Method and device for storing heat

Abstract

The invention relates to a method for discharging heat from a layered heat storage device which has a cold side and a warm side and through which a heat-transporting fluid flows and which has a filling of heat-storing solid matter which is located in the fluid flow and exchanges heat therewith, wherein the fluid between a connection for the inflow of cold heat-transporting fluid and a connection for the outflow of the heat-transporting fluid which is warm after absorbing heat has a pressure drop. During the discharge from the heat storage device, the fluid is conducted in the discharge flow direction between the inflow connection and the outflow connection through a throttle arrangement and is throttled therein in such a way that the pressure drop due to the throttling is 30% to 90% of the total pressure drop in the fluid between the two connections.

Description

Method and device for storing heatThe present invention relates to a method for generating a stream of warm, heat-transporting fluid from a layered heat storage device having a cold and a warm side, and to a heat storage device for carrying out this method.Besides many other applications, heat storage devices are used in power plants, especially solar power plants, where they must be designed for a 24-hour cycle to be charged with heat during the day and discharged at night. In a solar power plant, solar heat is concentrated in a receiver and carried away from it by a heat-transporting fluid, partly directly to a consumer, partly to a heat storage device, in order to have heat available when there is no solar radiation, as mentioned especially during the night, so that a charging-discharging cycle of 24 hours must be possible.Many industrial processes are potential consumers, increasingly including processes in which syngas is produced in a thermochemical reactor, containing, for example, the gases H2 (hydrogen) and CO (carbon monoxide), from which synthetic fuel is produced, for example, via the Fischer-Tropsch process. The production of syngas as a precursor to synthetic fuels using solar energy is generally known to experts, as is the production of synthetic fuels from syngas, for example by the Fischer-Tropsch process.The thermochemical reactor requires heat at temperatures above 1000 C, which is supplied to the reactor, for example, by the heat-transporting fluid heated in the receiver or heat storage device, wherein the fluid, which is cold after the heat has been released in the reactor, still has a temperature of 500 C or more.This creates the need for a heat storage device that can be charged by a charging cycle of heat-transporting fluid and discharged by a discharging cycle of heat-transporting fluid, wherein the stored heat is at an upper temperature to of, for example, 1000 C to 1500 C or more, and in the discharged heat storage device there is still a lower temperature tu of, for example, 500 C to 900 C. In contrast to a sensible heat storage devices, the discharge of the heat storage device must be constant at the upper temperature to and must not fluctuate or drop during discharge (within defined tolerances), otherwise a thermochemical reactor could not be operated with the stored heat. Furthermore, the constant consumption of heat in the reactor leads to an equally constant cooling of the heat-transporting fluid in the discharge cycle, so that the temperature of the cold fluid returning to the heat storage also remains at a constant level.Heat storage devices for larger quantities of heat are known as Cowpers or regenerators, used for blast furnaces and have corresponding cycle times of 30 to 60 minutes. Fluid-permeated, stacked and fire-resistant grid blocks are used to store heat, with stacks reaching a considerable height of up to 30 m. A disadvantage of Cowper or regenerators is that burners often have to be switched on or cold air mixed into the warm fluid in order to keep its upper temperature at the level desired for the blast furnaces. Another disadvantage is that such heat storage devices are not suitable for 24-hour operation. Furthermore, the flow resistance during the passage of the fluid is high, although the correspondingly reduced efficiency is not a major issue in blast furnace operation.WO 2012 / 027 854 discloses a heat storage device which appears to fundamentally meet the aforementioned conditions for operation in, for example, a solar power plant, by storing the heat in a solid such as gravel, which is located in a container and can be flowed through by the heat-transporting fluid. Warm fluid flows into the gravel filling from one side, heating it from the connection for the warm fluid, wherein the fluid cools down and leaves the gravel filling in a cold state via the outflow connection for the fluid. In the gravel filling, a temperature jump occurs in the direction of fluid flow between the already heated gravel and the still cold gravel, i.e. a thermocline which, as the heat storage device is charged, moves from the connection for the warm fluid through the gravel filling to the outflow connection for the discharge of the fluid. To discharge this heat storage device, the fluid is guided through the gravel filling in the opposite direction, wherein the thermocline then migrates back in the opposite direction to the connection for the warm fluid. If this heat storage device is deliberately operated in such a way that the thermocline does not reach any of the connections, but the flow direction of the fluid is reversed (or stopped) in time, the gravel filling at the connection for the warm fluid is always warm, and at the connection for the cold fluid it is always cold. This is intended to ensure that a constant upper temperature is achieved during the discharge of the disclosed heat storage device, without the need to additionally supply heat via a burner or reduce the upper temperature to its target level by admixing cold fluid. Since the gravel filling is supposed to heat up or cool down layer by layer with the moving thermocline, a heat storage device according to WO '854 is also referred to as a layered heat storage device, which has a cold and a warm side.WO 2016 / 162 839 also discloses such heat storage devices, in which the thermocline is designed as a wave, for the recuperation of heat during the operation of a reactor for the production of syngas.The advantage of heat storage devices with a cold and a warm side according to WO '854 or WO '839 is that a constant temperature should be present on the warm side, i.e., the effort required for the additional mixing of additionally heated or cooled fluid can be eliminated. A disadvantage, however, is that the thermocline does not actually move at a uniform speed in the cross-section relative to the flow direction of the fluid; in addition, the temperature gradient in the thermocline across this cross-section is uneven and generally quite small, eventually becoming considerably smaller during continuous operation with the result that the amount of heat that can be stored cannot be precisely determined and can also decrease with continuous operation, so that such a heat storage device is only conditionally suitable for use in industrial operations. Furthermore, the flow resistance in the fluid is high when passing through the gravel filling, and the efficiency is correspondingly reduced.Accordingly, the object of the invention is to provide an improved method for storing heat or an improved heat storage device, wherein the storage of heat in a 24-hour cycle can take place unchanged and with high efficiency and the upper temperature to does not have to be kept constant by additional aids such as burners.This object is achieved by a method having the features of claim 1 or by a heat storage device having the features of claim 13.By incorporating a throttling arrangement into the fluid flow, the fluid exhibits a uniform pressure across the entire dimension of the heat-storing solid matter, regardless of the specific path of a partial flow of the fluid and this results in a uniform flow across the entire dimension of the solid, which in turn allows a controlled thermocline to form within the solid. This thermocline extends uniformly transverse to the flow direction, exhibits a high temperature gradient, and significantly reduces drift over time. These effects become significant as soon as the pressure drop due to throttling is at least 30% of the total pressure drop in the fluid between the connections, wherein even a pressure drop due to throttling of 90% is advantageous and thus any efficiency loss caused by throttling is negligible in view of the advantageous properties of such a heat storage device, since other efficiency-reducing measures for controlling the temperatures can be omitted.Because, according to claim 8, the grid blocks form a stack with continuous, uninterrupted and straight heat exchange channels, in combination with the fluid throttling arrangement, a particularly favorable thermocline is formed in the grid blocks, with a very high and operationally stable temperature gradient across the entire dimensions of the stack of grid blocks, which leads to a high utilization of the stack and a uniform upper temperature to during discharge of the heat storage device within comparatively narrow tolerances. This arrangement also exhibits a particularly low flow resistance.Beyond the stated objective, according to claim 19, the arrangement of the stack of grid blocks on supports forming fluid channels enables a structurally simple and therefore cost-effective support of the considerable weight of the stack in conjunction with the special inventively designed supply of cold (but nevertheless having, for example, a temperature of 900 C) fluid through the support to the lower side of the stack.Further preferred embodiments have the features of the dependent claims.The invention is described in more detail below with reference to the figures.In the drawing:Figure 1 schematically shows a solar power plant with its associated infrastructure,Figure 2 schematically shows the temperature conditions in a heat storage device according to the invention,Figure 3a schematically shows a heat storage device according to the invention in an external view,Figure 3b schematically shows a section along the plane A of Figure 3a,Figure 3c schematically shows a section along the plane B of Figure 3a,Figure 4a shows a view of a grid block according to the invention,Figure 5a shows a view of the stack of grid blocks and its support,Figure 5b shows a view of the stack of Figure 5a with an embodiment of a throttle arrangement,Figure 6a shows a view of a distributor grid block according to the invention,Figure 6b shows a view of a section of the stack of grid blocks with a layer of distributor grid blocks from below, and.Figure 7 shows a view of a throttle grid block according to the invention, which represents a further embodiment of a throttle arrangement.Figure 1 shows an example of a scheme of a solar power plant 1 with a field of solar collectors 2 irradiated by the sun, which direct the sun rays 3 onto a receiver 4, which is arranged on a tower 5. In the receiver 4, heat-transporting fluid is heated. The warm fluid flows via a fluid supply line 6 selectively to a heat storage device 7 or to a thermoreactor 8 (or simultaneously to both), where it releases its heat in the heat storage device 7 and / or drives the thermoreactor 8 with its heat, and then returns as a cold fluid via a fluid return line 9 to the receiver 4, which heats it again. The heat storage device 7 or the thermal reactor 8, or both simultaneously, can therefore be supplied with heat in a closed loop via lines 6, 9.If the heat storage device 7 is charged with heat, it can be discharged by transferring its stored heat via a discharge line 10 through warm, heat-carrying fluid to the thermoreactor 8, where the fluid cools down through the operation of the thermoreactor 8 and returns to the heat storage device 7 as a cold fluid via a second return line 11. The fluid supply line 6 and the fluid return line 9 thus form a charging circuit, while the discharge line 10 and the second return line 11 form a discharge circuit for the heat storage device 7. The heat storage device 7 is generally charged during the day and discharged overnight, resulting in a 24-hour cycle for the heat storage device 7.As mentioned above, the thermoreactor 8 produces, for example, H2 and CO, i.e. , syngas, from CO2 and H2O, wherein CO2 and H2O are supplied to it via a reactor supply line 12 from a suitable source known to those skilled in the art, symbolized by arrow 22, while the produced H2 and CO are conveyed via a production line 13 to an installation 14 for further processing. As mentioned above, installation 14 can produce synthetic fuel from syngas, e.g., using the Fischer-Tropsch process.A system according to Figure 1 is generally known to those skilled in the art, as is the fact that the simple, cost-effective and reliable storage of heat in the above-mentioned temperature ranges is unsolved, especially when heat is to be stored on an industrial scale, e.g. the heat of a day production of a large solar power plant.Figures 2a and b schematically show the temperature conditions in a heat storage device 7 designed according to the invention, which is designed as a layered heat storage device having a cold and a warm side. Figure 2a shows a discharged heat storage device and Figure 2b shows a charged heat storage device with the corresponding temperature distribution.Figure 2a, left, schematically shows an embodiment of the heat storage device 7 in a section along its height H, which is discharged and is thus before the charging process.The heat storage device 7 has a connection 15 at the top for the fluid supply line 6 (Figure 1) for the supply of warm fluid (symbolized by the arrow 16) and at the bottom, in its base surface 17, a connection 18 of the fluid return line 9 (Figure 1) for the discharge of cold fluid (symbolized by the arrow 19) back to the receiver 4 (Figure 1). Between connections 15, 18, a charging flow direction of the fluid is from top to bottom through the heat storage device 7.The heat storage device 7 contains a filling of heat-storing solid material lying in the fluid flow and exchanging heat with it, which here is in the form of a stack 20 of grid building blocks 21, as described in detail below, among other things in the description of figures 5a to 6. In the section shown, the stack has a width B of its base surface 17 over its height H, the depth of which is also B in the case of a cubic stack.Between the connection 15 and the stack 20 there is a warm fluid chamber 24, in which warm, inflowing (arrow 16) fluid is distributed into the grid blocks 21 of layer 27, and warm, outflowing fluid (arrow 37 of figure 2b) from the grid blocks 21 of layer 27 collects towards the connection 15.Beneath the stack of grid blocks 21, between the connection 18 and the lowest layer of grid blocks 21, there is a cold fluid chamber 23, through which cold fluid exiting from the lowest layer 33 of grid blocks 21 is collected and directed into the cold connection 18, or cold incoming fluid (arrow 36 of figure 2b) is distributed to the lowest layer of grid blocks 21. The cold fluid chamber 23 has a throttling arrangement 22 for the fluid flow, which causes a pressure drop in the fluid flowing through it.Figure 2a, on the right, shows a diagram 25 with the temperature distribution over the height H of the stack 20 (as mentioned, in the discharged state of the heat storage device 7).On the horizontal axis of diagram 25, the temperature T is plotted with the temperatures tu and to, on the vertical axis the running height h, up to the height H of the stack. The temperature curve 26 shows that all grid blocks 21 have a temperature of tu and are therefore cold, with the exception of the layer 27 of warm grid blocks 21 located directly at connection 15 with a temperature of to and the subsequent layer 28 of less warm grid blocks 21 with an intermediate temperature between to and tu. The grid blocks 21 of layer 29 are, as mentioned, already cold. The warm grid blocks 21 are symbolized by four dots, the less warm ones by a single dot, and the cold grid blocks by no dots.The temperature curve 26 shows an advantageously steep thermocline 26* from to to tu over the height h, which extends only over the two layers 21 and 22. The temperature gradient of thermocline 26* is large.If warm fluid (arrow 16) now flows in the charging flow direction into the stack 17 for the charging of the heat storage device 7, it passes through all grid blocks 21 of layer 27 without heat exchange with them, as these are warm, but transfers heat to the layer 28 below until it is warm, and simultaneously heats the layer 29 further below to the intermediate temperature, while the layer below layer 29 remains cold. As the fluid flow continues, more and more layers from top to bottom become warm, while layers further and further down remain cold. The thermocline of curve 26 thus moves downwards in accordance with arrow 26'. The charging process of the heat storage device 7 is now continued until only the lowest layer 33 of the lower layers 30 to 33 is cold, whereupon the heat storage device 7 is fully charged and, as shown in Figure 2b, the thermocline has thus arrived in the lowest layer 33.Figure 2b shows the heat storage device 7 in the same representation as in Figure 2a, in a charged state, ready for discharge. The temperature curve 26' shows a thermocline 35*, which - since the heat storage device 7 is charged - has moved completely downwards in the stack 20 and is advantageously only slightly flatter over the height h than the thermocline 26* of figure 2a, thus extending over two layers 31 and 32 in the schematic representation of the grid blocks 21. The reason for the somewhat flatter form is that, during the charging phase, due to the heat exchange of the fluid with the grid blocks 21, these naturally cannot cool the fluid down exactly to tu, so the cold fluid flows with a minimally increased temperature against the next cold layer, where it becomes colder again. This effect continues until the heat storage device 7 is fully charged, and generally leads to a flattening of the thermocline 26** (which is however small in this case).The charged heat storage device 7 can now be discharged again by reversing the flow direction of the fluid (compared to Figure 2a), wherein cold fluid (arrow 36) then flows in the discharge flow direction through the connection 18 into a fluid supply arrangement 23, is throttled in the throttle arrangement 22, flows through the stack 20, is heated in this and is discharged as warm fluid (arrow 37) through the connection 15. As the heat storage device 7 is discharged, the thermocline 35* moves upwards again according to the arrow 35', whereby the warm layers 27 to 32 cool down again in the opposite way to their heating, until finally, when the heat storage device 7 is discharged, the state according to Figure 2a is reached again.The throttle arrangement 23, preferably designed as a perforated aperture, causes a uniform volume flow of fluid through it across its dimensions, with the result that fluid flowing in from the connection 18 after the throttle arrangement 23 flows into the bottom layer 33 of the grid blocks 21 with the same pressure and mass flow rate, which in turn ensures that the same heat transfer occurs in each grid block 21 as in its neighboring grid blocks 21 of a respective layer 27 to 33, so that the thermocline is formed at the same height h of the stack 20 transversely to the flow direction and at the same steepness in the flow direction.In principle, the throttle arrangement 23 can also be arranged in the warm fluid chamber 24, or at any height h in the stack, since a uniform volume flow after the throttle arrangement naturally corresponds to a uniform volume flow before the throttle arrangement. In the case of charging the heat storage device according to Figure 2a, the throttling arrangement is located after the stack 20 in the direction of flow, and not, as in the case of discharging the heat storage device 7 according to Figure 2b, in front of the stack 20.However, the effect of the throttle arrangement 20 is particularly advantageous when it is provided in the cold fluid chamber 23. Even with very good insulation of the stack 20, the outer grid blocks 21 have a slightly lower temperature than those located inside the stack 20. If the throttling arrangement 20 is now placed in the warm fluid chamber 24, and the heat storage device 7 is discharged, the volume flow rate of the fluid across its dimensions is the same, but not the mass flow rate: on the outer side of the stack 20, due to the slightly lower temperature of the grid blocks 21, the density of the fluid is slightly higher corresponding to the temperature difference. As a result, the fluid flowing from the cold fluid chamber 23 to the warm fluid chamber 24 absorbs slightly more heat from the grid blocks 21, thus cooling them slightly more than the inner grid blocks 21. Due to the different mass flow rates (with the same volume flow rate) through the throttling arrangement 20, the thermocline is undesirably distorted slightly, so that it lies somewhat closer to the cold chamber 23 in the core of the stack.If the throttle arrangement 20 is placed in the cold fluid chamber 23, the volume flow rate is the same across the dimensions of the throttle arrangement, as is the mass flow rate passing through (the fluid passing through has a uniform temperature tu). Equal mass flow through all grid blocks results in a more stable, less distorted thermocline, which is advantageous.When the heat storage device 7 is charged, the effect of the different fluid / mass flow rate is smaller because the temperature in the cold fluid chamber is lower. The advantage of arranging the throttling arrangement 20 in the cold fluid chamber 23 for the discharge of the heat storage device 7 is thus not eliminated again during the charging of the heat storage device 7, so that in the end the advantage outweighs the disadvantage.In contrast to the prior art, a more uniform temperature distribution and steeper thermocline can be achieved in the heat storage device 7 according to the invention, which leads to a significantly more uniform temperature release from the heat storage device and also to a better utilization of the stack 20 or, for a given stack 20, to the storage of a larger amount of heat. Storing a larger amount of heat for a given stack 20, i.e., an increased storage density, is particularly important for storing large amounts of heat: the necessary insulation of a smaller stack volume is simpler and more cost-effective and therefore easier to achieve.Figure 3a schematically shows an embodiment of a heat storage device 40 according to the invention from the outside, i.e. on the surface of its insulation, with a cold side 41 and a warm side 42, a projecting region 43 and the corresponding connections 18 for cold and 15 for warm fluid. The heat storage device 40 has a base surface 44 not visible in the figure, a front 45, a back 46 not visible in the figure, a right side 47, a left side 48 not visible in the figure and a top 49.During the discharge of the heat storage device 40, heat-transporting fluid flows from connection 18 for the supply of cold fluid through the heat storage device 40 under a pressure drop in the discharge flow direction and leaves it through connection 15 for the discharge of warm fluid. As mentioned above, the charging flow direction runs in the opposite direction from connection 15 to connection 18.The dashed line A denotes a section line of a first vertical section plane through the heat storage device 40 over its entire height H, the dashed line B denotes a section line of a second vertical section plane through the projecting region 43.Figure 3b shows the section through the heat storage device 40 in the first vertical section plane according to the section line A of Figure 3a. An insulation 50 surrounds a filling of heat-storing solid, here a stack 51 of grid blocks 52 shown schematically in the figure according to Figure 4. The stack 51 is supplemented by a layer 52 of distributor grid blocks 53 according to Figure 6a or throttle distributor grid blocks 54 according to Figure 6b.The stack 51 stands with the layer 52 of distributor grid blocks 53 or throttle distributor grid blocks 54 on a fluid line arrangement 55 of the cold fluid chamber 65, which is designed to support the stack 51 with the supplementary layer 52 and at the same time to guide the cold fluid supplied to the heat storage device 40 through the connection 18 (Figure 3a) evenly to the layer 52, so that it can enter the layer 52 (and the stack 51) at the same pressure, distributed over the entire base surface 56. The fluid line assembly 55 rests on an insulated base plate 57 of the heat storage device 40.A fluid line arrangement 55 is shown in Figures 5a and b in a view, which can support the load of a stack 51 of up to several thousand tons at a lower temperature tu of, for example, up to 900 C (the fluid line arrangement heats up to this temperature during operation with the stack) and is simple and cost-effective in design. In the discharge flow direction downstream from the connection 18, it has a pressure equalization chamber 58, then a perforated aperture 59 of the fluid throttling arrangement (see Figures 2a,b and 3c and 5b) and finally fluid channels 60 formed by U-beams 61 (see also Figure 5a). The U-beams 61 are connected at their front to the perforated aperture 59 and closed at their rear, but open at the top, so that fluid entering from the pressure equalization chamber 58 through the perforated aperture 59 can pass upwards along their entire length into the layer 52 and thus into the stack 51. The pressure equalization chamber 58 serves to calm the fluid entering via the connection 18 indicated by dashed lines in Figure 3b and to establish at least approximately equal pressure in the fluid in front of the perforated aperture 59, and across its entire dimensions. The perforated aperture 59 ensures that when the heat storage device 40 is discharged, each fluid channel 60 is supplied with the same volume flow and thus also with the same mass flow of fluid (the fluid has a uniform density, corresponding to the lower temperature tu). The same pressure builds up in each fluid channel 60, with the result that each grid block 53, 54 and 52 is supplied with fluid equally.It follows that preferably a pressure equalization chamber is provided between the connection for the fluid supply and the throttle arrangement, and further preferably the throttle arrangement is arranged below the stack.Finally, Figure 3b shows the warm chamber 62 in the warm region 42 of the heat storage device 40, in which the warm fluid leaving the stack 51 in the discharge flow direction collects, so that it can leave the heat storage device 40 through the connection 15 indicated by the dashed line.Figure 3c shows the section through the heat storage device 40 in the second vertical section plane according to the section line B of Figure 3a and 3b. The view is from the front, i.e. from left to right in Figure 3b, against the rear 46 of the heat storage device 40.The connection 18, which leads into the pressure equalization chamber 58, is clearly visible, on the rear side of which (in the direction of view) the perforated aperture 59 of the fluid throttling arrangement is arranged, which is composed of sections 59', each of which covers the openings of the U-beams 61. The U-beams 61 are arranged parallel to each other and spaced apart by spacer elements 63, and extend perpendicularly to the drawing plane from this plane backwards, under the entire stack 51. On each side of the pressure equalization chamber 58 there is a half spacer element 63' and a half section 59'' of the perforated aperture 59. Cover plates 64 lie between the perforated aperture 59 and the stack 51 on top of the U-beams. Behind each section 59',59'' a fluid channel 60 formed by the U-beams 61 extends.The cold fluid flowing into the pressure equalization chamber 58 through the connection 18 in the discharge flow direction is distributed in this chamber, flows through the sections 59',59'' of the perforated aperture 59 and thus enters the fluid channels 60, which extend over the entire base surface 56 (see also Figure 3b). The U-beams 61, spacer elements 63,63' and the sections 59',59'' of the perforated aperture 59 preferably consist of the same refractory material as the grid blocks 52,53 and 54, making them easy to manufacture, pressure-resistant and cost-effective.The cold fluid is throttled to a predetermined extent as it passes through the perforated aperture 59 of the throttling arrangement, namely such that during the discharge of the heat storage device 40 the pressure drop due to the throttling is 30% to 90% of the total pressure drop in the fluid between the connections 18 and 15. This ensures the uniform supply of fluid to the grid blocks 53, 54 and 52 as described in Figure 3b.This results in that the throttle arrangement preferably has a perforated aperture which is arranged on the side of the fluid supply line under the stack at the front face of the fluid channels and covers the inlet to the fluid channels in an operational manner.This results in a method for discharging heat from a layered heat storage device 40, having a cold side 41 and a warm side 42, through which a heat-transporting fluid flows, and containing a heat-storing solid material lying in the fluid flow and exchanging heat with it, wherein the fluid has a pressure drop between a inflow connection 18 of cold, heat-transporting fluid and a connection 15 for the discharge of the heat-transporting fluid, which is warm after absorbing heat, and wherein, during the discharge of the heat storage device 40, the fluid flows in the discharge flow direction between the inflow connection 18 and the outflow connection 15 through a throttling arrangement and is throttled therein, such that the pressure drop due to the throttling is 30% to 90% of the total pressure drop in the fluid between the two connections. Preferably, the pressure drop in the fluid due to throttling is more than 40%, more preferably more than 50%, more preferably more than 60%, and most preferably more than 70% or more than 80%. Furthermore, a method is obtained, preferably wherein, for at least partial throttling, the fluid flow is directed through a perforated aperture preferably upstream of the solid, located in the fluid flow, which throttles it. Furthermore, the fluid to be heated is preferably directed into a fluid pressure equalization chamber in the fluid line arrangement and at least partially throttled at its outlet.Figure 4 shows a view of an embodiment of a grid block 70 according to the invention, which is designed as a stackable cuboid, stands on its base surface and is vertically penetrated by a number of heat exchange channels 71. Preferably, two raised regions 72 on the top surface are formed opposite two depressions in the base surface, such that a further grid block 70, placed on or stacked on the grid block 70 shown, is centered on it, such that the heat exchange channels 71 of both grid blocks are aligned with each other.On the side walls 74 of the grid block 70 grooves 71' are arranged, the contour of which corresponds to half a heat exchange channel 71. When two grid blocks 70 are placed side by side (or end to end) next to each other, the opposing grooves 71' together form a heat exchange channel 71. Grooves 71'' are arranged at the corners of the grid block 70, the contour of which corresponds to a quarter of a heat exchange channel 71. If four grid blocks 70 are placed next to each other so that one corner of each abuts a corner of the other grid blocks 70, the four adjacent grooves 71'' together form a heat exchange channel 71. For example, this configuration of the grid blocks 70 allows the grid blocks 70 to be stacked without gaps to form a stack 50 (Figure 3b), wherein the heat exchange channels 71 and the heat exchange channels 71 formed from grooves 71', 71'' are then arranged in a regular pattern that extends over all grid blocks 70 of the stack 51.This results in a stackable grid block 70 for a layered heat storage, with a base surface and a surface and side surfaces and with heat exchange channels extending from the base surface to the surface, wherein these are preferably arranged parallel and at the same distance from each other, are round in cross-section, have an effective diameter of 50 mm or less, and wherein the distance (wall thickness between the channels) of adjacent heat exchange channels is 70 mm or less. More preferably, the diameter of the heat exchange channels of a grid block is 25 mm or less, more preferably 15 mm or less, most preferably 10 mm or less and most preferably 5 mm. Finally, the distance between adjacent heat exchange channels can preferably be 50 mm or less, more preferably 30 mm or less, more preferably 10 mm or less, most preferably 8 mm or less, more preferably 6 mm or less, but at least three times the average grain diameter of the material of the grid block. Refractory grid blocks for Cowper or regenerators are known to the person skilled in the art, i.e., also the material from which they can be made and their manufacture, i.e., by casting. The grid blocks according to the present invention can preferably consist of such materials and be produced by casting.For example, a grid block 70 according to Figure 4 can be used as a grid block 52 in the heat storage device 40 according to Figures 3a to 3c, such that the stack 51 is formed from grid blocks 70. Then the heat exchange channels 71 of the stacked grid blocks 70 are aligned and each forms a heat exchange channel 71* through the entire stack 51, as shown as an example in Figure 3b in the stack 51. Then, preferably according to Figure 3b, the heat exchange channels of the stack run vertically and the connection for the supply of cold, heat-transporting fluid is arranged below the stack. The discharge flow direction is thus preferably directed vertically from bottom to top.The comparatively small diameters of the heat exchange channels 71 (or the grooves 71',71'') are advantageous because this results in a favorable large surface region of the walls of the heat exchange channels 71 for the flowing volume of the fluid, which promotes the heat transfer between the fluid and the grid block 70. Such small diameters are possible because the supply through the fluid line arrangement 55 in the cold fluid chamber 65 ensures that each heat exchange channel 71* is supplied with the same fluid pressure. In order to produce the walls of the heat exchange channels 71 or the continuous heat exchange channels 71* flawlessly in a casting process, their diameter should be at least three times the average grain diameter of the material of the grid block - conversely, this means that such small diameters, unknown in the prior art, are possible according to the invention.It is found that the fluid is preferably guided through a solid formed as a stack of grid blocks, wherein the grid blocks have parallel, separate heat exchange channels, preferably with the same cross-section and preferably with the same distance from each other, and wherein the grid blocks are aligned with each other in such a way that the heat exchange channels of successively lying grid blocks are aligned with each other in the flow direction, so that aligned heat exchange channels together each form a straight, uninterrupted heat exchange channel through the stack, which is separated from the other heat exchange channels. Preferably, the fluid is passed through heat exchange channels arranged in the solid, which have the same cross-section and length and are arranged separately from each other at the same distance from each other.For example, Figure 3b shows that preferably the fluid is guided from the inflow connection to the solid during the discharge of the heat storage device and then through separate heat exchange channels arranged in the solid. Furthermore, it is preferably the case that the fluid is directed via a cold fluid chamber having a fluid line arrangement to the solid and preferably to heat exchange channels arranged in the solid.Figure 5a shows, to illustrate part of the fluid line arrangement 55 of the cold fluid chamber 23 (Figures 2a,b and 3a to c), a view of a stack 51 of grid blocks 70 which is supported on (multi-part in the figure) U-beams 61, as shown in Figures 3a to 3c. The U-beams 61 have lateral, upwardly directed legs 51',51'' which are connected to each other by connecting sections 51'''. Furthermore, the U-beams 61 are held parallel and at a distance by spacer elements 63, the spacer elements 63 being dimensioned such that the legs 51',51'' of all U-beams 61 have the same distance to each other and thus form fluid channels 60 with equal dimensions that extend under the entire underside of the stack 51. The fluid is supplied on one side of the fluid channels 60, while on the other side these are closed, so that during the discharge process, as mentioned above, the supplied fluid must inevitably enter upwards into the heat exchange channels 71* of the stack 51.The stack 51 rests with its weight on the U-beams 61, which are preferably made of the same material as the grid blocks 70, so that they are refractory, i.e. resistant to the temperatures prevailing in the heat storage. Furthermore, this material is pressure-resistant, so it can support the weight of the stack of 51. The advantage of the support provided by the U-beams 61 is that, in combination, a fluid line arrangement is enabled for the uniform supply of fluid over the entire base surface of the stack 51 and for the support of the considerable weight of the stack 51, with the manufacturing effort being very small.A heat storage device is preferably formed in which the cold fluid chamber has a number of adjacent supports arranged below the stack, which bear the weight of the stack, wherein the space between the supports forms a number of fluid channels which serve from one side for the fluid supply under and into the stack and are closed on their other side, and at the top of which the openings of the continuous heat exchange channels are located. It is further preferably found that wherein the supports are designed as parallel adjacent U-beams with upwardly directed U-legs, wherein the weight of the stack acts on the upper ends of the U-legs, and wherein the space between the U-legs forms the horizontally extending fluid channels, on the upper side of which the openings of the continuous heat exchange channels are located, and preferably the U-beams are arranged at a distance from each other via spacer elements, wherein the width of the spacer elements corresponds to the width of the connecting sections of the U-beams.Figure 5b shows, for clarification, a 3D view of the stack 51 of grid blocks 70, supported on the U-beams 61 according to Figure 5a, with an additional embodiment of a throttle arrangement 22 (Figures 2a and b) in the embodiment according to Figures 3b and c. The pressure equalization chamber 58 is shown with a dashed line to reveal the arrangement of sections 59', 59'' of the perforated aperture 59.Figure 6a shows a view of a distributor grid block 53 according to the invention, which, apart from the transverse channels 82 provided on its underside 81, is designed identically to the grid block 70 of Figure 4. The identical design, corresponding to the grid block 70, allows the distributor grid block 80 to be stacked like the grid blocks 70, namely without gaps and with heat exchange channels 71 which, when stacked, are aligned with those of the other grid blocks 70 and together form continuous heat exchange channels 71*. Thus, the distributor grid block 80, as shown in Figure 3b, can complement the stack 51 of grid blocks 70 in a bottom layer 52, since it has the same properties as the grid blocks 70 of the stack 51 with regard to the storage of heat and the transfer of heat to and from the flowing fluid.The transverse channels 84 preferably extend over the entire underside 81 of the distributor grid block 80, wherein a transverse channel 84' is preferably arranged on the outer side 74 of the distributor grid block 80, the outer side wall of which is missing. This allows a distributor grid block 80 placed adjacent to the outer side 74 to close the transverse channel 84' with its outer side wall 74', whereupon it functionally becomes a normal transverse channel 84. This is analogous to the formation of heat conduction channels 71 by adjacent grooves 71', see the description for Figure 4.Between the transverse channels 84 are support ribs 83, which form a base for the distributor grid block 53, on which the distributor grid block 53 rests.Figure 6b shows a 3D view of the stack 51 with a layer 52 of distributor grid blocks 53 according to Figure 3b, but only a section corresponding to the dashed region 83 with a view in the direction of the arrow 85 in Figure 5a is shown. In this view, the course of the transverse channels 84 in relation to the U-beams 61 is evident: The distributor grid blocks 53 rest on the legs 61', 61'' of the U-beams 61, wherein heat exchange channels 71 and 71* end on the support surface of the legs 61', 61'' and are now connected to the fluid channels 60 via the transverse channels 82. The transverse channels 82 thus ensure that heat exchange channels 71, 71* ending at the location of the legs 61', 61'' can be permeated with fluid in the same way as any of the heat exchange channels 71, 71*.This results in a distributor grid block for a layered heat storage device, with a base surface and a surface and side surfaces, and with heat exchange channels 71', 71* extending from the base surface to the surface, characterized in that the base surface is designed to support the distributor grid block in operation on parallel U-shaped legs 61', 61", which form fluid channels 60, wherein transverse channels 82 are provided in the base surface which can be connected to the fluid channels 60, and wherein the transverse channels 82 are designed such that, in operation, with the distributor grid block supported on the U-shaped legs, heat exchange channels 71, 71* ending at the location of the legs 61, 61' can be flown through by fluid in the same way as any of the heat exchange channels (71, 71*).As mentioned, for ease of manufacture, the transverse channels 84 preferably extend over the entire length of the distributor grid block 53, but can also be only as long as they extend sufficiently over the width of the legs 61', 61'' or of the respective support for the stack 51 to ensure the connection of the affected heat exchange channels 71 with the fluid channels 60. Preferably, in cross-section, the transverse channels 82 only connect adjacent, parallel heat exchange channels 71a and 71b in order to minimize the stress on the structure. The wider the transverse channels 84 are, the greater the stress on the material of the distributor grid block 53 due to the weight it bears of the grid blocks 52 stacked above it. Each heat exchange channel 71, 71* is assigned to only one transverse channel, which allows for optimal design of the transverse channels 84 together with the heat exchange channels 71, 71*. This results in a distributor grid block in which each heat exchange channel 71,71* is assigned to a transverse channel 82, such that between each two adjacent transverse channels 82 a support rib 83 with a bearing surface is formed by these.A method is derived in which the fluid is preferably guided through distributor grid blocks in front of the heat-storing solid, the distributor grid blocks having heat exchange channels which in turn are aligned with heat exchange channels provided in the solid, wherein aligned heat exchange channels together each form a heat exchange channel through this solid, and wherein furthermore the upstream inlet side of the distributor grid blocks in the discharge flow direction has transverse channels which only connect adjacent rows of heat exchange channels to each other, wherein each heat exchange channel is assigned to a transverse channel, such that a support rib is formed between each pair of adjacent transverse channels, on which the distributor grid blocks are supported.It further emerges that the heat storage device 40 preferably has distributor grid blocks which have the same arrangement of heat exchange channels as the grid blocks and are arranged without gaps between the cold fluid chamber and the stack such that their heat exchange channels are aligned with those of the grid blocks and thus form a section of the continuous heat exchange channels, and wherein the distributor grid blocks have transverse channels on their side facing the cold fluid chamber, which connect adjacent rows of the heat exchange channels of the distributor grid blocks, each heat exchange channel being assigned to a transverse channel, such that a support rib is formed between each pair of adjacent transverse channels, on which the distributor grid blocks are connected to the cold fluid chamber. Furthermore, a distributor grid block is formed in which transverse channels running along the underside of the distributor grid block are provided, connecting adjacent rows of the heat exchange channels of the grid blocks to each other, and each heat exchange channel is assigned to only one transverse channel, such that a support rib with a bearing surface is formed between each pair of adjacent transverse channels.Figure 7 shows a 3D view of a section of a throttle grid block 54 according to the invention, which, with the exception of the heat exchange channels 90, is designed identically to the distributor grid block 53. To simplify the figure, the projections 72 of the grid blocks 52 and distributor grid blocks 53 have been omitted – however, the throttle grid blocks 54 can be stacked gap-free in the same way as these. On the outer sides of the throttle grid block 54 there are grooves 90' which correspond to one half of a heat exchange channel 90, as is the case with the grooves 71' of the grid blocks 52 and distributor grid blocks 53 - if two throttle grid blocks 54 are positioned next to each other without gaps, two opposing grooves 90' form a heat exchange channel 90.The heat exchange channels 90 of the throttle grid block 54 differ from the heat exchange channels 71 of a grid block 52 or a distributor grid block 53 in their diameter - apart from that, they are designed and arranged in the same way as is the case with a grid block 52 or a distributor grid block 53.The figure shows that the diameter of a heat exchange channel 90 on the underside 81 of the throttle grid block 54 is smaller than on its top side 91, which corresponds to a narrowing of the heat exchange channel 90, wherein the transition from the smaller to the larger diameter can consist, for example, of a conical step 94. The lower section 92 of the throttle grid block between the steps 94 and the transverse channels 84 thus corresponds to a throttle arrangement 22 (Figure 2a), which throttles the fluid in the same way as the perforated aperture 29, with the same effect, see the description of Figures 2a and b, 3b and c as well as 5a and b.A throttle grid block for a layered heat storage device is obtained, with a base surface and a surface and side surfaces and with heat exchange channels 71,71* extending from the base surface to the surface, characterized in that the heat exchange channels 71,71* have a smaller throttle diameter in a narrowed section extending from the base surface.Depending on the design of the heat storage device in the specific case, the person skilled in the art can provide the throttling arrangement 22 with a perforated aperture 29 and with a layer of throttle grid blocks 54 (see Figure 3b) or alternatively only with a perforated aperture (Figure 3b in which the layer 52 contains only distributor grid blocks 53) or only with throttle grid blocks if, in an arrangement according to Figure 3b, the perforated aperture 29 is omitted and the layer 52 contains only throttle grid blocks). Depending on the design of the heat storage device, the throttling of the fluid (between 30% and 90% of the total pressure drop) is achieved either entirely by a perforated orifice 29 or by throttle grid blocks 54, or partially by a perforated orifice 29 and partially by throttle grid blocks 54.It should be noted that the layer 52 of throttle grid blocks 54 according to Figure 3b can in principle also be arranged at the top of the stack 51 or in the stack 52 at any height. However, the position in the discharge flow direction in front of stack 51 appears particularly advantageous, since the slightly disturbing influence of the possibly colder outer side of stack 51 on the thermocline is then eliminated, see the description for Figure 2b. This preferably results in a heat storage device in which the throttling arrangement is provided between the connection for the supply of cold fluid and the stack.A method is derived according to claim 1 wherein the fluid is guided upstream of the heat-exchanging solid during the discharge of the heat storage device through throttle grid blocks which have heat exchange channels which in turn are aligned with heat exchange channels provided in the solid, wherein aligned heat exchange channels together each form a heat exchange channel through which the solid passes, and wherein the heat exchange channels of the throttle grid blocks have a constriction designed as a throttling, such that at least part of the throttling takes place through the throttle grid blocks. Furthermore, a heat storage device is obtained in which the throttling arrangement comprises throttle grid blocks which have the same arrangement of heat exchange channels as the grid blocks and are arranged without gaps between the cold fluid chamber and the stack in such a way that their heat exchange channels are aligned with those of the grid blocks and thus form a section of the continuous heat exchange channels, and wherein the heat exchange channels of the throttle grid blocks have a constriction designed as a throttling, such that at least part of the pressure drop of the fluid during throttling is caused by the throttle grid blocks arranged on the stack. Finally, a throttle grid block for a heat storage device is obtained, whereby the heat exchange channels have a smaller throttle diameter in a narrowed section extending from the base surface. This means that preferably the heat exchange channels of the distributor grid blocks have a constriction designed as a throttle, such that at least part of the pressure drop of the fluid is caused by the throttle grid blocks arranged on the stack. With reference to the perforated aperture 29 in a heat storage device according to the invention, this means that the throttling arrangement has a perforated aperture which is designed in such a way that during the discharge of the heat storage device the pressure drop in the fluid flowing through the perforated aperture corresponds at least partially to the pressure drop caused by the throttling.In summary, a heat storage device according to the invention has a connection for supplying cold, heat-transporting fluid and a connection for discharging the warm, heat-transporting fluid after absorbing heat, and a heat-storing solid arranged between the connections, having fluid channels, and further a cold fluid chamber for supplying fluid to the stack, wherein the solid is designed as a gap-free stack of grid blocks having parallel heat exchange channels and being stacked such that the heat exchange channels of successive grid blocks are aligned with each other and aligned heat exchange channels together form a continuous heat exchange channel running through the stack, wherein a throttling arrangement is provided between the inflow connection and the outflow connection for discharging fluid, which is designed such that, during operation of the heat storage device during its discharge, the pressure drop in the fluid through the throttling arrangement is 30% to 90% of the total pressure drop in the fluid between the connections.  

Claims

1. A method for discharging heat from a layered heat storage device which has a cold side and a warm side and through which a heat-transporting fluid flows and which has a filling of heat-storing solid matter which is located in the fluid flow and exchanges heat therewith, wherein the fluid between a connection for the inflow of cold heat-transporting fluid and a connection for the outflow of the heat-transporting fluid which is warm after absorbing heat has a pressure drop, characterized in that, during the discharge from the heat storage device, the fluid is conducted in the discharge flow direction between the inflow connection and the outflow connection through a throttle arrangement and is throttled therein in such a way that the pressure drop due to the throttling is 30% to 90% of the total pressure drop in the fluid between the two connections.2.The method according to claim 1, wherein the fluid is guided during the discharge of the heat storage device from the inflow connection to the solid matter and then through separate heat exchange channels arranged in the solid, 3.The method according to claim 1, wherein the fluid is directed via a cold fluid chamber having a fluid line arrangement to the solid matter and preferably to heat exchange channels arranged in the solid matter.4.The method according to claim 1, wherein the pressure drop in the fluid caused by the throttling is more than 40%, preferably more than 50%, particularly preferably more than 60%, most preferably more than 70%, or more than 80%.5.The method according to claim 1, wherein preferably, for at least partial throttling, the fluid flow is directed through a perforated aperture, preferably upstream of the solid, located in the fluid flow, which throttles it. 6.The method according to claim 2, wherein the discharge flow direction in vertically extending heat exchange channels is directed from bottom to top. 7.The method according to claim 3, wherein the fluid to be heated is directed into a fluid pressure equalization chamber in the fluid line arrangement and is at least partially throttled at its outlet. 8.The method according to claim 1, wherein the fluid is preferably guided through a solid formed as a stack of grid blocks, wherein the grid blocks have parallel, separate heat exchange channels, preferably with the same cross-section and preferably with the same distance from each other, and wherein the grid blocks are aligned with each other in such a way that the heat exchange channels of successively lying grid blocks are aligned with each other in the flow direction, so that aligned heat exchange channels together each form a straight, uninterrupted heat exchange channel through the stack, which is separated from the other heat exchange channels.9.The method according to claim 1, wherein the fluid is guided upstream of the heat-exchanging solid through throttle grid blocks which have heat exchange channels which in turn are aligned with heat exchange channels provided in the solid, wherein aligned heat exchange channels together each form a heat exchange channel passing through the solid, and wherein the heat exchange channels of the throttle grid blocks have a constriction designed as a throttling, such that at least part of the throttling takes place through the throttle grid blocks. 10.The method according to claim 1, wherein the fluid is preferably guided through distributor grid blocks in front of the heat-storing solid, the distributor grid blocks having heat exchange channels which in turn are aligned with heat exchange channels provided in the solid, wherein aligned heat exchange channels together each form a heat exchange channel through this solid, and wherein furthermore the upstream inlet side of the distributor grid blocks in the discharge flow direction has transverse channels which only connect adjacent rows of heat exchange channels to each other, wherein each heat exchange channel is assigned to a transverse channel, such that a support rib is formed between each pair of adjacent transverse channels, on which the distributor grid blocks are supported. 11.The method according to claim 10, wherein the heat exchange channels of the distributor grid blocks have a constriction designed as a throttle such that at least part of the throttling takes place through the distributor grid blocks. 12.The method according to claim 1 or 2, wherein the fluid is passed through heat exchange channels arranged within the solid, which have the same cross-sectional area and length and are arranged at equal distances from one another.13.A layered heat storage device for carrying out the method according to claim 1, having a connection for supplying cold, heat-transporting fluid and a connection for discharging the warm, heat-transporting fluid after absorbing heat, a heat-storing solid arranged between the connections, having fluid channels, and a cold fluid chamber for supplying fluid to the stack, characterized in that the solid is designed as a gap-free stack of grid blocks having parallel heat exchange channels and being stacked such that the heat exchange channels of successive grid blocks are aligned with each other and aligned heat exchange channels together form a continuous heat exchange channel running through the stack, wherein a throttling arrangement is provided between the inflow connection and the outflow connection for discharging fluid, which is designed such that, during operation of the heat storage device during its discharge, the pressure drop in the fluid through the throttling arrangement is 30% to 90% of the total pressure drop in the fluid between the connections.14.The heat storage device according to claim 13 wherein the throttling arrangement is provided between the connection for the supply of cold fluid and the stack.15.The heat storage device according to claim 13, wherein the throttling arrangement is designed such that the pressure drop in the fluid due to the throttling is more than 40%, preferably more than 50%, particularly preferably more than 60%, most preferably more than 70% or more than 80%. 16.The heat storage device according to claim 13, wherein the throttling arrangement has a perforated aperture which is designed such that during the discharge of the heat storage device the pressure drop in the fluid flowing through the perforated aperture corresponds at least partially to the pressure drop caused by the throttling.17.The heat storage device according to claim 13, wherein the heat exchange channels of the stack run vertically and the connection for the supply of cold, heat-carrying fluid is arranged below the stack.

18. The heat storage device according to claim 13, wherein the throttling arrangement is arranged below the stack.

19. The heat storage device according to claim 13, wherein the cold fluid chamber has a number of adjacent supports arranged below the stack, which bear the weight of the stack, wherein the space between the supports forms a number of fluid channels which serve from one side for the fluid supply under and into the stack and are closed on their other side, and at the top of which the openings of the continuous heat exchange channels are located.20.The heat storage device according to claim 19, wherein the supports are designed as parallel adjacent U-beams with upwardly directed U-legs, wherein the weight of the stack acts on the upper ends of the U-legs, and wherein the space between the U-legs forms the horizontally extending fluid channels, on the upper side of which the openings of the continuous heat exchange channels are located, and preferably the U-beams are arranged at a distance from each other via spacer elements, wherein the width of the spacer elements corresponds to the width of the connecting sections of the U-beams. 21.The heat storage device according to claim 19, wherein the throttling arrangement has a perforated aperture that is arranged on the side of the fluid inlet below the stack at the end face of the fluid channels and operatively covers the inlet to the fluid channels. 22.The heat storage device according to claim 13, wherein a pressure equalization chamber is provided between the connection for the fluid supply and the throttling arrangement.23.The heat storage device according to claim 13, wherein the throttling arrangement comprises throttle grid blocks, which have the same arrangement of heat exchange channels as the grid blocks and are arranged between the cold fluid chamber and the stack without any gaps, such that their heat exchange channels are aligned with those of the grid blocks and thus form a section of the continuous heat exchange channels, and wherein the heat exchange channels of the throttle grid blocks comprise a constriction formed as a throttle, such that at least a portion of the pressure drop of the fluid resulting from the throttling is caused by the throttle grid blocks arranged on the stack.24.The heat storage device according to claim 13, wherein the has distributor grid blocks which have the same arrangement of heat exchange channels as the grid blocks and are arranged without gaps between the cold fluid chamber and the stack such that their heat exchange channels are aligned with those of the grid blocks and thus form a section of the continuous heat exchange channels, and wherein the distributor grid blocks have transverse channels on their side facing the cold fluid chamber, which connect adjacent rows of the heat exchange channels of the distributor grid blocks, each heat exchange channel being assigned to a transverse channel, such that a support rib is formed between each pair of adjacent transverse channels, on which the distributor grid blocks are connected to the cold fluid chamber. 25.The heat storage device according to claim 23, wherein the heat exchange channels of the distributor grid blocks have a constriction designed as a throttle such that at least part of the pressure drop of the fluid of the throttling takes place through the distributor grid blocks arranged on the stack. 26.A stackable grid block for a layered heat storage device according to claim 11, comprising a base surface and a surface and side surfaces and heat exchange channels extending from the base surface to the surface, characterized in that these are arranged parallel and at equal distances from each other, have a round cross-section, an effective diameter of 50 mm or less, and in that the distance between adjacent heat exchange channels is 70 mm or less.27.The grid block according to claim 26, wherein the diameter of the heat exchange channels is 25 mm or less, or 20 mm or less, preferably 15 mm or less, most preferably 10 mm or less.28.The grid block according to claim 26, wherein the distance between adjacent heat exchange channels is 50 mm or less, more preferably 30 mm or less, and more preferably 10 mm or less, and at least three times the average grain diameter of the material of the grid block.29.The throttle grid block according to claim 26, wherein the heat exchange channels have a smaller throttle diameter in a narrowed section extending from the base surface.30.The distributor grid block according to claim 26, wherein transverse channels running along the underside of the distributor grid block are provided, connecting adjacent rows of the heat exchange channels of the grid blocks to each other, and each heat exchange channel is assigned to one transverse channel, such that a support rib with a bearing surface is formed between each pair of adjacent transverse channels.

31. A distributor grid block for a layered heat storage device, with a base surface and a surface and side surfaces, and with heat exchange channels (71', 71*) extending from the base surface to the surface, characterized in that the base surface is designed to support the distributor grid block in operation on parallel U-shaped legs (61', 61"), which form fluid channels (60), wherein transverse channels (82) are provided in the base surface which can be connected to the fluid channels (60), and wherein the transverse channels (82) are designed such that, in operation, with the distributor grid block supported on the U-shaped legs, heat exchange channels (71, 71*) ending at the location of the legs (61, 61') can be flown through by fluid in the same way as any of the heat exchange channels (71, 71*).

32. The distributor grid block according to claim 31, wherein each heat exchange channel (71, 71*) is associated with a transverse channel (82), such that a support rib (83) with a bearing surface is formed between each pair of adjacent transverse channels (82) by these.

33. A throttle grid block for a layered heat storage device, with a base surface and a surface and side surfaces and with heat exchange channels (71,71*) extending from the base surface to the surface, characterized in that the heat exchange channels (71,71*) have a smaller throttle diameter in a narrowed section extending from the base surface.

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