US20080210218A1 - Dynamic heat accumulator and method for storing heat - Google Patents

Dynamic heat accumulator and method for storing heat Download PDF

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Publication number
US20080210218A1
US20080210218A1 US12/011,188 US1118808A US2008210218A1 US 20080210218 A1 US20080210218 A1 US 20080210218A1 US 1118808 A US1118808 A US 1118808A US 2008210218 A1 US2008210218 A1 US 2008210218A1
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Prior art keywords
accumulator
medium
heat
elements
heat accumulator
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Abandoned
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US12/011,188
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English (en)
Inventor
Mathias Hanel
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KBA Metalprint GmbH and Co KG
Kraftanlagen Muenchen GmbH
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KBA Metalprint GmbH and Co KG
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Assigned to KBA-METALPRINT GMBH reassignment KBA-METALPRINT GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: HANEL, MATHIAS
Publication of US20080210218A1 publication Critical patent/US20080210218A1/en
Assigned to KBA-METALPRINT GMBH, KRAFTANLAGEN MUNCHEN GMBH reassignment KBA-METALPRINT GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: DOERBECK, TILL
Abandoned legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D17/00—Regenerative heat-exchange apparatus in which a stationary intermediate heat-transfer medium or body is contacted successively by each heat-exchange medium, e.g. using granular particles
    • F28D17/02—Regenerative heat-exchange apparatus in which a stationary intermediate heat-transfer medium or body is contacted successively by each heat-exchange medium, e.g. using granular particles using rigid bodies, e.g. of porous material
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D17/00—Regenerative heat-exchange apparatus in which a stationary intermediate heat-transfer medium or body is contacted successively by each heat-exchange medium, e.g. using granular particles
    • F28D17/04—Distributing arrangements for the heat-exchange media

Definitions

  • the present disclosure relates to a heat accumulator having a heat accumulator structure.
  • Heat accumulators have a housing that is filled with a heat-storing material, in particular a ceramic material.
  • a heat-storing material in particular a ceramic material.
  • a hot medium flow is conducted through the material so that the latter heats up.
  • a cold medium flow is conducted through the hot material, so that the medium flow heats up and is available as a hot medium flow.
  • Ceramic honeycombs in particular are used for the ceramic material.
  • Fill and/or plates can also be used. They have a plurality of through-flow channels for the medium. Heat is added and heat is removed as a function of the energy flows during charging and discharging, and these energy flows can be of different magnitudes. This can cause local temperature increases in the heat accumulator structure of the heat accumulator.
  • a heat profile occurs, that is, the heat-storing material on the input side has the highest temperature.
  • the temperature of the heat-storing material decreases in the direction of the output of the accumulator. The same applies for the temperature distribution when heat is removed. If the accumulator is idle, that is, if no heat energy is being added or removed, the temperature equalizes from the warm side to the cold side across the volume of the heat accumulator structure.
  • the underlying object of the invention is to create a heat accumulator having a heat accumulator structure in which a desired in particular horizontal and/or vertical temperature distribution state is maintained, even during lengthy idle periods. In particular a reproducible state is maintained so that optimum operation with high efficiency is possible.
  • the heat accumulator structure of the heat accumulator has at least two accumulator elements through which a medium flows for charging and that thus each form a “hot end” and a “cold end” by temperature layering, a medium rinse device being provided that in a rinse operation for the heat accumulator produces at least one cold medium rinse flow and introduces it into the cold end of at least one of the accumulator elements, the hot medium rinse flow exiting from the hot end of the aforesaid accumulator element entering via at least one rinse path the hot end that is in the charged state and that is of the at least one other accumulator element.
  • the cold end of the at least one accumulator element is acted upon by means of the medium rinse flow, which in particular is produced by the medium rinse device when the heat accumulator is in the idle state.
  • the rinse medium flow passes through the accumulator element in the opposite direction to the medium charging flow.
  • the medium charging flow produces a heat profile, that is, the accumulator element is hotter in the input zone than in the output zone. This results in temperature layering, starting from the hot end to the cold end, the latter representing the output end of the accumulator element for the medium charging flow.
  • the medium rinse flow which relative to the medium charging flow has a lower temperature, that is, is “cold”, is now introduced into the cold end of the charged accumulator element, the medium rinse flow heats up as it passes through the accumulator element and exits from the hot end of the aforesaid accumulator element as a hot medium rinse flow.
  • This hot medium rinse flow is now introduced via the at least one rinse path into the hot end that is in the charged state and that is of the at least one other accumulator element.
  • the hot end of this other accumulator element is the end that a hot medium charging flow acts upon during normal charging.
  • the “hot end” state only exists in the other accumulator element if there has been a corresponding charging.
  • the wording “hot end that is in the charged state” was selected, which thus does not mean that when the hot medium rinse flow is introduced into the (hot) end of the other accumulator element there must be a charged accumulator element, that is, a hot end having a high temperature. Therefore this can also be an uncharged or partly charged other accumulator element, that is, an accumulator element that does not have any temperature profile or that has a corresponding pronounced temperature profile.
  • the other accumulator element also has a charged or at least partly charged state, that is, that the hot medium rinse flow exiting from the one accumulator element meets the hot end of the other accumulator element.
  • the available temperature layering produced by the charging process remains present in a first accumulator element because the cold end is “cooled” by the cold medium rinse flow and the hot medium rinse flow exiting from the hot end is supplied to the hot end of the other, second accumulator element. Consequently the hot medium rinse flow in the second accumulator element also ensures that its temperature profile, that is, its temperature layering, is maintained, because the hot medium rinse flow cools off while it passes through the other accumulator element so that the other accumulator element has a higher temperature on the input side than on the output side with respect to the flow-through direction of the medium rinse flow.
  • this rinsing with the medium rinse flow is repeated during an extended idle period, the cold end of the other, second accumulator element then being acted on by a cold medium rinse flow that exits from the hot end of the second accumulator element and is conducted to the hot end of the one, first accumulator element.
  • Equalization of the temperatures of the accumulator elements is therefore prevented so that there are reproducible conditions and largely uniform temperatures are available for the charging and discharging, that is, the exit temperature of the charging flow from the cold end of the at least one, first accumulator element is always approximately the same and the removal temperature during discharging of the at least one, first accumulator element is also reproducible so that downstream heat consuming processes can be conducted with optimum efficiency.
  • the hot ends form upper ends of the accumulator elements and the cold ends form lower ends of the accumulator elements.
  • the accumulator elements consequently have a vertical extension, the medium charging flow that is introduced into the upper ends exiting from the lower ends.
  • the cold medium rinse flow enters into the lower end of at least one accumulator element.
  • the hot medium rinse flow produced thereby exits from the upper end of this accumulator element and is introduced into the upper end of at least one additional accumulator element and exits from the lower end of the latter accumulator element as a cold medium rinse flow.
  • the rinse path connecting the at least two accumulator element [sic] at their hot ends is embodied as a common connecting chamber arranged above the accumulator elements and extending at least partially across them.
  • the accumulator elements are communicatingly connected to one another via the common connecting chamber so that the hot medium rinse flow can enter into at least one accumulator element, specifically its hot end, from at least one other accumulator element.
  • the first medium openings form first heat input openings when the heat exchanger is charging and form first heat output openings when the heat accumulator is discharging.
  • the connecting chamber preferably has the first medium openings. Consequently the medium charging flow can be supplied to the corresponding accumulator element from above via the first medium opening allocated to each accumulator element, the medium charging flow exiting downward from the first medium opening that forms a first heat input opening, passing through the connecting chamber in a largely vertical manner, and meeting the upper end of the aforesaid associated accumulator element.
  • a cold medium flow is supplied to the lower end of the accumulator element in question.
  • a cold medium rinse flow flows into the cold, lower end of at least one charged accumulator element and exits from the upper, hot end of this accumulator element.
  • the hot medium rinse flow is deflected in the connecting chamber such that it is supplied to the hot end of at least one other accumulator element for instance during the course of a 180° deflection.
  • a first blocking/cross-section adjustment element is upstream of each of the first medium openings, as seen from the direction of flow of the medium during charging. Furthermore, it is advantageous when the first blocking/cross-section adjustment elements are upstream of the connecting chamber as seen from the direction of flow of the medium during charging.
  • the first blocking/cross-section adjustment elements are upstream of the connecting chamber as seen from the direction of flow of the medium during charging.
  • Charging or non-charging of the associated accumulator element occurs depending on whether the first blocking/cross-section adjustment elements of corresponding accumulator elements are opened or closed.
  • the charging process can be controlled or regulated by intentionally supplying the medium charging flow to the desired accumulator elements.
  • a closed blocking/cross-section adjustment element of an accumulator element leads to the hot medium rinse flow exiting from the associated accumulator element not being supplied to an external heat consumer, but rather being deflected via the connecting chamber and being supplied to at least one other accumulator element.
  • the degree of blocking or opening of a blocking/cross-section adjustment element always leads to the associated medium flow being adjustable in terms of its volume flow.
  • the first blocking/cross-section adjustment elements can preferably be embodied as dampers.
  • the embodiment as dampers represents a robust and simple solution.
  • At least one second medium opening is provided beneath each of the accumulator elements.
  • the second medium openings form medium return openings for the medium charging flow in the cycle.
  • the second medium openings form medium supply openings.
  • the medium charging flow or at least a portion thereof passes through at least one accumulator element and exits from the lower, cold end of the accumulator element and travels to the associated second medium opening. From there the now cold medium charging flow is returned to a heat source in order to be reheated so that it can again be conducted to the heat accumulator as a hot medium charging flow. Consequently there is a medium cycle.
  • the function of the heat accumulator is also conceivable in an exemplary embodiment in which the cycle is not closed.
  • a hot medium discharging flow exits from the upper, hot end of the accumulator element in question and is supplied to a heat consumer.
  • the heat consumer cools the medium discharging flow.
  • the latter is then returned to the heat accumulator in that it enters into the lower, cold end of the associated accumulator element through the second medium opening, that is, the medium supply opening, and passes upward through the accumulator element, whereby it is heated and can be supplied again to the heat consumer as a hot medium discharging flow.
  • each at least two accumulator elements is adjacent to an individual chamber, the individual chambers being arranged beneath the accumulator elements.
  • the individual chambers ensure that the medium can flow through the entire cross-section of the respective associated accumulator element.
  • the individual chambers consequently represent medium distribution chambers, both for charging and for discharging operations, as well as for rinsing operations.
  • Each area of the connecting chamber disposed above an accumulator element acts in a similar fashion.
  • a second blocking/cross-section adjustment element is preferably upstream of each of the second medium openings as seen in the direction of flow of the medium during discharge.
  • the second blocking/cross-section adjustment elements is upstream of the individual chambers as seen in the direction of flow of the medium during discharge.
  • the associated medium charging flow or medium discharging flow exits laterally from the individual chambers or enters the individual chambers laterally.
  • the individual chambers have the second medium openings. These are embodied on the sides of the individual chambers.
  • the individual chambers preferably have walls to which the second blocking/cross-section adjustment elements are allocated.
  • the medium preferably flows laterally into the individual chambers or out of the individual chambers.
  • the accumulator elements are arranged in accumulator chambers of a housing of a heat accumulator.
  • the accumulator chambers are embodied adjacent to one another and are separated from one another by means of at least one common separating wall.
  • the separating wall is preferably a vertical wall.
  • the individual chambers are also preferably adjacent to one another and are separated from one another by means of a common separating wall.
  • Gas in particular air, is preferably used for the medium.
  • the accumulator elements preferably have ceramic material that guarantees high heat accumulating capacity.
  • the accumulator elements in particular constitute individual elements. For instance saddle shapes and/or sphere shapes can be used for fill for individual elements.
  • honeycombs In addition or alternatively the individual elements can preferably be embodied as honeycombs.
  • the honeycombs have medium through-flow channels so that there are very large heat exchange surface areas with low flow losses.
  • the invention furthermore relates to a method for storing heat in a heat accumulator that has accumulator elements, in particular in a heat accumulator as described in the foregoing, having the steps: introducing a hot medium into at least one accumulator element for charging and embodying one hot end and one cold end due to temperature layering in the accumulator element, introducing at least one cold medium rinse flow into the cold end of the accumulator element and introducing the hot medium rinse flow exiting therefrom from the hot end of the accumulator element into a hot end, in the charged state, of at least one additional accumulator element.
  • the introduction of the at least one cold medium rinse flow is performed multiple times such that heat is transported back and forth between at least two accumulator elements by means of the hot medium rinse flow.
  • the heat is thus transmitted from the one accumulator element to the other accumulator element and then again from the one accumulator element to an accumulator element and so on. This always maintains the temperature layering, that is, the temperature profile of the accumulator element in question.
  • FIG. 1 depicts a heat accumulator system having a heat accumulator
  • FIG. 2 is a perspective elevation of the heat accumulator from FIG. 1 ;
  • FIG. 3 depicts the representation from FIG. 2 at a slightly oblique angle and from below;
  • FIG. 4 is a block diagram of the heat accumulator system in accordance with FIG. 1 ;
  • FIG. 5 is a perspective elevation of another exemplary embodiment of a heat accumulator
  • FIGS. 6 through 8 are two side views and a top view of the heat exchanger in accordance with FIG. 5 .
  • FIG. 1 depicts a heat accumulator system 1 that has a heat accumulator 2 .
  • the heat accumulator 2 is consequently operated by means of a heat source 5 .
  • the heat accumulator 2 can also be used in conjunction with a plurality of heat energy sources, which heat energy sources also may be different from one another, without departing from the subject-matter of the invention.
  • the heat source 5 is attached to a medium cycle, air being used as the medium.
  • the medium cycle 6 Disposed in the medium cycle 6 are two fans 7 and 8 , at least one fan 7 or 8 transporting air to the heat source 5 via a line 9 while heat is added using the heat source 5 .
  • the air is very intensely heated in the heat source 5 and the heated air is supplied to a branch 11 via a lien 10 .
  • a line 12 that is attached to a heat absorber 13 goes out from the branch 11 .
  • the hot air preferably has a temperature of several hundred degrees Celsius at in particular 1 bar.
  • the air leaving the heat absorber 13 which is cooled and has a pressure of preferably 1 bar, is again supplied to the heat source 5 by means of the fan 8 and/or 7 .
  • a branch 19 Disposed between the two fans 7 and 8 is a branch 19 from which an accumulator line 20 runs that leads to the heat accumulator 2 . Furthermore branching from the branch 11 is an accumulator line 21 that also leads to the heat accumulator 2 .
  • the accumulator line 20 leads to the “cold end” 22 and the accumulator line 21 leads to the “hot end” 23 of the heat accumulator 2 .
  • the significance of these terms shall be explained in greater detail in the following.
  • the hot air flow that heats the heat accumulator 2 cools as it passes through the heat accumulator 2 from for instance approximately 700° C. (the temperature ranges in particular from 300° C. to 1000° C.) to for instance 150° C. (the temperature ranges in particular from 50° C. to 250° C.) and leaves the cold end 22 of the heat accumulator 2 via the accumulator line 20 .
  • the air passing through the heat accumulator 2 is resupplied to the heat source 5 .
  • the heat absorber 13 is not active for certain operational reasons.
  • the heat accumulator 2 is discharged during periods when no heat energy or insufficient heat energy is delivered by the heat source 5 .
  • the fan 7 is turned off and the heat source 5 is separated from the cycle by closing two valves 24 .
  • the fan 8 is active and supplies air to the cold end 22 of the heat accumulator 2 via the accumulator line 20 .
  • the air passes through the heat accumulator 2 and heats up for instance preferably to approximately 700° C. and leaves the heat accumulator 2 via the accumulator line 21 .
  • the hot air then flows via the line 12 to the heat absorber 13 (for instance heat exchanger) and from there back to the fan 8 . It is clear from this that the heat absorber 13 can also be operated during periods in which no heat energy or insufficient heat energy is delivered by the heat source 5 .
  • FIGS. 2 and 3 illustrate the structure of the heat accumulator 2 using an exemplary embodiment.
  • the heat accumulator 2 has a housing 25 that is divided into a plurality of accumulator chambers 26 through 29 .
  • Four accumulator chamber 26 through 29 are provided in the exemplary embodiment depicted.
  • Disposed in each accumulator chamber 26 through 29 is an accumulator element 30 through 33 that is able to accumulate store energy.
  • the accumulator elements 30 through 33 preferably comprise ceramic material, for instance ceramic honeycombs, that is, the accumulator elements 30 through 33 are made up of individual elements.
  • the accumulator chambers 26 through 29 are arranged adjacent to one another and are separated from one another by means of separating walls 34 through 37 .
  • Embodied in the housing 25 above the accumulator chambers 26 through 29 is a common connecting chamber 38 that creates a connection for the medium, in particular the aforesaid air, among the accumulator elements 30 through 33 .
  • a first medium opening 39 through 42 is disposed above each accumulator element 30 through 33 , the first medium openings 39 through 42 being embodied in a cover 43 for the connecting chamber 38 .
  • the accumulator line 21 divides into four individual lines 44 through 47 , first blocking/cross-section adjustment elements 48 through 51 being arranged in the individual lines 44 through 47 .
  • the first blocking/cross-section adjustment elements 48 through 51 are embodied as dampers, in particular double baffles.
  • the individual lines 44 through 47 are attached to the first medium openings 39 through 42 , respectively.
  • Individual chambers 52 through 55 are disposed beneath each accumulator element 30 through 33 or beneath the accumulator chambers 26 through 29 , whereby in terms of flow engineering there is a connection between each corresponding accumulator chamber 26 through 29 and the individual chamber 52 through 55 disposed therebeneath.
  • the individual chambers 52 through 55 are adjacent to one another and are separated from one another by means of common separating walls 56 through 59 .
  • a deflection chamber 60 through 63 is allocated to each individual 52 through 55 , the deflection chambers 60 through 63 being disposed laterally on the housing 25 , each in the area of its associated individual chamber 52 through 55 .
  • Each individual chamber 52 through 55 is connected to an associated deflection chamber 60 through 63 via a second medium opening 64 through 67 .
  • the deflection chambers 60 through 63 have floors 68 through 71 that are provided with second blocking/cross-section adjustment elements 72 through 75 .
  • the second blocking/cross-section adjustment elements 72 through 75 are preferably embodied as disk valves.
  • the accumulator line 20 (not shown in FIGS. 2 and 3 ) is attached to the second blocking/cross-section adjustment elements 72 through 75 .
  • deflection chambers 76 through 79 are deflection chambers 76 through 79 , each of which is connected to its associated individual chamber 52 through 55 in terms of flow engineering.
  • the individual chambers 52 through 55 are each connected via medium rinse openings 80 through 83 to respective associated deflection chambers 76 through 79 .
  • the deflection chambers 76 through 79 have floors 84 through 87 that are provided with third blocking/cross-section adjustment elements 88 through 91 and attached to a medium rinse line 92 ( FIG. 4 ) that is not shown in FIGS. 2 and 3 .
  • the third blocking/cross-section adjustment elements 88 through 91 are preferably embodied as disk valves.
  • FIG. 4 uses a block diagram to illustrate the heat accumulator 1 .
  • the heat source 5 and the heat absorber 13 are drawn in broken lines as boxes.
  • further valve 93 are provided that cannot be seen in FIG. 1 and that are allocated to the heat absorber 13 .
  • the valve 24 allocated to the fan 7 is arranged downstream of the fan 7 , rather than upstream thereof, but this does not represent a difference in terms of function.
  • the medium rinse line 92 is fed by a medium rinse fan 94 that can supply ambient air to the third blocking/cross-section adjustment elements 88 through 91 via an air filter 95 .
  • the heat source 5 delivers heat energy for heating up the air that forms the medium and that is caused to circulate in the cycle by means of the fan 7 and/or the fan 8 .
  • the hot air is preferably 700° C. and preferably is at 1 bar pressure. It is returned via the line 10 , the open valve 24 , the line 12 , and the open valve 93 to the heat absorber 13 and from there via the fan 8 , the open valve 93 , the fan 7 , the open valve 24 , and the line 9 back to the heat source 5 . However, it is also possible to release the air directly into the environment via the fan 7 . After the hot air has left the heat absorber 13 it is preferably still 150° C. at a pressure of 1 bar.
  • the heat absorber 13 does not require all of the heat energy, some of the hot air is deflected at the branch 12 and supplied via the accumulator line 2 to at least one of the accumulator elements 30 through 33 .
  • the accumulator element 30 through 33 or accumulator elements 30 through 33 is/are selected by opening or partly opening the first blocking/cross-section adjustment elements 48 through 51 . For instance, if all of the first blocking/cross-section adjustment elements 48 through 51 are opened, a corresponding partial hot air flow is supplied via the common connecting chamber 38 to each of the accumulator elements 30 through 33 . Because the hot air flows through the accumulator elements 30 through 33 , the latter are heated up and a temperature profile is created.
  • each accumulator element 30 through 33 there is consequently a temperature profile across the length of the respective accumulator element 30 through 33 , the hot end having a temperature of preferably approximately 700°, and the cold end having a temperature of approximately 150° C., each at 1 bar.
  • This temperature profile can also be called temperature layering of the respective accumulator element 30 through 33 .
  • the hot air flowing through each accumulator element 30 through 33 leaves the heat accumulator 2 via the respective associated individual chambers 52 through 55 and the corresponding opened second blocking/cross-section adjustment element 72 through 75 and travels via a common valve 96 in the accumulator line 20 and via the branch 19 back to the collector 5 , in order to be reheated there.
  • valves 24 are closed for discharging the heat accumulator 2 so that the heat energy is delivered only by the heat accumulator 2 .
  • This operation can occur for instance when no energy is available, that is, the heat generator 5 is not providing any heat energy.
  • the fan 8 is operated so that a corresponding air flow is supplied via the line 20 and the valve 96 and the second blocking/cross-section adjustment elements 72 through 75 and the respective individual chambers 52 through 55 to the cold ends 22 of the accumulator elements 30 through 33 .
  • the fan 8 is operated so that a corresponding air flow is supplied via the line 20 and the valve 96 and the second blocking/cross-section adjustment elements 72 through 75 and the respective individual chambers 52 through 55 to the cold ends 22 of the accumulator elements 30 through 33 .
  • the fan 8 is operated so that a corresponding air flow is supplied via the line 20 and the valve 96 and the second blocking/cross-section adjustment elements 72 through 75 and the respective individual chambers 52 through 55 to the cold ends 22 of the accumulator elements 30 through 33 .
  • the latter heat up according to the temperature profile in each accumulator element 30 through 33 so that hot air leaves each accumulator element 30 through 33 at a temperature of for instance 700° and travels through the common connecting chamber 38 and the opened first blocking/cross-section adjustment elements 48 through 51 , the accumulator line 21 , and the line 12 to the heat absorber 13 . Then the air that has been cooled to approximately 150° C. because it has passed through the heat absorber 13 is available to pass through the cycle again.
  • Heat energy can be provided to the absorber and collected in the heat accumulator 2 in parallel. It is also possible to provide heat energy to the absorber and remove it from the heat accumulator 2 in parallel.
  • the temperature layering is not equalized during an idle period for the heat accumulator 2 that is when heat energy is neither supplied thereto nor removed therefrom. If left alone, the temperature layering within the accumulator elements 30 through 33 would slowly even out so that there is no longer a temperature gradient (in this exemplary instance 700° C. at the hot end 23 and 150° C. at the cold end 22 ). However, the consequence of this would be that the accumulator would no longer be fully utilizable in terms of capacity, which would substantially reduce the efficiency of the entire system. However, due to the option of rinsing with a medium rinse device 98 it is provided that the desired temperature layering can be maintained while the heat accumulator 2 is idle.
  • ambient air is suctioned by means of the medium rinse fan 94 via the air filter 96 and, with only a very low volume flow, that is a low throughput, is supplied for instance via the opened third blocking/cross-section adjustment element 91 and the associated individual chamber 55 to the cold end 22 of the accumulator element 33 .
  • This air passes through the accumulator element 33 from below to above and in doing so heats up in the lower area for instance to approximately 150° C. and in the upper area, that is at the hot end 23 , for example to 700° C.
  • the air then enters the connecting chamber 38 at the upper end 23 and is supplied from there for instance to the accumulator element 31 .
  • the connecting chamber 38 consequently forms a rinse path 99 .
  • first blocking/cross-section adjustment elements 48 through 51 are closed and the second blocking/cross-section adjustment elements 72 , 74 , 75 are also in the closed position.
  • the third blocking/cross-section adjustment elements 88 , 89 , 90 are also closed. Only the second blocking/cross-section adjustment element 73 is in the open position, so that the hot air that has been heated to approximately 700° C. enters into the hot end 23 of the accumulator element 31 from the connecting chamber 38 and passes through the accumulator element 31 from above to below so that the air exits from the cold end 22 at approximately 150° C.
  • the heat accumulator By operating the heat accumulator appropriately, it is possible to adapt to corresponding energy flows during charging and discharging, in particular also during partial load operation, so that the heat energy is stored in a controlled manner and there are no local increases in temperature that are not desired. Furthermore, equalization in the temperature profile in the accumulator elements is prevented. If there is an undesired equalization in the temperature layering, the output temperature increases when the accumulator is charged and decreases when it is discharged. Such an accumulator can thus be used in an only partial manner and must be completely emptied or shut down for full charging or discharging. The invention avoids this.
  • the hot side or the hot ends of the accumulator elements it is always possible for the hot side or the hot ends of the accumulator elements to be acted upon by the charging flow and the cold side or the cold ends to be acted upon by the discharging flows.
  • rinsing is performed from the cold side, that is from the cold end, using rinse air that is distributed on the hot side, that is on the hot end, to at least one other accumulator element or to different other accumulator elements.
  • the objective is to store the maximum quantity of energy at a charge that is as high as possible.
  • FIGS. 5 through 8 depict another exemplary embodiment of a heat accumulator 2 , the structure of which however largely corresponds to that of the exemplary embodiment described in the foregoing.
  • FIGS. 5 through 8 illustrate an exemplary embodiment in which, compared to FIG. 4 , no first blocking/cross-section adjustment elements 48 through 51 are provided.
  • the accumulator line 21 runs directly into the connecting chamber 38 , dividing first in order to be able to supply the air to the accumulator elements 30 through 33 as uniformly as possible.
  • the blocking/cross-section adjustment elements 88 through 91 and/or 72 through 75 are actuated appropriately.
  • the common accumulator line 20 can be seen clearly in FIGS.
  • FIGS. 5 through 8 it is not shown in the exemplary embodiment in FIGS. 2 and 3 ).
  • the connection of the medium rinse line 92 ( FIG. 4 ) to the third blocking/cross-section adjustment elements 88 through 91 is not shown in FIGS. 5 through 8 . Otherwise the statements regarding FIGS. 1 through 4 also apply correspondingly to the exemplary embodiment in FIGS. 5 through 8 .

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  • Engineering & Computer Science (AREA)
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  • Thermotherapy And Cooling Therapy Devices (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)
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US12/011,188 2007-01-29 2008-01-24 Dynamic heat accumulator and method for storing heat Abandoned US20080210218A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007005331A DE102007005331A1 (de) 2007-01-29 2007-01-29 Dynamischer Wärmespeicher sowie Verfahren zum Speichern von Wärme
DE102007005331.4 2007-01-29

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US (1) US20080210218A1 (de)
EP (1) EP1953489B1 (de)
CN (1) CN101251350B (de)
AT (1) ATE473408T1 (de)
AU (1) AU2008200399B2 (de)
DE (2) DE102007005331A1 (de)
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DE102010062144B4 (de) 2010-11-29 2015-11-12 Koenig & Bauer Ag Druckmaschine mit mindestens einem einen Heißlufttrockner aufweisenden Trocknersystem sowie Verfahren zum Betreiben eines einen Heißlufttrockner aufweisenden Trocknersystems
DE102010062142B4 (de) 2010-11-29 2015-11-12 Koenig & Bauer Ag Druckmaschine mit einem Trocknersystem sowie Verfahren zum Betrieb eines Trockners einer Bedruckstoff be- und/oder verarbeitenden Druckmaschine
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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100089391A1 (en) * 2008-10-13 2010-04-15 Addie Andrew R System and process for using solar radiation to produce electricity
US9658004B2 (en) 2011-03-23 2017-05-23 Energy Technologies Institute Llp Layered thermal store with selectively alterable gas flow path
US9709347B2 (en) 2011-03-23 2017-07-18 Energy Technologies Institute Llp Thermal storage system

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DE102007005331A1 (de) 2008-07-31
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AU2008200399A1 (en) 2008-08-14
ATE473408T1 (de) 2010-07-15
CN101251350A (zh) 2008-08-27
EP1953489B1 (de) 2010-07-07
AU2008200399B2 (en) 2011-11-10
PT1953489E (pt) 2010-09-22
ES2348317T3 (es) 2010-12-02

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