Cooling module, cooling group, cooling system, method, hot rolled metal belt-like product, and use

Abstract

The present invention relates to a cooling module of a cooling device for cooling a belt-like product of hot-rolled metal with a coolant, the cooling module comprising: at least one cooling bar having a coolant chamber and a plurality of coolant discharge pipes, the coolant discharge pipes being connected in fluid communication with the coolant chamber and each of the coolant discharge pipes having at least one coolant discharge opening for applying coolant to the belt-like product; at least one coolant inlet connected in at least indirect fluid communication with the coolant chamber, the coolant inlet being connected in at least indirect fluid communication with a coolant reservoir, a coolant inlet port, wherein the coolant reservoir is set up to provide a pressure difference between the coolant reservoir and the coolant outlet port; and at least one coolant valve, wherein the coolant valve is arranged between the coolant inlet port and the coolant chamber; wherein the cooling module has a time-varying behavior of the coolant velocity at the coolant outlet port under the influence of the pressure difference, which can be described by a time-varying step function having a delay time and a compensation time when the coolant valve suddenly opens completely, and the sum of the delay time and the compensation time is not more than 3.0 s, preferably not more than 2.0 s, and particularly preferably not more than 1.5 s.

Description

[Technical Field]

[0001] The present invention relates to a cooling module, a cooling group, a cooling system, a method, a hot rolled metal belt-like product, and uses.

[0002] The cooling module described herein for cooling belt-like products, particularly hot rolled metal belt-like products, can be utilized to cool such products, including at least one cooling bar having a coolant chamber and a plurality of coolant discharge pipes connected in fluid communication with the coolant chamber for applying liquid coolant to the belt-like product.

[0003] It is known to use cooling bars extending across the width of the conveying section along which the metal products are transported for the production of flat or belt-like metal products, in particular metal belts or metal plates. To this end, the cooling bars can have a coolant chamber supplied with a liquid coolant, from which a number of coolant outlet pipes branch out for the discharge of the coolant, in particular for application to the belt-like products. Cooling bars of this kind can be components of a cooling module and / or cooling group and / or cooling system.

[0004] The problem on which the present invention is based is to provide an improvement or alternative to the prior art.

[0005] In a first aspect of the present invention, the problem is solved by a cooling module of a cooling device for cooling a belt-shaped product of hot rolled metal by means of a coolant, the cooling module comprising: - at least one cooling bar having a coolant chamber and a plurality of coolant discharge pipes, the coolant discharge pipes being connected in fluid communication with the coolant chamber and each of the coolant discharge pipes having at least one coolant discharge opening for applying coolant to the belt-like product; - at least one coolant inlet connected in at least indirect fluid communication with the coolant chamber, the coolant inlet being set up to be connected in at least indirect fluid communication with a coolant reservoir, the coolant reservoir being set up to provide a pressure differential between the coolant reservoir and the coolant discharge opening; at least one coolant valve, the coolant valve being arranged between the coolant inlet and the coolant chamber; the cooling module has a time-varying behavior of the coolant velocity at the coolant discharge opening under the influence of a pressure difference, which can be described by a time-varying step function having a delay time and a compensation time when the coolant valve suddenly opens completely, The sum of the delay time and the compensation time is 3.0 seconds or less, preferably 2.0 seconds or less, and particularly preferably 1.5 seconds or less.

[0006] In this regard, the following terms are explained. It is expressly mentioned at the outset that within the scope of this patent application, indefinite articles and numerical indications such as "one", "two", etc. are generally to be understood as indications of "at least", i.e. as "at least one", "at least two", etc., unless this is clear from the respective context or is not obvious to a person skilled in the art or technically it can only mean "exactly one", "exactly two", etc.

[0007] In this patent application, the expression "particularly" is always to be understood as introducing any preferred features. This expression should not be understood in the sense of "and" or "i.e."

[0008] By "cooling device" it is understood that an installation is set up for cooling flat and / or belt-shaped metal products, in particular hot-rolled metal belt-shaped products, with the aid of a liquid coolant.

[0009] It is intended that the metal belt-shaped product can be conveyed in the conveying direction on the conveying section so that it can be brought into operational relationship with the cooling device, in particular by means of an operational relationship with the liquid coolant discharged from the cooling device as envisaged, for which purpose the metal belt-shaped product can be conveyed past at least one cooling bar of the cooling device and / or between at least two cooling bars of the cooling device.

[0010] The cooling device may have at least one cooling bar, in particular one or more first cooling bars, arranged above the metal belt-like product, to which liquid coolant is supplied via a coolant inlet, the cooling bar preferably extending substantially transversely to the conveying direction and preferably having a plurality of coolant outlet pipes, via which the liquid coolant can be brought into operative contact with the metal belt-like product.

[0011] Similarly, the cooling device may have at least one cooling bar, in particular one or more second cooling bars, arranged below the metal belt-like product, set up to bring a liquid coolant into operative relationship with the metal belt-like product.

[0012] In the conveying direction of the metal belt-like product, the cooling device can have a number of cooling bars which can be arranged above and / or below the metal belt-like product.

[0013] The one or more cooling bars of the cooling device may be organized and / or arranged in one or more cooling modules and / or one or more cooling groups and / or one or more cooling systems.

[0014] A cooling module can have several cooling bars that can be supplied with coolant at least indirectly via a common cooling module branch, whereas a "cooling group" can have several cooling modules that can be supplied with coolant at least indirectly via a common cooling group branch. The cooling modules of a cooling group can in particular be operated with different adjustment values, in particular with different volumetric flow rates of liquid coolant exiting the associated coolant outlet openings.

[0015] A "cooling system" has at least one cooling module and / or at least one cooling group, as well as at least one coolant reservoir and at least one "main coolant inlet," the at least one main coolant inlet being connected in at least indirect fluid communication with the at least one coolant reservoir and with the at least one cooling module and / or at least one cooling group.

[0016] Preferably, the cooling system has a superordinate electronic control unit and / or control unit, which is set up to control and / or control the cooling system. The superordinate electronic control unit and / or control unit may be set up to control and / or control at least one coolant valve. Alternatively, the superordinate electronic control unit and / or control unit may be in data connection with at least one electronic control unit and / or control unit, which is set up to control and / or control the cooling modules and / or cooling groups.

[0017] A coolant reservoir is set up to store and / or provide coolant.

[0018] "Coolant" is understood to mean a fluid that can be used to cool the metal belt-like product, and the coolant can have different temperature states. In particular, the coolant can be a gaseous and / or liquid substance, or a mixture of gaseous and / or liquid substances. It is intended that the coolant then flows out of the coolant outlet opening at least predominantly in liquid form. The heat flow of the metal belt-like product relative to the coolant can cause the coolant to at least partially vaporize.

[0019] In its liquid state, the refrigerant is considered to be incompressible.

[0020] A "cooling bar" essentially consists of a substantially elongated coolant chamber, a plurality of coolant discharge pipes connected in fluid communication with the coolant chamber and arranged in series or in pairs in the longitudinal direction of the cooling bar, and a coolant intake opening.

[0021] The "coolant chamber" is set up to relieve the pressure of the coolant flowing into the cooling bar through the coolant intake opening in a planned manner, thereby achieving a substantially uniform distribution of the coolant volume flow from the coolant chamber to the coolant discharge pipes. In the plurality of coolant discharge pipes in direct fluid connection with the coolant chamber, means for hydraulic adjustment can be provided at the transition between the cooling chamber and at least one coolant discharge pipe, which is set up to quantitatively match the partial coolant volume flows flowing out in a planned manner from the plurality of coolant discharge pipes in direct fluid connection with the cooling chamber.

[0022] By "coolant discharge pipe" is understood a tubular extension of the cooling bar that is set up to discharge coolant from the cooling bar through the "coolant discharge opening". The coolant discharge pipe may preferably be welded or screwed to the coolant chamber or may be otherwise connected to the coolant chamber.

[0023] The coolant discharge pipe may be straight, or alternatively, the coolant discharge pipe may be J-shaped and / or shaped to resemble a swan's neck.

[0024] By "coolant valve" is understood a device for controlling the flow rate of coolant in a coolant closing area of ​​the coolant valve, which can be completely shielded.

[0025] The coolant valve may be electrically and / or electronically position adjustable at least indirectly, and in particular may be configured as a coolant control valve set up to control the coolant flow rate to an externally set target value.

[0026] The coolant valve may have a data interface set up to connect the coolant valve with an electronic data processing and evaluation unit, the electronic data processing and evaluation unit being set up to control and / or manage the coolant valve.

[0027] Preferably, the maximum possible free cross-section of the coolant valve, in particular of the coolant closing region, is greater than or equal to the nominal width of the coolant inlet and / or greater than or equal to the nominal width of the coolant intake opening of the cooling bar and / or greater than or equal to the nominal width of the coolant chamber of the cooling bar.

[0028] A "coolant module" is understood to be a unit consisting of at least one cooling bar, at least one coolant valve and at least one "coolant inlet" for supplying the cooling module with coolant.

[0029] Preferably, the coolant valve is at least indirectly fluidly connected with exactly one cooling bar.

[0030] "Coolant inlet" can be understood to mean a region of the coolant guiding means that is in direct fluid connection with the coolant valve, in particular the inlet region of the coolant valve, in particular the free cross-section of the coolant valve flange, in particular the free cross-section of the coolant valve flange that is arranged on the side complementary to the side of the coolant valve that is in fluid communication with the cooling bar. Alternatively, the coolant inlet can be understood to be a region of the coolant tube that is in direct fluid connection with the coolant valve.

[0031] The coolant inlet may be set up to be at least indirectly fluidly connected to a coolant reservoir for storing and / or providing coolant.

[0032] By "pressure difference" is understood the total pressure difference between the water level in the coolant reservoir and the coolant discharge opening of the cooling module.

[0033] This total pressure difference can arise at the coolant-passable connection between the coolant reservoir and at least one coolant discharge pipe as a result of a difference in geodetic height between the water level of the coolant reservoir and the coolant discharge opening of the cooling module, and / or as a result of a difference in pressure loss between the coolant reservoir and the coolant discharge opening of the cooling module, and / or as a result of a pressure change using the delivery device, in particular using the main coolant delivery device.

[0034] Preferably, the pressure difference is 3·10 5 kg / (m·s 2 ) or more, and more preferably the pressure difference is 4·10 5 kg / (m·s 2 ) or more, and preferably the pressure difference is 5.10 5 kg / (m·s 2 ) or more, and especially preferred is a pressure difference of 6.10 5 kg / (m·s 2 )That's all.

[0035] "Coolant velocity" is understood to be the cross-sectionally averaged velocity at a reference cross section of the cooling device between the coolant reservoir and the coolant discharge opening of the cooling module.

[0036] Preferably, coolant velocity refers to the average velocity at the coolant discharge opening of the cooling module.

[0037] "Time-varying behavior" means a system behavior in which the system response depends not only on the time of observation, but also on the time of the jump change in the adjustment quantity at the input of the system. In particular, the coolant velocity at the coolant outlet opening of the cooling module depends on the adjustment of the coolant valve, in particular on the jump position adjustment of the coolant valve, and on the acting pressure difference.

[0038] The "time-varying step function" of coolant velocity versus time describes the progression of the coolant velocity at the coolant discharge opening of the cooling module depending on the time after the sudden opening of the coolant discharge opening and the corresponding coolant valve, and after a certain time a steady state occurs as the system response.

[0039] When assessing the time-varying system behavior with reference to the time course until a steady state is reached, attention can be paid in particular to the compensation time and / or delay time as a time-varying step function quantity characteristic of the system. The time-varying system behavior allows the description of the controlled object in the context of control, in particular in the context of the control of a cooling module.

[0040] "Delay time" can be a measure of higher-order influences on time-varying system behavior, and can be obtained from a time-varying step function by the following steps: -The inflection points of the time-varying step function of the coolant velocity are determined; - Tangent lines are drawn through the inflection points of the time-varying step function; and The delay time is determined as the difference between the moment when the tangent line intersects the horizontal axis and the moment of the jump in the adjustment quantity, in particular the jump in the opening of the coolant valve.

[0041] The "compensation time" can be a measure of the inertia of the time-varying system behavior, i.e., a measure of the first-order influence on the time-varying system behavior, and can be obtained from a time-varying step function by the following steps: - In particular, the inflection points of the time-varying step function of the coolant velocity are determined; -Tangential lines are drawn through the inflection points of a time-varying step function; - Determining the steady-state asymptote of the time-varying system behavior that occurs after a jump in the adjustment quantity; and -The compensation time is determined as the difference between the time when the tangent line intersects the asymptote and the time when the tangent line intersects the horizontal axis.

[0042] "Cooling rate" is understood to mean the rate at which a hot-rolled metal belt-shaped product is cooled, which can be expressed in units of K / s. Preferably, when a hot-rolled metal belt-shaped product is cooled from an average temperature of 1,150 K at a constant cooling rate of 50 K / s, the product has an average temperature of 650 K after a cooling time of 10 s.

[0043] The cooling rate is inter alia a function of the amount of coolant and of the thickness of the metal belt-like product: as the thickness of the metal belt-like product increases, while all other quantities are kept constant, the cooling rate decreases as a result of temperature compensation processes in the metal belt-like product.

[0044] The progress of phase transformation in steel affects the microstructural composition of the steel, which in turn affects the properties of the steel.

[0045] The progression of the phase transformation of the steel material is substantially determined by the cooling rate and its progression over time. Preferably, in a first cooling stage, the hot-rolled metal belt product is actively cooled to a first target temperature by a cooling system using a liquid coolant, and in a second cooling stage, the hot-rolled metal belt product is passively cooled to an ambient temperature. More preferably, the hot-rolled metal belt product is coiled immediately after reaching the first target temperature.

[0046] The structural composition of the steel, in particular the proportions of ferrite and / or pearlite and / or bainite and / or martensite and / or austenite in the steel structure, and thus its material properties, are determined, in particular, by the cooling rate of the cooling system, the first target temperature to which active cooling is performed, and the alloy composition of the steel. A cooling rate that preferably avoids or prevents pearlite precipitation can be achieved, thereby reducing the hardness of the material and thereby improving its formability. Alternatively, a relatively low cooling rate can be used to achieve or precisely adjust the pearlite proportion in the metal composition, which increases the hardness of the hot-rolled metal belt-shaped product.

[0047] Hot rolling of belt-like products of hot rolled metal is primarily a continuous process, in which a rolling frame is stationary and the metal product is transported through the rolling frame for rolling. Correspondingly, active cooling after rolling by a cooling system is also a continuous process, in which the hot rolled metal product is primarily continuously transported past at least one stationary cooling bar of the cooling system and / or between at least two stationary cooling bars of the cooling system.

[0048] Accordingly, in the continuous active cooling process, multiple coolant discharge openings are involved in the conveying direction of the metal belt-shaped product passing by and / or through the cooling devices of the cooling system, so that the course of the cooling rate, and therefore also the properties of the hot-rolled metal product, is influenced by multiple cooling bars and coolant discharge openings along the conveying direction and by the amount of coolant delivered or discharged in each case.

[0049] In other words, there is an operational relationship between the properties of the hot-rolled metal product and the coolant volume flows exiting from a plurality of coolant discharge openings, in particular from a plurality of coolant discharge openings arranged in the conveying direction, in particular from a plurality of coolant discharge openings of different cooling bars arranged in the conveying direction.

[0050] Experiments have shown that, under favorable time profiles of the cooling rate along the transport direction of the hot-rolled metal product, cost-intensive alloying elements can be reduced in proportion to achieve the same material properties. In this sense, the ability to quickly and / or accurately change the time profile of the cooling rate is particularly advantageous, especially in relation to the interaction of multiple cooling bars that influence the cooling rate.

[0051] The cooling rate has a number of physical effects that affect it, but here we will only discuss those that have a particular, stable effect on the cooling rate.

[0052] Experiments have already shown that it is preferable to be able to precisely control and / or regulate the cooling rate in relation to a single cooling bar, in particular in relation to just one cooling bar and the associated assumed stationary coolant volume flow.

[0053] Furthermore, experiments have shown that some effects which are physically related to the cooling rate have particularly high dynamics, so that it has surprisingly proven to be particularly advantageous to be able to control and / or regulate the assumed stationary coolant volume flow with improved dynamics, in particular already in a function relationship with one cooling bar, preferably with just one cooling bar.

[0054] A first dynamical function of the cooling rate is related to the Leidenfrost effect: the temperature of the hot-rolled metal product before entering the cooling device is usually above the Leidenfrost temperature, which may be between about 300 K and 600 K depending on the characteristics of several parameters. As a result, a coolant vapor layer is formed between the hot-rolled metal product and the liquid coolant by the cooling device, at least in the first region of the conveying section of the hot-rolled metal product, which reduces the heat transfer coefficient and therefore the cooling rate.

[0055] Unintended coolant total pressure fluctuations at the top surface of the coolant vapor layer can lead to its locally limited rupture, which results in a temporary significant increase in the local cooling rate in a location-limited manner in interaction with the coolant vaporization entropy acting directly on the hot-rolled metal product, causing structural inhomogeneities.

[0056] A second effect is related to the compactness of the coolant volumetric flow discharged from the coolant discharge opening. After the coolant is discharged from the coolant discharge opening, after a collapse time or, in conjunction with the velocity of the coolant volumetric flow, after a collapse length, the coolant volumetric flow may disintegrate into droplets, which may result in local pressure changes in the coolant vapor layer. This effect, if it occurs, is also particularly dynamic.

[0057] It has been shown that critical pressure changes in the coolant vapor layer can be preferably mitigated or prevented by a compact coolant volume flow that is as continuous as possible, provided that local interventions on the local coolant volume flow can be carried out sufficiently accurately and / or quickly.

[0058] Atomization or undulation of the coolant volume flow after it is discharged from the coolant discharge opening can have a negative effect on the coolant vapor layer, so the physical relationship with the total pressure of the coolant in front of the coolant discharge opening can also be important for a cooling rate that is as uniform as possible.

[0059] A further physical interaction with the cooling rate exists with respect to the thickness and alloy composition of the hot rolled metal product.

[0060] The above-described interactions are at least partially systematically coupled with each other and influence each other: even small disturbance effects during active cooling with, for example, a liquid coolant, can lead to local structural inhomogeneities in the produced hot-rolled metal product, which can cause inhomogeneities in the material properties.

[0061] The required material properties of the metal belt-like product specify minimum values ​​that must be observed at each part of the product. Therefore, a particularly good uniformity of the structure of the metal belt-like product is advantageous and allows a particularly large reduction in cost-intensive alloying elements.

[0062] In other words, a cooling rate that is as precise as possible and / or adhered to under disturbance influences allows for a structure that is as uniform as possible and therefore a reduction in cost-intensive alloying elements for the metal belt-like product.

[0063] The disturbances affecting the cooling rate have a high degree of temporal dynamics according to the experiments carried out, which can lead to highly resolved deviations from the desired tissue structure.

[0064] Therefore, a cooling module is proposed having a coolant valve arranged between a coolant inlet and a coolant chamber, the coolant inlet may be a component of the coolant valve, and the coolant inlet is arranged on the side of the coolant closing area facing away from the coolant chamber, on the side of the coolant closing area.

[0065] Preferably, the coolant valve is in direct fluid connection with the coolant chamber, and less than one flow-guiding component is arranged between the coolant valve and the coolant chamber, in particular between the coolant valve and the integrally constructed coolant chamber, which may in particular be understood as a welded structure.

[0066] In a preferred embodiment, fewer than one fluid branch is disposed between the coolant valve and the coolant chamber, in other words, the coolant valve may be in fluid connection with just one coolant chamber.

[0067] The fluid connection between the coolant valve and the coolant chamber may be configured such that the coolant valve allows only that chamber to receive a supply of coolant.

[0068] The proposed cooling module allows for the adjustment of a predetermined volumetric coolant flow at a point along the metal belt-like product conveying section defined by the position of the cooling bar, preferably by directly allocating the coolant valves and the coolant chambers of the cooling bar. This allows for a high degree of spatial resolution of the cooling rate along the conveying section of the metal belt-like product passing by at least one cooling module, and therefore allows for a more accurate determination of the time course of the temperature of the metal belt-like product, which affects its texture. The precision of the adjustment of the proposed cooling module therefore allows for a reduction in cost-intensive alloying elements in the metal belt-like product, while still maintaining the same minimum required material properties.

[0069] The coolant valve of the proposed cooling module preferably acts on only one cooling bar. Accordingly, the amount of coolant downstream of the coolant valve up to at least one coolant discharge opening, which is preferably directly affected by adjusting and / or positioning the coolant valve, is significantly reduced compared to previously known systems. In known cooling systems, a single coolant valve acts on multiple cooling bars and therefore on a relatively large amount of coolant downstream of the coolant valve up to at least one coolant discharge opening. Thus, the proposed cooling module allows for the adjustment and / or positioning of the coolant valve to accelerate only a relatively small amount of coolant. As a result, less inertial resistance is generated by the amount of coolant to be accelerated. This inertial resistance acts to damp the time-varying behavior of the coolant velocity at the coolant discharge opening of the cooling module. In other words, the proposed cooling module reduces the compensation time induced by the cooling module. The proposed cooling module therefore allows for a dynamic response to possible disturbances and optimally reduces the disturbance-induced structural changes in terms of their characteristics. This property of the proposed cooling module can be used to reduce cost-intensive alloying elements while maintaining the same minimum required material properties of the metal belt-like product.

[0070] The compensation time of the cooling module is essentially influenced by the inertia of the coolant mass to be accelerated, whereas the delay time is influenced by the acting gravitational acceleration, the geodesic water level difference between the coolant inlet of the cooling module and the at least one coolant outlet opening of the cooling module, and the total pressure loss of the cooling module between the coolant inlet and the at least one coolant outlet opening, which can be read from the following differential equation of the coolant particle in the cooling module:

[0071]

number

number

number

[0072] The coolant is preferably water. The total pressure difference is preferably

number

number

number

number

[0073] Preferably, the sum of the delay time and compensation time for the time-varying step function of the cooling module is 5.0 seconds or less, more preferably 2.5 seconds or less, more preferably 1.5 seconds or less, and especially preferably 0.5 seconds or less.

[0074] The delay time for the time-varying step function of the cooling module may be greater than 0.0 s, preferably less than 0.8 s, more preferably less than 0.5 s, more preferably less than 0.3 s, and especially preferably less than 0.1 s.

[0075] The compensation time for the time-varying step function of the cooling module may be greater than 0.0 s, preferably less than 2.5 s, more preferably less than 2.0 s, more preferably less than 1.5 s, and especially preferably less than 1.0 s.

[0076] The influence of the sum of the delay time and compensation time of the cooling module on the achievable structural homogeneity and the corresponding scrap rate due to non-achievement of the required material specifications, with a simultaneous reduction in the usage of cost-intensive alloying elements, has been investigated experimentally and can be seen in Table 1. It is clear that the reduction of the delay time and compensation time of the cooling module by the design configuration of the cooling module has a favorable effect on the achievable structural homogeneity.

[0077] The uniformity of the structure is the distribution of the structure proportion V g can be evaluated by: where

number

number

number

[0078] [Table 1]

[0079] In an advantageous embodiment, the coolant valve has a time-varying behavior of the coolant velocity in the coolant chamber that can be described by a time-varying coolant valve step function having a coolant valve time constant under the influence of a pressure difference when the coolant valve is suddenly fully opened, the coolant valve time constant being 1.5 s or less, preferably 1.0 s or less, and particularly preferably 0.5 s or less.

[0080] Preferably, the coolant valve time constant is less than 0.75 seconds, more preferably less than 0.35 seconds, more preferably less than 0.25 seconds, and especially preferably less than 0.1 seconds.

[0081] In this regard, the following terms are explained. A "time-varying coolant valve step function" describes the opening state of the coolant valve between fully closed and fully open over time after a jump in the coolant valve fully open, such that after some time the fully open state of the coolant valve occurs.

[0082] In determining the time-varying system behavior with reference to the time course until a steady state is reached, attention can be paid in particular to the "coolant valve time constant" as a quantity of the time-varying coolant valve step function characteristic of the system. The time-varying system behavior allows the description of the controlled object within the framework of control, in particular within the framework of the control of the coolant valve.

[0083] The coolant valve may have a time behavior of a first-order delay element. The determination of the coolant valve time constant is based on literature relating to the determination of time constants for first-order delay elements, particularly since the opening of the coolant valve can be descriptively determined from ordinary differential equations.

[0084] The effect of the coolant valve time constant on the delay time of the cooling module has been investigated experimentally and can be seen in Table 2. It has been found that the coolant valve time constant of the coolant valve has a functional relationship with the delay time of the cooling module.

[0085] [Table 2]

[0086] Advantageously, the coolant valve has, in the fully open position, a coolant valve loss coefficient ζ of less than or equal to 0.46, preferably less than or equal to 0.44, particularly preferably less than or equal to 0.24. Ventil It has.

[0087] Preferably, the coolant valve has a coolant valve loss coefficient ζ of less than or equal to 0.23, more preferably less than or equal to 0.22, preferably less than or equal to 0.21, especially preferably less than or equal to 0.19, when in the fully open position. Ventil It has.

[0088] More preferably, the coolant valve loss coefficient ζ, when in the fully open position, is less than 0.15, more preferably less than 0.12, preferably less than 0.10, especially preferably less than 0.08. Ventil It has.

[0089] In this regard, the following terms are explained. "Coolant valve loss coefficient" ζ Ventil is understood to be a dimensionless resistance coefficient for a coolant valve and describes a measure of the pressure loss in the coolant valve through which a supposed coolant flows in the fully open position of the coolant valve. As a reference cross section for the coolant valve loss coefficient, a coolant blocking area can be used, which represents the cross section of the central part of the coolant valve through which the coolant can flow when the valve is fully open, and which is blocked to the coolant when the coolant valve is fully closed.

[0090] Coolant valve loss coefficient ζ Ventil can be determined as follows:

[0091]

number

number

[0092] It has been found through experiments that the coolant valve loss coefficient has a function relationship with the delay time of the cooling module. At this time, it has been found that if the coolant valve has a low coolant valve loss coefficient, the delay time of the cooling module can be shortened. Accordingly, it is proposed herein to select a coolant valve with a low coolant valve loss coefficient for the cooling module.

[0093] Preferably, the coolant valve has a nominal width of DN80 or more, preferably DN150 or more, particularly preferably DN200 or more.

[0094] In this regard, the following terms are explained. By "nominal width" of a coolant valve is understood the nominal width as defined in EN ISO 6708. The symbol DN is followed by a dimensionless number which approximately corresponds to the inner diameter of the coolant valve in millimeters.

[0095] [Table 3]

[0096] Preferably, the coolant valve has a nominal width of DN 60 or more, more preferably DN 120 or more, preferably DN 250 or more, especially preferably DN 300 or more.

[0097] Experiments with the nominal diameter of the coolant valve have shown that the nominal width of the coolant valve influences both the delay time and the compensation time of the cooling module, see also Table 3.

[0098] The nominal width of the coolant valve has a functional relationship with the compensation time of the cooling module. The larger the nominal width, the larger the assumed mass of coolant downstream of the coolant closing region of the coolant valve up to at least one coolant discharge opening. Under assumed changes in the opening state of the coolant valve, a larger nominal width of the coolant valve results in a higher inertial resistance of the cooling module, so that the compensation time of the cooling module also increases with an increase in the nominal width of the coolant valve.

[0099] The delay time of the cooling module also has a function relationship with the nominal width of the coolant valve. On the one hand, a coolant valve with a relatively large nominal width can have a relatively large coolant valve time constant, whereby the delay time of the cooling module increases with the changed coolant time constant. On the other hand, a coolant valve with a relatively small nominal width has a relatively high average velocity in the coolant valve closing region of the coolant valve under an assumed constant coolant volume flow discharged from at least one coolant discharge opening. In this regard, coolant valves ζ with different nominal widths but the same coolant valve loss coefficient can be used. Ventil By comparison, a coolant valve having a smaller nominal width experiences a higher total pressure loss of the coolant. Correspondingly, the delay time of the cooling module, when measured against total pressure loss, increases with decreasing nominal width.

[0100] In another preferred embodiment, the coolant valve has a nominal width of DN 300 or less, preferably DN 250 or less, particularly preferably DN 120 or more.

[0101] Preferably, the coolant valve has a nominal width of DN200 or less, more preferably DN150 or less, preferably DN80 or less, especially preferably DN60 or less.

[0102] Preferably, the coolant valve has a distance of less than 500 mm, preferably less than 325 mm, particularly preferably less than 275 mm, from the transition from the coolant chamber to the coolant discharge pipe.

[0103] The distance between the coolant valve of the cooling module and the transition from the coolant chamber to the coolant discharge pipe is understood to be the distance between the flange of the coolant chamber at the sealing surface of the flange for connection with the coolant valve and the surface center of gravity of the transition between the coolant chamber and the coolant discharge pipe.

[0104] A coolant chamber having several coolant discharge pipes can be configured so that the coolant discharge pipes are arranged consecutively in the longitudinal direction of the coolant chamber or consecutively in pairs. In corresponding embodiments with several coolant discharge pipes, the spacing is based on the transition to the coolant discharge pipe next to the valve flange.

[0105] Preferably, the coolant valve has a distance from the transition from the coolant chamber to the coolant discharge pipe of less than 750 mm, more preferably less than 625 mm, more preferably less than 400 mm, especially preferably less than 250 mm.

[0106] Advantageously, the transition from the coolant chamber to the coolant discharge pipe is well chamfered, in particular with a transition loss factor of less than 0.3, preferably less than 0.15, particularly preferably less than 0.08.

number

[0107] In this regard, the following terms are explained. The "transition" from the coolant chamber to the coolant discharge pipe is understood to mean the smallest free cross-section through which the coolant must flow starting from the coolant chamber in order to enter the coolant pipe. The transition can then be arranged directly on the leg of the coolant discharge pipe.

[0108] Transition loss factor

number

[0109]

number

number

[0110] The minimum free cross section that must be traversed starting from the coolant chamber by the envisaged coolant to be able to enter the coolant piping may correspond to the cross section of the coolant discharge pipe.

[0111] The well-chamfered transitions can be configured as throttles, and in particular for multiple coolant discharge pipes that start from the coolant chamber and lead via varying free cross sections of the individual transitions to the individual coolant discharge pipes, hydraulic adjustment can be achieved so that essentially the same volumetric coolant flow can be predictably delivered from each associated coolant discharge opening, thereby improving the uniformity of the structure, especially across the width of the metal belt-like product.

[0112] Preferably, the transition from the coolant chamber to the coolant discharge pipe has a transition loss factor of less than 0.4, preferably less than 0.22, particularly preferably less than 0.11.

number

[0113] Experiments have shown that the transition loss factor

number

[0114] Optionally, the cooling module comprises a flow-through measurement device.

[0115] The flow-through measuring device is set up for metrological detection of the coolant velocity and / or the coolant volume flow, and reacts tactilely with the coolant in question or acts contactlessly on the coolant.

[0116] The flow-through measuring device may be manufactured as a structural unit together with the coolant valve and / or be operatively associated with the coolant chamber and / or with at least one coolant discharge pipe.

[0117] The proposed flow-through measuring device can provide actual values ​​of the coolant velocity and / or coolant volume flow, which can be utilized within the framework of the control and / or regulation of the cooling module.

[0118] In one optional embodiment, the cooling module may have an outlet for the bypass passage, particularly in direct fluid communication with the coolant inlet and / or in direct fluid communication with the coolant chamber.

[0119] In this regard, the following terms are explained. An "outlet" of the cooling module is understood to be a free cross section, different from the coolant discharge opening, through which the intended coolant can exit the cooling module, in particular into a bypass passage, without cooling the metal belt-like product, in other words, through which a coolant volume flow can flow that is not directly intended for cooling the metal belt-like product.

[0120] The outlet may be located before or after the coolant valve in the expected direction of flow of the coolant.

[0121] If the outlet is located before the coolant valve, the coolant volume flow can be moving in the coolant inlet until it reaches the outlet, even when the coolant valve is closed and the cooling module is not used to cool the metal belt-like product. When the coolant valve is opened, the already moving coolant can be used, and the coolant is at least partially diverted from the outlet through the coolant valve, so that overall it only needs to be subjected to a relatively low acceleration value to reach the desired coolant velocity. The moving coolant has a function relationship with the compensation time of the cooling module in relation to the inertial resistance of the cooling module, so that the compensation time of the cooling module can be advantageously shortened through the outlet of the cooling module.

[0122] In order to avoid having to discard the coolant that is expected to flow out through the outlet, the outlet is preferably in fluid communication with a "bypass passage" set up to supply the coolant at least indirectly to the coolant reservoir and / or the main coolant inlet and / or the cooling group branch and / or the coolant inlet.

[0123] The bypass passage is preferably in fluid communication with a coolant delivery device set up to deliver coolant to the coolant reservoir and / or the main coolant inlet and / or the cooling group branch and / or the coolant inlet, so that the circulation pressure loss of the coolant can be preferably compensated.

[0124] Conveniently, the outlet is in fluid connection with a bypass valve.

[0125] In this regard, the following terms are explained. By "bypass valve" is understood a valve set up to regulate and / or control the assumed volumetric flow of coolant through the bypass passage.

[0126] The cooperation of the coolant valve and the bypass valve allows a preferably high dynamics of the coolant volume flow to be maintained in the cooling module even when the cooling module is not currently being used to cool metal belt-like products.

[0127] The bypass valve may be controlled and / or controlled by an electronic control and / or control.

[0128] This has the advantage that a relatively low total pressure difference of the coolant can be realized in at least a partial region of the cooling module, which is not currently used for cooling the metal belt-like product, thereby reducing the delay time of the cooling module.In addition, a relatively high coolant velocity can be realized in at least a partial region of the cooling module, which is not currently used for cooling the metal belt-like product, thereby reducing the inertial resistance and therefore the compensation time of the cooling module.

[0129] Cooling modules not currently used for cooling metal belt-like products are understood to be those in which the assumed coolant velocity at the coolant discharge openings is substantially zero.

[0130] In a preferred embodiment, the cooling module comprises: at least two cooling bars each having a coolant chamber and a plurality of coolant discharge pipes connected in fluid communication with the coolant chamber, each of which has at least: - a coolant discharge opening for applying coolant to the belt-like product; and a cooling module branch in fluid communication with the at least two cooling bars.

[0131] In this regard, the following terms are explained. "Cooling module branch" means a flow division in the inlet region to a plurality of cooling bars. The envisaged coolant volume flow can be divided from the cooling module branch to a plurality of cooling bars, in particular to two, three, four, five or more cooling bars. Preferably, the coolant volume flow is divided into substantially identical portions.

[0132] The cooling module branch may be set up to be connected in at least indirect flow communication with the coolant reservoir.

[0133] Here, a cooling module is proposed which has a cooling module branch downstream of the coolant valve, which is preferably manufactured integrally with the cooling bars.

[0134] Preferably, the cooling module branch has a cooling module branch loss coefficient ζ of less than 0.2, preferably less than 0.15, particularly preferably less than 0.11. Modulverz It has.

[0135] More preferably, the cooling module branch has a cooling module branch loss coefficient ζ of less than 0.3, preferably less than 0.25, especially preferably less than 0.08. Modulverz It has.

[0136] In this regard, the following terms are explained. Cooling module branch loss coefficient ζ Modulverz can be determined as follows:

[0137]

number

number

[0138] Experiments have shown that the cooling module branch loss coefficient ζ Modulverz can have a functional relationship with the delay time of the cooling module, and a relatively low cooling module branch loss coefficient can shorten the delay time of the cooling module.

[0139] In an advantageous embodiment, the height difference between the coolant valve and the at least one coolant discharge opening is less than or equal to 500 mm, preferably less than or equal to 400 mm, particularly preferably less than or equal to 250 mm.

[0140] Further preferably, the height difference between the coolant valve and the at least one coolant discharge opening is not more than 325 mm, preferably not more than 200 mm, especially preferably not more than 175 mm.

[0141] With respect to the height difference specified herein, the height difference refers to the direction of gravity, and the height reference point of the coolant valve is the center point of the reference cross section of the coolant valve, in particular the center point of the coolant blocking area.

[0142] For short delay times it has been found to be advantageous if the coolant valve has a small height difference relative to the at least one coolant discharge opening.

[0143] Preferably, the cooling module has an electronic control unit and / or a control unit that is set up to control and / or regulate the cooling module. The electronic control unit and / or the control unit may be set up to control and / or regulate at least one coolant valve, in particular depending on the coolant speed and / or the coolant volumetric flow and / or the specific water load and / or the cooling rate and / or the texture of the metal belt-like product and / or the temperature of the metal belt-like product and / or the temperature profile along the conveying section of the metal belt-like product.

[0144] The mechanical properties of the metal belt-like product and / or the grain size of the metal belt-like product's structure and / or the phase composition of the metal belt-like product can be determined, in particular, using laser ultrasonic and / or magnetic measuring methods.

[0145] In a second aspect of the invention, the problem is solved by a cooling group of a cooling device for cooling a belt-shaped product of hot-rolled metal by means of a coolant, which comprises: - at least two cooling modules according to the first aspect of the invention; and - A cooling group branch in fluid communication with at least two cooling modules.

[0146] In this regard, the following terms are explained. A "cooling group branch" is understood to mean a flow division into several cooling modules in the inlet region. The cooling group branch can divide the envisaged coolant volume flow into several cooling modules, in particular into two, three, four, five or more cooling modules. Preferably, the coolant volume flow is divided into substantially identical portions.

[0147] The cooling group branch may be set up to be connected in at least indirect fluid communication with the coolant reservoir.

[0148] Here, a cooling group is proposed which has a plurality of cooling modules and a common coolant supply, so that the coolant can be split in a predictable manner from the cooling group branch to the plurality of cooling modules.

[0149] Preferably, the cooling group has a bypass outlet before the cooling group branch, the bypass outlet being set up to feed coolant back into the coolant reservoir and / or main coolant inlet.

[0150] The cooling group can have a flow-through measuring device, especially upstream of a cooling group branch.

[0151] Naturally, the advantages of the cooling module according to the first aspect of the invention also extend to a cooling group comprising at least two cooling modules according to the first aspect of the invention, as explained above.

[0152] Preferably, the cooling group branches have a cooling group branch loss coefficient ζ of less than 0.2, preferably less than 0.15, particularly preferably less than 0.11. Gruppenverz It has.

[0153] More preferably, the cooling group branches have a cooling group branch loss coefficient ζ of less than 0.3, preferably less than 0.25, and especially preferably less than 0.08. Gruppenverz It has.

[0154] In this regard, the following terms are explained. Cooling group branch loss coefficient ζ Gruppenverz can be determined as follows:

[0155]

number

number

[0156] In the experiment using the cooling group proposed here, the coolant group branch loss coefficient ζ Gruppenverz It has been found that the loss coefficient of the cooling group branch can be in a functional relationship with the delay time of the cooling module connected in fluid communication, and a relatively low loss coefficient of the cooling group branch can reduce the delay time of the cooling module.

[0157] Preferably, the cooling group has an electronic control unit and / or a control unit which is set up to control and / or regulate the cooling group. The electronic control unit and / or the control unit may be set up to control and / or regulate at least one coolant valve, in particular depending on the coolant speed and / or the coolant volume flow and / or the specific water load and / or the cooling rate and / or the texture of the metal belt-like product and / or the temperature of the metal belt-like product and / or the temperature profile along the conveying section of the metal belt-like product.

[0158] It is expressly pointed out that the subject matter of the second aspect may be advantageously combined with the subject matter of the above aspects of the invention, both individually and cumulatively in any combination.

[0159] In a third aspect of the present invention, the problem is solved by a cooling system for cooling a hot rolled metal belt-like product with a coolant, comprising: -Cooling equipment; at least one cooling module according to the first aspect of the invention and / or a cooling group according to the second aspect of the invention; and a coolant reservoir in fluid communication with a main coolant inlet, the main coolant inlet in fluid communication with at least one cooling module and / or at least one cooling group;

[0160] In this regard, the following terms are explained. "Main coolant inlet" means a fluid connection located downstream of a coolant reservoir and upstream of a cooling group and / or cooling module.

[0161] Preferably, the main coolant inlet has an internal diameter of at least 0.6 m, preferably at least 0.9 m, particularly preferably at least 1.3 m. The main coolant inlet has an internal diameter of at least 0.28 m normal to the expected direction of coolant flow. 2 More than 0.63m, preferably 2 Above 1.32m, especially preferred 2 The free cross-sectional area can be equal to or greater than this.

[0162] Here, a cooling system is proposed for actively cooling a belt-like product of hot rolled metal by means of a coolant, comprising at least one cooling module according to the first aspect of the invention and / or at least one cooling group according to the second aspect, wherein the at least one cooling module and / or the at least one cooling group is connected in fluid communication with a coolant reservoir at least indirectly and by means of a main coolant inlet.

[0163] The cooling system may have an electronic control unit and / or a control unit, preferably a higher-level electronic control unit and / or a control unit.

[0164] By "electronic control unit and / or control unit" is understood a device set up to monitor and / or regulate and / or control the cooling system, in particular depending on the coolant velocity and / or coolant volume flow and / or the specific water load and / or cooling rate and / or the organizational structure of the metal belt-like product.

[0165] The electronic control unit and / or the control unit may have an interface for receiving data, an interface for transmitting data and a device for processing data. In particular, the device for processing data may be configured to execute an algorithm, in particular for implementing the method according to the fourth aspect of the invention. Preferably, the electronic control unit and / or the control unit may have a device for storing data, in particular a data storage device.

[0166] Naturally, the advantages of a cooling module according to the first aspect of the invention and / or a cooling group according to the second aspect of the invention also extend to a cooling system comprising a cooling module according to the first aspect of the invention and / or a cooling group according to the second aspect of the invention, as explained above.

[0167] Particularly preferably, the cooling system has a temperature of 3·10 4 kg / (m·s 2 ) or more, preferably 4·10 4 kg / (m·s 2 ) or more, more preferably 4,5-10 4 kg / (m·s 2 ) or more, especially preferably 5-10 4 kg / (m·s 2 ) or greater pressure difference between the coolant reservoir and the coolant discharge opening.

[0168] The cooling system is 5.5-10 4 kg / (m·s 2 ) or more, preferably 6.10 4kg / (m·s 2 ) or more, preferably 6.5-10 4 kg / (m·s 2 ) or more, especially preferably 7-10 4 kg / (m·s 2 ) or more pressure difference between the coolant reservoir and the coolant discharge opening.

[0169] The pressure difference values ​​specified here allow for particularly short delay times to be achieved for at least one cooling module and / or at least one cooling group, and experiments have shown that, under otherwise identical conditions, the delay times can be reduced as the pressure difference increases.

[0170] In a preferred embodiment, the cooling system is 20 m 3 / (m 2 ·h) or more, preferably 50·m 3 / (m 2 ·h), more preferably 100·m 3 / (m 2 ·h) or more, particularly preferably 150·m 3 / (m 2 · h.) or more, may be set up for specific water loads.

[0171] The cooling system is 75 m 3 / (m 2 ·h) or more, preferably 125·m 3 / (m 2 ·h), and more preferably 175·m 3 / (m 2 ·h) or more, especially preferably 200·m 3 / (m 2 ·h) or more, may be set up for a specific water load.

[0172] In this regard, the following terms are explained. "Specific water load" is understood to mean the amount of coolant applied by the cooling system to the metal belt-like product for active cooling, based on the area of ​​the metal belt-like product and based on the time unit of the active cooling process. In particular, specific water load is understood to be the time-averaged and / or area-averaged water load.

[0173] Particularly preferably, the cooling system may be set up for a cooling rate of 50·K / (s·mm) or more, preferably 200·K / (s·mm) or more, more preferably 300·K / (s·mm) or more, especially preferably 500·K / (s·mm) or more.

[0174] The cooling system may be set up for a cooling rate of 100 K / (s·mm) or more, preferably 150 K / (s·mm) or more, more preferably 250 K / (s·mm) or more, and especially preferably 400 K / (s·mm) or more.

[0175] In a particularly advantageous embodiment, the cooling system may have at least one first cooling bar and a second cooling bar, the first cooling bar being set up to apply a coolant to an upper surface of the belt-like product and the second cooling bar being set up to apply a coolant to a lower surface of the belt-like product.

[0176] The proposed cooling system allows the metal belt-like product to be loaded with coolant simultaneously from both sides of the belt, thereby advantageously increasing the cooling rate.

[0177] Optionally, the cooling system has a main coolant delivery device set up to increase the pressure differential between the coolant reservoir and the coolant discharge opening.

[0178] In this regard, the following terms are explained. By "main coolant delivery device" is understood an active delivery device set up for delivering coolant directly at the transition to the main coolant inlet and / or at the main coolant inlet.

[0179] The proposed main coolant delivery device allows for an increased pressure differential and therefore a reduced delay time for at least one cooling module and / or at least one cooling group.

[0180] It is expressly pointed out that the subject matter of the third aspect may be advantageously combined with the subject matter of the above aspects of the invention, both individually and cumulatively in any combination.

[0181] In a fourth aspect of the present invention, the problem is solved by a method for actively cooling a hot rolled metal belt-like product, wherein for the active cooling of the hot rolled metal belt-like product a cooling module according to the first aspect of the present invention and / or a cooling group according to the second aspect of the present invention and / or a cooling system according to the third aspect of the present invention is used.

[0182] Preferably, the method comprises controlling and / or regulating at least one cooling module and / or at least one cooling group and / or at least one cooling system, and / or controlling at least one coolant valve and / or at least one bypass valve and / or at least one coolant delivery device and / or at least one main coolant delivery device, wherein the controlling and / or regulating may be configured in particular as a function of the coolant velocity and / or the coolant volume flow and / or the specific water load and / or the cooling rate and / or the texture of the metal belt product and / or the temperature of the metal belt product and / or the temperature profile along the conveying section of the metal belt product.

[0183] It is expressly pointed out that the subject matter of the fourth aspect may be advantageously combined with the subject matter of the above aspects of the invention, both individually and cumulatively in any combination.

[0184] In a preferred embodiment, the method is set up to regulate and / or control the degree of distribution of at least one tissue component, in particular to achieve a degree of distribution of 0.85 or more, preferably 0.9 or more, especially preferably 0.95 or more.

[0185] Here, a method for active cooling of a hot rolled metal belt-like product is proposed, which is set up for controlling and / or regulating the uniformity of the texture, which can be determined by the distribution of at least one texture constituent, and which is intended to at least indirectly detect the texture and to utilize at least one of the above-described adjustment variables of the cooling modules and / or cooling groups and / or cooling systems for controlling and / or regulating the distribution of at least one texture constituent.

[0186] Preferably, the method regulates and / or controls the distribution of two, or three, or four, or more tissue components.

[0187] Preferably, a degree of distribution of 0.875 or more, more preferably 0.925 or more, preferably 0.97 or more, especially preferably 0.98 or more is achieved.

[0188] The method is advantageously set up to reduce the head length of the metal belt-like product, in particular to achieve a head length of less than 10 m, preferably less than 8 m, particularly preferably less than 6 m.

[0189] "Head length" is understood to be the front length section of the metal belt-like product, the structure of which does not yet have sufficient uniformity, so that at least one mechanical property required for the metal belt-like product is not yet achieved in the head length region.

[0190] More advantageously, the method is set up to reduce the leg length of the metal belt-like product, in particular to achieve a leg length of 10 m or less, preferably a leg length of 8 m or less, particularly preferably a leg length of 6 m or less.

[0191] "Leg length" is understood to be a rear length section of the metal belt-like product, the structure of which does not yet have sufficient uniformity, so that at least one mechanical property required for the metal belt-like product is not yet achieved in the leg length region.

[0192] It is expressly pointed out that the subject matter of the fourth aspect may be advantageously combined with the subject matter of the above aspects of the invention, both individually and cumulatively in any combination.

[0193] In a fifth aspect of the present invention, a hot rolled metal belt-like product produced by the method according to the fourth aspect of the present invention has a strength of, in particular, 560 N / mm 2 A hot rolled metal product having a tensile strength equal to or greater than 1.5% by weight of manganese and a niobium percentage lower than 0.05% by weight solves the problem.

[0194] Preferably, the manganese content of the hot-rolled metal belt-like product is less than 1.45% by weight, more preferably less than 1.4% by weight, more preferably less than 1.35% by weight, and especially preferably less than 1.2% by weight.

[0195] Preferably, the niobium content of the hot rolled metal belt product is less than 0.045% by weight, more preferably less than 0.04% by weight, preferably less than 0.035% by weight, and especially preferably less than 0.03% by weight.

[0196] Preferably, the hot rolled metal belt product has a tensile strength of 565 N / mm 2 More preferably, 570N / mm 2 More than 575N / mm 2 Above 580N / mm 2 is.

[0197] Naturally, the benefits of the method according to the fourth aspect of the invention extend to the hot rolled metal products produced by this method, as explained above.

[0198] It is expressly pointed out that the subject matter of the fifth aspect may be advantageously combined with the subject matter of the above aspects of the invention, both individually and cumulatively in any combination.

[0199] In a sixth aspect of the present invention, the problem is solved by the use of a cooling module according to the first aspect of the invention, and / or a cooling group according to the second aspect of the invention, and / or a cooling system according to the third aspect of the invention, and / or a method according to the fourth aspect of the invention for actively cooling a hot-rolled metal belt-shaped product by means of a coolant.

[0200] Naturally, the cooling module according to the first aspect of the invention and / or the cooling group according to the second aspect of the invention and / or the cooling system according to the third aspect of the invention and / or the method according to the fourth aspect of the invention also directly extends to the use of a cooling module according to the first aspect of the invention and / or a cooling group according to the second aspect of the invention and / or a cooling system according to the third aspect of the invention and / or a method according to the fourth aspect of the invention for cooling a belt-like product of hot-rolled metal, as explained above.

[0201] It is expressly mentioned that the subject matter of the sixth aspect can be advantageously combined with the subject matter of the above aspects of the invention, either individually or cumulatively in any combination.

[0202] Further advantages, details and features of the invention will become apparent from the examples described below. [Brief explanation of the drawings]

[0203] [Figure 1] 1 shows a schematic diagram of a cooling module according to a first embodiment; [Figure 2] 1 is a schematic cross-sectional view of a cooling module. [Figure 3] 3 shows a schematic diagram of a cooling module according to a second embodiment; [Figure 4] 1 shows a schematic diagram of a cooling system. [Figure 5] 1 shows a schematic representation of a time-varying coolant valve step function. [Figure 6] 1 shows a schematic representation of a time-varying step function for a cooling module.

[0204] In the following description, the same reference numerals indicate the same components or features, so that the description of components given in one figure is valid for the other figures to avoid repetition. Furthermore, individual features described in connection with one embodiment can also be used separately in other embodiments.

[0205] The cooling module 100 of FIG. 1 essentially consists of a cooling bar 110, a coolant inlet 116, and a coolant valve 118.

[0206] The cooling module 100 may be a component of a cooling device (not shown) for cooling a hot-rolled metal belt-like product (not shown) with a coolant (not shown), which may be discharged from the cooling module 100 as envisaged and, after discharge, may be in operative relationship with the belt-like product, particularly the hot-rolled metal belt-like product, to effect cooling.

[0207] The cooling bar 110 includes a coolant chamber 112 and a plurality of coolant discharge tubes 114 (only partially labeled) connected in fluid communication with the coolant chamber 112. Each coolant discharge tube 114 has at least one coolant discharge opening (not labeled) for applying coolant to the belt-like product.

[0208] The coolant chamber 112 is connected and / or fluidly coupled to the coolant inlet 116 in at least indirect fluid communication. In particular, the coolant valve 118 is disposed between the coolant inlet 116 and the coolant chamber 112.

[0209] The coolant inlet 116 is set up to be connected in at least indirect fluid communication with a coolant reservoir (not shown), which is set up to provide a pressure differential between the coolant reservoir and at least one coolant outlet opening (not numbered).

[0210] The cooling module 100 has a transition 112a from the coolant chamber 112 to the coolant discharge pipe 114, which transition 112a is preferably well chamfered and has a transition loss coefficient of less than 0.3, preferably less than 0.15, and particularly preferably less than 0.08.

number

[0211] Naturally, a transition 112 a is provided between each coolant discharge pipe 114 and the coolant chamber 112 .

[0212] The coolant valve 118 has a distance 118a of not more than 500 mm, preferably not more than 325 mm, and particularly preferably not more than 275 mm from the transition from the coolant chamber 112 to the coolant discharge pipe 114. The distance 118a between the coolant valve 118 of the cooling module 100 and the transition 112a from the coolant chamber 112 to the coolant discharge pipe 114 is understood as the distance 118a between the flange (not numbered / not shown) of the coolant chamber 112 at the sealing surface (not numbered / not shown) of the flange for connection with the coolant valve 118 and the surface center of gravity (not numbered / not shown) of the transition 112a between the coolant chamber 112 and the coolant discharge pipe 114.

[0213] Naturally, the spacing 118a is understood to be the spacing 118a relative to the shortest coolant discharge pipe 114, i.e., the coolant valve 118, when there are multiple coolant discharge pipes 114.

[0214] The cooling module 100 can have a flow-through measuring device 140 (schematically shown), in particular in the form of a tactile or non-tactile flow-through measuring device 140. The flow-through measuring device 140 can be arranged in the coolant inlet 116, in the coolant valve 118, or in the coolant chamber 112 downstream of the coolant valve 118 and upstream of the coolant outlet pipe 114 located nearest to the coolant valve 118.

[0215] In FIG. 2, a cross-sectional view of the cooling module 100 shown in FIG. 1 can be seen.

[0216] The coolant chamber 112 of the cooling bar 110 of the cooling module 100 has a transition 112 a to a coolant exhaust pipe 114 .

[0217] The coolant discharge tube 114 has a coolant discharge opening 114a through which a coolant (not shown) can be discharged.

[0218] Between the height reference point 118b of the coolant valve 118 and the coolant discharge opening 114a, there is a height difference 120 in the direction of gravity (not shown). The height difference 120 may be 500 mm or less, preferably 400 mm or less, and particularly preferably 250 mm or less.

[0219] The cooling module 100 of FIG. 3 has an outlet 150 for a bypass passage 152 that is configured to be in direct fluid communication with the coolant chamber 112 .

[0220] The outlet 150 is fluidly connected to a bypass valve 154 and can be opened and closed by the bypass valve 154 .

[0221] The cooling system 400 of Figure 4 essentially comprises a cooling device 300 for cooling the metal belt-like product 10 with a coolant 20, a coolant reservoir 410 for storing the coolant 20, the cooling device 300 for applying the coolant 20 to the metal belt-like product 10, and a main coolant inlet 420 for fluidly connecting the coolant reservoir 410 with the cooling device 300.

[0222] The cooling system 400 may include a main coolant delivery system 430 for increasing the total pressure of the coolant 20 in the cooling system 300 .

[0223] It is intended that the metal belt-like product 10 can be conveyed in a conveying direction (not shown) on a conveying section (not numbered) and thereby brought into operative relationship with the cooling device 300, in particular by operative relationship with the liquid coolant 20 discharged from the cooling device 300 as envisaged. To this end, the metal belt-like product 10 can be conveyed beside at least one cooling module 100 of the cooling device 300 and / or can be conveyed so as to pass between at least two cooling modules 100 of the cooling device 300.

[0224] The cooling device 300 may have at least one cooling module 100, in particular one or more first cooling modules 100, arranged above the metal belt-like product 10, to which liquid coolant 20 is supplied via a main coolant inlet 420, the cooling modules 100 preferably extending transversely to the conveying direction (not indicated) and preferably having a plurality of coolant outlet pipes (not shown) through which the liquid coolant 20 can be brought into operative contact with the metal belt-like product 10.

[0225] Accordingly, the cooling device 300 may have at least one cooling module 100, in particular one or more second cooling modules 100, arranged below the metal belt-like product 10, set up to bring the liquid coolant 20 into operative relationship with the metal belt-like product 10.

[0226] In the conveying direction of the metal belt-like product 10 , the cooling device 300 can have a number of cooling modules 100 which can be arranged above and / or below the metal belt-like product 10 .

[0227] One or more cooling modules 100 may be arranged in one or more cooling groups 200 in the cooling system 300 .

[0228] The coolant reservoir 410 is in fluid communication with a main coolant inlet 420 , which is in fluid communication with at least one cooling module 100 and / or at least one cooling group 200 .

[0229] The cooling device 300 has two cooling groups 200 arranged above the metal belt-like product 10, which are fluidly connected to the main coolant inlet 420 by cooling group branch portions 210 also arranged above the metal belt-like product 10.

[0230] The cooling device 300 has two cooling groups 200 arranged below the metal belt-like product 10, which are fluidly connected to the main coolant inlet 420 by cooling group branches 210 also arranged below the metal belt-like product 10.

[0231] Each cooling group 200 has two cooling modules 100 fluidly connected to respective cooling group branches by cooling module branches 160 .

[0232] Furthermore, the cooling system 400 is 20 m 3 / (m 2 ·h) or more, preferably 50·m 3 / (m 2 ·h) or more, particularly preferably 150·m 3 / (m 2 ·h) or more, may be set up for a specific water load.

[0233] The cooling system 400 may be set up for a cooling rate of 50·K / (s·mm) or more, preferably 200·K / (s·mm) or more, particularly preferably 500·K / (s·mm) or more.

[0234] 5 represents the time course of the coolant velocity 22 immediately downstream of the coolant valve (not shown), or at the narrowest cross section of the coolant valve (not shown), versus time 24 after the coolant valve suddenly opens. The origin of the coolant valve step function 40 represents the time when the coolant valve suddenly opens and the coolant velocity 22 has a value of zero.

[0235] The coolant valve step function 40 represents the time-varying system behavior of the coolant valve (not shown) after a sudden opening of the coolant valve (not shown).

[0236] As the coolant valve opens, the coolant velocity 22 immediately downstream of the coolant valve, or at the narrowest cross section of the coolant valve, converges towards a constant (unsigned) value of the coolant velocity 22 .

[0237] The coolant valve step function 40 may alternatively be described and / or characterized by a coolant valve time constant 42, which may be graphically determined from the coolant valve step function 40 by determining the intersection (unsigned) of a tangent line (unsigned) drawn at the origin to the coolant valve step function 40 with the value of the coolant rate 22 to which the coolant valve step function 40 is converging, and determining the time difference between this intersection and the instant of the coolant valve jump opening.

[0238] 6 represents the time course of the coolant velocity 22 at the coolant discharge opening (not shown) versus time 24 after the coolant valve (not shown) has suddenly opened. The origin of the coolant valve step function 40 represents the time when the coolant valve has suddenly opened and the coolant velocity 22 has a value of zero.

[0239] The coolant valve step function 30 may represent the time-varying system behavior of a cooling module (not shown) after a sudden opening of a coolant valve (not shown).

[0240] As the coolant valve opens, the coolant velocity 22 at the coolant discharge opening converges towards a constant (unsigned) value of coolant velocity 22 .

[0241] Step function 30 may alternatively be described and / or characterized by a delay time 32 and a compensation time 34 , which may be determined graphically from step function 30 .

[0242] The delay time 32 can be a measure of higher order influences on the time-varying system behavior of the cooling module and is obtained by the following steps from the time-varying step function 30: - determining the inflection points (unsigned) of the time-varying step function 30, in particular of the coolant velocity 22; - Tangents (unsigned) are drawn through the inflection points of the time-varying step function 30, and The delay time 32 is determined as the difference between the time instant (unsigned) at which the tangent line intersects the horizontal axis (time axis) and the time instant (unsigned) of the jump in the adjustment quantity, in particular the jump in the opening of the coolant valve.

[0243] The compensation time 34 can be a measure of the inertia of the time-varying system behavior, i.e., a measure of the first-order influence on the time-varying system behavior, and is obtained by the following steps from the time-varying step function 30: - the inflection points (without sign) of the time-varying step function 30, in particular of the coolant velocity 22, are determined; - Tangents (unsigned) are drawn through the inflection points of the time-varying step function 30; and - determining the steady-state asymptote of the time-varying step function 30 that occurs after a jump in the adjustment amount; and -The compensation time 34 is determined as the difference between the time when the tangent line intersects the asymptote and the time when the tangent line intersects the horizontal axis. [Explanation of symbols]

[0244] 10 Metal belt-like products 20 Coolant 22 Coolant velocity 24 hours 30 Step Functions 32 Delay Time 34 Compensation time 40 Coolant Valve Step Function 42 Coolant Valve Time Constant 100 Cooling Module 110 Cooling Bar 112 Coolant chamber 112a Transition 114 Coolant discharge pipe 114a Coolant discharge opening 116 Coolant inlet 118 Coolant Valve 118a spacing 118b Height Reference Point 120 height difference 140 Flow-Through Measurement Device 150 Exit 152 Bypass Passage 154 Bypass valve 160 Cooling module branch 200 Cooling Group 210 Cooling group branch 300 Cooling device 400 Cooling System 410 Coolant Reservoir 420 Main coolant inlet 430 Main coolant delivery device ζ Ventil Coolant Valve Loss Coefficient

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Claims

1. A cooling module (100) of a cooling device (300) for cooling a hot-rolled metal belt-like product (10) by means of a coolant (20), comprising: at least one cooling bar (110) having a coolant chamber (112) and a plurality of coolant discharge pipes (114), said coolant discharge pipes (114) being connected in fluid communication with said coolant chamber (112) and each of said coolant discharge pipes (114) having at least one coolant discharge opening (114a) for applying a coolant (20) to the belt-like product (10); at least one coolant inlet (116) connected in at least indirect fluid communication with said coolant chamber (112), said coolant inlet (116) being set up to be connected in at least indirect fluid communication with a coolant reservoir (410), said coolant reservoir (410) being set up to provide a pressure difference between said coolant reservoir (410) and said coolant outlet opening (114a); at least one coolant valve (118), said coolant valve (118) being arranged between said coolant inlet (116) and said coolant chamber (112); The cooling module (100) has a time-varying behavior of the coolant velocity (22) at the coolant discharge opening (114a) under the influence of a pressure difference, which can be described by a time-varying step function (30) having a delay time (32) and a compensation time (34) when the coolant valve (118) suddenly opens completely, A cooling module, characterized in that the sum of the delay time (32) and the compensation time (34) is less than or equal to 3.0 s, preferably less than or equal to 2.0 s, particularly preferably less than or equal to 1.5 s.

2. 2. The cooling module (100) of claim 1, wherein the coolant valve (118) has a time-varying behavior of the coolant velocity (22) in the coolant chamber (112) that can be described by a time-varying coolant valve step function (40) having a coolant valve time constant (42) under the influence of a pressure difference when the coolant valve (118) is suddenly fully opened, the coolant valve time constant (42) being 1.5 s or less, preferably 1.0 s or less, and particularly preferably 0.5 s or less.

3. The coolant valve (118) has a coolant valve loss coefficient ζ of less than 0.46, preferably less than 0.44, and particularly preferably less than 0.24 in a fully open position. Ｖｅｎｔｉｌ 3. The cooling module (100) according to claim 1, characterized in that it comprises:

4. 4. The cooling module (100) according to any one of claims 1 to 3, characterized in that the coolant valve (118) has a nominal width of DN 80 or more, preferably DN 150 or more, particularly preferably DN 200 or more.

5. 5. The cooling module (100) according to any one of claims 1 to 4, characterized in that the coolant valve (118) has a nominal width of DN 300 or less, preferably DN 250 or less, particularly preferably DN 120 or more.

6. 6. The cooling module (100) according to claim 1, wherein the coolant valve (118) has a spacing (118a) of less than 500 mm, preferably less than 325 mm, particularly preferably less than 275 mm, relative to the transition from the coolant chamber (112) to the coolant discharge pipe (114).

7. The transition (112a) from the coolant chamber (112) to the coolant discharge pipe (114) is preferably chamfered and has a transition loss coefficient of less than 0.3, preferably less than 0.15, particularly preferably less than 0.

08. [Equation 1] 7. The cooling module (100) according to any one of claims 1 to 6, characterized in that it comprises:

8. 8. The cooling module (100) according to any one of claims 1 to 7, characterized in that the cooling module (100) comprises a flow-through measuring device (140).

9. 9. The cooling module (100) according to claim 1, characterized in that it has an outlet (150) for a bypass passage (152), in particular in direct fluid communication with the coolant inlet (116) and / or in direct fluid communication with the coolant chamber (112).

10. The cooling module (100) of claim 9, wherein the outlet (150) is fluidly connected to a bypass valve (154).

11. The cooling module (100) has at least two cooling bars (110), each having one coolant chamber (112) and a plurality of coolant discharge openings (114) connected in fluid communication with the coolant chamber (112), each having at least one coolant discharge opening (114a) for applying coolant (20) to the belt-like product (10); and a cooling module branch (160) in fluid communication with at least two of said cooling bars (110); A cooling module (100) according to any one of claims 1 to 10, characterized in that

12. The cooling module branch (160) has a cooling module branch loss coefficient ζ of less than or equal to 0.2, preferably less than or equal to 0.15, particularly preferably less than or equal to 0.

11. Ｍｏｄｕｌｖｅｒｚ The cooling module (100) of claim 11, characterized in that it comprises:

13. 13. The cooling module (100) according to any one of claims 1 to 12, characterized in that the height difference (120) between the coolant valve (118) and the at least one coolant discharge opening (114a) is not more than 500 mm, preferably not more than 400 mm, and particularly preferably not more than 250 mm.

14. A cooling group (200) of a cooling device (300) for cooling a hot-rolled metal belt-like product (10) by a coolant (20), At least two cooling modules (100) according to any one of claims 1 to 13; a cooling group branch (210) fluidly connected to at least two of said cooling modules (100).

15. The cooling group branch (210) has a cooling group branch loss coefficient ζ of less than 0.2, preferably less than 0.15, particularly preferably less than 0.

11. Ｇｒｕｐｐｅｎｖｅｒｚ The cooling group (200) according to claim 14, characterized in that it comprises:

16. A cooling system (400) for cooling a hot rolled metal belt-like product (10) with a coolant (20), comprising: a cooling system (400); at least one cooling module (100) according to any one of claims 1 to 13 and / or at least one cooling group (200) according to any one of claims 14 or 15; a coolant reservoir (410) in fluid communication with a main coolant inlet (420), the main coolant inlet (420) being in fluid communication with at least one of the cooling modules (100) and / or at least one of the cooling groups (200).

17. The cooling system (400) is 3.10 ４ kg / (m·s ２ ) or more, preferably 4.10 ４ kg / (m·s ２ ) or more, especially preferably 4, 5, 10 ４ kg / (m·s ２ 17. The cooling system (400) of claim 16, wherein the cooling system (400) is set up for a pressure difference between the coolant reservoir (410) and the coolant discharge opening (114a) of at least 1 / 2 psi.

18. The cooling system (400) has a capacity of 20 m ３ / (m ２ ·h) or more, preferably 50 ·m ３ / (m ２ ·K) or more, particularly preferably 150 ·m ３ / (m ２ 18. Cooling system (400) according to claim 16 or 17, characterized in that it is set up for a specific water load of at least h).

19. 19. Cooling system (400) according to any one of claims 16 to 18, characterized in that the cooling system (400) is set up for a cooling rate of 50 K / (s-mm) or more, preferably 200 K / (s-mm) or more, particularly preferably 500 K / (s-mm) or more.

20. The cooling system (400) according to any one of claims 16 to 19, characterized in that the cooling system (400) has at least one first cooling bar (10) and a second cooling bar (10), the first cooling bar (110) being set up to apply a coolant (20) to an upper surface of the belt-like product (10), and the second cooling bar (110) being set up to apply a coolant (20) to a lower surface of the belt-like product (10).

21. 21. The cooling system (400) according to any one of claims 16 to 20, characterized in that the cooling system (400) has a main coolant delivery device (430) set up to increase the pressure difference between the coolant reservoir (410) and the coolant discharge opening (114a).

22. 1. A method for actively cooling a hot-rolled metal belt-shaped product (10), characterized in that a cooling module (100) according to any one of claims 1 to 13 and / or a cooling group (200) according to any one of claims 14 or 15 and / or a cooling system (400) according to any one of claims 16 to 21 is used for the active cooling of the hot-rolled metal belt-shaped product (10).

23. 23. A method for active cooling of a hot-rolled metal belt-like product (10) according to claim 22, characterized in that the method is set up to control and / or regulate the distribution of at least one texture component, in particular to achieve a distribution of 0.85 or more, preferably 0.9 or more, particularly preferably 0.95 or more.

24. 24. A method for active cooling of a hot-rolled metal belt-like product (10) according to claim 22 or 23, characterized in that the method is set up to reduce the head length of the metal belt-like product (10), in particular to achieve a head length of less than 10 m, preferably less than 8 m, particularly preferably less than 6 m.

25. 25. A method for actively cooling a hot-rolled metal belt-like product (10) according to any one of claims 22 to 24, characterized in that the method is set up to reduce the leg length of the metal belt-like product (10), in particular to achieve a leg length of 10 m or less, preferably a leg length of 8 m or less, particularly preferably a leg length of 6 m or less.

26. A hot-rolled metal belt-shaped product (10) manufactured by the method according to any one of claims 22 to 25, in particular a belt-shaped product (10) having a strength of 560 N / mm ２ 1. A hot rolled metal product (10) having a tensile strength of or greater than 1.5 wt. % manganese and a niobium percentage of less than 0.05 wt. %.

27. Use of a cooling module (100) according to any one of claims 1 to 13, and / or a cooling group (200) according to any one of claims 14 or 15, and / or a cooling system (400) according to any one of claims 16 to 21, and / or a method according to any one of claims 22 to 25 for actively cooling a belt-shaped product (10) of hot-rolled metal by means of a coolant (20).

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