Cooling module, cooling assembly, cooling system, method, hot-rolled metal strip-shaped product, and use

Abstract

The invention relates to a cooling module of a cooling device for cooling a hot-rolled metal strip-shaped product using a coolant, the cooling module comprising: - at least one cooling bar having a coolant chamber and a plurality of coolant outlet pipes, which are fluid-communicatingly connected to the coolant chamber and each comprise at least one coolant outlet opening for applying the coolant to the strip-shaped product; - at least one coolant feed, which is at least indirectly fluid-communicatingly connected to the coolant chamber, wherein the coolant feed is designed to be at least indirectly fluid-communicatingly connected to a coolant reservoir, wherein the coolant reservoir is designed to provide a pressure difference between the coolant reservoir and the coolant outlet opening; - at least one coolant valve, wherein the coolant valve is arranged between the coolant feed and the coolant chamber; - wherein, under the influence of the pressure difference, when the coolant valve is fully opened in a step-like manner, the cooling module exhibits a time-variant behaviour of a coolant rate in the coolant outlet opening, which behaviour can be described using a time-variant Heaviside step function comprising a delay time and an equalisation time; and - wherein the sum of the delay time and the equalisation time is less than or equal to 3.0 s, preferably less than or equal to 2.0 s, and particularly preferably less than or equal to 1.5 s.

Description

[0001] Page 1 / 65 Applicant: SMS group GmbH Our reference: P80649DE October 26, 2022 Cooling module, cooling group, cooling system, method, hot-rolled metallic strip product, and use The invention relates to a cooling module, a cooling group, a cooling system, a method, a hot-rolled metallic strip product, and a use. The cooling module described here for cooling a strip product, in particular a hot-rolled metallic strip product, has at least one cooling beam with a coolant chamber and several coolant outlet pipes communicating with the coolant chamber for applying a liquid coolant to the strip product, and can be used to cool the same. For the production of flat or strip metal products, in particular metal strips or metal sheets, it is known to provide cooling of the metal products using cooling beams.which extend across the width of a conveyor line along which the metal products are transported. For this purpose, the cooling beam can have a coolant chamber that is supplied with the liquid coolant and from which several coolant outlet pipes lead out to allow the coolant to escape, in particular for applying the coolant to the strip-shaped product. Such cooling beams can be part of a cooling module and / or a cooling group and / or a cooling system. Page 2 / 65 P80649DE The invention is based on the object,to provide an improvement or an alternative to the prior art. According to a first aspect of the invention, the object is achieved by a cooling module of a cooling device for cooling a hot-rolled metallic strip-shaped product with a coolant, comprising: - at least one cooling beam with a coolant chamber and a plurality of coolant outlet pipes connected in fluid communication with the coolant chamber, each having at least one coolant outlet opening for applying the coolant to the strip-shaped product; - at least one coolant inlet connected at least indirectly in fluid communication with the coolant chamber, wherein the coolant inlet is configured to be connected at least indirectly in fluid communication with a coolant reservoir,wherein the coolant reservoir is configured to provide a pressure difference between the coolant reservoir and the coolant outlet opening; - at least one coolant valve, wherein the coolant valve is arranged between the coolant inlet and the coolant chamber; - wherein the cooling module, under the influence of the pressure difference, exhibits a time-variant behavior of a coolant velocity in the coolant outlet opening upon sudden, complete opening of the coolant valve, which behavior can be described with a time-variant step function having a delay time and a compensation time; and - wherein the sum of the delay time and the compensation time is less than or equal to 3.0 s, preferably less than or equal to 2.0 s, and particularly preferably less than or equal to Page 3 / 65 P80649DE The following is explained in terms of terms: First, it should be expressly pointed out thatthat in the context of this patent application, indefinite articles and numerical expressions such as "one", "two", etc., should generally be understood as "at least" expressions, i.e., as "at least one...", "at least two...", etc., unless it is expressly clear from the respective context or it is obvious or technically necessary for the person skilled in the art that only "exactly one...", "exactly two...", etc. can be meant. In the context of this patent application, the expression "in particular" should always be understood as introducing an optional, preferred feature. The expression is not to be understood as "namely" or "namely." A "cooling device" can be understood as a system designed to cool a flat and / or strip-shaped metal product using a liquid coolant, in particular a hot-rolled metallic strip-shaped product. It is provided thatthat the metallic strip-shaped product can be conveyed along a conveyor line in a transport direction such that it can come into operative contact with the cooling device, in particular through an operative contact with a liquid coolant specifically emerging from the cooling device. For this purpose, the metallic strip-shaped product can be conveyed past at least one cooling beam of the cooling device and / or between at least two cooling beams of the cooling device. The cooling device can have at least one cooling beam arranged above the metallic strip-shaped product, in particular one or more first cooling beams, to which the liquid coolant is supplied via a coolant inlet, wherein the cooling beam preferably extends substantially transversely to the transport direction and preferably has a plurality of coolant outlet pipes,via which the liquid coolant can be brought into operative connection with the metallic strip-shaped product. Analogously, the cooling device can have at least one cooling beam arranged below the metallic strip-shaped product, in particular one or more second cooling beams, which are designed to bring the liquid coolant into operative connection with the metallic strip-shaped product. In the conveying direction of the metallic strip-shaped product, the cooling device can have a plurality of cooling beams, which can be arranged above and / or below the metallic strip-shaped product. One or more cooling beams of a cooling device can 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. While one cooling module can have a plurality of cooling beams,which can be supplied with coolant at least indirectly via a common cooling module branch, a "cooling group" can have a plurality of cooling modules, which can be supplied with coolant at least indirectly via a common cooling group branch. A plurality of cooling modules of a cooling group can be operated, in particular, with different setting values, in particular different volume flows of the liquid coolant flowing out of a respective associated coolant outlet opening. Page 5 / 65 P80649DE A "cooling system" has, in addition to at least one cooling module and / or at least one cooling group, at least one coolant reservoir and at least one "main coolant inlet",wherein the at least one main coolant inlet is at least indirectly fluidically connected to the at least one coolant reservoir and the at least one cooling module and / or the at least one cooling group. Preferably, a cooling system has a higher-level electronic control and / or regulating unit, wherein the higher-level electronic control and / or regulating unit is configured to control and / or regulate the cooling system. The higher-level electronic control and / or regulating unit can be configured to control and / or regulate at least one coolant valve. Alternatively, the higher-level electronic control and / or regulating unit can be data-connected to at least one electronic control and / or regulating unit.wherein the electronic control and / or regulating unit is configured to control and / or regulate the cooling module and / or a cooling group. A coolant reservoir is configured to store and / or provide coolant. A "coolant" is understood to mean a fluid that can be used to cool the metallic strip-shaped product, wherein the coolant can have different temperature states. In particular, the coolant can be a gaseous and / or liquid substance or a gaseous and / or liquid mixture of substances. Here, it is provided thatthat the coolant flows out of a coolant outlet opening at least predominantly in liquid form. Due to a heat flow from the metallic strip-shaped product to the coolant, the coolant can at least partially evaporate. Page 6 / 65 P80649DE In the liquid state, the coolant is considered incompressible. A "cooling beam" essentially consists of a substantially longitudinally extending coolant chamber, a plurality of coolant outlet pipes connected in fluid communication with the coolant chamber and arranged one behind the other or in pairs in the longitudinal direction of the cooling beam, and a coolant inlet opening. The "coolant chamber" is designed to relax the pressure of the coolant flowing into the cooling beam through the coolant inlet opening.whereby a predominantly uniform distribution of a coolant volume flow from the coolant chamber to the coolant outlet pipes can be achieved. In the case of a plurality of coolant outlet pipes directly fluidically connected to a coolant chamber, a means for hydraulic balancing can be provided at the transition between the cooling chamber and at least one coolant outlet pipe, which means is designed to quantitatively harmonize the partial coolant volume flows flowing out from a plurality of coolant outlet pipes directly fluidically connected to the cooling chamber. A "coolant outlet pipe" is understood to mean a tubular extension of the cooling beam,which is designed to allow the coolant to exit the cooling beam through a "coolant outlet opening." A coolant outlet pipe can preferably be welded or screwed to the coolant chamber or otherwise connected to the coolant chamber. A coolant outlet pipe can extend in a straight line. Alternatively, a coolant outlet pipe can extend in a J-shape and / or be shaped like a gooseneck. Page 7 / 65 P80649DE A "coolant valve" is understood to mean a device for controlling a flow rate of the coolant in a coolant closure region of the coolant valve, wherein a coolant closure region can be completely shut off. A coolant valve can be at least indirectly electrically and / or electronically adjustable. In particular, a coolant valve can be designed as a coolant control valve, which is designed toto regulate a flow rate of the coolant to an externally specified setpoint. A coolant valve can have a data interface that is configured to connect the coolant valve to an electronic data processing and evaluation unit, wherein the electronic data processing and evaluation unit is configured to control and / or regulate the coolant valve. Preferably, the largest possible free cross-section of a coolant valve, in particular that of a coolant closure area, is greater than or equal to a nominal diameter of a coolant inlet and / or a nominal diameter of a coolant inlet opening of a cooling beam and / or a nominal diameter of a coolant chamber of a cooling beam. A "cooling module" is a unit comprising at least one cooling beam,at least one coolant valve and at least one "coolant inlet" for supplying the cooling module with coolant. Preferably, exactly one coolant valve is at least indirectly fluidically connected to exactly one cooling beam. Page 8 / 65 P80649DE A "coolant inlet" can be understood as a region of a coolant guide means that is directly fluidically connected to a coolant valve, in particular an inlet region of the coolant valve, in particular a free cross-section of a coolant valve flange, in particular of that coolant valve flange that is arranged on the complementary side to the side of the coolant valve that is in fluid communication with the cooling beam. Alternatively, a coolant inlet can be understood as a region of a coolant pipe that is directly fluidically connected to the coolant valve. A coolant inlet can be configured toto be fluidly connected at least indirectly to a coolant reservoir for storing and / or providing coolant. A "pressure difference" is understood to mean a total pressure difference between the level of the coolant reservoir and a coolant outlet opening of a cooling module. The total pressure difference can result from a difference in the geodetic height between the level of the coolant reservoir and a coolant outlet opening of a cooling module, and / or from pressure losses between the coolant reservoir and the coolant outlet opening of the cooling module, and / or from a pressure change using a conveying device, in particular a main coolant conveying device, in a connection that is passable for the coolant between the coolant reservoir and at least one coolant outlet pipe. ^ ^^ ⁄ ( ^ ∙ ^ ^), furthermore preferably the pressure difference is greater than or equal to 4 ∙ 10 ^ ^^⁄ (^ ∙ ^ ^ ), preferably the pressure difference Page 9 / 65 P80649DE is greater than or equal to 5 ∙ 10 ^ ^^ ⁄ ( ^ ∙ ^ ^) and particularly preferably the pressure difference is greater than or equal to 6 ∙ 10 ^ ^^⁄ (^ ∙ ^ ^). A "coolant velocity" is understood to mean the cross-sectionally averaged velocity in a reference cross-section of the cooling device between the coolant reservoir and a coolant outlet opening of a cooling module. Preferably, the coolant velocity means the averaged velocity in a coolant outlet opening of a cooling module. A "time-variant behavior" means a system behavior whose system response depends both on the observation time and on the time of a sudden change in a manipulated variable at the system input. In particular, the coolant velocity in a coolant outlet opening of the cooling module depends on a setting of a coolant valve, in particular a sudden adjustment of the coolant valve, and the acting pressure difference.A "time-variant step function" of the coolant velocity over time describes the course of the coolant velocity in a coolant outlet opening of the cooling module as a function of time after a sudden opening of the coolant valve corresponding to the coolant outlet opening, with a steady state occurring after a certain time as the system response. When evaluating the time-variant system behavior based on the time course until the steady state is reached, a compensation time and / or a delay time can be considered, in particular, as system-dependent and thus characteristic variables of the time-variant step function. The time-variant system behavior can be used to describe a controlled system within the framework of a control system, particularly within the framework of a control system for a cooling module.The "delay time" can represent a measure of the higher-order influences on a time-variant system behavior and results from the time-variant step function through the following steps: - Determination of the inflection point of the time-variant step function, in particular the coolant velocity; - Drawing a tangent through the inflection point of the time-variant step function; and - Determination of the delay time as the difference between the time at which the tangent intersects the abscissa and the time of the sudden change in the manipulated variable, in particular the sudden opening of the coolant valve.The "settlement time" can represent a measure of the inertia of a time-variant system behavior, i.e. a measure of the first-order influences on a time-variant system behavior, and is obtained from the time-variant step function through the following steps: - Determining the inflection point of the time-variant step function, in particular the coolant velocity; - Drawing a tangent through the inflection point of the time-variant step function; - Determining an asymptote for the steady state of the time-variant system behavior resulting after the step-like change in the manipulated variable; and - Determining the settlement time as the difference between the time at which the tangent intersects the asymptote and the time at which the tangent intersects the abscissa.Page 11 / 65 P80649DE A "cooling rate" is understood to be the speed at which a hot-rolled metallic strip product is cooled. The cooling rate can be specified in the unit K / s. If a hot-rolled metallic strip product is cooled from an average temperature of 1,150 K at a constant cooling rate of 50 K / s, it will have an average temperature of 650°K after a cooling time of 10 s. The cooling rate is dependent, among other things, on the amount of coolant and the thickness of the metallic strip product. If the thickness of the metallic strip product increases while all other parameters remain constant, the cooling rate decreases as a result of temperature equalization processes in the metallic strip product. The course of the phase transformation of steel influences the microstructure of the steel.The microstructure of steel, in turn, influences its properties. The course of the phase transformation of steel is essentially determined by the cooling rate and the temporal progression of the cooling rate. Preferably, in a first cooling phase, the hot-rolled metallic product is actively cooled with a cooling system using a liquid coolant to a first target temperature, and in a second cooling phase, the hot-rolled metallic product cools passively until the ambient temperature is reached. Furthermore, preferably, the hot-rolled metallic product is coiled shortly after reaching the first target temperature.The microstructure of steel, in particular the ferrite content and / or the pearlite content and / or the bainite content and / or the martensite content and / or the austenite content of the steel structure, and thus its material properties, are determined, among other things, by the cooling rate of the cooling system, the first target temperature up to which active cooling takes place, and the alloy composition of the steel. Preferably, a cooling rate can be achieved that reduces or prevents pearlite precipitation, thereby reducing the hardness of the material and thus improving formability. Alternatively, a pearlite content in the metallic structure can be achieved or specifically adjusted with a comparatively lower cooling rate, which increases the hardness of the hot-rolled metallic product.The hot rolling of a hot-rolled metallic product is a predominantly continuous process, with the rolling stands being stationary and the metallic product being conveyed through the rolling stands for rolling. Accordingly, active cooling after rolling by means of a cooling system is also a continuous process, in which the hot-rolled metallic product is predominantly continuously conveyed past at least one stationary cooling beam of the cooling system and / or between at least two stationary cooling beams of the cooling system.Accordingly, in the continuous active cooling process, a plurality of coolant outlet openings are involved in the conveying direction of the metallic strip-shaped product past and / or through the cooling device of the cooling system, so that the course of the cooling rate and thus also the properties of the hot-rolled metallic product along the conveying direction are influenced by a plurality of cooling beams and coolant outlet openings and the respective conveyed or exiting coolant quantities.In other words, there is a causal relationship between the properties of a hot-rolled metallic product and the coolant volume flows flowing out of a plurality of coolant outlet openings, in particular the coolant volume flows flowing out of a plurality of coolant outlet openings arranged in the conveying direction, in particular the coolant volume flows flowing out of a plurality of coolant outlet openings arranged in the conveying direction of different cooling beams. Tests have shown that with an advantageous temporal progression of the cooling rate along the conveying direction of a hot-rolled metallic product, cost-intensive alloying elements can be proportionally reduced to achieve the same material properties.In this respect, it is particularly advantageous to be able to vary the temporal progression of the cooling rate quickly and / or precisely, in particular in a causal relationship with a plurality of cooling beams influencing the cooling rate. The cooling rate exhibits causal relationships with a plurality of physical effects, whereby at this point only those causal relationships will be discussed which have a particularly sensitive impact on the cooling rate. Tests have shown it to be advantageous to be able to precisely control and / or regulate the cooling rate in causal relationships with one cooling beam, in particular with exactly one cooling beam, and thus with a fixed, designed coolant volume flow.Furthermore, tests have shown that some effects physically related to the cooling rate exhibit particularly high dynamics, which unexpectedly proves particularly advantageous to be able to control and / or regulate a stationary, designated coolant volume flow with improved dynamics, particularly in conjunction with a single cooling beam, preferably with exactly one cooling beam. A first interaction with high dynamics on the cooling rate is the Leidenfrost effect. The temperature of the hot-rolled metallic product before entering the cooling device is regularly above the Leidenfrost temperature, which can be between approximately 300 K and 600 K, depending on the characteristics of a number of parameters.As a result, at least in the first section of the hot-rolled metallic product's conveyance through the cooling device, a coolant vapor layer forms between the hot-rolled metallic product and the liquid coolant, dampening the heat transfer coefficient and thus the cooling rate. Unwanted total pressure fluctuations of the coolant on the upper side of the coolant vapor layer can cause it to break up locally. This causes the local cooling rate to increase sharply for a short time in conjunction with the vaporization enthalpy of the coolant acting directly on the hot-rolled metallic product, causing inhomogeneity in the microstructure. A second causal relationship exists with the compactness of the coolant volume flow emerging from a coolant outlet opening.After the coolant exits a coolant outlet opening, the coolant volume flow may break up into drops after a certain decay time or, depending on the velocity of the coolant volume flow, after a certain decay length, resulting in local pressure variations in the coolant vapor layer. If such an effect occurs, it also exhibits particularly high dynamics. It has been shown that a critical pressure variation in the coolant vapor layer can be advantageously reduced or prevented by a compact coolant volume flow that is as continuous as possible (Page 15 / 65 P80649DE), provided that a local intervention on the local coolant volume flow can be carried out with sufficient precision and / or speed.Atomization or rippling of the coolant volume flow after exiting the coolant outlet opening can also have a negative effect on the coolant vapor layer, so that physical relationships with the total pressure of the coolant upstream of the coolant outlet opening can also be relevant for achieving the most homogeneous cooling rate possible. Further physical causal relationships to the cooling rate exist with the thickness and alloy composition of the hot-rolled metallic product. The causal relationships described above are at least partially systematically coupled with one another, so that they mutually influence one another. Even small disruptive influences during active cooling with the liquid coolant can therefore lead to inhomogeneities in the local microstructure of the manufactured hot-rolled metallic product, which can cause inhomogeneities in the material properties.When material properties are required for a metallic strip product, minimum values ​​are specified that must be maintained at every point of the product. Therefore, particularly good homogeneity of the microstructure of the metallic strip product is advantageous and enables particularly significant savings in cost-intensive alloy components. In other words, a cooling rate that is maintained as precisely as possible and / or under disturbing influences can enable the most homogeneous microstructure possible and thus a reduction in cost-intensive alloy components for the metallic strip product. According to experiments conducted, disturbances affecting the cooling rate can exhibit a high degree of temporal dynamics and thus cause high-resolution deviations from the desired microstructure.Therefore, a cooling module is proposed here which has a coolant valve arranged between the coolant inlet and the coolant chamber, wherein the coolant inlet can be a component of the coolant valve, wherein the coolant inlet is arranged on the side of the coolant closure region which is arranged on the side of the coolant closure region facing away from the coolant chamber. Preferably, the coolant valve is directly fluidically connected to the coolant chamber, wherein less than one flow-guiding component is arranged between the coolant valve and the coolant chamber, in particular between the coolant valve and a one-piece coolant chamber. A one-piece cooling chamber can be understood to mean, among other things, a welded construction.According to a preferred embodiment, less than one fluid branch is arranged between the coolant valve and the coolant chamber. In other words, the coolant valve can be fluidly connected to exactly one coolant chamber. The fluid connection between the coolant valve and the coolant chamber can be designed such that, using the coolant valve, only this coolant chamber can be supplied with a coolant. Page 17 / 65 P80649DE The cooling module proposed here, due to its preferably direct association of the coolant valve and the coolant chamber of the cooling beam, enables the precise adjustment of a designated coolant volume flow at a point on the conveying path of the metallic strip-shaped product, which point is determined by the position of the cooling beam.This enables a high degree of spatial resolution with respect to the cooling rate along the conveyor line of the metallic strip-shaped product past at least one cooling module, and thus an increase in precision for the temporal progression of the temperature of the metallic strip-shaped product, which influences the microstructure. Thus, the precision of the setting of the cooling module proposed here alone enables a reduction in cost-sensitive alloy components while maintaining the same minimum required material properties of the metallic strip-shaped product. The coolant valve of the cooling module proposed here preferably acts only on one cooling beam. Accordingly, the quantity of coolant downstream of the coolant valve up to the at least one coolant outlet opening, on which a setting and / or adjustment of the coolant valve preferably directly acts, is particularly small compared to previously known systems.In known cooling systems, a coolant valve acts on a plurality of cooling beams and thus also on a comparatively larger quantity of coolant downstream of the coolant valve up to the at least one coolant outlet opening. Thus, the cooling module proposed here allows only a comparatively small quantity of coolant to be accelerated when the coolant valve is set and / or adjusted. This results in a smaller inertial resistance due to the cooling water quantity to be accelerated. The inertial resistance has a dampening effect on the time-varying behavior of the coolant velocity in a coolant outlet opening of the cooling module. In other words, the cooling module proposed here can reduce the compensation time induced by the cooling module.The cooling module proposed here thus enables a more dynamic response to any disturbances that may occur and allows disturbance-induced structural changes to be optimally reduced in their severity. This property of the cooling module proposed here can be used to reduce cost-sensitive alloy components while maintaining the same minimum required material properties of the metallic strip product. While the equilibration time of the cooling module is essentially influenced by the inertia of the coolant quantity to be accelerated, the delay time is effectively related to the effective acceleration due to gravity, the geodetic level difference between the coolant inlet of the cooling module and the at least one coolant outlet opening of the cooling module, as well as the total pressure losses in the cooling module between the coolant inlet and the at least one coolant outlet opening.This can be seen from the following differential equation of a coolant particle in the cooling module:. Here, ^ is the location of the coolant particle, ^ is the time, ^ is the local acceleration due to gravity, ^ is the density of the coolant, ℎ is the geodetic height and ^ is the total pressure, where the indexing indicates the respective location, so that ∆^ ^^^the total pressure loss between location 1 and location 2, i.e. the sum of the individual total pressure losses between location 1 and location 2, in particular the total pressure losses caused by a coolant loss coefficient of a coolant valve and / or friction of a coolant line transporting coolant Page 19 / 65 P80649DE and / or a transition loss coefficient of a transition and / or a cooling module branching loss coefficient of a cooling module branch and / or a cooling group branching loss coefficient of a cooling group branch and / or the like. The coolant is preferably water. The total pressure difference is preferably greater than or equal to 20,000 ^∙^ ^ , furthermore preferably greater than or equal to 35,000 ^∙^ ^ , ^^ preferably greater than or equal to 45,000 and most preferably ^^ greater than or equal to 55,000 ^∙^ ^. Preferably, the sum of the delay time and the compensation time for the time-variant step function of the cooling module is less than or equal to 5.0 s, further preferably less than or equal to 2.5 s, preferably less than or equal to 1.5 s and particularly preferably less than or equal to 0.5 s. The delay time for the time-variant step function of the cooling module can be greater than 0.0 s. Preferably, the delay time for the time-variant step function of the cooling module is less than or equal to 0.8 s, further preferably less than or equal to 0.5 s, preferably less than or equal to 0.3 s and particularly preferably less than or equal to 0.1 s. The compensation time for the time-variant step function of the cooling module can be greater than 0.0 s. Preferably, the compensation time for the time-variant step function of the cooling module is less than or equal to 2.5 s, further preferably less than or equal to 2.0 s, preferably less than or equal to 1.5 s and particularly preferably less than or equal to 1.0 s.The influence of the sum of the delay time and the equalization time of the cooling module on the achievable structural homogeneity and the associated scrap rate due to failure to meet the required material specifications while simultaneously reducing the use of cost-sensitive alloying elements was investigated in tests and can be found in Table 1. It is evident that a reduction in the delay time and equalization time of the cooling module through structural design of the cooling module has a beneficial effect on the achievable structural homogeneity. The structural homogeneity can be correlated with the degree of distribution ^. ^ of a structural component: where ^ = ^ ^ corresponds to the concentration of the deposited microstructure fraction at position ^ and ^̅corresponds to the average concentration of the microstructure fraction in the metallic ribbon-shaped product. Tab. 1: Sum of delay time and equalization time of the cooling module, achievable structural homogeneity, scrap rate; + means positive characteristic, 0 means neutral characteristic; the more + there are, the more positive the characteristic. According to an expedient embodiment, the coolant valve, under the influence of the pressure difference during sudden, complete opening of the coolant valve, exhibits a time-variant behavior of the coolant velocity in the coolant chamber, which can be described with a time-variant coolant valve step function having a coolant valve time constant, wherein the coolant valve time constant is less than or equal to 1.5 s, preferably less than or equal to 1.0 s, and particularly preferably less than or equal to 0.5 s.The coolant valve time constant is preferably less than or equal to 0.75 s, further preferably less than or equal to 0.35 s, preferably less than or equal to 0.25 s and particularly preferably less than or equal to 0.1 s. The following terminology should be explained in this regard: A “time-variant coolant valve step function” describes an opening state of the coolant valve between a complete closure of the coolant valve and a complete opening over the course of time after a sudden complete opening of the coolant valve. Accordingly, after a certain time, the state in which the coolant valve is fully open arises. When evaluating the time-variant system behavior based on the time course until the steady state is reached, a “coolant valve time constant” in particular can be regarded as a system-dependent and thus characteristic variable of the time-variant coolant valve step function.The time-variant system behavior can be used to describe a controlled system within the framework of a control system, particularly within the framework of a control system for a coolant valve. A coolant valve can exhibit the time behavior of a first-order delay element. To determine the coolant valve time constant, reference is made to literature on determining a time constant for a first-order delay element, in particular by determining it from the ordinary differential equation describing the opening of the coolant valve. The influence of the coolant valve time constant on the delay time of the cooling module was investigated in experiments and can be found in Table 2. It was found that the coolant valve time constant of the coolant valve has a causal relationship to the delay time of the cooling module. Tab. 2: Coolant valve time constant of the coolant valve and delay time of the cooling module; + means positive characteristic, 0 means neutral characteristic; the more + there are, the more positive the characteristic. The coolant valve, when fully open, has a coolant valve loss coefficient ^ ^^^^^^ of less than or equal to 0.46, preferably less than or equal to 0.44 and particularly preferably less than or equal to 0.24. Preferably, the coolant valve in the fully open position has a coolant valve loss coefficient ^ ^^^^^^ of less than or equal to 0.23, further preferably of less than or equal to 0.22, preferably of less than or equal to 0.21 and particularly preferably of less than or equal to 0.19. Page 23 / 65 P80649DE Furthermore, the coolant valve preferably has a coolant valve loss coefficient ^ in the fully open position. ^^^^^^of less than or equal to 0.15, further preferably of less than or equal to 0.12, preferably of less than or equal to 0.10 and particularly preferably of less than or equal to 0.08. The following is explained in terms of terminology: The "coolant valve loss coefficient" ^ ^^^^^^ is understood as a dimensionless resistance coefficient for the coolant valve, which describes a measure of the pressure loss in the coolant valve through which the designated coolant flows when the coolant valve is fully open. The coolant closure area can be used as a reference cross-section for the coolant valve loss coefficient. This describes the cross-section in the center of the coolant valve through which a coolant can flow when the valve is fully open, while it is blocked for the coolant when the coolant valve is fully closed. The coolant valve loss coefficient ^ ^^^^^^ can be determined as follows: This is done under ^̅ ^ ^ ^^^^^the square of the area-averaged coolant velocity in the reference cross-section of the coolant valve, particularly in the coolant closure area. ∆^ describes the absolute pressure loss when coolant flows through the coolant valve, viewed over the entire extent of the coolant valve in the designated flow direction, and ^ describes the density of the coolant. Page 24 / 65 P80649DE Tests have shown that the coolant valve loss coefficient has a causal relationship to the delay time of the cooling module. It was discovered that the delay time of the cooling module can be reduced if the coolant valve has a smaller coolant valve loss coefficient. Accordingly, it is proposed here to select a coolant valve with a low coolant valve loss coefficient for the cooling module.The coolant valve preferably has a nominal diameter of greater than or equal to DN80, preferably greater than or equal to DN150, and particularly preferably greater than or equal to DN200. The following terminology is used: The "nominal diameter" of the coolant valve refers to the nominal diameter according to EN ISO 6708. The designation DN is followed by a dimensionless number approximately corresponding to the inner diameter of the coolant valve in millimeters. Table 3: Nominal diameter of the coolant valve, delay time of the cooling module, equalization time of the cooling module; + means positive characteristic, 0 means neutral characteristic; the more + there are, the more positive the characteristic. Page 25 / 65 P80649DE The coolant valve preferably has a nominal diameter greater than or equal to DN60, furthermore preferably greater than or equal to DN120, preferably greater than or equal to DN250 and particularly preferably greater than or equal to DN300. Tests on the nominal diameter of the coolant valve have shown that the nominal diameter of the coolant valve affects both the delay time and the equalization time of the cooling module; see also Table 3. The nominal diameter of the coolant valve has a causal relationship to the equalization time of the cooling module.The larger the nominal diameter, the greater the designated mass of the coolant downstream of the coolant closure region of the coolant valve up to the at least one coolant outlet opening. In the case of a designated change in the opening state of the coolant valve, a higher inertial resistance of the cooling module results from a larger nominal diameter of the coolant valve, whereby the compensation time of the cooling module also increases with an increasing nominal diameter of the coolant valve. The delay time of the cooling module also has a causal relationship to the nominal diameter of the coolant valve. On the one hand, coolant valves with a larger nominal diameter can also have a larger coolant valve time constant, whereby the delay time of the cooling module increases relative to the changed coolant time constant.On the other hand, coolant valves with a smaller nominal diameter exhibit a higher average velocity in the coolant closure region of the coolant valve at a designated constant coolant volume flow exiting from at least one coolant outlet opening. In this regard, coolant valves with different nominal diameters but the same coolant valve loss coefficient ^ are compared. ^^^^^^, greater total pressure losses of the coolant result in the coolant valve with the smaller nominal diameter. According to page 26 / 65 P80649DE, the delay time of the cooling module increases with respect to the total pressure losses with a smaller nominal diameter. According to a further preferred embodiment, the coolant valve has a nominal diameter of less than or equal to DN300, preferably less than or equal to DN250 and particularly preferably greater than or equal to DN120. Preferably, the coolant valve has a nominal diameter of less than or equal to DN200, furthermore preferably less than or equal to DN150, preferably less than or equal to DN80 and particularly preferably less than or equal to DN60. Advantageously, the coolant valve has a distance from a transition from the coolant chamber to a coolant outlet pipe of less than or equal to 500 mm, preferably less than or equal to 325 mm and particularly preferably less than or equal to 275 mm.The distance between the coolant valve of the cooling module and the transition from the coolant chamber to the coolant outlet pipe is understood as the distance between the flange of the coolant chamber at the sealing surface of the flange for connection to the coolant valve and the center of gravity of the transition between the coolant chamber and the coolant outlet pipe. Coolant chambers with a plurality of coolant outlet pipes can be constructed such that the coolant outlet pipes are arranged one after the other or in pairs in the longitudinal direction of the coolant chamber. In a corresponding embodiment with multiple coolant outlet pipes, the distance refers to the transition to a coolant outlet pipe closest to the valve flange.Page 27 / 65 P80649DE The coolant valve preferably has a distance from a transition from the coolant chamber to a coolant outlet pipe of less than or equal to 750 mm, further preferably less than or equal to 625 mm, preferably less than or equal to 400 mm, and particularly preferably less than or equal to 250 mm. A transition from the coolant chamber to a coolant outlet pipe is expediently designed to be well-rounded, in particular having a transition loss coefficient ^. Ü^^^^^^^of less than or equal to 0.3, preferably less than or equal to 0.15, and particularly preferably less than or equal to 0.08. The following terminology is used: A "transition" from the coolant chamber to a coolant outlet pipe is understood to be the smallest free cross-section through which a designated coolant must flow from the coolant chamber in order to flow into a coolant outlet pipe. The transition can be arranged directly at the base of the coolant outlet pipe. The transition loss coefficient ^ Ü^^^^^^^ can be determined as follows: ^ Here, ^̅ Ü^^^^^^^^ is the square of the area-averaged coolant velocity in the reference cross-section of the transition, in particular in the smallest free cross-section that a designated coolant must pass through from the coolant chamber in order to flow into a coolant outlet pipe. ∆^ describes the absolute pressure loss Page 28 / 65 P80649DE when coolant flows through the transition, and ^ describes the density of the coolant. The smallest free cross-section that a designated coolant must pass through from the coolant chamber in order to flow into a coolant outlet pipe can correspond to the cross-sectional area of ​​the coolant outlet pipe. A well-rounded transition can be designed as an orifice plate.In particular, with a plurality of coolant outlet pipes extending from a coolant chamber, hydraulic balancing can be achieved via varying free cross sections of the individual transitions to the individual coolant outlet pipes, so that essentially the same coolant volume flow can flow out of each associated coolant outlet opening, thereby improving the homogeneity of the microstructure, particularly in the width direction of the metallic strip-shaped product. Preferably, a transition from the coolant chamber to a coolant outlet pipe is designed such that it has a transition loss coefficient. of less than or equal to 0.4, preferably less than or equal to 0.22 and particularly preferably less than or equal to 0.11. Tests have shown that the transition loss coefficient ^ Ü^^^^^^^can have an operative connection to the delay time of the cooling module, wherein a smaller transition loss coefficient can reduce the delay time of the cooling module. Optionally, the cooling module has a flow measuring device. A flow measuring device is configured for the metrological detection of a coolant velocity and / or a coolant volume flow. Page 29 / 65 P80649DE A flow measuring device can interact tactilely with a designated coolant or act without contact with the coolant. A flow measuring device can be designed as a structural unit with the coolant valve and / or be operatively connected to the coolant chamber and / or at least one coolant outlet pipe.The flow measuring device proposed here can provide an actual value for a coolant velocity and / or a coolant volume flow, which can be used within the framework of a control and / or regulation of the cooling module. According to an optional embodiment, the cooling module can have an outlet for a bypass channel, in particular in direct fluid communication with the coolant inlet and / or in direct fluid communication with the coolant chamber. The following terminology is explained in this regard: An "outlet" in the cooling module is understood to mean a free cross-section that differs from a coolant outlet opening, through which a designated coolant can flow out of the cooling module, in particular into a bypass channel, without cooling the metallic strip-shaped product.In other words, a coolant volume flow that is not directly intended for cooling the metallic strip-shaped product can flow through an outlet. The outlet can be arranged upstream or downstream of the coolant valve in the designated flow direction of the coolant. Page 30 / 65 P80649DE If the outlet is arranged upstream of the coolant valve, a coolant volume flow can be in motion in the coolant inlet until it reaches the outlet, even if the coolant valve is closed and the cooling module is therefore not being used to cool a metallic strip-shaped product. When the coolant valve is opened, direct use can be made of the already moving coolant, with the coolant being at least partially redirected from the outlet through the coolant valve and thus requiring a smaller overall acceleration value to achieve the desired coolant speed.The moving coolant, coupled to the inertial resistance of the cooling module, has an effective relationship with the equalization time of the cooling module, so that the equalization time of the cooling module can be advantageously reduced by an outlet in the cooling module. To ensure that the coolant flowing out through the outlet does not have to be discarded, the outlet is preferably in fluid communication with a "bypass channel" which is designed to feed the coolant at least indirectly back into the coolant reservoir and / or a main coolant inlet and / or a cooling group branch and / or a coolant inlet. The bypass channel is preferably in fluid communication with a coolant conveying device which is designed to convey the coolant into the coolant reservoir and / or a main coolant inlet and / or a cooling group branch and / or a coolant inlet.This advantageously compensates for circuit pressure losses of the coolant. The outlet is expediently fluidically connected to a bypass valve. The following terminology is explained in this regard: Page 31 / 65 P80649DE A "bypass valve" is understood to be a valve that is designed to control and / or regulate a designated coolant volume flow that flows through the bypass channel. The interaction of the coolant valve and the bypass valve advantageously maintains a highly dynamic coolant volume flow in the cooling module, even when the cooling module is not currently being used to cool the metallic strip-shaped product. The bypass valve can be controlled and / or regulated by an electronic control and / or regulating unit.This advantageously makes it possible to achieve a smaller total pressure difference of the coolant in at least some areas of the cooling module in the cooling module not currently being used to cool the metallic strip-shaped product, thereby reducing the delay time of the cooling module. Additionally, a higher coolant velocity can be achieved in at least some areas of the cooling module in the cooling module not currently being used to cool the metallic strip-shaped product, thereby reducing the inertial resistance and thus the equalization time of the cooling module. A cooling module not currently being used to cool the metallic strip-shaped product is understood to mean that the designated coolant velocity of a coolant outlet opening is essentially zero.According to a preferred embodiment, the cooling module has - at least two cooling beams, each with a coolant chamber and each with a plurality of coolant outlet pipes fluidly connected to the coolant chamber, each having at least one coolant outlet opening for applying the coolant to the strip-shaped product; and - a cooling module branch fluidly communicating with the at least two cooling beams. The following terminology is explained in this regard: A "cooling module branch" means a flow divider in the inflow area to a plurality of cooling beams. A designated coolant volume flow can be divided by the cooling module branch between a plurality of cooling beams, in particular between two, three, four, five or more cooling beams. The coolant volume flow is preferably divided into essentially equal parts.The cooling module branch can be configured to be at least indirectly fluidically connected to a coolant reservoir. Here, a cooling module is proposed which has a cooling module branch downstream of the coolant valve. The cooling module branch is preferably formed integrally with the plurality of cooling beams. The cooling module branch preferably has a cooling module branch loss coefficient ^. ^^^^^^^^^ of less than or equal to 0.2, preferably less than or equal to 0.15 and particularly preferably less than or equal to 0.11. Furthermore, the cooling module branching preferably has a cooling module branching loss coefficient ^ ^^^^^^^^^ of less than or equal to 0.3, preferably less than or equal to 0.25 and particularly preferably less than or equal to 0.08. Page 33 / 65 P80649DE The following is explained in terms of terms: The cooling module branching loss coefficient ^ ^^^^^^^^^ can be determined as follows: This is done under ^̅ ^ ^ ^^^^^^^^ the square of the area-averaged coolant velocity in the reference cross-section of the cooling module branch, in particular in the summed free cross-section of the individual branches directly at the level of the flow divider through which the designated coolant flows. ∆^ describes the absolute pressure loss when flowing through the cooling module branch with coolant, and ^ describes the density of the coolant. Tests have shown that the cooling module branch loss coefficient ^ ^^^^^^^^^can have an operative connection to the delay time of the cooling module, wherein a smaller cooling module branching loss coefficient can reduce the delay time of the cooling module. According to an expedient embodiment, a height difference between the coolant valve and at least one coolant outlet opening is less than or equal to 500 mm, preferably less than or equal to 400 mm, and particularly preferably less than or equal to 250 mm. Furthermore, the height difference between the coolant valve and at least one coolant outlet opening is preferably less than or equal to 325 mm, preferably less than or equal to 200 mm, and particularly preferably less than or equal to 175 mm. Page 34 / 65 P80649DE With regard to the height difference specified here, the height difference in the direction of gravity is meant, wherein the height reference point of the coolant valve is the center of the reference cross-section of the coolant valve, in particular the center of the coolant closure region.It has been found that, in order to achieve a short delay time, it is advantageous if the coolant valve has a small height difference to the at least one coolant outlet opening. Preferably, a cooling module has an electronic control and / or regulating unit, wherein the electronic control and / or regulating unit is configured to control and / or regulate the cooling module. The electronic control and / or regulating unit can be configured to control and / or regulate at least one coolant valve, in particular as a function of a coolant velocity and / or a coolant volume flow and / or a specific water application and / or a cooling rate and / or a microstructure of the metallic strip-shaped product and / or a temperature of the metallic strip-shaped product and / or a temperature profile along a conveying path of the metallic strip-shaped product.Mechanical properties of the metallic strip product and / or grain sizes of the microstructure of the metallic strip product and / or phase components of the metallic strip product can be determined, inter alia, using laser ultrasound methods and / or magnetic measuring methods. According to a second aspect of the invention, the object is achieved by a cooling group of a cooling device for cooling a hot-rolled metallic strip product with a coolant, comprising: - at least two cooling modules according to the first aspect of the invention; and - a cooling group branch in fluid communication with the at least two cooling modules. The following terminology is explained in this regard: A "cooling group branch" is understood to mean a flow divider in the inflow area to a plurality of cooling modules.A designated coolant volume flow can be distributed by the cooling group branching to a plurality of cooling modules, in particular to two, three, four, five or more cooling modules. Preferably, the coolant volume flow is distributed into substantially equal parts. The cooling group branching can be configured to be connected, at least indirectly, to a coolant reservoir in a fluid-communicating manner. A cooling group is proposed here which has a plurality of cooling modules and a common coolant supply, so that the coolant can be distributed by the cooling group branching to the plurality of cooling modules in a designated manner. Preferably, a cooling group has a bypass outlet upstream of the cooling group branching, wherein the bypass outlet can be configured to return the coolant to the coolant reservoir and / or the main coolant inlet.The cooling group can have a flow measuring device, in particular upstream of the cooling group branch. Page 36 / 65 P80649DE It is understood that the advantages of a cooling module according to the first aspect of the invention extend to a cooling group having at least two cooling modules according to the first aspect of the invention, as described above. The cooling group branch preferably has a cooling group branch loss coefficient ^^^^^^^^^^^^ of less than or equal to 0.2, preferably of less than or equal to 0.15, and particularly preferably of less than or equal to 0.11. Furthermore, the cooling group branch preferably has a cooling group branch loss coefficient ^^^^^^^^^^^^ of less than or equal to 0.3, preferably of less than or equal to 0.25, and particularly preferably of less than or equal to 0.08. The following is explained in terms of terminology: The cooling group branch loss coefficient ^^^^^^^^^^^^ can be determined as follows: Here, ^̅ ^ ^^^^^^^^^^^ is understood to be the square of the area-averaged coolant velocity in the reference cross-section of the cooling group branching, in particular in the summed free cross-section of the individual branches directly at the level of the flow divider, through which the designated coolant flows. ∆^ describes the absolute pressure loss when coolant flows through the cooling group branching, and ^ describes the density of the coolant. Page 37 / 65 P80649DE During experiments with a cooling group proposed here, it was discovered that the cooling group branching loss coefficient ^^^^^^^^^^^^ can have an active connection to the delay time of the fluid-communicating cooling modules, whereby a smaller cooling group branching loss coefficient can reduce the delay time of a cooling module.Preferably, a cooling group has an electronic control and / or regulating unit, wherein the electronic control and / or regulating unit is configured to control and / or regulate the cooling group. The electronic control and / or regulating unit can be configured to control and / or regulate at least one coolant valve, in particular as a function of a coolant velocity and / or a coolant volume flow and / or a specific water exposure and / or a cooling rate and / or a microstructure of the metallic strip-shaped product and / or a temperature of the metallic strip-shaped product and / or a temperature profile along a conveying path of the metallic strip-shaped product.It should be expressly noted that the subject matter of the second aspect can be advantageously combined with the subject matter of the preceding aspect of the invention, both individually or cumulatively in any desired combination. According to a third aspect of the invention, the object is achieved by a cooling system for cooling a hot-rolled metallic strip-shaped product with a coolant comprising: - a cooling device; - 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 of the invention; and Page 38 / 65 P80649DE - a coolant reservoir in fluid communication with a main coolant inlet, wherein the main coolant inlet is in fluid communication with the at least one cooling module and / or the at least one cooling group.The following terminology is used: A "main coolant inlet" refers to a fluid connection arranged downstream of the coolant reservoir and upstream of a cooling group and / or a cooling module. The main coolant inlet preferably has an internal diameter of greater than or equal to 0.6 m, preferably greater than or equal to 0.9 m, and particularly preferably greater than or equal to 1.3 m. The main coolant inlet can have a free cross-sectional area normal to the designated flow direction of the coolant of greater than or equal to 0.28 m², preferably greater than or equal to 0.63 m², and particularly preferably greater than or equal to 1.32 m².A cooling system for actively cooling a hot-rolled metallic strip product with a coolant is proposed, which cooling system comprises at least one cooling module according to the first aspect and / or at least one cooling group according to the second aspect of the invention, wherein the at least one cooling module and / or the at least one cooling group is fluidly connected to a coolant reservoir at least indirectly and using a main coolant inlet. The cooling system can comprise an electronic control and / or regulating unit, preferably a higher-level control and / or regulating unit.An "electronic control and / or regulating unit" is understood to mean a device that is configured to monitor and / or control and / or regulate the cooling system, in particular as a function of a coolant velocity and / or a coolant volume flow and / or a specific water loading and / or a cooling rate and / or a microstructure of the metallic strip-shaped product. The electronic control and / or regulating unit can have an interface for receiving data, an interface for transmitting data, and a device for processing data. In particular, the device for processing data can be configured to execute an algorithm, in particular implementing a method according to a fourth aspect of the invention.The electronic control and / or regulating unit can preferably comprise a device for storing data, in particular a data memory. It is understood that 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, as described above, extend directly 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. The cooling system is particularly preferably designed for a pressure difference between the coolant reservoir and the coolant outlet opening of greater than or equal to 3 ∙ 10. ^ ^^⁄ (^ ∙ ^ ^ ), preferably greater than or equal to 4 ∙ 10 ^ ^^ ⁄ ( ^ ∙ ^ ^) , furthermore preferably greater than or equal to 4.5 ∙ 10 ^ ^^ ⁄ ( ^ ∙ ^ ^) . and particularly preferably greater than or equal to 5 ∙ 10 ^ ^^ ⁄ ( ^ ∙ ^^) . The cooling system can be designed for a pressure difference between the coolant reservoir and the coolant outlet opening of greater than or equal to 5.5 ∙ 10 ^ ^^⁄ (^ ∙ ^ ^ ), preferably greater than or equal to 6 ∙ 10 ^ ^^⁄ (^ ∙ ^ ^ ), preferably greater than or equal to Page 40 / 65 P80649DE 6.5 ∙ 10 ^ ^^ ⁄ ( ^ ∙ ^ ^) and particularly preferably greater than or equal to 7 ∙ 10 ^ ^^ ⁄ ( ^ ∙ ^ ^) . The pressure difference values ​​specified here allow particularly short delay times to be achieved for the at least one cooling module and / or the at least one cooling group. Tests have shown that the delay time can be reduced with increasing pressure difference under otherwise identical conditions. According to a preferred embodiment, the cooling system is designed for a specific water loading of greater than or equal to 20 ∙ ^ ^⁄ ( ^ ^ ∙ ℎ) furnished, preferably greater than or equal to 50 ∙ ^ ^ ⁄ (^ ^ ∙ ℎ), furthermore preferably greater than or equal to 100 ∙ ^ ^ ⁄ (^ ^ ∙ ℎ) and particularly preferably greater than or equal to 150 ∙ ^ ^ ⁄ (^ ^ ∙ ℎ). The cooling system can be designed for a specific water load of greater than or equal to 75 ∙ ^ ^ ⁄ (^ ^ ∙ ℎ), preferably greater than or equal to 125 ∙ ^ ^ ⁄ (^ ^ ∙ ℎ), furthermore preferably greater than or equal to 175 ∙ ^ ^⁄ ( ^ ^ ∙ ℎ ) and particularly preferably greater than or equal to 200 ∙ ^ ^⁄ ( ^ ^ ∙ ℎ ). The following terminology is explained in this regard: A "specific water application" is understood to mean a quantity of coolant that can be applied by the cooling system to the metallic strip-shaped product for active cooling, based on an area of ​​the metallic strip-shaped product and based on a time unit of an active cooling process. In particular, the specific water application is understood to mean the time- and / or area-averaged water application. Page 41 / 65 P80649DE The cooling system is particularly preferably designed for a cooling rate of greater than or equal to 50 ∙ ^ ⁄ ( ^ ∙ ^^ ) set up, preferably greater than or equal to 200 ∙ ^ ⁄ ( ^ ∙ ^^ ) , furthermore preferably greater than or equal to 300 ∙ ^ ⁄ ( ^ ∙ ^^ ) and particularly preferably greater than or equal to 500 ∙ ^⁄ (^ ∙ ^^). The cooling system can be designed for a cooling rate of greater than or equal to 100 ∙ ^ ⁄ ( ^ ∙ ^^ )be set up, preferably greater than or equal to 150 ∙ ^ ⁄ ( ^ ∙ ^^ ) , furthermore preferably greater than or equal to 250 ∙ ^ ⁄ ( ^ ∙ ^^ ) and particularly preferably greater than or equal to 400 ∙ ^ ⁄ ( ^ ∙ ^^ )According to a particularly expedient embodiment, the cooling system comprises at least a first cooling beam and a second cooling beam, wherein the first cooling beam is configured to apply the coolant to the top side of the strip-shaped product and the second cooling beam is configured to apply the coolant to the bottom side of the strip-shaped product. With the proposed cooling system, a metallic strip-shaped product can be simultaneously exposed to coolant from both sides of the strip, thereby advantageously increasing the cooling rate. Optionally, the cooling system comprises a main coolant conveying device configured to increase the pressure difference between the coolant reservoir and the coolant outlet opening.The following terminology is explained in this regard: A "main coolant delivery device" is understood to mean an active delivery device that is directly equipped with a coolant at the transition to the main coolant inlet and / or in the main coolant inlet. Page 42 / 65 P80649DE With the main coolant delivery device proposed here, the pressure difference can be increased and thus the delay time for the at least one cooling module and / or the at least one cooling group can be reduced. It should be expressly noted that the subject matter of the third aspect can be advantageously combined with the subject matters of the preceding aspects of the invention, both individually or cumulatively in any desired combination.According to a fourth aspect of the invention, the object is achieved by a method for actively cooling a hot-rolled metallic strip-shaped product, wherein 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 is used for actively cooling the hot-rolled metallic strip-shaped product. Preferably, the method comprises controlling and / or regulating the at least one cooling module and / or the at least one cooling group and / or the at least one cooling system, wherein at least one coolant valve and / or at least one bypass valve and / or at least one coolant conveying device and / or at least one main coolant conveying device is controlled and / or regulated.A control and / or regulation can be configured, in particular, as a function of a coolant velocity and / or a coolant volume flow and / or a specific water loading and / or a cooling rate and / or a microstructure of the metallic strip-shaped product and / or a temperature of the metallic strip-shaped product and / or a temperature profile along a conveying path of the metallic strip-shaped product. Page 43 / 65 P80649DE It should be expressly noted that the subject matter of the fourth aspect can be advantageously combined with the subject matters of the preceding aspects of the invention, both individually or cumulatively in any desired combination.According to a preferred embodiment, the method is designed to control and / or regulate a degree of distribution of at least one structural component, in particular to achieve a degree of distribution of greater than or equal to 0.85, preferably greater than or equal to 0.9, and particularly preferably greater than or equal to 0.95. A method for actively cooling the hot-rolled metallic strip-shaped product is proposed here, which is designed to control and / or regulate the homogeneity of the microstructure, wherein the homogeneity of the microstructure can be determined using the degree of distribution of at least one structural component. It is provided that the method at least indirectly detects the microstructure and uses at least one of the above-described setting variables of the cooling module and / or the cooling group and / or the cooling system to control and / or regulate the degree of distribution of at least one structural component.The method preferably controls and / or regulates the degree of distribution of two or three or four or more structural components. Preferably, a degree of distribution of greater than or equal to 0.875 is achieved, furthermore preferably a degree of distribution of greater than or equal to 0.925, preferably greater than or equal to 0.97, and particularly preferably greater than or equal to 0.98. The method is expediently configured to reduce a head length of the metallic strip-shaped product, in particular to achieve a head length of less than or equal to 10 m, preferably less than or equal to 8 m, and particularly preferably less than or equal to 6 m.The “head length” is understood to mean the front longitudinal section of the metallic strip-shaped product whose microstructure does not yet have sufficient homogeneity, so that at least one required mechanical property for the metallic strip-shaped product is not achieved in the region of the head length. Furthermore, the method is expediently designed to reduce a foot length of the metallic strip-shaped product, in particular to achieve a foot length of less than or equal to 10 m, preferably less than or equal to 8 m and particularly preferably less than or equal to 6 m. The “foot length” is understood to mean the rear longitudinal section of the metallic strip-shaped product whose microstructure does not have sufficient homogeneity, so that at least one required mechanical property for the metallic strip-shaped product is not achieved in the region of the foot length.It should be expressly noted that the subject matter of the fourth aspect can be advantageously combined with the subject matters of the preceding aspects of the invention, both individually or cumulatively in any combination. According to a fifth aspect of the invention, the object is achieved by a hot-rolled metallic strip product produced by a method according to the fourth aspect of the invention, in particular a hot-rolled metallic product with a tensile strength of greater than or equal to 560 N / mm² and a manganese content of less than 1.5 wt.% and a niobium content of less than 0.05 wt.%. Page 45 / 65 P80649DE The manganese content of the hot-rolled metallic strip product is preferably less than or equal to 1.45 wt.%, furthermore preferably less than or equal to 1.4 wt.%, preferably less than or equal to 1.35 wt.%, and particularly preferably less than or equal to 1.2 wt.%.The niobium content of the hot-rolled metallic strip product is preferably less than or equal to 0.045 wt.%, further preferably less than or equal to 0.04 wt.%, preferably less than or equal to 0.035 wt.%, and particularly preferably less than or equal to 0.03 wt.%. The tensile strength of the hot-rolled metallic strip product is preferably greater than or equal to 565 N / mm², further preferably greater than or equal to 570 N / mm², preferably greater than or equal to 575 N / mm², and particularly preferably greater than or equal to 580 N / mm². It is understood that the advantages of a method according to the fourth aspect of the invention, as described above, extend to a hot-rolled metallic product produced using the method. It is expressly noted that the subject matter of the fifth aspect can be advantageously combined with the subject matters of the preceding aspects of the invention, both individually or cumulatively in any combination.According to a sixth aspect of the invention, the object is achieved by using 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 Page 46 / 65 P80649DE for actively cooling a hot-rolled metallic strip-shaped product with a coolant.It is understood that 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 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, as described above, extend directly 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 hot-rolled metallic strip-shaped product. It should be expressly noted that the subject matter of the sixth aspect can be advantageously combined with the subject matters of the preceding aspects of the invention, both individually or cumulatively in any combination.Further advantages, details, and features of the invention will become apparent from the following detailed embodiments. These show: Figure 1: schematically shows a cooling module according to a first embodiment; Figure 2: schematically shows a sectional view through a cooling module; Figure 3: schematically shows a cooling module according to a second embodiment; Figure 4: schematically shows a cooling system; Page 47 / 65 P80649DE Figure 5: schematically shows a time-variant coolant valve step function; and Figure 6: schematically shows a time-variant step function of a cooling module. In the following description, the same reference symbols designate the same components or the same features, so that a description given with reference to one figure regarding a component also applies to the other figures, thus avoiding repetitive description.Furthermore, individual features that were described in connection with one embodiment can also be used separately in other embodiments. The cooling module 100 in Figure 1 essentially consists of a cooling beam 110, a coolant inlet 116, and a coolant valve 118. The cooling module 100 can be part of a cooling device (not shown) for cooling a hot-rolled metallic strip-shaped product (not shown) with a coolant (not shown), wherein the coolant can be specifically allowed to exit the cooling module 100 and, after exiting, can enter into a cooling operative connection with the strip-shaped product, in particular with the hot-rolled metallic strip-shaped product. The cooling beam 110 has a coolant chamber 112 and a plurality of coolant outlet pipes 114 (only partially designated) that are fluidly connected to the coolant chamber 112.Each coolant outlet pipe 114 has at least one coolant outlet opening (not labeled) for applying the coolant to the strip-shaped product. Page 48 / 65 P80649DE The coolant chamber 112 is at least indirectly fluidly connected to the coolant inlet 116 and / or fluidly connected. In particular, the coolant valve 118 is arranged between the coolant inlet 116 and the coolant chamber 112. The coolant inlet 116 is configured to be at least indirectly fluidly connected to a coolant reservoir (not shown), wherein the coolant reservoir is configured to provide a pressure difference between the coolant reservoir and the at least one coolant outlet opening (not labeled).The cooling module 100 has a transition 112a from the coolant chamber 112 to a coolant outlet pipe 114, wherein this transition 112a is preferably well rounded, in particular having a transition loss coefficient ^. Ü^^^^^^^of less than or equal to 0.3, preferably less than or equal to 0.15, and particularly preferably less than or equal to 0.08. It is understood that a transition 112a is provided between each coolant outlet pipe 114 and the coolant chamber 112. The coolant valve 118 has a distance 118a from a transition from the coolant chamber 112 to a coolant outlet pipe 114 of less than or equal to 500 mm, preferably less than or equal to 325 mm, and particularly preferably less than or equal to 275 mm.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 outlet pipe 114 is understood as the distance 118a between a flange (not labeled / not shown) of the coolant chamber 112 at a sealing surface (not labeled / not shown) of the flange for connection to the coolant valve 118 and a center of gravity (not labeled) of the transition 112a between the coolant chamber 112 and the coolant outlet pipe 114. It is understood that the distance 118a is understood as the distance 118a which is the shortest among the plurality of coolant outlet pipes 114, i.e. to the coolant outlet pipe 114 closest to the coolant valve 118. The cooling module 100 can have a flow measuring device 140 (shown schematically), in particular in the form of a tactile or a non-tactile flow measuring device 140.The flow measuring device 140 can be arranged in the coolant inlet 116, in the coolant valve 118, or downstream of the coolant valve 118 and upstream of the coolant outlet pipe 114 closest to the coolant valve 118 in the coolant chamber 112. Figure 2 shows a sectional view through a cooling module 100 according to Figure 1. The coolant chamber 112 of the cooling beam 110 of the cooling module 100 has a transition 112a to a coolant outlet pipe 114. The coolant outlet pipe 114 has a coolant outlet opening 114a through which a coolant (not shown) can exit. Between a height reference point 118b of the coolant valve 118 and the coolant outlet opening 114a there is a height difference 120 in the direction of gravity (not shown). The height difference 120 can be less than or equal to 500 mm, preferably less than or equal to 400 mm and particularly preferably less than or equal to 250 mm.Page 50 / 65 P80649DE The cooling module 100 in Figure 3 has an outlet 150 for a bypass channel 152, wherein the outlet 150 is designed to be in direct fluid communication with the coolant chamber 112. The outlet 150 is fluidly connected to a bypass valve 154 and can be opened and closed by means of the bypass valve 154. A cooling system 400 in Figure 4 essentially consists of a cooling device 300 for cooling a metallic strip-shaped product 10 by means of a coolant 20, a coolant reservoir 410 for storing the coolant 20, a cooling device 300 for applying the coolant 20 to the metallic strip-shaped product 10 and a main coolant inlet 420 for fluidly connecting the coolant reservoir 410 to the cooling device 300. The cooling system 400 can have a main coolant conveying device 430 for increasing the total pressure of the coolant 20 in the cooling device 300.It is provided that the metallic strip-shaped product 10 can be conveyed on a conveyor line (not designated) in a transport direction (not shown) in such a way that it can come into operative contact with the cooling device 300, in particular through operative contact with a liquid coolant 20 designed to emerge from the cooling device 300. For this purpose, the metallic strip-shaped product 10 can be conveyed past at least one cooling module 100 of the cooling device 300 and / or between at least two cooling modules 100 of the cooling device 300.Page 51 / 65 P80649DE The cooling device 300 can have at least one cooling module 100 arranged above the metallic strip-shaped product 10, in particular one or more first cooling modules 100, to which the liquid coolant 20 is supplied via the main coolant inlet 420, wherein the cooling module 100 preferably extends substantially transversely to the transport direction (not designated) and preferably has a plurality of coolant outlet pipes (not shown) via which the liquid coolant 20 can be brought into operative connection with the metallic strip-shaped product 10. Analogously, the cooling device 300 can have at least one cooling module 100 arranged below the metallic strip-shaped product 10, in particular one or more second cooling modules 100, which are configured to bring the liquid coolant 20 into operative connection with the metallic strip-shaped product 10.In the conveying direction of the metallic strip-shaped product 10, the cooling device 300 can have a plurality of cooling modules 100, which can be arranged above and / or below the metallic strip-shaped product 10. One or more cooling modules 100 can be arranged in one or more cooling groups 200 in a cooling device 300. The coolant reservoir 410 is in fluid communication with the main coolant inlet 420, wherein the main coolant inlet 420 is in fluid communication with the at least one cooling module 100 and / or the at least one cooling group 200. The cooling device 300 has two cooling groups 200 arranged above the metallic strip-shaped product 10, which are fluidly connected to the main coolant inlet 420 by means of a cooling group branch 210 likewise arranged above the metallic strip-shaped product 10. Page 52 / 65 P80649DEThe cooling device 300 has two cooling groups 200 arranged below the metallic strip-shaped product 10, which are fluidly connected to the main coolant inlet 420 by means of a cooling group branch 210 also arranged below the metallic strip-shaped product 10. Each cooling group 200 has two cooling modules 100, each of which is fluidly connected to a cooling group branch by means of a cooling module branch 160. The cooling system 400 can be designed for a specific water pressure of greater than or equal to 20 ∙ ^. ^ ⁄ (^ ^ ∙ ℎ), preferably greater than or equal to 50 ∙ ^ ^ ⁄ (^ ^ ∙ ℎ) and particularly preferably greater than or equal to 150 ∙ ^ ^ ⁄ (^ ^∙ ℎ). The cooling system 400 can be configured for a cooling rate of greater than or equal to 50 ∙ ^⁄ (^ ∙ ^^), preferably greater than or equal to 200 ∙ ^⁄ (^ ∙ ^^) and particularly preferably greater than or equal to 500 ∙ ^⁄ (^ ∙ ^^). The coolant valve step function 40 in Figure 5 describes a temporal profile of a coolant velocity 22 immediately downstream of a coolant valve (not shown) or in a narrowest cross-section (not shown) of the coolant valve over time 24 after a sudden opening of the coolant valve. The origin of the coolant valve step function 40 describes the point in time at which the coolant valve is suddenly opened and the coolant velocity 22 has the value zero. Page 53 / 65 P80649DE The coolant valve step function 40 can describe a time-variant system behavior of a coolant valve (not shown) after the sudden opening of the coolant valve (not shown).When the coolant valve opens, the coolant velocity 22 converges directly downstream of the coolant valve or in a narrowest cross section of the coolant valve to a constant value (not labeled) of the coolant velocity 22. The coolant valve step function 40 can alternatively be described and / or characterized by means of a coolant valve time constant 42, wherein the coolant valve time constant 42 can be determined graphically from the coolant valve step function 40 by determining a time from an intersection point (not labeled) of a tangent (not labeled) at the origin to the coolant valve step function 40 with the value of the coolant velocity 22 to which the coolant valve step function 40 converges, and determining a difference time between this intersection point and the time of the sudden opening of the coolant valve.The step function 30 of a cooling module (not shown) in Figure 6 describes a temporal progression of a coolant velocity 22 in a coolant outlet opening (not shown) over time 24 after a sudden opening of a coolant valve (not shown). The origin of the coolant valve step function 40 describes the point in time at which the coolant valve is suddenly opened and the coolant velocity 22 has the value zero. The step function 30 can describe a time-variant system behavior of a cooling module (not shown) after the sudden opening of the coolant valve (not shown). Page 54 / 65 P80649DE With the opening of the coolant valve, the coolant velocity 22 in the coolant outlet opening converges to a constant value (not labeled) of the coolant velocity 22.The step function 30 can alternatively be described and / or characterized by means of a delay time 32 and a compensation time 34, wherein the delay time 32 and the compensation time 34 can be determined graphically from the step function 30.The delay time 32 can represent a measure of the higher-order influences on a time-variant system behavior of the cooling module and results from the time-variant step function 30 through the following steps: - Determination of an inflection point (not labeled) of the time-variant step function 30, in particular the coolant velocity 22 - Applying a tangent (not labeled) through the inflection point of the time-variant step function 30, and - Determination of the delay time 32 as the difference between the time (not labeled) at which the tangent intersects the abscissa (time axis) and the time (not labeled) of the sudden change in the manipulated variable, in particular the sudden opening of the coolant valve.The compensation time 34 can represent a measure of the inertia of a time-variant system behavior, i.e. a measure of the first-order influences on a time-variant system behavior, and is obtained from the time-variant step function 30 through the following steps: - Determining an inflection point (not labeled) of the time-variant step function 30, in particular the coolant velocity 22, page 55 / 65 P80649DE - Applying a tangent (not labeled) through the inflection point of the time-variant step function 30; - Determining an asymptote for the stationary state of the time-variant step function 30 resulting after the step-like change in the manipulated variable; and - Determining the compensation time 34 as the difference between the time at which the tangent intersects the asymptote and the time at which the tangent intersects the abscissa.

[0002] Page 56 / 65 P80649EN List of Reference Symbols 10 metallic strip-shaped product 20 coolant 22 coolant velocity 24 time 30 step function 32 delay time 34 equalization time 40 coolant valve step function 42 coolant valve time constant 100 cooling module 110 cooling beam 112 coolant chamber 112a transition 114 coolant outlet pipe 114a coolant outlet opening 116 coolant inlet 118 coolant valve 118a distance 118b height reference point 120 height difference 140 flow measuring device 150 outlet 152 bypass channel 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 conveying device ^ ^^^^^^ Coolant valve loss coefficient Page 57 / 65 P80649DE ^ Ü^^^^^^^ Transition loss coefficient ^ ^^^^^^^^^ Cooling module branching loss coefficient ^^^^^^^^^^^^Cooling group branching loss coefficient

Claims

Page 58 / 65 P80649DE Patent claims 1. Cooling module (100) of a cooling device (300) for cooling a hot-rolled metallic strip-shaped product (10) with a coolant (20), comprising: - at least one cooling bar (110) with a coolant chamber (112) and a plurality of coolant outlet pipes (114) connected in fluid communication with the coolant chamber (112), each having at least one coolant outlet opening (114a) for applying the coolant (20) to the strip-shaped product (10); - at least one coolant inlet (116) connected at least indirectly in fluid communication with the coolant chamber (112), wherein the coolant inlet (116) is configured to be connected at least indirectly in fluid communication with a coolant reservoir (410), wherein the coolant reservoir (410) is configured to provide a pressure difference between the coolant reservoir (410) and the coolant outlet opening (114a);and - at least one coolant valve (118), wherein the coolant valve (118) is arranged between the coolant inlet (116) and the coolant chamber (112); wherein the cooling module (100), under the influence of the pressure difference, has a time-variant behavior of a coolant velocity (22) in the coolant outlet opening (114a) upon sudden, complete opening of the coolant valve (118), which can be described with a time-variant step function (30) having a delay time (32) and a compensation time (34); 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, and particularly preferably less than or equal to 1.5 s. Page 59 / 65 P80649DE 2. Cooling module (100) according to claim 1, wherein the coolant valve (118) under the influence of the pressure difference during the sudden complete opening of the coolant valve (118) has a time-variant behavior of the coolant velocity (22) in the coolant chamber (112), which can be described with a time-variant coolant valve jump function (40) having a coolant valve time constant (42), characterized in that the coolant valve time constant (42) is less than or equal to 1.5 s, preferably less than or equal to 1.0 s and particularly preferably less than or equal to 0.5 s.

3. Cooling module (100) according to one of claims 1 or 2, characterized in that the coolant valve (118) in the fully open position has a coolant valve loss coefficient ^ ^^^^^^of less than or equal to 0.46, preferably less than or equal to 0.44 and particularly preferably less than or equal to 0.

24.

4. Cooling module (100) according to one of the preceding claims, characterized in that the coolant valve (118) has a nominal diameter of greater than or equal to DN80, preferably greater than or equal to DN150 and particularly preferably greater than or equal to DN200.

5. Cooling module (100) according to one of the preceding claims, characterized in that the coolant valve (118) has a nominal diameter of less than or equal to DN300, preferably less than or equal to DN250 and particularly preferably greater than or equal to DN120.

6. Cooling module (100) according to one of the preceding claims, characterized in that the coolant valve (118) has a distance (118a) to a transition from the coolant chamber (112) to a coolant outlet pipe (114) of less than or equal to Page 60 / 65 P80649DE 500 mm, preferably less than or equal to 325 mm and particularly preferably less than or equal to 275 mm.

7. Cooling module (100) according to one of the preceding claims, characterized in that a transition (112a) from the coolant chamber (112) to a coolant outlet pipe (114) is well rounded, in particular having a transition loss coefficient ^ Ü^^^^^^^of less than or equal to 0.3, preferably less than or equal to 0.15, and particularly preferably less than or equal to 0.

08.

8. Cooling module (100) according to one of the preceding claims, characterized in that the cooling module (100) has a flow measuring device (140).

9. Cooling module (100) according to one of the preceding claims, characterized in that the cooling module (100) has an outlet (150) for a bypass channel (152), in particular directly fluid-communicating with the coolant inlet (116) and / or directly fluid-communicating with the coolant chamber (112).

10. Cooling module (100) according to claim 9, characterized in that the outlet (150) is fluid-connected to a bypass valve (154). 11.Cooling module (100) according to one of the preceding claims, characterized in that the cooling module (100) - at least two cooling bars (110), each with a coolant chamber (112) and a plurality of coolant outlet pipes (114) connected in fluid communication with the coolant chamber (112), each having at least one coolant outlet opening (114a) for applying the coolant (20) to the strip-shaped product (10); and. Page 61 / 65 P80649DE - a cooling module branch (160) fluidly communicating with the at least two cooling beams (110).

12. Cooling module (100) according to claim 11, characterized in that the cooling module branch (160) has a cooling module branch loss coefficient ^ ^^^^^^^^^of less than or equal to 0.2, preferably less than or equal to 0.15, and particularly preferably less than or equal to 0.

11.

13. Cooling module (100) according to one of the preceding claims, characterized in that a height difference (120) between the coolant valve (118) and at least one coolant outlet opening (114a) is less than or equal to 500 mm, preferably less than or equal to 400 mm, and particularly preferably less than or equal to 250 mm.

14. Cooling group (200) of a cooling device (300) for cooling a hot-rolled metallic strip-shaped product (10) with a coolant (20), comprising: - at least two cooling modules (100) according to one of claims 1 to 13; and - a cooling group branch (210) fluidly communicating with the at least two cooling modules (100). 15.Cooling group (200) according to claim 14, characterized in that the cooling group branch (210) has a cooling group branch loss coefficient ^^^^^^^^^^^^ of less than or equal to 0.2, preferably of less than or equal to 0.15 and particularly preferably of less than or equal to 0.

11.

16. Cooling system (400) for cooling a hot-rolled metallic strip-shaped product (10) with a coolant (20), comprising: - a cooling system (400);. Page 62 / 65 P80649DE - at least one cooling module (100) according to one of claims 1 to 13 and / or at least one cooling group (200) according to one of claims 14 or 15; and - a coolant reservoir (410) fluidly communicating with a main coolant inlet (420), wherein the main coolant inlet (420) is fluidly communicating with the at least one cooling module (100) and / or the at least one cooling group (200).

17. Cooling system (400) according to claim 16, characterized in that the cooling system (400) is designed for a pressure difference between the coolant reservoir (410) and the coolant outlet opening (114a) of greater than or equal to 3 × 10 ^ ^^⁄ (^ ∙ ^ ^ ), preferably greater than or equal to 4 ∙ 10 ^ ^^ ⁄ ( ^ ∙ ^ ^) and particularly preferably greater than or equal to 4.5 ∙ 10 ^ ^^ ⁄ ( ^ ∙ ^ ^)18. Cooling system (400) according to one of claims 16 or 17, characterized in that the cooling system (400) is designed for a specific water loading of greater than or equal to 20 ∙ ^ ^ ⁄ (^ ^ ∙ ℎ), preferably greater than or equal to 50 ∙ ^ ^ ⁄ (^ ^ ∙ ℎ) and particularly preferably greater than or equal to 150 ∙ ^ ^⁄ ( ^ ^ ∙ ℎ ) 19. Cooling system (400) according to one of claims 16 to 18, characterized in that the cooling system (400) is designed for a cooling rate of greater than or equal to 50 ∙ ^ ⁄ ( ^ ∙ ^^ ) is set up, preferably greater than or equal to 200 ∙ ^ ⁄ ( ^ ∙ ^^ )and particularly preferably greater than or equal to 500 ∙ ^⁄ (^ ∙ ^^).

20. Cooling system (400) according to one of claims 16 to 19, characterized in that the cooling system (400) comprises at least a first cooling beam (110) and a second cooling beam (110), wherein the first cooling beam (110) is designed to apply the coolant (20) to the upper side of the strip-shaped product Page 63 / 65 P80649DE (10) and the second cooling bar (110) is configured to apply the coolant (20) to the underside of the strip-shaped product (10).

21. Cooling system (400) according to one of claims 16 to 20, characterized in that the cooling system (400) has a main coolant conveying device (430) configured to increase the pressure difference between the coolant reservoir (410) and the coolant outlet opening (114a).

22. A method for actively cooling a hot-rolled metallic strip product (10), characterized in that a cooling module (100) according to one of claims 1 to 13 and / or a cooling group (200) according to one of claims 14 or 15 and / or a cooling system (400) according to one of claims 16 to 21 is used for actively cooling the hot-rolled metallic strip product (10). 23.Method for actively cooling a hot-rolled metallic strip-shaped product (10) according to claim 22, characterized in that the method is set up to control and / or regulate a degree of distribution of at least one structural component, in particular to achieve a degree of distribution of greater than or equal to 0.85, preferably of greater than or equal to 0.9 and particularly preferably of greater than or equal to 0.

95.

24. Method for actively cooling a hot-rolled metallic strip-shaped product (10) according to one of claims 22 or 23, characterized in that the method is set up to reduce a head length of the metallic strip-shaped product (10), in particular to achieve a head length of less than or equal to 10 m, preferably of less than or equal to 8 m and particularly preferably of less than or equal to 6 m. Page 64 / 65 P80649DE 25. A method for actively cooling a hot-rolled metallic strip-shaped product (10) according to one of claims 22 to 24, characterized in that the method is designed to reduce a root length of the metallic strip-shaped product (10), in particular to achieve a root length of less than or equal to 10 m, preferably less than or equal to 8 m and particularly preferably less than or equal to 6 m.

26. Hot-rolled metallic strip-shaped product (10) produced by a method according to one of claims 22 to 25, in particular a hot-rolled metallic product (10) with a tensile strength of greater than or equal to 560 N / mm² and a manganese content of less than 1.5 wt.% and a niobium content of less than 0.05 wt.%. 27.Use of a cooling module (100) according to one of claims 1 to 13 and / or a cooling group (200) according to one of claims 14 or 15 and / or a cooling system (400) according to one of claims 16 to 21 and / or a method according to one of claims 22 to 25 for actively cooling a hot-rolled metallic strip-shaped product (10) with a coolant (20).

Images