
  • This has a cylindrical working space 43 with a piston 93 moved therein, the movement of which with the
  • Movement of the closure element 9 is coupled, in particular by being firmly connected to one another, in particular formed in one piece.
  • the coupling takes place by means of a piston connecting element 94.
  • this is a piston rod
  • this is a hollow cylinder.
  • the piston 93 divides the working space 43 into a first volume 41 and a second volume 42. There is no seal between a cylinder inner wall 44 of the working space 43 and the piston 93. In particular, there can also be a small gap, hereinafter referred to as piston gap 96. This allows a gas exchange between the two volumes and acts in particular as a throttle. In other embodiments, a separate line can be arranged between the first volume 41 and the second volume 42 and have a throttle which, in addition or as an alternative to the piston gap 96, allows the gas exchange. Such a throttle can also be used as a piston throttle 100 through one or more bores the piston 93 can be realized, which thus also allows a gas exchange between the two volumes.
  • a gas pressure of the control medium in the first volume 41 causes a force counter to the direction of the opening movement of the closure element 9, one effective area being a first piston area 91.
  • a gas pressure of the control medium in the second volume 42 causes a force in the direction of the opening movement of the closure element 9, one effective area being a second piston area 92.
  • the second piston surface 92 is smaller than the first piston surface 91, for example. at least five or ten or twenty percent smaller.
  • the piston 93 has a piston closure element 95 which closes a cylinder inlet / outlet 45 or inlet / outlet opening of the first volume 41 in the course of the opening movement.
  • the cylinder inlet / outlet 45 is drawn here concentrically to the working chamber 43, but could alternatively also be arranged laterally. Closing the cylinder inlet / outlet 45 slows down or dampens the end position of the opening movement.
  • the compressed air valve 49 is also protected from a pressure surge through the compressed air filling line 48.
  • the cylinder inlet / outlet 45 can be opened by a cylinder exhaust valve 46.
  • the control medium flows out through a drain or vent line 102, for example.
  • the cylinder discharge valve 46 can have a relatively large valve cross-section compared to a fill line. A sudden pressure reduction in the first volume 41 can thus be achieved.
  • the cylinder discharge valve 46 is held closed by pressure in a compressed air fill line 48. This pressure can be reduced by opening a discharge pilot valve 47 become. The opening movement of the closure element is thus triggered by opening the drain pilot valve.
  • the cylinder discharge valve 46 is, for example, a seat valve with a movable shut-off body.
  • the shut-off body has a piston surface 52 on which it is acted upon by the compressed air from the compressed air filling line 48 in a discharge valve volume 51.
  • a valve surface 53 which is acted upon by the pressure in the cylinder inlet / outlet 45, is smaller than the piston surface 52.
  • the forces on the piston surface 52 and the valve surface 53 are opposite to one another.
  • the compressed air filling line 48 also feeds the first volume 41 via a section 101 of the compressed air filling line 48.
  • the compressed air filling line 48 in turn is fed via a compressed air valve 49.
  • a ventilation line 97 effects a pressure equalization between the ambient air and an intermediate cylinder.
  • the intermediate cylinder lies between a rear end of the closure element 9 and the active gas spring or the pneumatic actuator 4b.
  • the working space 43 and the piston 93 are implemented in a compact manner.
  • the same mode of operation can, however, also be implemented with separate first and second volumes and with separate pistons with different piston surfaces.
  • a line with a throttle is arranged between the two volumes and the movements of the two pistons are mechanically coupled. This means that a linear movement of one of the two pistons always results in a linear movement of the other piston.
  • a piston travel can be, for example, between 20 mm and 150 mm, in particular between 30 mm and 80 mm.
  • a diameter of the piston can for example be between 20 mm and 200 mm, in particular between 40 mm and 120 mm.
  • a heating element 99 is present.
  • the pressurized working medium in the pressure chamber 2 can thus be heated. This can increase the energy of the pressure wave generated.
  • FIGS. 1 and 2 show the pneumatic actuator 4b in combination with a pressure wave generator 1.
  • Opening the compressed air valve 49 with the drain pilot valve 47 closed This has the following effects:
  • the pressure in the compressed air filling line 48 (eg 70 bar) closes the cylinder drain valve 46.
  • the compressed air filling line 48 provides the first volume 41 with compressed air applied.
  • the second volume 42 is also acted upon through the piston gap 96, the same pressure being present in both volumes over time. Because the first piston surface 91 is larger than the second piston surface 92, the piston 93 and thus the closure element 9 are moved into a closed position (opposite to the direction of the opening movement).
  • Closing the cylinder discharge valve 46 in particular by closing the discharge pilot valve 47. This can be done by increasing a piston surface via which the compressed air in the compressed air filling line 48 presses the cylinder discharge valve 46 or its shut-off element into the closed position is as a surface on which the compressed air acts in the opposite direction on the cylinder discharge valve 46 or its shut-off body. After closing the cylinder drain valve 46, the pressure in the first volume 41 can still be sufficiently high (e.g. 20 bar) to move the piston 93 back and thus the closure element 9 into the closed position even after pressure equalization with the second volume 42 bring to.
  • the pressure in the first volume 41 can still be sufficiently high (e.g. 20 bar) to move the piston 93 back and thus the closure element 9 into the closed position even after pressure equalization with the second volume 42 bring to.
  • the process can then be started again by opening the compressed air valve 49.
  • the closure element is moved in the opening direction by moving the pneumatic actuator in the second direction.
  • the closure element is moved in the closing direction by moving the pneumatic actuator in the first direction.
  • FIG. 2 shows an embodiment with an alternative pneumatic actuator 4b that differs from that of FIG.
  • a cylinder discharge valve 46 with a section 101 of the compressed air filling line can be combined with a pressure wave generator 1 according to FIG. Furthermore, the embodiment can also have a heating element 99 (not shown).
  • the mode of operation is basically the same as that of the embodiment of FIG. 1, with the following differences in the implementation of individual elements:
  • the piston connecting element 94 which connects the piston 93 to the closure element 9, is formed by a hollow cylinder.
  • the piston 93 encloses a rear closure guide 98, which can be designed as a general cylinder, in particular as a circular cylinder, and can be moved linearly along the same in the direction of movement.
  • the piston connecting element 94 surrounds the bearing element 14, which is firmly connected to a housing 16.
  • the second volume 42 lies between the rear closure guide, the piston 93 and the inside of the hollow cylinder or the piston connecting element 94.
  • the throttle between the first volume 41 and the second volume 42 is implemented as a piston throttle 100 through one or more bores through the piston 93. Additionally or alternatively, however, the function of the piston throttle can also be perceived through a gap between the piston 93 and the rear closure guide 98.
  • the section 101 of the compressed air filling line 48, through which the first volume 41 is supplied with the control medium, does not run through the housing 16 but through the shut-off body of the cylinder discharge valve 46, for example as a bore, and can also be a piston throttle of the cylinder discharge valve 46 to be named.
  • the first volume 41 is thus supplied with the control medium via the drain valve volume 51.
  • End position cushioning can be dispensed with. If end position damping is to be implemented in the embodiment of FIG. 5, this can be done, as in FIG. 1, by a protruding piston closure element 95, which enters the cylinder inlet / outlet 45, or by the cylinder inlet / outlet 45 laterally is introduced into the first volume 41 and is closed by the piston 93 sliding over the cylinder inlet / outlet 45 during the opening movement.
  • two or three or more closure elements 9 are arranged parallel to one another in order to increase a total outlet area. They can be triggered synchronously with one another or at the same time in order to generate a pressure wave of higher energy than with a single closure element 9.
  • closure elements are connected to a single pressure chamber 2 and are actuated by a single pneumatic actuator.
  • Such a parallel arrangement of closure elements 9 can also be implemented with pressure wave generators which use explosions to generate the pressure in the pressure chamber and / or to drive the closure element.
  • a controller 20 is set up to carry out the method steps described. To this end, the controller 20 is set up to control the compressed air valve 49, the working medium valve 10 and the cylinder discharge valve 46. The cylinder discharge valve 46 can be activated by means of the discharge pilot valve 47.
  • Figures 3 and 4 show embodiments with a heater 80 for heating the working medium.
  • the heater 80 is arranged for heating the working medium when it flows through the first filling line or working medium filling line 12. The heated air does not experience any pressure increase.
  • the heater 80 is arranged for heating the working medium when it flows through a circulation line 84.
  • the circulation line 84 leads from the pressure chamber 2 through the heater 80 and back to the pressure chamber 2. Both the temperature and the pressure in the pressure chamber 2 are increased by the heating.
  • a circulation fan 85 can be arranged for conveying the working medium through the circulation line 84.
  • the heater can each have a heat exchanger 81 with heat exchanger elements 82 around which the working medium flows.
  • the heat exchanger elements 82 can be heated by an electric heater 83.
  • heat exchanger elements 82 are arranged in the pressure chamber 2.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Remote Sensing (AREA)
  • Acoustics & Sound (AREA)
  • Environmental & Geological Engineering (AREA)
  • Geology (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • General Physics & Mathematics (AREA)
  • Geophysics (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Multimedia (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

L'invention concerne un procédé de fonctionnement d'un générateur d'ondes de pression (1) comprenant une chambre de pression (2), ledit générateur d'ondes de pression (1) comprenant : un élément de fermeture (9) qui, dans une position fermée, ferme la chambre de pression (2) par rapport à une sortie (14) et, dans une position ouverte, permet un écoulement sortant du fluide de travail depuis la chambre de pression (2) dans la sortie (15) ; un actionneur au moyen duquel l'élément de fermeture (9) peut être amené de la position fermée à la position ouverte et peut en particulier également être amené de la position ouverte à la position fermée. Ledit procédé comprenant les étapes suivantes : remplissage de la chambre de pression (2) avec un fluide de travail gazeux ayant une pression supérieure à cent bars ; déplacement de l'actionneur et ainsi déplacement de l'élément de fermeture (9) dans une direction d'ouverture en vue d'ouvrir la chambre de pression (2) par rapport à une sortie (15), et évacuation du fluide de travail sous pression de la chambre de pression (2) à travers la sortie (15) au sein d'une période d'évacuation inférieure à quinze millisecondes.
EP20790036.6A 2019-10-23 2020-10-20 Générateur d'ondes de pression et procédé de fonctionnement d'un générateur d'ondes de pression Pending EP4042209A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH01347/19A CH716723A1 (de) 2019-10-23 2019-10-23 Druckwellengenerator und Verfahren zum Betreiben eines Druckwellengenerators.
PCT/EP2020/079524 WO2021078754A1 (fr) 2019-10-23 2020-10-20 Générateur d'ondes de pression et procédé de fonctionnement d'un générateur d'ondes de pression

Publications (1)

Publication Number Publication Date
EP4042209A1 true EP4042209A1 (fr) 2022-08-17

Family

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Application Number Title Priority Date Filing Date
EP20790036.6A Pending EP4042209A1 (fr) 2019-10-23 2020-10-20 Générateur d'ondes de pression et procédé de fonctionnement d'un générateur d'ondes de pression

Country Status (8)

Country Link
US (1) US20230010643A1 (fr)
EP (1) EP4042209A1 (fr)
JP (1) JP2022553136A (fr)
KR (1) KR20220083711A (fr)
CN (1) CN114667463A (fr)
CA (1) CA3154019A1 (fr)
CH (1) CH716723A1 (fr)
WO (1) WO2021078754A1 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU2022432659A1 (en) 2022-01-13 2024-06-13 P-Wave Ag Pressure wave generator

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2145430A1 (de) * 1971-09-10 1973-03-15 Butterworth Hydraulic Dev Ltd Durch stroemungsmitteldruck betaetigter, hin- und hergehender motor
GB1392918A (en) * 1973-05-17 1975-05-07 Burnside M Seismic pneumatic energy source with bubble eliminator and signal oscillation attenuator
FR2629216B1 (fr) * 1988-03-25 1991-01-04 Inst Francais Du Petrole Dispositif perfectionne pour engendrer des ondes acoustiques par percussion d'une masse chutant sur un element-cible couple avec les parois d'un puits
US5224392A (en) * 1992-01-23 1993-07-06 Eaton Corporation Variable pressure range section actuator piston
JP4035069B2 (ja) * 2003-02-27 2008-01-16 財団法人名古屋産業科学研究所 熱音響効果を利用した音波増幅・減衰器を備えた配管装置
WO2007028264A2 (fr) 2005-09-05 2007-03-15 Explo Engineering Gmbh Procede et dispositif de production d'ondes de choc
DE102006011482B4 (de) * 2006-03-14 2010-07-15 Festo Ag & Co. Kg Pneumatischer Linearantrieb
DE102007061946A1 (de) * 2007-12-21 2009-06-25 Robert Bosch Gmbh Verfahren zum Betreiben einer Kraftstoff-Einspritzvorrichtung
CH699486A2 (de) * 2008-09-04 2010-03-15 Explo Engineering Gmbh Vorrichtung und verfahren zum erzeugen von explosionen.
EP2329153B1 (fr) * 2009-12-18 2016-02-17 TÜNKERS MASCHINENBAU GmbH Dispositif à entraînement par air comprimé, équipé d'une fonction double piston et destiné à être utilisé dans le domaine de la carrosserie pour l'industrie automobile
KR101476085B1 (ko) * 2011-02-25 2014-12-23 제너럴 퓨전, 아이엔씨. 매질 내에서 압력파를 생성하기 위하여 이동식 제어 로드를 갖는 압력파 생성기
CN104968444B (zh) * 2013-02-08 2016-12-28 全面熔合有限公司 具有发射载体发射式柱塞的压力波发生器
US9804280B2 (en) * 2015-10-17 2017-10-31 Stephen Chelminski Method and apparatus for tuning the rise time of the initial pulse of an air gun
CH714963A1 (de) * 2018-05-02 2019-11-15 Explotechnik AG Druckwellengenerator und Verfahren zum Betreiben eines Druckwellengenerators, sowie pneumatischer Aktuator.

Also Published As

Publication number Publication date
CA3154019A1 (fr) 2021-04-29
CH716723A1 (de) 2021-04-30
JP2022553136A (ja) 2022-12-22
WO2021078754A1 (fr) 2021-04-29
KR20220083711A (ko) 2022-06-20
US20230010643A1 (en) 2023-01-12
CN114667463A (zh) 2022-06-24

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