EP2040021B1 - Cleaning device with nozzle fitting for cooling pipes - Google Patents

Abstract

The device has an injection-nozzle carrier arranged on top of cooling registers in a displaceable manner in a longitudinal direction of a cooling pipe, bearing a nozzle holder (50) with cleaning nozzles. A shallow beam run together with cooling fins transverse to a longitudinal direction of cooling pipes. The shallow beam includes variations from middle of a cooling pipe gap. A diameter of the cooling pipes is smaller than 40 millimeters, calculated without fins, not exceeding 5 degrees, or larger than 60 millimeters to 150 millimeters not exceeding 15 degrees.

Description

The invention relates to a cleaning method with nozzle for cooling tubes in heat exchangers, in particular air conditioning systems, and an associated cleaning device.

Air condensation plants (Lukos) are used as a closed system for condensing the exhaust steam or the excess steam of turbine plants. The total cooling surface is designed for the amount of steam produced. It is assumed that a certain heat transfer from the cooling surface into the ambient air. The heat transfer, however, does not remain constant. On the cooling surfaces it comes to the outside for pollution. Pollution is caused, inter alia, by pollen, leaves, industrial emissions, flue dust and leads to deposits on the cooling surfaces. As a result, the heat transfer deteriorates.
Partly the cooling registers are closing. In places, the heat transfer is not only drastically reduced. There may also be overheating with various adverse consequences.

Initially occurring impurities can be compensated by possibly existing speed reserves of the fans. This already has the disadvantage of higher energy consumption for operating the system.
Further pollution can not be compensated. It leads to a reduction of the heat transfer and thus to a reduced cooling capacity for the steam consumption.

As a result of the decreasing cooling effect, the vapor pressure in the exhaust steam line increases. The turbine loses power. The power generation of the generator is reduced. Usually, the systems react to this. For example, if turbines are designed for an exhaust steam pressure of O, 2bar absolute, they are switched off by monitoring devices when the vapor pressure rises to 0.8 bar.

With water coolers and product coolers, as they occur preferably in the chemical industry, the same problems are found. Again, a decrease in the heat transfer initially be compensated by existing air volume reserves. Thereafter, however, there is a steady increase in temperature in the water cycle or product flow. This will lead to a malfunction in the foreseeable future.

The above relationships are well known to the operators.
It is obvious that the contamination of the cooling surfaces is counteracted by cleaning.

Previously, cleaning was done manually. The cleaning work was usually transferred to the cleaning crews, which are also subject to other cleaning work. There is a tendency to award this work as a complete package. However, the cleaning companies only had manual steam jet equipment or high pressure water jet equipment available. The success of working with a handheld device was low. It was rinsed off only the loose-fitting dirt. In addition, the cooling surfaces are often arranged in multiple layers or consist of Rippenkühlem with very high ribs. In the case of multi-layer cooling tubes, an improper procedure or the use of unsuitable equipment only causes a loosening of dirt on the upper layer and an attachment to lower rows / layers. Cooling surfaces with high ribs are at the same risk. On the way, the cooling air can even be blocked from passing through the radiator.

In addition, it has been shown on coolers with aluminum cooling fins that can be easily caused by the high pressure equipment damage to the ribs. Excessive pressure will bend the ribs if handled improperly. This is not immediately obvious to the operators, because the cooling surfaces are usually not regularly driven, i. to be watched. Thus, it is not possible to control when and who caused what damage and have encountered situations in which the radiator were unusable by cleaning.

Compared to manual cleaning, the use of cleaning devices which has been customary for some time now involves considerable progress.

An older proposal provides stationary cleaning facilities, with which a reliable cleaning of the cooling surfaces is achieved. In such cleaning devices are usually nozzle sticks with multiple rows of nozzles use. In two rows of nozzles, the nozzles of one row usually have a slope relative to the vertical to the cooling tubes, so that the cleaning jets impinge obliquely on one side of the cooling tubes. The nozzles of the second row are inclined in the opposite direction, so that the nozzles are directed against the other side of the cooling tubes. The cleaning nozzles, their position and the cleaning pressure can be adapted to the cooling surfaces. This will allow actual cleaning without the risk of damage.
Another prior proposal provides that a cleaning device for multiple cooling surfaces (cooling registers) of a system is used. This is achieved by means of a driving system. The driving system resembles a crane track, with which the device is converted from one cooling surface to the other.
However, the stationary cleaning devices and the implementable cleaning device have in common that initially a considerable investment must be made. This naturally precludes the use of such devices.

1. a) eine tragbare Reinigungsvorrichtung mit einem sich vertikal über die Höhe des Kühlregisters erstreckenden Fahrwagen geschaffen wird, der horizontal verfahrbar ist und einen darauf vertikal verfahrbaren Düsenstock trägt.
2. b) der Düsenstock mehrere Kühlrohre oder auch mehrere Kühlregister übergreift und
3. c) die Reinigungsvorrichtung eine Tragkonstruktion mit einem in Fahrrichtung des Fahrwagens verlaufenden Kantprofil besitzt und der Fahrwagen auf dem Kantprofil verfahrbar angeordnet ist und/oder die Tragkonstruktion durch Steckverbindungen längenänderbar ist

According to another older proposal of the DE 19800018 A The above problems are met by

1. a) a portable cleaning device is provided with a vertically over the height of the cooling register extending carriage, which is horizontally movable and carries a vertically movable thereon nozzle.
2. b) the nozzle sticks over a plurality of cooling tubes or even a plurality of cooling registers and
3. c) the cleaning device has a support structure with a running in the direction of travel of the trolley edge profile and the carriage is arranged movably on the edge profile and / or the support structure is length-adjustable by connectors

In this case, two or more edge profiles can be arranged side by side. However, the use of a single Kantprofile includes a special step to an optimally lightweight and at the same time functionally reliable device. The weight advantage of a single Kantprofiles is not readily apparent because several juxtaposed edge profiles have the same cost of material computationally greater bending resistance than a single edge profile. Nevertheless, it is not only on the larger moment of resistance. It is also important that the guide rollers do not cause deformation of the rolling surfaces. This leads to a minimum thickness of the rolling surfaces and edge profiles. Two minimum-thickness edge profiles can result in a greater cost of materials than a single, stable edge profile.

Preferably, the edge profile is formed as a hollow profile and length-adjustable by connectors. The extensibility facilitates working with a single device on different lugs or the like. Regardless of the edge profile of the extensibility and the connector are therefore also of particular importance. The edge profile and the plug connection are favorable for a change in length. After the older proposal, the edge profile can be composed of several parts. However, the device may also have a head and a foot and between the head and foot a changeable for length change edge profile.

The plug-in connection is brought about by means of separate spikes / pins, which engage in two pipe ends to be connected to each other. But it can also spikes / pins are attached to the pipe ends, so that engages a pipe with a mandrel / pin in the other tube.
To further weight savings, the mandrels / pins hollow or in turn be designed as tubes.
The connector may be designed self-clamping and / or designed a mechanical fuse.
Optionally, according to the older proposal at the head and foot of the device arms for different purposes, eg for supporting and / or guiding and / or holding the device and / or for holding guide rollers / wheels / discs and / or for holding drives and Be provided / or pumps.
The holders for wheels / wheels / discs can be arranged adjustable or fixed.

Optionally, the arms and / or head and / or foot may be releasably assembled from parts so that replacement in adaptation to particular needs is possible. Cheap can be a plug connection as in the edge profile. This is beneficial if the arms, head and foot are made up of the same profiles.

Preferably, the drive includes a power transmission means such as a belt, chain, rope or belt, in particular a toothed belt, and a geared motor with a drive pinion. With the rollers / wheels / discs, the power transmission means is preferably passed over the head and foot and generates the necessary tension. To generate voltage, the associated roller / wheel / disc is adjustable transversely to the longitudinal direction of the power transmission means.
The power transmission means engages the carriage and is moved by means of the geared motor. In this case, the power transmission means can be guided around the drive pinion or pressed by means of another roller / wheel / disc against the drive pinion.

To reduce weight, the use of aluminum for the profiles and a limited width of the nozzles or the nozzle assembly in the carriage contribute. The restriction is given with the number of nozzles arranged on a pipe in the nozzle.

Despite limited width, the nozzles or the nozzle block can clean all the cooling tubes below by processes along the entire width / length of the trolley. The heavy weight reduction also protects the cooling coils. This is especially important for cooling coils with sensitive cooling fins. The sensitive cooling tubes / ribs include e.g. those with a rectangular cross-section, between which the cooling fins are moved back and forth as meandemdes metal strip.

In addition, the low weight brings no risk of excessive load on the cooling coil with it.

By overlapping several cooling registers and methods of cleaning nozzles in the carriage of a cooling coil optimal work design and labor and operating time utilization is achieved.

The water supply to the cleaning device can take place via a hose line entrained. Optionally, the water through an intermediate pump on the desired pressure brought. The pump can be attached to the device or placed separately in front of the device.

In particularly wide cooling systems with a plurality of juxtaposed registers, it is advantageous to provide in the upper part of the cooling coil and / or on the holder and / or on the building rails in or on which the device is movable, so that the cleaning device to implement on an adjacent cooling coil no longer needs to be solved, but can be moved.

Also known is a cleaning device for a flat cooler, WO92 / 04589 , Although this document shows a cleaning device for a flat cooler, which is spanned by the horizontally extending cleaning device in its entire width and the design is chosen so that the movable nozzle detects the entire surface to be cleaned. However, this construction has compared to a construction, as from the DE 19800018 A1 is known, significant static disadvantages. In addition, the intended for the flat cooler cleaning device is not on cleaning devices of DE 19800018 A1 applicable. In addition, the known cleaning device is not suitable for cleaning Kühlem with different dimensions.

From the FR 2389090 and US 3843409 Cleaning devices are also known. The local construction, however, do not go beyond the state of the art WO92 / 04589 out. The DE 101 26 700 describes a cleaning method according to the preamble of claims 1 and 2.

According to another older proposal portable cleaning devices are provided.

An essential feature of the older proposal form portal-shaped bracket, under which the nozzle floor carriage is movable.

In a preferred embodiment, a conductor is attached to the temples of the cleaning device. This can be represented by the fact that the stirrups consist at least partially of a conductor profile.

Optionally, a height adjustment is provided on the ladder.

It is favorable if the ladder has foldable steps or rungs and / or a foldable railing.

1. a)es finden Flachstrahldüsen Anwendung
2. b)die Flachstrahldüsen werden vorzugsweise in einer oder mehreren Reihen angeordnet., wobei die Flachstrahldüsen in einem Abstand von 150 bis 300 mm, vorzugsweise in einem Abstand von 200 bis 250 mm, von den zu reinigenden Flächen am Kühlregister angeordnet, wobei die Düsen vorzugsweise zu benachbarten Düsen einen Abstand von 80 bis 120 mm, vorzugsweise zu benachbarten Düsen einen Abstand von 90 bis 110 mm aufweisen,
3. c) wobei die Düsen einer Reihe in der Draufsicht so gegeneinander versetzt sind, daß mit einem Strahl aus einer benachbarten Düse höchstens eine Überlappung von 10% bezogen auf Strahlbreite beim Auftreffen auf des Kühlregister stattfindet, vorzugsweise eine Überlappung von höchstens 5% bezogen auf die Strahlbreite beim Auftreffen auf das Kühlregister stattfindet,
4. cc)wobei die Flachstrahlen in der anderer Ansicht parallel zu den Kühlrohren sich jedoch um mindestens 5%, bezogen auf die Strahlbreite beim Auftreffen auf die Kühlregister, überlappen, vorzugsweise um mindestens 10%, bezogen auf die Strahlbreite beim Auftreffen auf die Kühlregister, überlappen,
5. d)wobei das Reinigungswasser mit einem Druck von bis 120 bar, vorzugsweise 40 bis 100 bar aus den Düsen austritt, noch weiter bevorzugt
6. dd)bei Kühlrohren mit ovalem oder elliptischem oder rundem Querschnitt mit einem Druck von 70 bis 100 bar austritt und
7. ddd)bei Kühlrohren mit rechteckigem Querschnitt mit einem Druck von 40 bis 50 bar austritt. und/oder
8. e)die Flachstrahlen mit Ihrer Mitte in die Kühlrohrgasse weisen, wobei die Flachstrahlen bei quer zur Längsrichtung der Kühlrohre verlaufenden Kühlrippen auch quer zur Längsrichtung der Kühlrohre verlaufen und folgende Abweichungen von der Mitte der Kühlrohrgasse aufweisen können:
9. ee)bei einem Durchmesser der Kühlrohre von kleiner 40mm, gerechnet ohne Kühlrippen, höchstens 5 Grad
10. eee)bei einem Durchmesser der Kühlrohre von 40 bis 60mm, gerechnet ohne die Kühlrippen, höchstens 10 Grad
11. eeee)bei einem Durchmesser der Kühlrohre von größer 60mm bis 150mm höchstens 15 Grad

Although in particular the portable cleaning device has proven itself, the invention has set itself the task to improve the cleaning devices yet. The invention is based on the consideration that the possibilities of changing the known cleaning device are so varied that a proper cleaning is more or less coincidence. According to the invention, despite the various forms of cleaning pipes and tube bundles, the possibilities of changing the cleaning device are severely restricted by a method according to claim 1 and claim 2 and an apparatus according to claim 8. The following measures are essential:

1. a) find it flat fan nozzles application
2. b) the flat jet nozzles are preferably arranged in one or more rows, wherein the flat jet nozzles arranged at a distance of 150 to 300 mm, preferably at a distance of 200 to 250 mm, of the surfaces to be cleaned on the cooling coil, the nozzles preferably to adjacent nozzles have a distance of 80 to 120 mm, preferably to adjacent nozzles a distance of 90 to 110 mm,
3. c) wherein the nozzles of a row in the plan view are offset from one another so that with a beam from an adjacent nozzle at most an overlap of 10% based on jet width when hitting the cooling coil takes place, preferably an overlap of at most 5% based on the beam width occurs when hitting the cooling coil,
4. cc ) the flat beams in the other view parallel to the cooling tubes but overlap by at least 5%, based on the beam width when hitting the cooling registers overlap, preferably at least 10%, based on the beam width when hitting the cooling registers overlap,
5. d) wherein the cleaning water emerges from the nozzles at a pressure of up to 120 bar, preferably 40 to 100 bar, even more preferred
6. dd ) at cooling tubes with oval or elliptical or round cross-section at a pressure of 70 to 100 bar emerges and
7. ddd ) at cooling tubes with rectangular cross-section at a pressure of 40 to 50 bar emerges. and / or
8. e) have the flat jets with their center in the cooling pipe lane, wherein the flat jets also extend transversely to the longitudinal direction of the cooling tubes cooling fins transverse to the longitudinal direction of the cooling tubes and may have the following deviations from the center of the cooling tube lane:
9. ee ) with a diameter of the cooling tubes of less than 40mm, calculated without cooling fins, at most 5 degrees
10. eee ) with a diameter of the cooling tubes from 40 to 60mm, calculated without the cooling fins, at most 10 degrees
11. eeee ) with a diameter of the cooling tubes of greater than 60mm to 150mm at most 15 degrees

The cooling fins are molded or mounted on the cooling tubes depending on the design.
The cooling ribs usually run transversely to the longitudinal direction of the cooling tubes.
The cooling fins come with different shape. Frequently, there are cooling tubes of circular cross-section, including circular-shaped fins. Such cooling tubes often interlock with your ribs. The ribs can also have the function of spacers.
Occasionally, the combination of different cooling tubes and / or different cooling fins occurs.

The flat steel nozzles are usually arranged in one or more rows.
The arrangement in rows results from the fact that the nozzles are arranged directly on a common line of the nozzle. Conveniently, two rows of nozzles on the nozzle, so that each register surface is taken in a nozzle movement through both rows of nozzles. Here, the first effective row of nozzles causes a partial cleaning and a pre-softening of the adhering dirt and the subsequent effective row of nozzles further purification. This process can be repeated several times by moving the nozzle assembly back and forth until sufficient cleaning is ensured.

The known flat jet nozzles have a widening jet. The impact area of the nozzle jet on the cooling register (plane in which the cooling tubes lie with their upper edge) includes an enlarged image of the nozzle opening. At the distances given above and usual jet cones with an angle of 22 to 40 degrees enclosed by the conical surface
In order to prevent the flat rays touching excessively and thereby excessively energy of the flat jets is destroyed, the nozzles are arranged so that the incident surfaces with its longitudinal axis to the nozzle row offset / run.

At the same time an overlap of the nozzle jets is provided in the view along the cooling tubes, because the energy of the flat jets decreases towards the edge more and thereby the cleaning effect is weaker. By this arrangement, the cleaning surfaces associated with the nozzles overlap. In the overlapping area, cleaning is intensified. As a result, the energy drop at the edge of the flat jets is compensated in whole or in part. The overlap is preferably at least 5%, preferably at least 10%, based on the impact area of the jets on the cooling register.

The offset of the nozzles is carried out either in a known manner in that the nozzles are mounted on a nozzle tube, which runs exactly transverse to the cooling tube longitudinal direction. Or the nozzles are mounted on a nozzle tube, which runs obliquely to the cooling tube longitudinal direction. In exactly transverse to the cooling tube longitudinal direction extending nozzle tube the nozzles are placed with their nozzle slot so that the exiting flat jet cuts obliquely in the plan view of the nozzle tube of this tube. At the same time the different flat jets are parallel to each other. The distance between the parallels is chosen so large that at most the above-described overlap or contact between the flat rays occurs. In the nozzle tube extending obliquely to the cooling tube longitudinal direction, the nozzles can be made with their nozzle slot so that the exiting flat jet in the plan view of the nozzle rod tube is perpendicular to the cooling tube longitudinal axis. This also results in parallel flat rays. Their distance is chosen exactly as in the previously explained parallel flat beams.

The cooling pipe alley describes the free passage between the cooling pipes. When considering the free passage, the cooling fins remain out of consideration, as long as the cooling fins run in a conventional form transverse to the longitudinal direction of the cooling tubes.

In single-layer cooling registers only one layer of cooling tubes is provided. Then the cooling pipe in the sense of the invention runs exactly perpendicular to the cooling register, if it is uniform cooling tubes. The uniform cooling tubes preferably have a symmetrical cross-section, such as cooling tubes with a circular or oval tube cross-section, as well as a rectangular tube cross-section.

The cooling fins on the cooling tubes serve to improve the heat transfer.
They follow the cross-sectional shape of the cooling tubes, with circular tube cross-section with a circular shape, with oval or elliptical tube cross-section with appropriate shape. In relation to this, the ribs on cooling tubes with a rectangular cross-section are clearly different. The tubes have with one narrow side of the cross section upwards and with the other narrow side down. Between the tubes ribs are provided which extend in the plan view transversely to the tube longitudinal direction. In a cross-section of the register, the ribs fill the gap between two adjacent tubes in the register.

In practice, all the usual cooling tubes come in single-layer cooling registers.
For multi-layer cooling registers that is different. The cooling tubes with rectangular tube cross-section do not occur in practice in multi-layered registers.

In multi-layer cooling registers, the free passage between the cooling tubes depends on whether and how the further layers are arranged in relation to the first layer. With the same arrangement, it remains within the meaning of the invention in the vertical Kühlrohrgasse.

In most cases, the cooling tubes of the second layer but offset from the first position, so that there is a cooling tube of the second layer under the gap between two cooling tubes of the first layer. The third layer is then usually arranged again as the first layer, the fourth layer as the second layer, etc.
In the above description, the first layer denotes the cooling tube layer next to the cleaning device, with the second layer, the second cooling tube layer arranged below the first layer with respect to the cleaning device. This designation does not take into account the flow direction of the cooling air.
The flow of cooling air meanders substantially between the cooling tubes of the various cooling tube layers. The invention provides in the cleaning less on the course of the cooling air than from that the cleaning water penetrates with sufficient cleaning energy to the farthest cooling pipe layer. According to the invention therefore cooling pipe alleys are to be used, in which part of the flat jet can penetrate unbroken to the farthest cooling pipe layer. Even if influences from the turbulence of the penetrating into the cooling pipe alley flat beam part and it is unavoidable that a part of the flat jet is deflected by cooling pipes arranged on both sides of the cooling pipe, this is Cleaning result still better than cleaning without using the cooling pipe lanes. The nozzle should point according to the invention in the nozzle alley. This leads to an angular position of the nozzles, which is equal to the angle under which the nozzle lanes run. However, there are two nozzle lanes in the staggered cooling tube layers described above. Preferably, of the nozzles of the two rows of nozzles described above a) the nozzles of one row in the one nozzle lane and
b) the nozzles of the other nozzle row directed into the other nozzle lane.
The angles at which the two nozzle lanes run are identical to the angles at which the cooling pipes belonging to each pipe lane are aligned

In this case, the center of the flat jet does not have to be exactly aligned with the cooling pipe, but if the center of the flat jet have a slight deviation thereof.

In the case of multilayer cooling registers, the cooling pipe passages consist of cooling tubes with a circular cross-section and with offset cooling pipe layers normally under 45 degrees to the cooling pipe layers. There are twice as many cooling pipe lanes as cooling pipes of the first cooling pipe layer. That is, it can be sprayed on both sides of each cooling pipe in a running at 45 degrees cooling pipe alley with water.
Normally, the distance between the cooling tube layers is equal to the distance between the cooling tubes of a layer and so large that a free passage is given.
The course of the cooling pipe alley changes depending on whether the distance between the cooling pipe layers is increased or reduced in the range of the possible. The limits of the possible are given where the flat jet no free passage is given.

In multi-layer cooling registers of cooling registers with oval cross-section results in a different course of the cooling pipe lanes regularly. In the simplest case, this becomes clear in registers whose oval cooling tubes, although they measure on the narrow side of their cross-section, are equal to the diameter of the cooling tubes of circular cross-section described above. On the other hand, in the example, the broad side of the oval cross section has twice the dimension as the diameter of the above-described cooling tubes having a circular cross section. In this cross-section, the cooling pipe lanes normally run at an inclination of 22.5 degrees to the perpendicular to the Cooling coil. Compared to the previously described example with the cooling tubes of circular cross-section that involves a halving of the angle of inclination.

In all multi-layer cooling registers, in which a flat jet can penetrate partially unhindered between the cooling tubes from the first to the last position and arise on the way Kühlrohrgassen, the cooling pipe lanes are limited on both flanks of cooling tubes. The central axes of these associated cooling tubes lie in planes which are parallel to the middle of the cooling tube lane.
The displacement of the cooling tube layers in a multi-layer cooling coil may be in the form that, for example, the first first layer tube and the second second layer tube, as well as the tenth first layer tube with the tenth second layer tube, define a cooling tube lane , The same applies to the tubes of the second layer in relation to the tubes of the third layer and so on.
As far as the offset of the second layer is also connected to a reduction in the number of cooling tubes, the second cooling tube of the first layer with the first cooling tube of the second layer can limit a cooling tube alley.

According to the invention, an adaptation of the nozzle assembly to the geometry of the cooling tubes or the cooling tube bundles takes place on the way.

Preferably, an adapted nozzle stock is kept for each cooling register.

The nozzles are fed by pumps with cleaning water.
It is advantageous to use a pump with a pump capacity of more than 150 liters per minute to feed 12 nozzles. The pump capacity may also be greater, eg having a capacity of more than 180 liters per minute, even more than 210, even 250 liters and more per minute, and controlled down as needed.
The required pump capacity depends not only on the number of nozzles, but also on the cross-section of the services leading to the nozzles and on the nozzle cross-section. Pipes according to DN 25 and / or DN 32 as well as larger pipelines are used. Preferably, the line for water quantities of 5 to 25 cubic meters to the nozzle has a nominal diameter of DN 32 and in the nozzle a nominal diameter DN25. At the transition from the nominal diameter DN 32 to the nominal diameter DM25 there is a reducer in the line.

The nominal diameter DN is regulated according to DIN 11850. The inside diameter for DN 25 is 26mm, for DN 32 it is 32mm. If other nominal diameters are used, it is provided that these nominal diameters do not deviate more than 10%, preferably not more than 5%, from the nominal diameters DN 25 or DN 32.

It is favorable if only straight pieces and elbows instead of elbows occur in the pipeline. It is also advantageous if the cross section of the water supply line to the nozzles is larger. The larger the water supply line cross section, the lower the flow loss. On the other hand, the demands on the strength of the high-pressure line increase with increasing diameter.

In the drawing, an embodiment of the invention is shown.

The Fig. 1 to 3 and 4a show in accordance with the EP 1604164 B1 different views. In the side view Fig. 1 the slope of the cooling register is shown. This results in very cramped conditions at the upper end of the cooling register, in the exemplary embodiment because of a wind wall support. As a result, the square profile 2 can not be extended so far that the cleaning device reaches with its head the upper end of the cooling register. To Fig. 1 this can be compensated by the fact that the nozzle assembly 50 in the upper position protrudes correspondingly far beyond the head of the cleaning device. Here, the nozzle is supported by a nozzle floor trolley, which runs on the profile 2.
The method beyond the head and foot is possible in the embodiment due to the portal-shaped bracket 53, with which the cleaning device is held.
The portal-shaped bracket 53, together with the edge profile 2 a trolley, which is laterally movable on the cooling registers. The wagon carries all belonging to the cleaning device components, as they are already the subject of an earlier proposal. These include in the exemplary embodiment, a toothed belt drive (instead Belt drive can also chain hoist or other pulling device with tape or rope be provided), the drive and the nozzle floor carriage 50th
For moving the nozzle floor carriage 53 driving rollers are provided at the bottom of the bracket. The castors have a detent in the form of a clamp. The profile 2 is suspended in the brackets 53. The suspension is a strut 54. The edge profile 2 is arranged so that a diagonal of the cross section is vertical. This creates inclined surfaces. On the inclined surfaces of the Kantprofiles 2 run rollers 55. The rollers are mounted on metal strips 56. The metal strips are folded at the upper end so that the mounting surfaces for the rollers are at 90 degrees to each other. The same angle, the side surfaces of the Kantprofiles 2 each between them.

At the lower ends of the metal strip bolts 57 are provided. The bolts 57 at the same time form spacers for the metal strips and also fasteners for the nozzle 50th

To Fig. 3 is for fastening the nozzle assembly 50 to the nozzle floor carriage on the construction formed by the bolt 57 a screw provided. The screw connection allows quick assembly and disassembly.

The nozzle block carriage is moved parallel to the cooling tubes. To the nozzle 50 include two tubes 60 and 61 which are perpendicular to the direction of travel of the nozzle floor carriage and nozzles 62 and 63 wear ( Fig. 4a ). The nozzles 62 and 63 are flat jet nozzles. The flat jet generated by the nozzles propagates at an angle whose flanks are designated 72 and 73. The bisector also forms the center 69, 74 of the flat jet.

The impact area of a flat jet at the top of the first cooling tube layer in the cooling register has an oblong shape when the observer imagines the landing surface as a flat surface. The length of the impact surface indicates the width of the flat jet, while the width of the impact surface indicates the thickness of the flat jet. In reality, the first cooling tube layer has a very complicated surface with the curved tube surfaces and their spacing and with the cooling fins.

The nozzles 62 on the tube 60 are inclined in the direction of the tube 60.
The nozzles 63 on the pipe 61 are inclined in the direction of the pipe 61, in the opposite direction as the nozzles 62nd
The inclination is defined in the embodiment as a deviation of the center 69 of the cooling pipe alley. The cooling tube alley refers to the free passage of the cleaning water between the cooling tubes 65 from the jet direction of the nozzle 62. This free passage follows in the exemplary embodiment Fig. 2 with a four-layer cooling register parallel to the plane in which the cooling pipes in Fig. 2 lie with their longitudinal axis, the in the drawing after Fig. 2 be hit by the middle 69.
The nozzles 63 is associated with another Kühlrohrgasse.

The cooling tubes are in Fig. 2 of oval cross-section and provided with cooling fins, not shown. The (measured perpendicular to the impact surface) distance of the nozzles 62 and 63 of the surface to be cleaned of the cooling register is in the embodiment 200 mm. With regard to the determination of the distance, the surface to be cleaned is the surface of the plane in which the cooling tubes of the first layer lie with their upper edge.
The spacing of adjacent nozzles 62 on the tube 60 is 100 mm.

The conduits which lead to the nozzle are flexible high-pressure pipes of reinforced plastic, in other embodiments of reinforced rubber. The water-contact solid lines are made in the embodiment of stainless steel, VA. The supporting parts of the cleaning device are made of aluminum.

Fig. 4 shows a nozzle with a tube 70 and downwardly facing nozzles 71. The nozzles 71 are directed against a single layer of cooling tubes 75. The cooling tubes are in the Fig. 4 shown with the longitudinal direction parallel to the tube 70, at the same time to show the ribs on the cooling tubes 75. In reality, the cooling tubes 75 are parallel to the driving profile 76.
In Fig. 4 from the nozzles 71 also flat jets with flanks 72 and 73 and a center 74 from. The center 74 runs with a slight inclination of 5 degrees to the vertical to the plane in which the cooling tubes lie.

Fig. 5 shows a schematic representation of a tube 80 on a nozzle according to the invention, wherein the tube 80 six nozzles 81 are located. Flat jets 82 emerge from the nozzles 81. The impact surface of the flat jets 82 on the surface to be cleaned is designated by 83. As the surface to be cleaned, the plane is designated, in which the cooling tubes of the uppermost layer lie with its upper edge. The center of the flat jets is denoted by 84, the vertical to the surface to be cleaned is indicated by 85, the inclination of the nozzles 81 in the direction of the tube 80 by 86. In the view Fig. 5 is also shown that the nozzles are made obliquely, that the landing surfaces 83 do not touch each other. In this case, the impact surfaces 83 extend obliquely to the longitudinal axis of the tube 80. In the view in the longitudinal direction of the cooling tubes, the impact surfaces overlap each other with the measure 87. The impact surfaces at the same time characterize the cleaning, so that emanating from a nozzle cleaning in the overlap area described is supplemented by the adjacent nozzle.

Fig. 7 shows the oblique course of the impact surfaces 83 in a direction perpendicular to the direction of travel of the nozzle with schematically illustrated cooling tubes 95 extending tube 98 in a plan view
Fig. 6 shows on the basis of the center 84 and the vertical 85 in another view that the nozzles 81 and the associated flat jets are inclined at the same time slightly in the direction of the cooling tubes. The apparent in this view additional inclination is designated 90 and is in the embodiment 2 degrees, resulting from manufacturing and assembly inaccuracies. With accurate production and assembly, the deviation 90 may be less than 1 degree. The smaller the deviation, the safer the ribs are from being damaged by the cleaning water.

The nozzle after Fig. 5 to 7 is intended for a cooling coil, as it is in Fig. 4 is shown. The cooling pipe lanes shown there run at an angle of 22.5 degrees to the vertical to the cooling coil. The cooling tubes have an average diameter ranging between 40 and 60 mm. The deviation 86 is 27 degrees in the embodiment.
Fig. 8 shows another embodiment in which the designated tube 97 is oblique to the direction of travel. In this case, the oblique pipe course allows employment of the nozzles arranged exactly perpendicular to the direction of travel and cooling tube longitudinal direction nozzles and exactly perpendicular to the direction of travel and cooling tube longitudinal direction extending impact surface 96th

Claims (15)

1. A process for cleaning cooling pipes (82, 84) in cooling registers of heat exchangers, especially heat exchangers for air-cooled condensers, water coolers and chemical plants,

   a) wherein the cooling pipes are spray washed with cleaning water,

   b) wherein a plurality of cleaning nozzles (62,63,71,81) are used, which are arranged to be movable in the longitudinal direction of the cooling pipe (82, 84),

   c) wherein an injection block (50) is used, on which the cleaning nozzles are arranged in one or more rows, and wherein flat spray nozzles are used as the cleaning nozzles, characterised in that

   d) the cleaning nozzles (62,63,71,81) are arranged at a distance of 150 to 300 mm, preferably at a distance of 200 to 250 mm, from the surfaces to be cleaned (83, 96) on the cooling register,

   e) wherein the cleaning nozzles (62,63,71,81) are brought up to a distance of 60 to 120 mm to neighbouring cleaning nozzles (62,63,71,81), preferably up to a distance of 90 to 110 mm to neighbouring cleaning nozzles (62,63,71,81),

   f) wherein the cleaning nozzles (62,63,71,81) of a series are offset to one another in the top view such that with a flat spray (82, 84) out of a neighbouring cleaning nozzle (62,63,71,81) an overlap of at most 10%, based on the spray width, occurs during the impact onto the cooling register, preferably an overlap of at most 5% based on the spray width during the impact onto the cooling register

   g) wherein the flat sprays (82, 84) in the other view parallel to the cooling pipes (65, 75) are brought into an overlap of at least 5%, based on the spray width during impact onto the cooling register, preferably at least 10%, based on the spray width during impact onto the cooling register,

   h) wherein the pressure of the cleaning water on exiting the cleaning nozzles (62,63,71,81) is adjusted to 120 bar at most, preferably a pressure of 40 to 100 bar, even more preferably

   hh) for cooling pipes (65, 75) with an oval or elliptical or circular cross section, a pressure of 70 to 100 bar is set at the nozzle exit and

   hhh) for cooling pipes (65, 75) with a right angled cross section, a pressure of 40 to 50 bar is set at the nozzle exit.
2. A process for cleaning cooling pipes (82, 84) in cooling registers of heat exchangers, especially heat exchangers for air-cooled condensers, water coolers and chemical plants,

   a) wherein the cooling pipes are spray washed with cleaning water,

   b) wherein a plurality of cleaning nozzles (62,63,71,81) are used, which are arranged to be movable in the longitudinal direction of the cooling pipe (82, 84),

   c) wherein an injection block (50) is used, on which the cleaning nozzles are arranged in one or more rows, and wherein flat spray nozzles are used as the cleaning nozzles, characterised in that

   d) the cleaning nozzles (62,63,71,81) are arranged at a distance of 150 to 300 mm, preferably at a distance of 200 to 250 mm, from the surfaces to be cleaned (83, 96) on the cooling register,

   e) wherein the cleaning nozzles (62,63,71,81) are brought up to a distance of 80 to 120 mm to neighbouring cleaning nozzles (62,63,71,81), preferably up to a distance of 90 to 110 mm to neighbouring cleaning nozzles (62,63,71,81),

   f) wherein the cleaning nozzles (62,63,71,81) of a series are offset to one another in the top view such that with a flat spray (82, 84) out of a neighbouring cleaning nozzle (62,63,71,81) an overlap of at most 10%, based on the spray width, occurs during the impact onto the cooling register,

   g) wherein the flat sprays (82, 84) in the other view parallel to the cooling pipes (65, 75) are brought into an overlap of at least 5%, based on the spray width during impact onto the cooling register, preferably at least 10%, based on the spray width during impact onto the cooling register,

   h) wherein the flat sprays are directed with their centre into the cooling pipe lane, such that the flat sprays for cooling ribs that run transversely to the longitudinal direction of the cooling pipes (65, 75) also run transversely to the longitudinal direction of the cooling pipes (65, 75) and can have the following deviations from the centre of the cooling pipe lane,

   hh) for a diameter of the cooling pipes (65, 75) of less than 40 mm, calculated without cooling ribs, maximum 5 degrees,

   hhh) for a diameter of the cooling pipes (65, 75) of 40 to 60 mm, calculated without cooling ribs, maximum 10 degrees,

   hhhh) for a diameter of the cooling pipes (65, 75) of greater than 60 mm, maximum 15 degrees.
3. The process according to claim 1, characterised in that

   i) the flat sprays are directed with their centre into the cooling pipe lane, such that the flat sprays for cooling ribs that run transversely to the longitudinal direction of the cooling pipes (65, 75) also run transversely to the longitudinal direction of the cooling pipes (65, 75) and can have the following deviations from the centre of the cooling pipe lane,

   ii) for a diameter of the cooling pipes (65, 75) of less than 40 mm, calculated without cooling ribs, maximum 5 degrees,

   iii) for a diameter of the cooling pipes (65, 75) of 40 to 60 mm, calculated without cooling ribs, maximum 10 degrees,

   iiii) for a diameter of the cooling pipes (65, 75) of greater than 60 to 150 mm, maximum 15 degrees.
4. The process according to claim 2 or 3, characterised by the use on heat exchangers with a single-layered cooling register, in which the cooling pipes have a uniform cross section, wherein the centre of the cooling pipe lane stands perpendicular to the plane, in which the cooling pipes (65, 75) lie with their upper edge.
5. The process according to claim 2 or 3, characterised by the use on heat exchangers with a multi-layered cooling register with offset cooling pipe layers running parallel to the plane, wherein the centre of the cooling pipe lane runs parallel to the plane, in which middle axes of a cooling pipe lane formed by cooling pipes (65, 75) lie.
6. The process according to one of claims 2, 3 and 5, characterised by the use on heat exchangers with cooling pipe lanes, which without taking into account other influences, allow a partial free passage to the flat spray (82, 84) from a nozzle (62,63,71,81).
7. The process according to one of claims 1 to 6, characterised in that the flat 14. sprays (82, 84) are aligned in such a way that from the perspective in the longitudinal direction of the cooling pipes (65, 75) they overlap on the impact surfaces (83, 96) and the overlap of the flat sprays (82, 84) on the impact surface (83, 96) of the first cooling pipe layer is at least 5%, preferably at least 10% of the width of the spray on the impact surface (83, 96).
8. A device for carrying out the process according to one of claims 1 to 7, characterised by an injection block that can be moved above the cooling registers in the longitudinal direction thereof, said injection block being equipped with 4 to 12 nozzles (62, 63, 71, 81).
9. The device according to claim 8, characterised by a pipe of the injection block (50) that supports the nozzles (62, 63, 71, 81), said pipe having a greater cross section than other water supply pipes.
10. The device according to claim 8 or 9, characterised by injection block pipes running perpendicular to the drive direction with inclined nozzles (62, 63, 71,81).
11. The device according to claim 8 or 9, characterised by injection block pipes running at an angle to the drive direction with nozzles (62, 63, 71, 81) employed perpendicular to the drive direction and cooling pipe longitudinal direction.
12. The device according to one of claims 8 to 11, characterised in that a pump with a flow rate of at least 150, preferably at least 180, even more preferably 210 or more litres per minute and/or an adjustable pump is provided in the water supply line to the injection block.
13. The device according to one of claims 8 to 12, characterised by a water supply line to the injection block (50) with a nominal diameter of DN25 and/or DN32 or another nominal diameter that varies from the given values by 10% at most.
14. The device according to one of claims 8 to 13, characterised by a ladder that is arranged above the cooling register and preferably having a guardrail.
15. The device according to claim 14, characterised in that at least the guardrail is hinged.

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