CN114777539A - Plate-fin heat exchanger applied to SOFC system - Google Patents

Plate-fin heat exchanger applied to SOFC system Download PDF

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Publication number
CN114777539A
CN114777539A CN202210417509.0A CN202210417509A CN114777539A CN 114777539 A CN114777539 A CN 114777539A CN 202210417509 A CN202210417509 A CN 202210417509A CN 114777539 A CN114777539 A CN 114777539A
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China
Prior art keywords
heat exchanger
plate
fluid
sofc system
fin heat
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CN202210417509.0A
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Chinese (zh)
Inventor
陈烁烁
刘杰鹏
邱基华
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Shenzhen Sanhuan Electronic Co ltd
Chaozhou Three Circle Group Co Ltd
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Shenzhen Sanhuan Electronic Co ltd
Chaozhou Three Circle Group Co Ltd
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Priority to CN202210417509.0A priority Critical patent/CN114777539A/en
Publication of CN114777539A publication Critical patent/CN114777539A/en
Pending 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
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0081—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by a single plate-like element ; the conduits for one heat-exchange medium being integrated in one single plate-like element
    • 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
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/04—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being formed by spirally-wound plates or laminae
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/08—Elements constructed for building-up into stacks, e.g. capable of being taken apart for cleaning

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

The invention relates to the technical field of heat exchangers, and particularly discloses a plate-fin heat exchanger applied to an SOFC (solid oxide fuel cell) system, which comprises a plurality of partition plates which are sequentially arranged from top to bottom, wherein the left side and the right side of each adjacent partition plate are connected through a seal; an accommodating cavity is formed between every two adjacent partition plates, and fins are arranged in the accommodating cavity; end face key strips are arranged on the front side and the rear side of the containing cavity, the front end face key strip and the rear end face key strip on the same partition plate are arranged in a staggered mode, and the upper end face key strip and the lower end face key strip on the adjacent partition plates are arranged in a staggered mode. The heat exchanger has compact volume and higher tolerance, prevents deformation failure and improves the efficiency of a fuel cell system.

Description

Plate-fin heat exchanger applied to SOFC system
Technical Field
The invention relates to the technical field of heat exchangers, in particular to a plate-fin heat exchanger applied to an SOFC system.
Background
The operating temperature of a medium-high temperature Solid Oxide Fuel Cell (SOFC) is usually 650-1000 ℃, reactants introduced into the fuel cell need to be preheated, the temperature difference between the reactants and the optimal operating temperature is reduced, the working efficiency is improved, and meanwhile, the temperature of tail gas discharged by the fuel cell in operation extremely contains a large amount of high-grade heat energy, so that a heat exchanger is usually adopted in a solid oxide fuel cell system for the purposes of recovering the heat energy of flue gas and preheating the reactants.
Under the current high-temperature working condition, most shell-and-tube heat exchangers with low heat exchange efficiency are adopted to achieve the purpose of heat exchange, the heat transfer efficiency of the shell-and-tube heat exchangers is low, the temperature gradient is not concentrated, the heat exchanger deformation caused by thermal stress is not obvious, but the internal pipeline arrangement of the heat exchanger is not compact, the size of a fluid flow channel is large, the heat transfer is insufficient, the heat exchange area contained in unit volume is small, the volume required by realizing specific heat exchange load is huge, the compactness is low, and the size is usually lower than 50m2/m3If the solid oxide fuel cell is used in an SOFC system, the solid oxide fuel cell occupies a very large volume, and is rarely applied to the SOFC system due to the compactness. The common compact heat exchanger generally adopts a plate-fin type, the heat transfer elements are thin and concentrated, the heat exchange area contained in unit volume is large, and the compactness can reach 700m2/m3Above, can realize great heat transfer, but the most adoption metal aluminium of current plate-fin heat exchanger material all adopts metallic aluminum or titanium, and the temperature that is suitable for all is less than 600 ℃, can not satisfy SOFC system high temperature heat transfer's demand. Another optional heat exchanger is a microchannel heat exchanger manufactured by stainless steel etching and diffusion welding, the heat exchanger also has higher compactness and is suitable for high-temperature working conditions, but the heat exchanger is limited by an etching processing technology, the interval of flow channels of the heat exchanger is thicker, so that the overall weight of the heat exchanger is heavier, the flow resistance of the heat exchanger is higher under the same flow rate, and the cost of the heat exchanger is higher.
In addition, the temperature of an air inlet in the SOFC system is usually normal temperature, the temperature of the combusted tail gas can reach 850 ℃, the temperature difference of two ends of a heat exchanger adopting countercurrent heat exchange can reach 825 ℃, and the heat exchanger needs to consider to avoid thermal deformation failure caused by the temperature difference because the heat exchanger has high compactness and the temperature change of unit length in the flowing direction of fluid is severe. In the conventional plate-fin heat exchanger, two adjacent layers of fluid inlets are isolated from cold and hot fluids by adopting end face key strips which are arranged in a staggered manner, and guide fins are required to be designed between the fins and the end face key strips to realize uniform distribution of the flow of the fluid introduced into the heat exchanger, so that the heat exchanger is large in size to a certain extent, the flow form of a guide area is complex, and the flow resistance of the heat exchanger is high.
For example, chinese patent 201921461743.3 provides a plate-fin heat exchanger, which increases the brazing area between a seal and a spacer by increasing the width of the seal in the region near the top of the core of the heat exchanger, but the structure increases the width of the seal, occupies the area of the fin, so that a part of the volume is not effectively utilized, the heat exchange area contained in the unit volume of the heat exchanger is reduced, the compactness is reduced, and the heat exchange efficiency is low by using a cross-flow manner.
For example, chinese patent 201510324622.4 provides a printed circuit board heat exchanger, utilize modes such as photochemical etching, laser etching and machining to the two side processing runners of heat transfer board of certain thickness, first heat transfer board and second heat transfer board interval arrangement, the novel structure of fused passageway is adopted to the import distribution section, but this structure processing cost is higher, use in high pressure occasion usually, and the baffle of this structure can be thicker, make the whole weight of heat exchanger increase, holistic cost has been increased, this type of microchannel heat exchanger flow resistance can be higher than plate-fin heat exchanger when the same flow in addition, pressure loss has been increased, thereby the generating efficiency of system will be reduced.
Disclosure of Invention
The invention aims to provide a plate-fin heat exchanger applied to an SOFC system, which has the advantages of high compactness, higher structural strength, good heat exchange effect and capability of improving the energy utilization efficiency of a fuel cell system.
In order to solve the technical problem, the invention provides a plate-fin heat exchanger which comprises a plurality of partition plates which are sequentially arranged from top to bottom, wherein the left side and the right side of each adjacent partition plate are connected through a seal; an accommodating cavity is formed between every two adjacent partition plates, and fins are arranged in the accommodating cavity; the front side and the rear side of the accommodating cavity are provided with end face key strips, the end face key strips on the same partition plate are arranged in a staggered mode, and the end face key strips on the adjacent partition plates are arranged in a staggered mode.
Preferably, at least one end of the end surface key strip is connected with the seal strip on the same partition plate.
Preferably, a fluid inlet and a fluid outlet are formed between at least one end of the end face key strip and the seal, the fluid inlet comprises a cold end fluid inlet and a hot end fluid inlet, and the fluid outlet comprises a cold end fluid outlet and a hot end fluid outlet.
Preferably, the width of the fluid inlet and the fluid outlet is 10% to 90% of the width of the heat exchanger. More preferably, the widths of the fluid inlet and the fluid outlet may be uniform or nonuniform.
Preferably, the cold end fluid inlet and the hot end fluid outlet are located on one side of the accommodating cavity, and the cold end fluid outlet and the hot end fluid inlet are located on the other side of the accommodating cavity.
Preferably, the accommodating cavity can further comprise a diversion strip. More preferably, the flow guide strips may be connected to the end-face key strips, or may be independently disposed in gaps between the end-face key strips and the fins. More preferably, the flow guide strips may be disposed parallel to the fluid flow direction, or may have an angle with the fluid flow direction.
Preferably, a fluid flow passage is formed between the fin and the separator.
Preferably, the partition plate, the seal strip and the end face key strip are all made of high-temperature-resistant metal.
Preferably, the fins occupy 40% to 90% of the length of the heat exchanger.
Preferably, on the same partition plate, the minimum distance from the end face key strip to the fin is 5% -20% of the length of the heat exchanger.
The length direction of the heat exchanger is the direction in which cold and hot fluid is conveyed through the fins.
The invention has the following beneficial effects:
(1) the heat exchanger adopts a plate-fin design, has high compactness, can reduce the volume of a hot box part of an SOFC system, further reduce the volume of the whole system, and meet the requirement of distributed power generation;
(2) compared with other heat exchangers with unit volumes, the heat exchanger adopts a plate-fin design, the secondary heat exchange area of the fin part is increased, and the increased area of the fin can be used as a heat transfer surface, so that the heat exchange area is higher, the heat loss brought away by smoke in the battery operation process can be reduced, the high-efficiency mode of the electric pile is maintained under the high fuel utilization rate, and the power generation efficiency is further improved;
(3) the heat exchanger is made of high-temperature alloy and can stably operate at high temperature for a long time; the heat exchanger has high overall heat exchange efficiency, the design working condition of the heat exchanger can heat the normal temperature gas to over 600 ℃, the temperature gradient distribution of the heat exchanger can be ensured to be reasonable under the working condition, and the stress concentration phenomenon of the heat exchanger at high temperature is further ensured to be avoided, so that the long-term reliable operation of the heat exchanger is ensured.
(4) Compared with other plate-fin heat exchangers, the flow directions of hot side fluid and cold side fluid at an inlet, in the heat exchanger and at an outlet of the heat exchanger are the same as the length direction of the heat exchanger, the hot side fluid and the cold side fluid do not turn at right angles, the fluid distribution effect and the pressure drop balance are better under the condition that an inlet and an outlet of the fluid are parallel to the flow direction, under the condition that the same flow is required to be uniformly distributed, the pressure drop of the fluid flowing to a parallel opening of the heat exchanger is reduced by about 40% -60% compared with the pressure drop of the fluid flowing to a vertical opening, the local pressure loss of the fluid flowing in the heat exchanger is small, and the unit pressure loss of the fluid flowing in the heat exchanger is small. The fluid in the SOFC system flows and is provided with kinetic energy by a fan, the power consumption of the fan is generated by the system, if the pressure loss of the fluid in the system is overlarge, the kinetic energy required to be provided by the fan is also larger, and the output efficiency of the system is correspondingly reduced. The invention has lower hot end and cold end pressure loss, can avoid consuming extra energy, and improve the efficiency of the fuel cell system;
(5) the fins are arranged, meanwhile, the overall pressure loss of the heat exchanger is maintained in a reasonable range, and the flow deflectors of the plate-fin heat exchanger are replaced by the key strips and the inlet and outlet positions in a shunting manner, so that the flow resistance of the heat exchanger is further reduced, and the heat exchanger is guaranteed to have higher structural strength.
(6) Because the cold and hot side fluid flows in the heat exchanger without turning in the characteristic (4), the end sockets at two ends of the heat exchanger can be arranged side by side at two ends of the heat exchanger; in the traditional plate-fin heat exchanger, the end sockets of fluid on one side are arranged on the left side and the right side of the heat exchanger, so that the heat exchanger needs smaller installation space and is more beneficial to reducing the overall size of an SOFC system; furthermore, because the flowing directions of the fluid at the inlet, in the heat exchanger and at the outlet are the same as the length direction of the heat exchanger, the heat exchanger does not need to be additionally provided with additional guide fins in the accommodating cavity, the processing cost and the manufacturing difficulty are reduced, and the pressure drop of the heat exchanger is more favorably reduced, so that the energy consumption of the SOFC system is reduced.
(7) Compared with the prior cross-flow heat exchanger, the heat exchanger of the invention is used for counter-flow heat exchange. Because the heat exchanger aims at achieving a certain heat exchange heat load Q (W), the calculation formula of the heat exchange heat load Q is as follows:
Q＝hA△T
wherein Q is the thermal load (W); h is the convective heat transfer coefficient (W/(m)2K)); a is the heat exchange area (m)2) (ii) a Δ T is the heat transfer average temperature difference (K).
From a great deal of experimental experience in the aspect of heat transfer, the counter-flow heat exchanger has a higher heat transfer temperature difference than the cross-flow heat exchanger, and the delta T of the cross-flow heat exchanger is 0.6-0.95 times of the delta T of the counter-flow heat exchanger, so that under the condition of ensuring that Q is unchanged, the heat exchange area A needs to be correspondingly increased due to the fact that the delta T of the cross-flow heat exchanger is smaller than that of the counter-flow heat exchanger. The inventor obtains through a large amount of experimental calculations that the heat exchange area of the cross-flow heat exchanger needs to be increased by 10% -50% compared with the heat exchange area of the counter-flow heat exchanger under the condition of achieving the same heat exchange effect. Therefore, compared with a cross-flow heat exchanger, the heat exchanger can achieve the same heat exchange effect as a target by using a smaller heat exchange area.
Drawings
Fig. 1 is a schematic structural diagram of a plate-fin heat exchanger according to an embodiment of the present invention;
fig. 2 is an internal structural view of a plate-fin heat exchanger according to an embodiment of the present invention;
reference numerals are as follows: 1. a partition plate; 2. a seal; 3. end face splines; 4. a fin; 5. an accommodating chamber; 6. and (4) a flow guide strip.
Detailed Description
The technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the drawings in the embodiments of the present application, and it is obvious that the described embodiments are only a part of the embodiments of the present application, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present application.
In the description of the present application, it is to be understood that the terms "center", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", and the like indicate orientations or positional relationships based on those shown in the drawings, and are only for convenience in describing the present application and simplifying the description, but do not indicate or imply that the referred device or element must have a particular orientation, be constructed in a particular orientation, and be operated, and thus should not be construed as limiting the present application.
In the description of the present application, it is to be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, e.g., as meaning either a fixed connection, a removable connection, or an integral connection; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meaning of the above terms in this application will be understood to be a specific case for those of ordinary skill in the art.
Referring to fig. 1-2, a preferred embodiment of the present invention provides a plate-fin heat exchanger, which includes a plurality of partition plates 1 sequentially arranged from top to bottom, wherein the left and right sides of adjacent partition plates 1 are connected by seals 2; an accommodating cavity 5 is arranged between the adjacent partition plates 1, and fins 4 are arranged in the accommodating cavity 5; the front side and the rear side of the accommodating cavity 5 are provided with end face key strips 3, the same end face key strips 3 on the partition plate 1 are arranged in a staggered mode, and the end face key strips 3 on the adjacent partition plate 1 are arranged in a staggered mode.
Based on the above scheme, the working principle of the plate-fin heat exchanger of the preferred embodiment of the present invention is as follows: on the same partition plate 1, cold end fluid enters from one side of the accommodating cavity 5, passes through the fins 4, absorbs heat of the fins 4 and then flows out from the other side of the accommodating cavity 5; on the adjacent partition board 1, the flow direction of the hot end fluid is opposite to that of the cold end fluid, and the hot end fluid passes through the fins 4 to transfer heat to the fins 4; thus, heat exchange is completed.
Preferably, at least one end of the end surface key strip 3 is connected to the seal strip on the partition board 1 on the same partition board.
Preferably, a fluid inlet and a fluid outlet are formed between at least one end of the end face key strip 3 and the seal 2 on the partition plate 1, the fluid inlet includes a cold-end fluid inlet and a hot-end fluid inlet, and the fluid outlet includes a cold-end fluid outlet and a hot-end fluid outlet. The cold end fluid inlet and the hot end fluid outlet are positioned on one side of the accommodating cavity, and the cold end fluid outlet and the hot end fluid inlet are positioned on the other side of the accommodating cavity. Fluid flow passages are formed between the fins 4 and the separator 1. The end face key bars are arranged on the adjacent partition plates in a staggered mode, and cross leakage of cold and hot fluids of the adjacent partition plates can be prevented.
Preferably, the width of the fluid inlet and the fluid outlet is 10% -90% of the width of the heat exchanger. More preferably, the widths of the fluid inlet and the fluid outlet may be uniform or nonuniform. For example, the width of the fluid inlet is 10% of the width of the heat exchanger, and the width of the fluid outlet is 90% of the width of the heat exchanger, so that the purpose of heat exchange can be achieved.
Preferably, the containing cavity can further comprise a diversion strip 6. The flow guide strips 6 can cooperate with the end face key strips to uniformly distribute fluid in the heat exchanger, so that the heat exchange surface is fully utilized. More preferably, the flow guide strips 6 may be connected with the end-face key strips, or may be independently disposed in the gaps between the end-face key strips and the fins. More preferably, the flow guide strips 6 may be disposed parallel to the fluid flow direction, or may be disposed at an angle to the fluid flow direction.
Preferably, the partition board 1, the seal 2 and the end surface key strip 3 are made of high-temperature-resistant metal.
As a further preferable mode, the high temperature resistant metal includes iron-based alloy, nickel-based alloy or other metal alloy having high temperature resistance to oxidation, such as SUS310s, SUS316s, SUS444, SUS420, inconel600, inconel625, GH3030, and the like. Specifically, the plate-fin heat exchanger is prepared from a high-temperature-resistant metal material, and is suitable for the high-temperature operation working condition of the SOFC, so that the plate-fin heat exchanger has high yield strength, high tolerance to the thermal stress generated by the temperature difference of a heat transfer unit, and deformation failure is prevented.
Preferably, the fins 4 occupy 40% -90% of the length of the heat exchanger. The length direction of the heat exchanger is the direction in which cold and hot fluid is conveyed through the fins. Specifically, the distribution difference of the heat exchanger with the overlarge length of the fins 4 is large, the pressure loss of the heat exchanger is obviously increased, the power generation efficiency of the system is reduced, the compactness of the heat exchanger with the overlarge length of the fins 4 is reduced, and the required volume of the heat exchanger is increased.
Preferably, on the same partition board 1, the minimum distance between the end face key strips 3 and the fins 4 is 5% -20% of the length of the heat exchanger. Specifically, if the pitch is less than 5%, maldistribution of the fluid flow rate is easily caused, and if the pitch is more than 20%, collapse of the separator 1 during brazing is also easily caused. The uniform distribution of the heat exchanger is mainly realized by the lengths of the keybars at the inlet and the outlet and the distance between the front end of the fin 4 and the keybars, the inlet and the outlet of the heat exchanger are staggered in geometry, the distance between the front end of the fin 4 and the keybars is constant, and the flow deviation of fluid flowing through each channel of the fin 4 can be realized within an expected range by adjusting the lengths of the inlet and the outlet keybars.
The working principle of the invention is as follows: on the same partition plate 1, cold end fluid enters from one side of the accommodating cavity 5, passes through the fins, absorbs heat of the fins 4 and then flows out from the other side of the accommodating cavity 5; on the adjacent partition board 1, the flow direction of the hot end fluid is opposite to that of the cold end fluid, and the hot end fluid passes through the fins 4 to transfer heat to the fins 4; thus, heat exchange is completed.
To sum up, a preferred embodiment of the present invention provides a plate-fin heat exchanger, which is compared with the prior art:
(1) the heat exchanger disclosed by the invention adopts a plate-fin design, has high compactness, can reduce the volume of a hot box part of an SOFC system, further reduces the volume of the whole system, and meets the requirement of distributed power generation;
(2) compared with other heat exchangers with unit volumes, the heat exchanger adopts a plate-fin design, the secondary heat exchange area of the fin part is increased, and the increased area of the fin can be used as a heat transfer surface, so that the heat exchange area is higher, the heat loss brought away by smoke in the battery operation process can be reduced, the high-efficiency mode of the electric pile is maintained under the high fuel utilization rate, and the power generation efficiency is further improved;
(3) the heat exchanger is made of high-temperature alloy, and can stably operate at high temperature for a long time; the heat exchanger has high overall heat exchange efficiency, the design working condition of the heat exchanger can heat the normal temperature gas to over 600 ℃, the temperature gradient distribution of the heat exchanger can be ensured to be reasonable under the working condition, and the stress concentration phenomenon of the heat exchanger at high temperature is further ensured to be avoided, so that the long-term reliable operation of the heat exchanger is ensured.
(4) Compared with other plate-fin heat exchangers, the flow directions of hot side fluid and cold side fluid at an inlet, in the heat exchanger and at an outlet of the heat exchanger are the same as the length direction of the heat exchanger, the hot side fluid and the cold side fluid do not turn at right angles, the fluid distribution effect and the pressure drop balance are better under the condition that an inlet and an outlet of the fluid are parallel to the flow direction, under the condition that the same flow is required to be uniformly distributed, the pressure drop of the fluid flowing to a parallel opening of the heat exchanger is reduced by about 40% -60% compared with the pressure drop of the fluid flowing to a vertical opening, the local pressure loss of the fluid flowing in the heat exchanger is small, and the unit pressure loss of the fluid flowing in the heat exchanger is small. The fluid in the SOFC system flows and is provided with kinetic energy by a fan, the power consumption of the fan is generated by the system, if the pressure loss of the fluid in the system is too large, the kinetic energy required to be provided by the fan is also large, and the output efficiency of the system is correspondingly reduced. The invention has lower hot end and cold end pressure loss, can avoid consuming extra energy, raise the system efficiency of the fuel cell;
(5) the fins are arranged, meanwhile, the overall pressure loss of the heat exchanger is maintained in a reasonable range, and the flow deflectors of the plate-fin heat exchanger are replaced by the key strips and the inlet and outlet positions in a shunting manner, so that the flow resistance of the heat exchanger is further reduced, and the heat exchanger is guaranteed to have higher structural strength.
(6) Because the cold and hot side fluid flows in the heat exchanger without turning in the characteristic of (4), the end sockets at two ends of the heat exchanger can be arranged side by side at two ends of the heat exchanger; in the traditional plate-fin heat exchanger, the end sockets of fluid on one side are arranged on the left side and the right side of the heat exchanger, so that the heat exchanger needs smaller installation space and is more beneficial to reducing the overall size of an SOFC system; furthermore, because the flowing directions of the fluid at the inlet, in the heat exchanger and at the outlet are the same as the length direction of the heat exchanger, the heat exchanger does not need to be additionally provided with additional guide fins in the accommodating cavity, the processing cost and the manufacturing difficulty are reduced, and the pressure drop of the heat exchanger is more favorably reduced, so that the energy consumption of the SOFC system is reduced.
(7) Compared with the prior cross-flow heat exchanger, the heat exchanger of the invention is used for counter-flow heat exchange. Because the heat exchanger aims at achieving a certain heat exchange heat load Q (W), the calculation formula of the heat exchange heat load Q is as follows:
Q＝hA△T
wherein Q is the thermal load (W); h is the convective heat transfer coefficient (W/(m)2K)); a is the heat exchange area (m)2) (ii) a Delta T is heat transferAverage temperature difference (K).
From a great deal of experimental experience in the aspect of heat transfer, the counter-flow heat exchanger has a higher heat transfer temperature difference than the cross-flow heat exchanger, and the delta T of the cross-flow heat exchanger is 0.6-0.95 times of the delta T of the counter-flow heat exchanger, so that under the condition of ensuring that Q is unchanged, the heat exchange area A needs to be correspondingly increased due to the fact that the delta T of the cross-flow heat exchanger is smaller than that of the counter-flow heat exchanger. The inventor obtains through a large amount of experimental calculations that the heat exchange area of the cross-flow heat exchanger needs to be increased by 10% -50% compared with the heat exchange area of the counter-flow heat exchanger under the condition of achieving the same heat exchange effect. Therefore, compared with a cross-flow heat exchanger, the heat exchanger can achieve the same heat exchange effect as a target by using a smaller heat exchange area.
The above description is only a preferred embodiment of the present invention, and it should be noted that, for those skilled in the art, various modifications and substitutions can be made without departing from the technical principle of the present invention, and these modifications and substitutions should also be regarded as the protection scope of the present invention.

Claims (10)

1. The plate-fin heat exchanger applied to the SOFC system is characterized by comprising a plurality of partition plates which are sequentially arranged from top to bottom, wherein the left side and the right side of each adjacent partition plate are connected through a seal; an accommodating cavity is formed between every two adjacent partition plates, and fins are arranged in the accommodating cavity; the front side and the rear side of the accommodating cavity are provided with end face key strips, the end face key strips on the same partition plate are arranged in a staggered mode, and the end face key strips on the adjacent partition plates are arranged in a staggered mode.
2. The plate fin heat exchanger for use in an SOFC system as set forth in claim 1 wherein at least one end of said end-face splines are connected to said seal on the same separator plate.
3. The plate fin heat exchanger for use in SOFC system as set forth in claim 1, wherein a fluid inlet and a fluid outlet are provided between at least one end of said end surface splines and said seal.
4. The plate fin heat exchanger for use in an SOFC system of claim 3, wherein the fluid inlets comprise a cold side fluid inlet and a hot side fluid inlet and the fluid outlets comprise a cold side fluid outlet and a hot side fluid outlet.
5. The plate fin heat exchanger for use in an SOFC system of claim 4, wherein the cold side fluid inlet and the hot side fluid outlet are located on one side of the receiving cavity and the cold side fluid outlet and the hot side fluid inlet are located on the other side of the receiving cavity.
6. The plate fin heat exchanger for use in an SOFC system of claim 3, wherein the fluid inlet and the fluid outlet have a width of between 10% and 90% of the width of the heat exchanger.
7. The plate fin heat exchanger for use in SOFC system as set forth in claim 1, wherein said receiving cavity further comprises a flow guide strip.
8. The plate fin heat exchanger for use in an SOFC system as set forth in claim 1, wherein the separator, seal and end key are made of refractory metal.
9. The plate fin heat exchanger for use in an SOFC system of claim 1, wherein the fins comprise between 40% and 90% of the length of the heat exchanger.
10. The plate fin heat exchanger for use in an SOFC system as set forth in claim 1 wherein the minimum spacing of said end-face splines to said fins on the same said separator plate is between 5% and 20% of the length of the heat exchanger.
CN202210417509.0A 2022-04-18 2022-04-18 Plate-fin heat exchanger applied to SOFC system Pending CN114777539A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202210417509.0A CN114777539A (en) 2022-04-18 2022-04-18 Plate-fin heat exchanger applied to SOFC system

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202210417509.0A CN114777539A (en) 2022-04-18 2022-04-18 Plate-fin heat exchanger applied to SOFC system

Publications (1)

Publication Number Publication Date
CN114777539A true CN114777539A (en) 2022-07-22

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CN202210417509.0A Pending CN114777539A (en) 2022-04-18 2022-04-18 Plate-fin heat exchanger applied to SOFC system

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