Cleaning machine and method

Abstract

The invention relates to a cleaning machine (10) and a method for cleaning at least one blowpipe of a plurality of blowpipes of a converter, for example a Peirce-Smith converter, wherein the blowpipes are arranged in a preferably horizontally aligned row laterally on a container of the converter, wherein a gas, in particular oxygen, can be blown into the melt through the blowpipes below a level of a melt that can be received in the container, wherein the cleaning machine is designed to be movable on a path, preferably in the form of a rail guide, running along the row of blowpipes, wherein the cleaning machine comprises a punching system (16), wherein the punching system comprises a punching device (17) with at least one puncher (19) and a drive device (20) with at least one linear actuator (21), wherein the puncher and the blowpipe can be brought into alignment with one another, wherein, when the puncher is aligned with the blowpipe, using the drive device, the punching device can be driven to carry out a forward movement of the punching device, in which the puncher can be transferred from a retracted position of the puncher into a forward position of the puncher, and a backward movement of the punching device, in which the puncher can be transferred from the forward position into the retracted position, wherein the puncher can be inserted into the blowpipe through an opening of the blowpipe during the transfer from the retracted position to the forward position in order to clean the blowpipe and can subsequently be guided out of the blowpipe during the transfer from the forward position to the retracted position, wherein the linear actuator is in the form of a, preferably pneumatic, double-acting cylinder, wherein the cylinder has a piston, a first chamber and a second chamber, wherein the first chamber can be pressurised to carry out a forward movement of the piston to execute the forward movement of the punching device and the second chamber can be pressurised at least to execute a backward movement of the piston to execute the backward movement of the punching device, wherein the punching system comprises a valve device fluidically connected to the cylinder for actuating the cylinder, wherein the cylinder is designed without a piston rod and / or the second chamber can optionally be depressurised, closed in a pressure-tight manner or pressurised via the valve device.

Description

[0001] Cleaning machine and process

[0002] The invention relates to a cleaning machine and a method for cleaning at least one blowpipe of a plurality of blowpipes of a converter, for example a Peirce-Smith converter, wherein the blowpipes are arranged in a preferably horizontally aligned row laterally on a container of the converter, wherein a gas, in particular oxygen, can be blown into the melt through the blowpipes below a level of a melt that can be accommodated in the container, wherein the cleaning machine is designed to be movable on a track, preferably designed as a rail guide, running along the row of blowpipes, wherein the cleaning machine comprises an impact system, wherein the impact system comprises an impact device with at least one ram and a drive device with at least one linear actuator, wherein the ram and the blowpipe can be brought into alignment with one another, wherein, when the ram is aligned with the blowpipe,by means of the drive device, the pushing device can be driven to carry out a forward movement of the pushing device, in which the plunger can be transferred from a retracted position of the plunger into an advancing position of the plunger, and a backward movement of the pushing device, in which the plunger can be transferred from the advancing position to the retracted position, wherein the plunger can be inserted into the blowpipe through an opening of the blowpipe during the transfer from the retracted position to the advancing position for piercing the blowpipe to clean the blowpipe and can subsequently be removed from the blowpipe during the transfer from the advancing position to the retracted position, wherein the linear actuator is designed as a, preferably pneumatic, double-acting cylinder, wherein the cylinder has a piston, a first chamber and a second chamber,wherein the first chamber is pressurizable for executing a forward movement of the piston for executing the forward movement of the impact device and the second chamber is pressurizable at least for executing a backward movement of the piston for executing the backward movement of the impact device, wherein the impact system comprises a valve device fluidically connected to the cylinder for controlling the cylinder.

[0003] In the extraction of metal, in particular copper, a converter, for example a Peirce-Smith converter, is used for the smelting metallurgical refining of a metal-containing intermediate product, in particular copper matte. In the converter, the metal-containing intermediate product is blown into another metal-containing intermediate product, in particular raw copper, in order to remove impurities. In this process, a gas, in particular oxygen, is blown from the metal-containing intermediate product into the melt below a level of a melt held in the container through blowpipes of the converter, which are typically arranged in a horizontally aligned row on the side of a container of the converter and are also referred to as "tuyeres". The container is usually designed as a cylindrical drum and can be rotated about a horizontally aligned longitudinal axis of the container.Because the blowpipes are located below the water level, deposits or crusts regularly form in them. These deposits or crusts must be cleaned from time to time to prevent or eliminate blockages. The blowpipes are cleaned using a cleaning machine of the type described above.In this case, at least one plunger of a pushing device of a pushing system of the cleaning machine and a blowpipe to be cleaned are brought into alignment with one another, in particular by moving the cleaning machine on a track usually designed as a rail guide and running along the row of blowpipes, and optionally by rotating the container. When the plunger is aligned with the blowpipe, the pushing device is driven by a drive device of the pushing system comprising at least one linear actuator, such that the blowpipe is pierced by means of the plunger in order to clean the blowpipe. This piercing is also referred to as “punching”. After cleaning the blowpipe, the cleaning machine can, if necessary, be moved to another blowpipe to be cleaned so that the additional blowpipe can be cleaned.In this way, all blowpipes of the plurality of blowpipes that need to be cleaned can be cleaned one after the other. Such a converter and such a cleaning machine are known, for example, from DE 1 483 157 A.

[0004] In a cleaning machine known from the prior art, at least one linear actuator of a drive device of an impact system of the cleaning machine is regularly designed as a double-acting cylinder, wherein the cylinder comprises a piston and a piston rod coupled to the piston, wherein the piston rod is in turn coupled to an impact device of the impact system or at least one plunger of the impact device. Since the piston rod is exposed to comparatively high forces when piercing the blowpipes, it often happens that the piston rod bends or deforms, as a result of which the plunger can no longer be inserted into the blowpipe parallel to a longitudinal axis of the respective blowpipe. Therefore, the drive device is regularly equipped with a guide device for guiding the piston rod, which is intended to reduce the risk of bending or deformation of the piston rod.However, in practice, despite the presence of such a guide device, bending or deformation of the piston rod often occurs. The use of the cylinder enclosing the piston rod therefore results in increased wear on the blower pipes. Furthermore, the cleaning machine known from the prior art provides a valve device of the impact system which is fluidically connected to the cylinder and by means of which the cylinder can be controlled, wherein a first chamber of the cylinder and a second chamber of the cylinder can be selectively depressurized or pressurized via the valve device. The valve device comprises a first valve fluidically connected to the first chamber and a second valve fluidically connected to the second chamber, wherein, when the first valve or second valve is in a first position of the first valve or second valve, the first chamber orsecond chamber can be depressurized, wherein, when the first valve or second valve is in a second position of the first valve or second valve, the first chamber or the second chamber can be pressurized, wherein the first valve and the second valve are each designed as a 3 / 2-way valve. The first chamber or second chamber can be pressurized to execute a forward movement of the piston to execute a forward movement of the pushing device or a backward movement of the piston to execute a backward movement of the pushing device. When the forward movement of the piston or backward movement of the piston is executed, the second chamber or first chamber is depressurized. This valve device has only a very limited number of configurations for controlling the cylinder, linked to the positions of the valves.This valve device therefore cannot be used to control the cylinder to carry out a uniform movement of the piston or the impact device, which is beneficial for the blowpipes with regard to their wear. Furthermore, this valve device cannot be used to control, or in particular to limit, a maximum piston force or a maximum piston speed. For this reason, the plunger regularly impacts the respective blowpipe or a closure element closing an opening in the respective blowpipe, in particular a ball valve or flap valve, which is opened or raised when the plunger is inserted through the opening into the respective blowpipe, with an excessively high force of the plunger or a speed of the plunger. This also results in increased wear on the blowpipes, in particular the closure elements.

[0005] The present invention is therefore based on the object of proposing a cleaning machine and a method for cleaning at least one blowpipe of a converter, which enables a less wear-related cleaning of the blowpipe.

[0006] This object is achieved by a cleaning machine having the features of claim 1 and a method having the features of claim 9.

[0007] The cleaning machine according to the invention for cleaning at least one blowpipe of a plurality of blowpipes of a converter, for example a Peirce-Smith converter, wherein the blowpipes are arranged in a preferably horizontally aligned row laterally on a container of the converter, wherein a gas, in particular oxygen, can be blown into the melt through the blowpipes below a level of a melt that can be accommodated in the container, is designed to be movable on a track, preferably designed as a rail guide, running along the row of blowpipes, wherein the cleaning machine comprises an impact system, wherein the impact system comprises an impact device with at least one ram and a drive device with at least one linear actuator, wherein the ram and the blowpipe can be brought into alignment with one another, wherein, when the ram is aligned with the blowpipe,by means of the drive device, the pushing device is drivable to carry out a forward movement of the pushing device, in which the plunger can be transferred from a retracted position of the plunger into an advancing position of the plunger, and a backward movement of the pushing device, in which the plunger can be transferred from the advancing position to the retracted position, wherein the plunger can be inserted into the blowpipe through an opening of the blowpipe during the transfer from the retracted position to the advancing position for piercing the blowpipe to clean the blowpipe and can subsequently be removed from the blowpipe during the transfer from the advancing position to the retracted position, wherein the linear actuator is designed as a, preferably pneumatic, double-acting cylinder, wherein the cylinder has a piston, a first chamber and a second chamber,wherein the first chamber is pressurizable for executing a forward movement of the piston to execute the forward movement of the impact device and the second chamber is pressurizable at least for executing a backward movement of the piston to execute the backward movement of the impact device, wherein the impact system comprises a valve device fluidically connected to the cylinder for controlling the cylinder, wherein the cylinder is designed without a piston rod and / or the second chamber is selectively pressure-relievable, pressure-tightly sealable or pressurizable via the valve device.

[0008] According to a first aspect of the invention, the cylinder is designed without a piston rod. Accordingly, the rodless cylinder does not comprise a piston rod coupled to the piston, which could bend or deform, so that the plunger can always be inserted through the opening into the blowpipe parallel to a longitudinal axis of the respective blowpipe. Furthermore, due to the absence of a piston rod, forces can be transmitted directly. The rodless cylinder is therefore characterized by a comparatively high force density. Furthermore, the rodless cylinder has the ability to better absorb high loads and moments and can transmit the same force during both the forward and backward movement of the piston. The use of the rodless cylinder therefore results in a comparatively smooth and precise forward and backward movement of the impact device.The use of the rodless cylinder therefore enables less wear and tear on the blowpipes. Furthermore, the cleaning machine can be designed comparatively compact. Furthermore, equipping the drive unit with a guide device for guiding a piston rod, which is intended to reduce the risk of bending or deformation of the piston rod, can be omitted. If the cylinder is a pneumatic cylinder, the rodless design of the cylinder can also reduce the consumption of expensive compressed air. Furthermore, omitting the piston rod leads to less wear and tear on the cylinder, which increases its service life and reduces maintenance requirements and downtime. Preferably, a longitudinal axis of the plunger and a longitudinal axis of the cylinder lie in a common horizontal plane.

[0009] The rodless cylinder can have a slider or carriage attached to the side of the cylinder and movable along the cylinder. On the one hand, the slider or carriage can be attached to the piston. On the other hand, the slider or carriage can be attached to a load, in particular the pusher or plunger. A sealing element of the rodless cylinder, preferably in a band shape and preferably made of metal, can enable movement of the slider or carriage and ensure reliable sealing of a slot in the cylinder.

[0010] The cylinder is preferably a pneumatic cylinder. However, it is also conceivable for the cylinder to be a hydraulic cylinder. The cylinder can have one-sided or two-sided, preferably adjustable, end-position damping. Furthermore, the impact system can comprise at least one compressed air generator, preferably a compressor, and / or at least one, preferably two, compressed air tanks for storing compressed air. The compressed air tank can be a component of the compressed air generator or compressor. Furthermore, the impact system can comprise at least one pressure sensor and / or at least one flow sensor.

[0011] According to a second aspect of the invention, which is provided alternatively or in addition to the first aspect of the invention, the second chamber can be selectively depressurized, closed pressure-tight, or pressurized via the valve device. The term “pressurization of the first chamber or second chamber” is to be understood as pressurizing the first chamber or second chamber with a fluid or introducing the fluid into the first chamber or second chamber in a way that increases or maintains the pressure in the first chamber or second chamber. The fluid is preferably compressed air. The fluid can also be a hydraulic fluid. The term “pressure relief of the first chamber or second chamber” is to be understood as depressurizing the first chamber or second chamber from the fluid or discharging the fluid from the first chamber or second chamber in a way that reduces or maintains the pressure in the first chamber or second chamber.The “pressure-tight closure of the first chamber or second chamber” means that there is neither pressurization of the first chamber or second chamber nor depressurization of the first chamber or second chamber, and that there is neither introduction of the fluid into the first chamber or second chamber nor discharge of the fluid from the first chamber or second chamber. The pressurization of the first chamber or second chamber can take place by means of the compressed air generator or compressor. As a result of the pressurization of the first chamber or second chamber, a pressure in the first chamber or second chamber, in particular starting from an atmospheric pressure prevailing in the first chamber or second chamber, can be increased to an operating pressure or outlet pressure of the compressed air generator or compressor, or during the forward movement of the piston or backward movement of the piston, in which a volume of the first chamber orsecond chamber can vary, can be maintained at the operating pressure or outlet pressure. The pressure relief of the first chamber or second chamber can be achieved by venting, in particular rapid venting, the first chamber or second chamber. As a result of the pressure relief or venting, in particular rapid venting, of the first chamber or second chamber, a pressure in the first chamber or second chamber can be reduced to atmospheric pressure or maintained at atmospheric pressure.

[0012] Because the second chamber can be optionally depressurized, sealed pressure-tight, or pressurized via the valve device, the valve device has a comparatively large number of configurations linked to the positions of the valve device's valves for controlling the cylinder. The cleaning machine can therefore be operated in at least one first operating mode of the cleaning machine and one second operating mode of the cleaning machine. The cleaning machine can switch between the first operating mode and the second operating mode.

[0013] Via the valve device, it is possible, particularly in the first operating mode, for the second chamber to be or become depressurized before the piston executes its forward movement when the piston is in a first end position. In other words, atmospheric pressure can then prevail in the second chamber before the piston executes its forward movement. Subsequently, when the piston executes its forward movement, the second chamber can be permanently depressurized, whereby the first chamber can be permanently pressurized. This makes it possible to achieve a comparatively high maximum piston force or piston speed if required, which can be advantageous, for example, in the case of a stuck closure element or a stuck deposit or crust.

[0014] On the other hand, particularly in the second operating mode, the valve device makes it possible for the second chamber to be pressurized before the piston executes its forward movement when the piston is in its first end position and then to be sealed pressure-tight. In other words, a pressure which may be higher than atmospheric pressure can be built up in the second chamber before the piston executes its forward movement when the piston is in its first end position. The pressurization of the second chamber can result from a previous pressurization of the second chamber to execute a backward movement of the piston to execute the backward movement of the impact device. The pressure can correspond to the operating pressure or output pressure of the compressed air generator or compressor. As a result of the pressure-tight closure of the second chamber, the pressure in the second chamber can be maintained.To execute the forward movement of the piston, the first chamber can be pressurized and the second chamber can be relieved of pressure. The pressurization of the first chamber can begin before the pressure is relieved in the second chamber. The operating pressure or outlet pressure of the compressed air generator or compressor can then prevail in both the first chamber and the second chamber when the piston is in the first end position. Alternatively, the pressurization of the first chamber and the pressure relief of the second chamber can also be initiated simultaneously when the piston is in the first end position. When the forward movement of the piston is executed, the second chamber can be relieved of pressure at least temporarily, whereby the first chamber can be pressurized at least temporarily.This results in a pressure reduction in the second chamber, whereby the pressure can be reduced, in particular to atmospheric pressure, while simultaneously pressurising the first chamber or building up pressure in the first chamber. This results in a comparatively uniform movement of the piston, and thus of the impact device, a comparatively rapid compensation of opposing forces and improved responsiveness of the piston. This enables comparatively gentle treatment of the blowpipe, in particular of a closure element closing the opening of the respective blowpipe, in particular a ball valve or flap valve, which is opened or raised when the plunger is inserted through the opening into the respective blowpipe, and thus less wear and tear when cleaning the blowpipe or the closure element.In addition, this makes it possible to control, in particular limit, the maximum piston force and maximum piston speed. Furthermore, the piston speed and the piston force decrease comparatively slowly after the closure element has been opened or lifted, so that the deposits or crusts located downstream of the closure element can be removed more effectively. Therefore, the valve device designed according to the second aspect of the invention also enables comparatively thorough cleaning of the blowpipes. Furthermore, the valve device designed according to the second aspect of the invention makes it possible, particularly in the second operating mode, to temporarily close the second chamber in a pressure-tight manner when the piston is moving forward, in particular to first relieve the pressure and then close it in a pressure-tight manner.Accordingly, the second chamber can first be relieved of pressure and then, before the piston has reached a second end position of the piston, preferably until the piston has reached the second end position, closed pressure-tight. Fluid in the second chamber can be compressed during the forward movement of the piston as a result of the pressure-tight closure of the second chamber, which can act on the piston like a counterforce and cause the piston to decelerate. This allows the maximum piston force and the maximum piston speed to be additionally controlled. In addition, the insertion depth of the plunger in the respective blowpipe can be adapted to the length of the respective blowpipe. Since blowpipes are subject to constant wear, they become shorter over time.If the plunger is inserted too far into the blowpipes, the ends of the blowpipes become thinner due to abrasion and wear out comparatively sooner. By limiting the insertion depth of the piston, the service life of the blowpipes can be extended. Furthermore, because the second chamber is pressure-tightly sealed during the forward movement of the piston, compressed air can already be present in the second chamber when the second chamber is subsequently pressurized to execute the backward movement of the piston, thus saving compressed air. In particular, for the purpose of cleaning the blowpipes with less wear, the cleaning machine can be operated in the second operating mode or switched to the second operating mode.

[0015] The valve device may be formed separately from the cylinder or integrally with the cylinder.

[0016] The converter can be a Peirce-Smith converter, a Noranda converter or another converter.

[0017] In an advantageous embodiment of the cleaning machine, the cleaning machine can comprise a drive motor, preferably an electric one, for moving the cleaning machine along the track. The drive motor can also be a pneumatic motor or a hydraulic motor. Furthermore, the cleaning machine can comprise wheels for moving the cleaning machine along the track.

[0018] In an advantageous embodiment of the invention, the valve device can comprise a first valve and a second valve connected in parallel to the first valve, wherein the first valve and the second valve can be fluidically connected to the second chamber, wherein, when the first valve is in a flow position of the first valve and the second valve is in a blocking position of the second valve, the second chamber can be depressurized orcan be vented, preferably quickly vented, wherein, when the first valve is in a blocking position of the first valve and the second valve is in a flow position of the second valve, the second chamber can be pressurized, wherein, when the first valve is in the blocking position of the first valve and the second valve is in the blocking position of the second valve, the second chamber can be closed in a pressure-tight manner, wherein preferably the first valve and the second valve can each be designed as a 2 / 2-way valve. The second valve can be fluidically connected to the compressed air generator or compressor.

[0019] In an advantageous embodiment of the cleaning machine, the first chamber can be selectively depressurized, sealed pressure-tight, or pressurized via the valve device. Therefore, the valve device makes it possible, particularly in the second operating mode, to temporarily depressurize the first chamber during the forward movement of the piston. This can save expensive compressed air.

[0020] In a preferred embodiment of the cleaning machine, the valve device can comprise a third valve and a fourth valve connected in parallel to the third valve, wherein the third valve and the fourth valve can be fluidically connected to the first chamber, wherein, when the third valve is in a flow position of the third valve and the fourth valve is in a blocking position of the fourth valve, the first chamber can be depressurized orcan be vented, preferably quickly vented, wherein, when the third valve is in a blocking position of the third valve and the fourth valve is in a flow position of the fourth valve, the first chamber can be pressurized, wherein, when the third valve is in the blocking position of the third valve and the fourth valve is in the blocking position of the fourth valve, the first chamber can be closed pressure-tight, wherein preferably the third valve and the fourth valve can each be designed as a 2 / 2-way valve. The fourth valve can be fluidically connected to the compressed air generator or compressor.

[0021] In a preferred embodiment of the cleaning machine, the cleaning machine can comprise a stop device, wherein the stop device can comprise at least one, preferably two, first stop elements for limiting the forward movement of the pushing device and the pushing device can comprise at least one, preferably two, first counter-stop elements for stopping against the first stop element and / or the stop device can comprise at least one, preferably two, second stop elements for limiting the backward movement of the pushing device and the pushing device can comprise at least one, preferably two, second counter-stop elements for stopping against the second stop element. The first stop element or the first stop elements can be arranged on a support of the stop device. The support can be guided in at least one, preferably two, guide means of the stop device, preferably designed as a guide rail.The first stop element and / or the second stop element and / or the first counter-stop element and / or the second counter-stop element can be designed with damping, preferably spring damping. Preferably, the longitudinal axes of the counter-stop elements lie in the horizontal plane in which the longitudinal axis of the plunger and the longitudinal axis of the cylinder can lie.

[0022] In a preferred embodiment of the cleaning machine, the cleaning machine can comprise a preferably hydraulic adjustment device for adjusting a position of the first stop element. By adjusting the position of the first stop element, a travel distance over which the impact device can move during the forward movement can be adjusted. In other words, by adjusting the position of the first stop element, a stroke of the linear actuator or cylinder can be adjusted. This also allows the insertion depth of the impactor into the respective blowpipe to be adapted to the length of the respective blowpipe. The adjustment device can comprise a hydraulic cylinder. Furthermore, the adjustment device can comprise a hydraulic pump and / or a valve, preferably a proportional valve, for actuating the hydraulic cylinder. Furthermore, the adjustment device can comprise a container for storing a hydraulic fluid.Furthermore, the adjustment device comprises a fluid circuit.

[0023] In a preferred embodiment of the cleaning machine, the impact device can comprise a plurality of, preferably three, plungers and / or the drive device can comprise a plurality of, preferably two, linear actuators. By means of the plurality of plungers, several blowpipes can be cleaned simultaneously. The plungers can preferably be arranged in a, preferably horizontally aligned, row. The plungers can then run in a, preferably horizontally aligned, common plane. Furthermore, the plungers in the row can be arranged at equal distances from one another. A horizontal distance between two adjacent plungers in the row of plungers can correspond to a horizontal distance between two adjacent blowpipes in the row of blowpipes. Furthermore, the impact device can comprise a support on which the plungers can be arranged. By means of a plurality of linear actuators, an impact force can be increased.The linear actuators can drive the carrier together with the plungers arranged on the carrier.

[0024] In a preferred embodiment of the cleaning machine, the cleaning machine can comprise a frame on which all components of the cleaning machine can be arranged. In a preferred embodiment of the cleaning machine, the cleaning machine can comprise a detection device for detecting a number of plungers arranged on the plunger device.

[0025] In a preferred embodiment of the cleaning machine, the detection device may comprise at least one inductive sensor.

[0026] In a preferred embodiment of the cleaning machine, a drilling device for cleaning the blowpipe by drilling through the blowpipe can be arranged on the cleaning machine, wherein the drilling device can comprise at least one drilling rod and a boring mechanism for driving the drilling rod. The ramming device can be removable from the cleaning machine, so that the drilling device can be arranged on the cleaning machine instead of the ramming device. A longitudinal axis of the drilling rod, when the drilling device is arranged on the cleaning machine, can be aligned with a longitudinal axis of a central ram when an odd number of rams, preferably three, is provided, when the ramming device is arranged on the cleaning machine.

[0027] In a preferred embodiment of the cleaning machine, the cleaning machine can comprise a measuring system for detecting a position of the blowpipe(s), wherein the plunger and the blowpipe(s) can be aligned with one another based on the position of the blowpipe(s). The plunger and the blowpipe(s) can be aligned with one another by moving the cleaning machine along the track and / or by rotating the container about a preferably horizontally oriented longitudinal axis of the container. The measuring system can comprise a first measuring device for determining a distance of the cleaning machine or the first measuring device from the converter or blowpipe(s). The first measuring device can comprise at least one, preferably two, laser sensors. Furthermore, the measuring system can comprise a second measuring device for determining a position of the cleaning machine along the track.The second measuring device can comprise at least one position sensor, preferably a rotary encoder.

[0028] In a preferred embodiment of the cleaning machine, the cleaning machine can comprise a control device for controlling the cleaning machine. The control device can, in particular, control the valve device for controlling the cylinder. In particular, the control device can control the valve device for switching between the two operating modes.

[0029] Further advantageous embodiments of the cleaning machine emerge from the descriptions of the features of the subclaims referring back to method claim 9.

[0030] The arrangement according to the invention comprises a converter, for example a Peirce-Smith converter, with a plurality of blowpipes, wherein the blowpipes are arranged in a preferably horizontally aligned row laterally on a container of the converter, wherein a gas, preferably oxygen, can be blown into the melt through the blowpipes below a level of a melt that can be received in the container, wherein the arrangement comprises a cleaning machine according to the invention. The arrangement can comprise a track on which the cleaning machine can be moved. The converter can comprise at least two blowpipes. The container can be designed as a cylindrical drum. Furthermore, the container can be rotatable about a preferably horizontally aligned longitudinal axis of the container.

[0031] In the method according to the invention for cleaning at least one blowpipe of a plurality of blowpipes of a converter, for example a Peirce-Smith converter, by means of a cleaning machine, wherein the blowpipes are arranged in a preferably horizontally aligned row laterally on a container of the converter, wherein a gas, in particular oxygen, can be blown into the melt through the blowpipes below a level of a melt that can be accommodated in the container, the cleaning machine is moved on a track, preferably designed as a rail guide, running along the row of blowpipes, wherein the cleaning machine comprises an impact system, wherein the impact system comprises an impact device with at least one ram and a drive device with at least one linear actuator, wherein the ram and the blowpipe are aligned with each other, wherein, when the ram is aligned with the blowpipe,by means of the drive device, the pushing device is driven to carry out a forward movement of the pushing device, in which the plunger is transferred from a retracted position of the plunger to an advancing position of the plunger, and a backward movement of the pushing device, in which the plunger is transferred from the advancing position to the retracted position, wherein the plunger is inserted into the blowpipe through an opening of the blowpipe during the transfer from the retracted position to the advancing position for piercing the blowpipe to clean the blowpipe and is subsequently guided out of the blowpipe during the transfer from the advancing position to the retracted position, wherein the linear actuator is designed as a, preferably pneumatic, double-acting cylinder, wherein the cylinder has a piston, a first chamber and a second chamber,The first chamber is pressurized to execute a forward movement of the piston for executing the forward movement of the impact device, and the second chamber is pressurized at least to execute a backward movement of the piston for executing the backward movement of the impact device. The impact system comprises a valve device fluidically connected to the cylinder for controlling the cylinder. The cylinder is designed without a piston rod and / or the second chamber can be selectively depressurized, sealed pressure-tight, or pressurized via the valve device. For the advantageous effects of the method according to the invention, reference is made to the description of the advantages of the cleaning machine according to the invention.

[0032] During the forward movement of the piston, the piston can be moved from a first end position to a second end position. During the backward movement of the piston, the piston can be moved from the second end position to the first end position.

[0033] The first chamber can be separated from the second chamber by the piston.

[0034] Before the piston executes its forward movement, the first chamber can be depressurized when the piston is in its first end position. Atmospheric pressure can then prevail in the first chamber. Alternatively, before the piston executes its forward movement, the first chamber can be pressure-tightly sealed when the piston is in its first end position. Atmospheric pressure can nevertheless prevail in the first chamber. During the piston's reverse movement, the first chamber can be depressurized, preferably permanently.

[0035] In a preferred embodiment of the method, in a first operating mode of the cleaning machine, the second chamber can be continuously depressurized during the forward movement of the piston. Accordingly, the second chamber can be continuously depressurized while the piston moves from the first end position to the second end position. This allows the pressure in the second chamber to be maintained at atmospheric pressure. This prevents the piston from decelerating.

[0036] In a preferred embodiment of the method, in the first operating mode, the first chamber can be continuously pressurized during the forward movement of the piston. Accordingly, the first chamber can be continuously pressurized while the piston moves from the first end position to the second end position.

[0037] In one embodiment of the method, in the first operating mode, the second chamber can be or be depressurized before the piston executes its forward movement. Accordingly, before the piston executes its forward movement, the second chamber can be or be depressurized when the piston is in the first end position. Atmospheric pressure can therefore prevail in the first chamber before the piston executes its forward movement. If the second chamber is or is initially depressurized, the piston can accelerate relatively quickly, reach a relatively high speed, and build up a force relatively quickly.

[0038] In a preferred embodiment of the method, in a second operating mode of the cleaning machine, during the forward movement of the piston, the second chamber can be relieved of pressure and subsequently sealed pressure-tight. Accordingly, during the forward movement of the piston, the second chamber can be temporarily relieved of pressure and temporarily sealed pressure-tight. Then, during the forward movement of the piston, the second chamber can be relieved of pressure while the piston moves from the first end position to a first intermediate position of the piston and subsequently sealed pressure-tight while the piston moves from the first intermediate position to the second end position.

[0039] In an advantageous embodiment of the method, in the second operating mode, when the piston is moving forward, the first chamber can be pressurized and subsequently relieved of pressure. Accordingly, when the piston is moving forward, the first chamber can be temporarily pressurized and temporarily relieved of pressure. Then, when the piston is moving forward, the first chamber can be relieved of pressure while the piston is moving from the first end position to a second intermediate position, and subsequently relieved of pressure while the piston is moving from the second intermediate position to the second end position. This can reduce the consumption of expensive compressed air. Due to the inertia of the piston, the piston can move from the second intermediate position to the second end position. The pressure in the first chamber can be relieved after the second chamber has been sealed pressure-tight.In other words, the second intermediate layer can be provided between the first intermediate layer and the second end position.

[0040] In one embodiment of the method, in the second operating mode, before the piston executes the forward movement, the second chamber can be or become pressurized and subsequently sealed pressure-tight. Accordingly, before the piston executes the forward movement, with the piston in the first end position, the second chamber can be or become pressurized and subsequently sealed pressure-tight. The pressurization of the second chamber can result from a previous pressurization of the second chamber to execute a backward movement of the piston to execute the backward movement of the impact device. A pressure which can be greater than atmospheric pressure can then prevail in the pressure-tightly sealed second chamber. The pressure can correspond to the operating pressure or output pressure of the compressed air generator or compressor.Once the second chamber has been pressure-tightly closed, the first chamber can be pressurized with the piston in its first end position. The pressure in the first chamber can then be as high as the pressure in the second chamber. Accordingly, the pressure in both the first chamber and the second chamber can correspond to the operating pressure or output pressure of the compressed air generator or compressor. The pressure relief of the second chamber can then be initiated to execute the forward movement of the piston, whereby the first chamber can continue to be pressurized. Alternatively, the pressurization of the first chamber and the pressure relief of the second chamber can also be initiated simultaneously with the piston in its first end position.When the piston is moving forward, the second chamber can be relieved of pressure at least temporarily, while the first chamber can be pressurized at least temporarily.

[0041] The cleaning machine can be operated in the first operating mode or in the second operating mode.

[0042] The cleaning machine can be switched from the first operating mode to the second operating mode or vice versa.

[0043] Further advantageous embodiments of the method emerge from the descriptions of the features of the subclaims referring back to device claim 1.

[0044] Preferred embodiments of the invention are explained below with reference to the accompanying drawings.

[0045] They show:

[0046] Fig. 1 is a side view of a cleaning machine;

[0047] Fig. 2 is a plan view of the cleaning machine;

[0048] Fig. 3 is a perspective side view of the cleaning machine;

[0049] Fig. 4 is a side view of the cleaning machine with rams of a ramming device of a ramming system of the cleaning machine inserted into ram pipes of a row of ram pipes;

[0050] Fig. 5 is a top view of the cleaning machine with the plungers inserted into the blowpipes; Fig. 6 is a front view of the cleaning machine with the plungers inserted into the blowpipes;

[0051] Fig. 7 a side view of the cleaning machine as a partial section;

[0052] Fig. 8 is a hydraulic circuit diagram of a hydraulic adjustment device of the cleaning machine;

[0053] Fig. 9a is a pneumatic circuit diagram of a shock system of a cleaning machine known from the prior art in a first configuration of the shock system or of a valve device of the shock system;

[0054] Fig. 9b is a pneumatic circuit diagram of the impact system of the cleaning machine known from the prior art in a second configuration of the impact system or the valve device;

[0055] Fig. 10a is a pneumatic circuit diagram of a shock system of a cleaning machine in a first operating mode of the cleaning machine in a first configuration of the shock system or of a valve device of the shock system;

[0056] Fig. 10b is a pneumatic circuit diagram of the impact system in the first operating mode in a second configuration of the impact system or the valve device;

[0057] Fig. 11 a is a pneumatic circuit diagram of the impact system in a second operating mode of the cleaning machine in a first configuration of the impact system or the valve device;

[0058] Fig. 11b shows a pneumatic circuit diagram of the impact system in the second operating mode in a second configuration of the impact system or the valve device; Fig. 11c shows a pneumatic circuit diagram of the impact system in the second operating mode in a third configuration of the impact system or the valve device;

[0059] Fig. l ld a pneumatic circuit diagram of the impact system in the second operating mode in a fourth configuration of the impact system or the valve device;

[0060] Fig. I le is a pneumatic circuit diagram of the impact system in the second operating mode in a fifth configuration of the impact system or the valve device;

[0061] Fig. 12a is a diagrammatic representation of a pressure difference in pneumatic cylinders of a drive device of the impact system as a function of time for the first operating mode and the second operating mode;

[0062] Fig. 12b is a diagrammatic representation of a piston speed as a function of time for the first operating mode and the second operating mode.

[0063] For the sake of simplicity, objects of the same construction or function are sometimes designated by the same reference symbol.

[0064] 1 to 7 shows a cleaning machine 10 for cleaning blowpipes 11 of a converter (not shown in detail here), wherein the blowpipes 11 are arranged in a horizontally aligned row. The blowpipes 11 are usually arranged laterally on a container of the converter. The blowpipes 11 can be embedded in a fireproof lining of a wall of the container. Each blowpipe 11 has a through-hole (not shown here). Each blowpipe 11 or through-hole has an opening 12 and a further opening 13. Furthermore, each blowpipe 11 has a closure element (not shown here), in particular a ball valve or flap valve, which closes the respective opening 12. Furthermore, each blowpipe 11 has a yet further opening 14 which opens into the respective through-hole.When viewed from the blowpipes 11 arranged on the container, the openings 12 and the further openings 14 are located outside the container, and the further openings 13 are located inside the container. Through the further openings.

[0065] 14, a gas, in particular oxygen, can be blown into the melt below a level of a melt that can be accommodated in the container. The closure elements prevent the gas from escaping via the openings 12. Since the blowpipes 11 are located below the level, deposits or crusts regularly form in the blowpipes 11, i.e., in particular in the through holes, but also in an area around the other openings 13 within the container. Therefore, the blowpipes 11 must be cleaned of these deposits or crusts from time to time in order to prevent or eliminate blockages in the blowpipes 11. This is done by means of the cleaning machine 10.

[0066] The cleaning machine 10 is arranged on a track designed as a rail guide, running along the row of blowpipes 11

[0067] 15 is designed to be movable, wherein the cleaning machine 10 comprises a pushing system 16, wherein the pushing system 16 comprises a pushing device 17 with three rod-like pushers 19 arranged on a carrier 18 of the pushing device 17 and a drive device 20 with two linear actuators 21, which are designed as rodless, pneumatic, double-acting cylinders, wherein the pushers 19 and three of the blow pipes 11 can be brought into alignment with one another, wherein, when the pushers 19 are aligned with the three respective blow pipes 11, the pushing device 17 can be moved forwards by means of the drive device 20, in which the pushers 19 can be transferred from a retracted position of the pushers 19 into an advancing position of the pushers 19, and a backwards movement of the pushing device 17, in which the Ram 19 can be moved from the advance position to the retraction position,wherein the plungers 19 can be inserted into the three respective blowpipes 11 through the three respective openings 12 during the transfer from the retracted position to the advance position for cleaning the respective three blowpipes 11 by opening or lifting the closure elements and can subsequently be guided out of the three respective blowpipes 11 through the three respective openings 12 during the transfer from the advance position to the retracted position.

[0068] The cleaning machine 10 comprises a measuring system 22 for detecting positions of the blowpipes 11, wherein the plungers 19 and the three respective blowpipes 11 can be brought into alignment with one another based on the detected positions of the blowpipes 11. The measuring system 22 comprises a first measuring device 23 for determining a distance of the cleaning machine 10 or the first measuring device 23 from the converter or the blow pipes 11, wherein the first measuring device 23 comprises two laser sensors 24 arranged laterally offset outwards from the pushing device 17 or the tappets 19 and offset rearwards from the pushing device 17 or the tappets 19 on the cleaning machine 10, wherein the measuring system 22 comprises a second measuring device 25 for determining a position of the cleaning machine 10 on the track 15, wherein the second measuring device 25 comprises a rotary encoder 26.By means of the rotary encoder 26, an angle of rotation of a shaft (not shown here) of an electric drive motor (not shown here) of the cleaning machine 10, which serves to move the cleaning machine 10 on the track 15, is determined, wherein on the basis of the determined angle of rotation a distance covered by the cleaning machine 10 on the track 15 is determined, which in turn is used to determine the position of the cleaning machine 10 on the track 15. By means of the measuring system 22, the positions of the blow pipes 11 are detected on the basis of the openings 12, wherein as the cleaning machine 10 moves on the track 15, the laser sensors 24 or laser beams (not shown here) emitted by the laser sensors 24 scan the converter at a height of the blow pipes 11 or openings 12, wherein by means of the measuring system 22 a distance of the cleaning machine 10 or the laser sensors 24 from the converter orthe blowpipes 11 as a function of the position of the cleaning machine 10 on the track 15.

[0069] The cleaning machine 10 further comprises a stop device 27, wherein the stop device 27 comprises two first stop elements 28 for limiting the forward movement of the pushing device 17 and the pushing device 17 comprises two first counter-stop elements 29 for stopping against the first stop elements 28 and the stop device 27 comprises two second stop elements 30 for limiting the backward movement of the pushing device 17 and the pushing device 17 comprises two second counter-stop elements 31 for stopping against the second stop elements 30, wherein the cleaning machine 10 comprises a hydraulic adjustment device 33 comprising a hydraulic cylinder 32 for adjusting a position of the first stop elements 28. The first counter-stop elements 29 and the second counter-stop elements 31 are arranged on the carrier 18.The first stop elements 28 are arranged on a support 34 of the stop device 27, which is guided in a guide means of the stop device 27, not shown here, designed as a guide rail.

[0070] Fig. 8 shows a hydraulic circuit diagram of the hydraulic adjustment device 33. The double-acting hydraulic cylinder 32, by means of which the position of the first stop elements 28 or the carrier 34 can be adjusted, is integrated into a fluid circuit 35 of the adjustment device 33. The hydraulic cylinder 32 has a piston 36, a first chamber 37 and a second chamber 38, wherein the first chamber 37 is separated from the second chamber 38 via the piston 36. By means of a hydraulic pump 39 of the adjustment device 33, a hydraulic fluid can be conveyed from a container 40 of the adjustment device 33, wherein depending on the position of a valve 41 of the adjustment device 33, which is designed as a 4 / 3-way valve, the first chamber 37 or the second chamber 38 can be selectively supplied with the hydraulic fluid. The hydraulic pump 39, the reservoir 40 and the valve 41 are integrated into the fluid circuit 35.Furthermore, a connection between the first chamber 37 or the second chamber 38 and the valve 41 can be interrupted via a valve 42 or 43 of the adjustment device 33, respectively, which are integrated into the fluid circuit 35, when the first stop elements 28 or the carrier 34 have been adjusted to a desired position. Furthermore, a valve 44 of the adjustment device 33, designed as a pressure compensation valve, is provided, via which the first chamber 37 is connected to the second chamber 38.

[0071] A combination of Figs. 9a and 9b shows a pneumatic circuit diagram of a shock system 45 of a cleaning machine known from the prior art but not shown in detail here. The shock system 45 comprises a drive device 46 with two linear actuators 47, each designed as a double-acting pneumatic cylinder, and a valve device 48 with a first valve 49 designed as a 3 / 2-way valve and a second valve 50 designed as a 3 / 2-way valve. The shock system further comprises a shock device 51 with three tappets 52. Each cylinder has a piston 53, a first chamber 54, and a second chamber 55, wherein the first chamber 54 is separated from the second chamber 55 by the piston 53. The second chamber 55 or first chamber 54 can be optionally depressurized, vented or pressurized via the valve 49 or 50.The pressure is applied by means of a compressor 56 of the shock system 45, with which the valve 49 or 50 is fluidly connected.

[0072] In a first configuration of the impact system 45 or the valve device 48 shown in Fig. 9a, the plungers 52 are in a retracted position. The second chamber 55 or first chamber 54 is depressurized or vented via the valve 49 or 50. Therefore, atmospheric pressure prevails in the first chamber 54 or second chamber 55.

[0073] In a second configuration of the impact system 45 or the valve device 48 shown in Fig. 9b, the impact device 51 executes a forward movement of the impact device 51, during which the plungers 52 are transferred from the retracted position to an advanced position of the plungers 52. During the execution of the forward movement of the impact device 51, the first chamber 54 is permanently pressurized via the valve 50, and the second chamber 55 is permanently depressurized or vented via the valve 49.

[0074] A summary of Fig. 10a to 11e shows, as pneumatic circuit diagrams, a shock system 57 of a cleaning machine not shown in detail here, which can, however, in particular be the cleaning machine 10, which comprises a drive device 79 with two linear actuators 58 designed as double-acting pneumatic cylinders and a valve device 59 with four valves 60, 61, 62, 63, each designed as a 2 / 2-way valve. The shock system 57 further comprises a shock device 64 with three tappets 65. Each cylinder has a piston 66, a first chamber 67 and a second chamber 68, the first chamber 67 being separated from the second chamber 68 by the piston 66. The valve 60 and the valve 61 connected in parallel to the valve are fluidly connected to the second chambers 68. The valve 63 and the valve 62 connected in parallel to the valve 63 are fluidically connected to the first chambers 67. The pressure is controlled via the valves 60, 61 and62, 63, the second chambers 68 and first chambers 67 can be optionally depressurized, sealed pressure-tight, or pressurized. Pressurization is achieved by a compressor 69 of the impact system 57. The valves 61 and 63 are fluidly connected to the compressor 69. Figs. 10a and 10b show a first operating mode of the cleaning machine. Figs. 11a to 11e show a second operating mode of the cleaning machine.

[0075] In a first configuration of the impact system 57 or the valve device 59 shown in Fig. 10a, the plungers 65 are in a retracted position. The second chambers 68 and the first chambers 67 are depressurized or vented via the valves 60 and 62, each of which is in a flow position. Therefore, atmospheric pressure prevails in the first chambers 67 and the second chambers 68. The valves 61 and 63 are each in a blocking position.

[0076] In a second configuration of the impact system 57 or the valve device 59 shown in Fig. 10b, the impact device 64 executes a forward movement of the impact device 64, in which the plungers 65 are moved from the retracted position to an advanced position of the plungers 65. The second chambers 68 are depressurized or vented via the valve 60, which is in the flow position, while the first chambers 67 are permanently pressurized via the valve 63, which is in the flow position. The valves 61 and 62 are in the blocking position.

[0077] In a third configuration of the impact system 57 or the valve device 59, not shown here, the impact device 64 performs a backward movement of the impact device 64, in which the plungers 65 are moved from the advance position into the retracted position of the plungers 65. The second chambers 68 are pressurized, preferably permanently, via the valve 61, which is in the flow position, while the first chambers 67 are depressurized or vented, preferably permanently, via the valve 62, which is in the flow position. The valves 60 and 63 are in the blocking position. In a first configuration of the impact system 57 or the valve device 59, shown in Fig. 1a, the plungers 65 are in the retracted position. The pistons 66 are in a first end position of the pistons 66, not visible here. The second chambers 68 are pressurized via the valve 61, which is in the flow position.Therefore, the pressure in the second chambers 68 corresponds to the operating pressure of the compressor 69. The valve 60 is in the closed position. Atmospheric pressure prevails in the first chambers 67. The valves 62 and 63 are in the closed position. The first chambers 67 are therefore pressure-tight. The valves 62 and 63 could also be in the flow position, so that the first chambers 67 are depressurized or vented.

[0078] In a second configuration, third configuration, or fourth configuration of the impact system 57 or the valve device 59 shown in Fig. 11b, 11c, or 11d, the impact device 64 executes a forward movement of the impact device 64, in which the plungers 65 are moved from the retracted position into an advanced position of the plungers 65. In the second configuration, the pistons 66 are moved from the first end position into a first intermediate position of the pistons 66. In the third configuration, the pistons 66 are moved from the first intermediate position into a second intermediate position of the pistons 66. In the fourth configuration, the pistons 66 are moved from the second intermediate position into a second end position of the pistons 66.

[0079] In the second configuration shown in Fig. 11b, the second chambers 68 are depressurized or vented via the valve 60 which is in the flow position, and the first chambers 67 are pressurized via the valve 63 which is in the flow position. The valves 61 and 62 are in the blocking position. The pressure previously built up in the second chambers 67 is reduced to atmospheric pressure. When the pistons 66 have reached the first intermediate position, according to the third configuration shown in Fig. 11c, the second chambers 68 are closed pressure-tight via the valves 60, 61 which are in the blocking position. The first chambers 67 continue to be pressurized via the valve 63. The valve 62 is in the blocking position. Air in the second chambers 68 is compressed, which acts on the pistons 66 like a counterforce that slows them down.

[0080] When the pistons 66 have reached the second intermediate position, the first chambers 67 are depressurized or vented via the valve 62 according to the fourth configuration shown in Fig. 11d. The valve 63 is in the closed position. The second chambers 68 are further sealed pressure-tight by the valves 60, 61, which are in the closed position. In the fourth configuration, the pistons 66 move to the second end position.

[0081] In the fifth configuration of the impact system 57 or the valve device 59 shown in Fig. 11e, the impact device 64 is moved back, with the plungers 65 being moved from the advance position back to the retracted position. Therefore, the second chambers 68 are pressurized via the valve 61. The valve 60 is in the blocking position. The first chambers 67 are depressurized or vented via the valve 62. The valve 63 is in the blocking position. Upon reaching the retracted position, the impact device 64 moves into the first configuration of the impact device 64.

[0082] In a method for cleaning a blowpipe, the impact system 57 or the valve device 59 can successively pass through the three configurations in the first operating mode or the five configurations in the second operating mode.

[0083] Fig. 12a shows diagrammatically a course 70 or 71 of a

[0084] Pressure difference in the linear actuators 58 or cylinders in the first operating mode or second operating mode as a function of time.

[0085] The pressure difference is plotted on an ordinate 72 in bar, while the time is plotted on an abscissa 73 in s. A vertical line 74 marks a point in time at which the plungers 65 impact the ball valves (not shown here) of blowpipes (not shown here).

[0086] Figure 12b diagrammatically shows a curve 75 or 76 of a piston speed or speed of the impact device 64 in the first operating mode or second operating mode, respectively, as a function of time. The speed is plotted in m / s on an ordinate 77, while a time in s is plotted on an abscissa 78.

[0087] From Figs. 12a and 12b it can be seen that in the first operating mode, the piston force is built up comparatively faster and a comparatively higher maximum piston speed is reached than in the second operating mode. However, the piston force and the piston speed decrease in the second operating mode after the

[0088] Impact on the ball valves is comparatively slower than in the first operating mode.

Claims

Patent claims 1. Cleaning machine (10) for cleaning at least one blowpipe (11) of a plurality of blowpipes of a converter, for example a Peirce-Smith converter, wherein the blowpipes are arranged in a preferably horizontally aligned row laterally on a container of the converter, wherein a gas, in particular oxygen, can be blown into the melt through the blowpipes below a level of a melt that can be received in the container, wherein the cleaning machine is designed to be movable on a track (15), preferably designed as a rail guide, running along the row of blowpipes, wherein the cleaning machine comprises an impact system (16, 57), wherein the impact system comprises an impact device (17, 64) with at least one plunger (19, 65) and a drive device (20, 79) with at least one linear actuator (21, 58), wherein the plunger and the blowpipe are arranged in relation to one another in Escape can be brought, whereby,when the ram is aligned with the blowpipe, by means of the drive device, the impact device to carry out a forward movement of the impact device, in which the ram moves from a retracted position of the ram into a forward position of the, plunger is transferable, and a backward movement of the impact device, in which the plunger is transferable from the advance position to the retracted position, wherein the plunger can be inserted into the blow tube through an opening (12) of the blow tube during the transfer from the retracted position to the advance position for piercing the blow tube in order to clean the blow tube and can subsequently be removed from the blow tube during the transfer from the advance position to the retracted position, wherein the linear actuator is designed as a, preferably pneumatic, double-acting cylinder, wherein the cylinder has a piston (66), a first chamber (67) and a second chamber (68), wherein the first chamber can be pressurized to execute a forward movement of the piston to execute the forward movement of the impact device and the second chamber can be pressurized at least to execute a backward movement of the piston to execute the backward movement of the impact device,wherein the impact system comprises a valve device (59) fluidically connected to the cylinder for controlling the cylinder, characterized in that the cylinder is designed without a piston rod and / or the second chamber can be selectively pressure-relieved, pressure-tightly closed or pressurized via the valve device.

2. Cleaning machine according to claim 1, characterized in that the valve device (59) comprises a first valve (60) and a second valve (61) connected in parallel to the first valve, wherein the first valve and the second valve are fluidically connected to the second chamber (68), wherein, when the first valve is in a flow position of the first valve and the second valve is in a blocking position of the second valve, the second Chamber can be depressurized, wherein, when the first valve is in a blocking position of the first valve and the second valve is in a flow position of the second valve, the second chamber can be pressurized, wherein, when the first valve is in the blocking position of the first valve and the second valve is in the blocking position of the second valve, the second chamber can be closed pressure-tight, wherein preferably the first valve and the second valve are each designed as a 2 / 2-way valve.

3. Cleaning machine according to claim 1 or 2, characterized in that the first chamber (67) can be optionally pressure-relieved, pressure-tightly closed or pressurized via the valve device (59).

4. Cleaning machine according to claim 3, characterized in that the valve device (59) comprises a third valve (62) and a fourth valve (63) connected in parallel to the third valve, wherein the third valve and the fourth valve are fluidically connected to the first chamber (67), wherein, when the third valve is in a flow position of the third valve and the fourth valve is in a blocking position of the fourth valve, the first chamber can be depressurized, wherein, when the third valve is in a blocking position of the third valve and the fourth valve is in a flow position of the fourth valve, the first chamber can be pressurized, wherein, when the third valve is in the blocking position of the third valve and the fourth valve is in the blocking position of the fourth valve, the first chamber can be closed in a pressure-tight manner,wherein preferably the third valve and the fourth valve are each designed as a 2 / 2-way valve., 5. Cleaning machine according to one of the preceding claims, characterized in that the cleaning machine (10) comprises a stop device (27), wherein the stop device comprises at least one, preferably two, first stop elements (28) for limiting the forward movement of the pushing device (17, 64) and the pushing device comprises at least one, preferably two, first counter-stop elements (29) for stopping against the first stop element, wherein the cleaning machine comprises a, preferably hydraulic, adjusting device (33) for adjusting a position of the first stop element.

6. Cleaning machine according to one of the preceding claims, characterized in that the pushing device (17, 64) comprises a plurality of, preferably three, push rods (19, 65) and / or the drive device (20, 79) comprises a plurality of, preferably two, linear actuators (21, 58).

7. Cleaning machine according to one of the preceding claims, characterized in that the cleaning machine (10) comprises a detection device for detecting a number of plungers (19, 65) arranged on the pusher device (17, 64).

8. An arrangement comprising a converter, for example a Peirce-Smith converter, with a plurality of blowpipes (11), the blowpipes being arranged in a preferably horizontally aligned row laterally on a container of the converter, a gas, preferably oxygen, being able to be blown into the melt through the blowpipes below a level of a melt that can be received in the container, the arrangement comprising a cleaning machine (10) according to one of the preceding claims.

9. A method for cleaning at least one blowpipe (11) of a plurality of blowpipes of a converter, for example a Peirce-Smith converter, by means of a cleaning machine (10), wherein the blowpipes are arranged in a preferably horizontally aligned row laterally on a container of the converter, wherein a gas, in particular oxygen, can be blown into the melt through the blowpipes below a level of a melt that can be received in the container, wherein the cleaning machine is moved on a track (15), preferably designed as a rail guide, running along the row of blowpipes, wherein the cleaning machine comprises an impact system (16, 57), wherein the impact system comprises an impact device (17, 64) with at least one plunger (19, 65) and a drive device (20, 79) with at least one linear actuator (21, 58), wherein the plunger and the blowpipe are brought into alignment with one another, where,When the plunger is aligned with the blowpipe, the drive device drives the pushing device to execute a forward movement of the pushing device, in which the plunger is transferred from a retracted position of the plunger to an advancing position of the plunger, and a backward movement of the pushing device, in which the plunger is transferred from the advancing position to the retracted position, wherein the plunger is inserted into the blowpipe through an opening (12) of the blowpipe during the transfer from the retracted position to the advancing position for piercing the blowpipe in order to clean the blowpipe and is subsequently led out of the blowpipe during the transfer from the advancing position to the retracted position, wherein the linear actuator is designed as a, preferably pneumatic, double-acting cylinder, wherein the cylinder has a piston (66), a first chamber (67) and a second chamber (68),wherein the first chamber is designed to carry out a forward movement of the piston to carry out the forward movement of the impact device and the second chamber is designed to carry out at least one, Reverse movement of the piston is pressurized to carry out the backward movement of the impact device, wherein the impact system comprises a valve device (59) fluidically connected to the cylinder for controlling the cylinder, characterized in that the cylinder is designed without a piston rod and / or the second chamber can be selectively pressure-relieved, pressure-tightly closed or pressurized via the valve device.

10. The method according to claim 9, characterized in that in a first operating mode of the cleaning machine (10) when the piston (66) is moved forward, the second chamber (68) is permanently depressurized.

11. Method according to claim 10, characterized in that in the first operating mode, when the piston (66) is moving forward, the first chamber (67) is permanently pressurized.

12. Method according to one of claims 9 to 11, characterized in that in a second operating mode of the cleaning machine (10) when the piston (66) is moved forward, the second chamber (68) is relieved of pressure and subsequently closed in a pressure-tight manner.

13. Method according to claim 12, characterized in that that in the second operating mode, when the piston (66) is moved forward, the first chamber (67) is pressurized and subsequently relieved of pressure.

14. Method at least according to claim 10 and 12, characterized in that the cleaning machine (10) is switched from the first operating mode to the second operating mode or vice versa.

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