CN113237097A - Heat exchanger for gas turbine - Google Patents
Heat exchanger for gas turbine Download PDFInfo
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- CN113237097A CN113237097A CN202110469732.5A CN202110469732A CN113237097A CN 113237097 A CN113237097 A CN 113237097A CN 202110469732 A CN202110469732 A CN 202110469732A CN 113237097 A CN113237097 A CN 113237097A
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- Prior art keywords
- heat exchanger
- wall
- runner
- flue gas
- cold
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23R—GENERATING COMBUSTION PRODUCTS OF HIGH PRESSURE OR HIGH VELOCITY, e.g. GAS-TURBINE COMBUSTION CHAMBERS
- F23R3/00—Continuous combustion chambers using liquid or gaseous fuel
- F23R3/42—Continuous combustion chambers using liquid or gaseous fuel characterised by the arrangement or form of the flame tubes or combustion chambers
- F23R3/58—Cyclone or vortex type combustion chambers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23R—GENERATING COMBUSTION PRODUCTS OF HIGH PRESSURE OR HIGH VELOCITY, e.g. GAS-TURBINE COMBUSTION CHAMBERS
- F23R3/00—Continuous combustion chambers using liquid or gaseous fuel
- F23R3/28—Continuous combustion chambers using liquid or gaseous fuel characterised by the fuel supply
- F23R3/283—Attaching or cooling of fuel injecting means including supports for fuel injectors, stems, or lances
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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
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
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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
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/0026—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for combustion engines, e.g. for gas turbines or for Stirling engines
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
The invention discloses a heat exchanger for a gas turbine, which comprises a heat exchanger inner wall, a heat exchanger outer wall and a heat exchanging part, wherein the heat exchanger inner wall is provided with a heat exchanging hole; a cold runner set and a hot runner set are arranged in the heat exchanging part; the cold runner set comprises a plurality of cold runners which are arranged in parallel in the vertical direction; the hot runner group comprises a plurality of hot runners which are arranged in parallel in the vertical direction; the cold runner and the hot runner are both spiral runners; according to the invention, through the cold runner set and the hot runner set which are alternately arranged in the heat exchange part, smoke generated by combustion in the combustion chamber is discharged from the hot runner set, air required by the combustion chamber is input into the combustion chamber from the cold runner set, the smoke is subjected to heat exchange and temperature reduction by adopting the air, the temperature of the smoke during emission can be reduced without using other temperature reduction media, the temperature of the air required to be input into the combustion chamber is increased, and the heat loss of the combustion chamber to the outside is effectively reduced; the cold runner and the hot runner are both spiral runners, so that the heat exchange process is prolonged, and a better heat exchange effect is ensured.
Description
Technical Field
The invention relates to the field of heat exchangers, in particular to a heat exchanger for a gas turbine.
Background
The gas turbine is a power machine widely applied to various industrial fields such as aviation, ships, electric power and the like, and plays a vital role in the development of national economy. Compared with the other gas turbines, the gas turbine has many advantages, has great advantages in the aspects of fuel consumption rate, noise, emission and vibration, can be used for traditional distributed power generation and various power generation modes such as grid-connected power generation and the like, is suitable for cities, and is widely popularized in remote areas by virtue of the advantages of convenience in carrying and reliability in work; except for transportation such as sea and land frontier defense, the gas turbine is applied to various fields such as new energy automobiles, electromechanical machining, metal materials and the like, so that the gas turbine is concerned by various military and major countries.
The traditional gas turbine directly discharges high-temperature gas flowing out of the turbine to the atmospheric environment, so that energy is wasted, and the heat efficiency of the whole machine is not high. Meanwhile, the temperature of air entering the combustion chamber is low, the temperature rise of the combustion chamber is not high, and the subsequent working capacity of airflow is influenced.
Based on the above situation, the present invention provides a heat exchanger for a gas turbine, which can effectively solve the above problems.
Disclosure of Invention
The invention aims to provide a heat exchanger for a gas turbine. The heat exchanger for the gas turbine has the advantages that the structure is simple, the use is convenient, smoke generated by combustion in the combustion chamber is discharged from the hot runner set through the cold runner set and the hot runner set which are alternately arranged in the heat exchange part, air required by the combustion chamber is input into the combustion chamber from the cold runner set, the air is directly adopted to carry out heat exchange and cooling on the smoke in the flowing process of the air and the smoke, the temperature of the smoke during discharge can be reduced without using other cooling media or cooling structures, the temperature of the air required to be input into the combustion chamber is increased, and the heat loss of the combustion chamber to the outside is effectively reduced; the cold runner and the hot runner are both spiral runners, so that the heat exchange process is prolonged, and a better heat exchange effect is ensured.
The invention is realized by the following technical scheme:
a heat exchanger for a gas turbine comprises a heat exchanger inner wall and a heat exchanger outer wall, wherein a heat exchanging part is arranged between the heat exchanger inner wall and the heat exchanger outer wall; cold runner sets and hot runner sets with equal quantity are arranged in the heat exchange part; the cold runner set and the hot runner set are alternately arranged at equal intervals in the circumferential direction of the heat exchanging part; each cold runner set comprises a plurality of cold runners which are arranged in parallel in the vertical direction, each cold runner is a spiral runner, and each cold runner is communicated with the inner wall of the heat exchanger and the outer wall of the heat exchanger; each hot runner group comprises a plurality of hot runners which are arranged in parallel in the vertical direction, the hot runners are spiral runners, and each hot runner is communicated with the inner wall of the heat exchanger and the outer wall of the heat exchanger.
According to the invention, through the cold runner set and the hot runner set which are alternately arranged in the heat exchange part, smoke generated by combustion in the combustion chamber is discharged from the hot runner set, air required by the combustion chamber is input into the combustion chamber from the cold runner set, the air is directly adopted to carry out heat exchange and temperature reduction on the smoke in the flowing process of the air and the smoke, the temperature of the smoke during emission can be reduced without using other temperature reducing media or temperature reducing structures, the temperature of the air required to be input into the combustion chamber is increased, and the heat loss of the combustion chamber to the outside is effectively reduced; the cold runner and the hot runner are both spiral runners, so that the heat exchange process is prolonged, and a good heat exchange effect is ensured.
Preferably, a plurality of air outlets are annularly arranged on the inner wall of one side of the inner wall of the heat exchanger at equal intervals, and each air outlet is provided with an air outlet cavity in the inner wall of the heat exchanger; a plurality of flue gas inlets are annularly arranged on the inner wall of the other side of the inner wall of the heat exchanger at equal intervals, and each flue gas inlet is provided with a flue gas inlet cavity in the inner wall of the heat exchanger; the inner wall of the heat exchanger is provided with a baffle plate used for guiding the flow direction of the flue gas at one side of the flue gas inlet.
Preferably, a plurality of bumps are arranged on the inner side of the outer wall of the heat exchanger corresponding to the plurality of air outlets, air inlets are arranged at one ends of the bumps, which are far away from the air outlets, and each air inlet is provided with an air inlet cavity in each bump; the outer wall of the heat exchanger, the heat exchanging part and the plurality of the lugs form a plurality of flue gas outlet cavities.
Preferably, the helix angle of each cold runner is 360 °; the cold runner comprises an air inlet elbow communicated to the air inlet cavity, an air outlet elbow communicated to the air outlet cavity and a first spiral runner connected with the air inlet elbow and the air outlet elbow; the first spiral flow channel is formed by connecting a plurality of first variable flow channel sections; the cross sections of the two ends of the first variable flow passage section are circular, and the cross section of the center of the first variable flow passage section is square.
Preferably, the spiral angle of each hot runner is 360 degrees; the hot runner comprises a flue gas inlet elbow communicated to the flue gas inlet cavity, a flue gas outlet elbow communicated to the flue gas outlet cavity and a second spiral flow channel connected with the flue gas inlet elbow and the flue gas outlet elbow; the second spiral flow channel is formed by connecting a plurality of second variable flow channel sections; the cross sections of the two ends of the second variable flow passage section are circular, and the cross section of the center of the second variable flow passage section is square.
Preferably, the number of the cold runner sets and the number of the hot runner sets are six; the number of the cold runners in each set of the cold runner sets is sixteen; the number of the hot runners in each hot runner group is sixteen.
Preferably, an oil injection ring is further fixed on the inner side of the inner wall of the heat exchanger, and a plurality of oil injection nozzles are annularly arranged on one side, close to the air outlet, of the oil injection ring; a first oil filling pipe is arranged on one side of the heat exchange part close to the air outlet; one end of the first oil filling pipe penetrates through the outer wall of the heat exchanger, and an oil filling opening is formed in the outer wall of the heat exchanger; the other end of the first oil injection pipe is communicated with the oil injection ring through a second oil injection pipe embedded in the inner wall of the heat exchanger.
Compared with the prior art, the invention has the following advantages and beneficial effects:
the heat exchanger for the gas turbine has the advantages that the structure is simple, the use is convenient, smoke generated by combustion in the combustion chamber is discharged from the hot runner set through the cold runner set and the hot runner set which are alternately arranged in the heat exchange part, air required by the combustion chamber is input into the combustion chamber from the cold runner set, the air is directly adopted to carry out heat exchange and cooling on the smoke in the flowing process of the air and the smoke, the temperature of the smoke during discharge can be reduced without using other cooling media or cooling structures, the temperature of the air required to be input into the combustion chamber is increased, and the heat loss of the combustion chamber to the outside is effectively reduced; the cold runner and the hot runner are both spiral runners, so that the heat exchange process is prolonged, and a better heat exchange effect is ensured.
Drawings
FIG. 1 is a schematic structural view of the present invention;
FIG. 2 is a schematic view of another embodiment of the present invention;
FIG. 3 is a schematic top view of the present invention;
FIG. 4 is a cross-sectional view taken at A-A of FIG. 3;
FIG. 5 is a cross-sectional view taken at B-B of FIG. 3;
FIG. 6 is a cross-sectional view taken at C-C of FIG. 3;
FIG. 7 is a schematic structural view of a portion of the cold runner and hot runner of the present invention;
FIG. 8 is a schematic cross-sectional view of FIG. 7;
FIG. 9 is a schematic structural view of a first flow variation segment according to the present invention;
fig. 10 is a schematic structural view of a second variable flow path segment according to the present invention.
Detailed Description
In order that those skilled in the art will better understand the technical solutions of the present invention, the following description of the preferred embodiments of the present invention is provided in conjunction with specific examples, but it should be understood that the drawings are for illustrative purposes only and should not be construed as limiting the patent; for the purpose of better illustrating the embodiments, certain features of the drawings may be omitted, enlarged or reduced, and do not represent the size of an actual product; it will be understood by those skilled in the art that certain well-known structures in the drawings and descriptions thereof may be omitted. The positional relationships depicted in the drawings are for illustrative purposes only and are not to be construed as limiting the present patent.
Example 1:
as shown in fig. 1 to 10, a heat exchanger for a gas turbine includes a heat exchanger inner wall 11 and a heat exchanger outer wall 12, and a heat exchanging portion 13 is provided between the heat exchanger inner wall 11 and the heat exchanger outer wall 12; cold runner sets 131 and hot runner sets 132 which are equal in number are arranged in the heat exchanging part 13; the cold runner set 131 and the hot runner set 132 are alternately arranged at equal intervals in the circumferential direction of the heat exchanging part 13; each cold runner set 131 comprises a plurality of cold runners 133 which are arranged in parallel in the vertical direction, each cold runner 133 is a spiral runner, and each cold runner 133 is communicated with the heat exchanger inner wall 11 and the heat exchanger outer wall 12; each hot runner group 132 comprises a plurality of hot runners 134 which are arranged in parallel in the vertical direction, the hot runners 134 are spiral runners, and each hot runner 134 is communicated with the inner wall 11 and the outer wall 12 of the heat exchanger.
According to the invention, through the cold runner set 131 and the hot runner set 132 which are alternately arranged in the heat exchanging part 13, flue gas generated by combustion in the combustion chamber is discharged from the hot runner set 132, air required by the combustion chamber is input into the combustion chamber from the cold runner set 131, and the air is directly adopted to carry out heat exchange and temperature reduction on the flue gas in the flowing process of the air and the flue gas, so that the temperature of the flue gas during emission can be reduced without using other temperature reducing media or temperature reducing structures, and the temperature of the air required to be input into the combustion chamber is increased, thereby effectively reducing the heat loss of the combustion chamber to the outside; the cold runner 133 and the hot runner 134 are both spiral runners, so that the heat exchange process is prolonged, and a good heat exchange effect is ensured.
And a cavity enclosed by the inner wall 11 of the heat exchanger is a combustion chamber.
Further, in another embodiment, a plurality of air outlets 111 are equidistantly arranged on the inner wall of one side of the heat exchanger inner wall 11, and each air outlet 111 is provided with an air outlet cavity 112 in the heat exchanger inner wall 11; a plurality of flue gas inlets 113 are annularly arranged on the inner wall of the other side of the inner wall 11 of the heat exchanger at equal intervals, and each flue gas inlet 113 is provided with a flue gas inlet cavity 114 in the inner wall 11 of the heat exchanger; the heat exchanger inner wall 11 is further provided with a baffle 115 for guiding the flow direction of the flue gas at the side where the flue gas inlet 113 is arranged.
The air outlet cavity 112 buffers the input air, so that the combustion effect of the combustion chamber can be prevented from being influenced when the air is sprayed out of the cold runner, the buffered air can not influence the combustion effect of the combustion chamber when the buffered air is sprayed out of the air outlet cavity, and sufficient air can be ensured when the combustion chamber is combusted; through the flue gas inlet 113 and the baffle 115, flue gas generated by combustion in the combustion chamber enters the flue gas inlet cavity 114 and then enters the hot runner 134 through the flue gas inlet cavity 114, so that excessive flue gas cannot be left in the combustion chamber, the air content in the combustion chamber is ensured to be sufficient, and the combustion effect is improved.
Further, in another embodiment, a plurality of protrusions 121 are arranged inside the heat exchanger outer wall 12 corresponding to the plurality of air outlets 111, an air inlet 122 is arranged at an end of the protrusion 121 facing away from the air outlets 111, and each air inlet 122 forms an air inlet cavity 123 in the protrusion 121; the outer wall 12 of the heat exchanger, the heat exchanging part 13 and the plurality of bumps 121 form a plurality of flue gas outlet cavities 124.
The air inlet cavities 123 and the flue gas outlet cavities 124 which are alternately arranged on the inner side of the heat exchanger outer wall 12 are formed by arranging a plurality of the lugs 121 at equal intervals in the circumferential direction of the inner side of the heat exchanger outer wall 12; the opening directions of the air inlet cavity 123 and the flue gas outlet cavity 124 are set to be opposite, so that the flue gas which is just discharged is prevented from being sucked by the air inlet cavity 123, and a good air inlet effect of the air inlet cavity 123 is ensured.
Further, in another embodiment, the helix angle of each of the cold runners 133 is 360 °; the cold runner 133 comprises an air inlet elbow 1331 communicated to the air inlet cavity 123, an air outlet elbow 1332 communicated to the air outlet cavity 112, and a first spiral runner 1333 connecting the air inlet elbow 1331 and the air outlet elbow 1332; the first spiral flow passage 1333 is formed by connecting a plurality of first variable flow passage sections 1334; the cross-sections of both ends of the first variable flow path section 1334 are circular, and the cross-section of the center of the first variable flow path section 1334 is square.
Through the air inlet elbow 1331, the cold runner 133 can be better communicated to the air inlet cavity 123, so as to ensure better air inlet effect; through the air outlet elbow 1332, the cold runner 133 can be better communicated to the air outlet cavity 112, so as to ensure a better air outlet effect.
Further, in another embodiment, the helix angle of each hot runner 134 is 360 °; the hot runner 134 comprises a flue gas inlet elbow 1341 communicated with the flue gas inlet cavity 114, a flue gas outlet elbow 1342 communicated with the flue gas outlet cavity 124, and a second spiral flow passage 1343 connected with the flue gas inlet elbow 1341 and the flue gas outlet elbow 1342; the second spiral flow passage 1343 is formed by connecting a plurality of second variable flow passage segments 1344; the cross-sections of both ends of the second variable flow passage section 1344 are circular, and the cross-section of the center of the second variable flow passage section 1344 is square.
Through the flue gas inlet elbow 1341, the hot runner 134 can be better communicated with the flue gas inlet cavity 114, so that a better gas inlet effect is ensured; through the air outlet elbow 1332, the hot runner 134 can be better communicated to the flue gas outlet cavity 124, so as to ensure a better air outlet effect.
The spiral angles of the cold runner 133 and the hot runner 134 are both 360 degrees, so that the cold runner 133 and the hot runner 134 are ensured to have enough heat exchange strokes, and the heat dissipation of the combustion chamber to the outside is effectively reduced.
The first variable flow passage section 1334 and the second variable flow passage section 1344 are both tapered flow passages, the cross sections of the two ends are circular, the cross section of the middle is square, namely, the transition from the circular cross section of one end to the square cross section of the middle is performed, and then the transition from the square cross section to the circular cross section of the other end is performed. In the process of section change, fluid on the section in the flow channel is forced to be redistributed, disturbance heat exchange among the fluids is increased, the temperature distribution of the fluid on the section in the flow channel is more uniform, and the heat exchange effect is better; in addition, the first change runner section 1334 and the second change runner section 1344 take thermal expansion and cold contraction of the runner into consideration, a space is left for runner deformation, a circular section can be changed into a square shape when being heated or bearing, and the square section can be changed towards the direction of the circular section when being heated or bearing.
The spiral angle of the first variable flow passage section 1334 and the second variable flow passage section 1344 is 2 °, that is, the first spiral flow passage 1333 is formed by 180 sections of the first variable flow passage section 1334, and the second spiral flow passage 1343 is formed by 180 sections of the second variable flow passage section 1344; the more the first change flow passage section 1334 and the second change flow passage section 1344 are, i.e. the more the change of the cross section of the flow passage is, the better the effect of resisting expansion and contraction and heat exchange is.
The cross section of the middle of the first variable flow passage section 1334 and the second variable flow passage section 1344 is square, and four sides of the square adopt concave arcs, so that the square can be better attached to a flow passage with a circular cross section.
Each of the cold runners 133 is surrounded by four of the hot runners 134, which increases the heat transfer area between the air and the flue gas. And the cold runner 133 and the hot runner 134 support each other, so that the strength of the heat exchanger is enhanced.
Further, in another embodiment, the number of the cold runner sets 131 and the hot runner sets 132 is six; the number of cold runners 133 in each set of the cold runner sets 131 is sixteen; the number of hot runners 134 in each hot runner group 132 is sixteen.
Further, in another embodiment, an oil injection ring 14 is further fixed on the inner side of the heat exchanger inner wall 11, and a plurality of oil injection nozzles 141 are annularly arranged on one side of the oil injection ring 14, which is close to the air outlet 111; a first oil filling pipe 142 is arranged at one side of the heat exchanging part 13 close to the air outlet 111; one end of the first oil filling pipe 142 penetrates through the heat exchanger outer wall 12, and an oil filling port 143 is formed in the heat exchanger outer wall 12; the other end of the first filler pipe 142 and the oil spray ring 14 communicate with each other through a second filler pipe 144 embedded in the heat exchanger inner wall 11.
The oil injection ring 14 serves as a transfer station of an oil path, oil pressure is stabilized, and the oil is uniformly sprayed out of the oil injection nozzle 141, so that a good oil injection effect is ensured.
The first spiral flow passage 1333 and the second spiral flow passage 1343 are integrally formed by an additive technology, so that the mechanical property is good, the shapes of the first spiral flow passage 1333 and the second spiral flow passage 1343 can be more conveniently manufactured, and the heat exchanging part 13 is ensured to have a good heat exchanging effect.
The heat exchanger for a gas turbine according to the invention can be easily manufactured or used by those skilled in the art from the description of the invention and the accompanying drawings, and can produce the positive effects described in the present invention.
Unless otherwise specified, in the present invention, if there is an orientation or positional relationship indicated by terms of "length", "width", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc., based on the orientation or positional relationship shown in the drawings, it is only for convenience of describing the present invention and simplifying the description, rather than to indicate or imply that the device or element so referred to must have a particular orientation, be constructed and operated in a particular orientation, therefore, the terms describing orientation or positional relationship in the present invention are for illustrative purposes only, and should not be construed as limiting the present patent, specific meanings of the above terms can be understood by those of ordinary skill in the art in light of the specific circumstances in conjunction with the accompanying drawings.
Unless expressly stated or limited otherwise, the terms "disposed," "connected," and "connected" are used broadly and encompass, for example, being fixedly connected, detachably connected, or integrally connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meanings of the above terms in the present invention can be understood in specific cases to those skilled in the art.
The above description is only a preferred embodiment of the present invention, and is not intended to limit the present invention in any way, and all simple modifications and equivalent variations of the above embodiments according to the technical spirit of the present invention are included in the scope of the present invention.
Claims (7)
1. A heat exchanger for a gas turbine, characterized by: the heat exchanger comprises a heat exchanger inner wall (11) and a heat exchanger outer wall (12), wherein a heat exchanging part (13) is arranged between the heat exchanger inner wall (11) and the heat exchanger outer wall (12); cold runner sets (131) and hot runner sets (132) with equal quantity are arranged in the heat exchanging part (13); the cold runner set (131) and the hot runner set (132) are alternately arranged at equal intervals in the circumferential direction of the heat exchanging part (13); each cold runner set (131) comprises a plurality of cold runners (133) which are arranged in parallel in the vertical direction, each cold runner (133) is a spiral runner, and each cold runner (133) is communicated with the inner wall (11) and the outer wall (12) of the heat exchanger; each hot runner group (132) comprises a plurality of hot runners (134) which are arranged in parallel in the vertical direction, each hot runner (134) is a spiral runner, and each hot runner (134) is communicated with the inner wall (11) and the outer wall (12) of the heat exchanger.
2. The heat exchanger for a gas turbine as claimed in claim 1, wherein: a plurality of air outlets (111) are annularly arranged on the inner wall of one side of the inner wall (11) of the heat exchanger at equal intervals, and each air outlet (111) is provided with an air outlet cavity (112) in the inner wall (11) of the heat exchanger; a plurality of flue gas inlets (113) are annularly arranged on the inner wall of the other side of the inner wall (11) of the heat exchanger at equal intervals, and each flue gas inlet (113) is provided with a flue gas inlet cavity (114) in the inner wall (11) of the heat exchanger; and a baffle (115) for guiding the flow direction of the flue gas is also arranged on one side of the inner wall (11) of the heat exchanger, which is provided with the flue gas inlet (113).
3. The heat exchanger for a gas turbine as claimed in claim 2, wherein: a plurality of bumps (121) are arranged on the inner side of the outer wall (12) of the heat exchanger corresponding to the plurality of air outlets (111), an air inlet (122) is arranged at one end of each bump (121) departing from the corresponding air outlet (111), and an air inlet cavity (123) is formed in each bump (121) by each air inlet (122); the heat exchanger outer wall (12), the heat exchange part (13) and the plurality of lugs (121) form a plurality of flue gas outlet cavities (124).
4. A heat exchanger for a gas turbine according to claim 3, wherein: -the helix angle of each cold runner (133) is 360 °; the cold runner (133) comprises an air inlet elbow (1331) communicated to the air inlet cavity (123), an air outlet elbow (1332) communicated to the air outlet cavity (112), and a first spiral runner (1333) connecting the air inlet elbow (1331) and the air outlet elbow (1332); the first spiral flow passage (1333) is formed by connecting a plurality of first variable flow passage sections (1334); the cross sections of the two ends of the first variable flow passage section (1334) are circular, and the cross section of the center of the first variable flow passage section (1334) is square.
5. The heat exchanger for a gas turbine according to claim 4, wherein: the helix angle of each hot runner (134) is 360 degrees; the hot runner (134) comprises a flue gas inlet elbow (1341) communicated with the flue gas inlet cavity (114), a flue gas outlet elbow (1342) communicated with the flue gas outlet cavity (124), and a second spiral flow channel (1343) connected with the flue gas inlet elbow (1341) and the flue gas outlet elbow (1342); the second spiral flow channel (1343) is formed by connecting a plurality of second variable flow channel sections (1344); the cross sections of the two ends of the second variable flow passage section (1344) are circular, and the cross section of the center of the second variable flow passage section (1344) is square.
6. The heat exchanger for a gas turbine as claimed in claim 5, wherein: the number of the cold runner sets (131) and the number of the hot runner sets (132) are six; the number of cold runners (133) in each set of the cold runner sets (131) is sixteen; the number of hot runners (134) in each of the hot runner groups (132) is sixteen.
7. The heat exchanger for a gas turbine as claimed in claim 2, wherein: an oil injection ring (14) is further fixed on the inner side of the inner wall (11) of the heat exchanger, and a plurality of oil injection nozzles (141) are annularly arranged on one side, close to the air outlet (111), of the oil injection ring (14); a first oil filling pipe (142) is arranged on one side, close to the air outlet (111), of the heat exchanging part (13); one end of the first oil filling pipe (142) penetrates through the heat exchanger outer wall (12) and forms an oil filling opening (143) on the heat exchanger outer wall (12); the other end of the first oil injection pipe (142) is communicated with the oil injection ring (14) through a second oil injection pipe (144) embedded in the inner wall (11) of the heat exchanger.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110469732.5A CN113237097A (en) | 2021-04-28 | 2021-04-28 | Heat exchanger for gas turbine |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110469732.5A CN113237097A (en) | 2021-04-28 | 2021-04-28 | Heat exchanger for gas turbine |
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| CN113237097A true CN113237097A (en) | 2021-08-10 |
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| CN202110469732.5A Pending CN113237097A (en) | 2021-04-28 | 2021-04-28 | Heat exchanger for gas turbine |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114543119A (en) * | 2022-02-28 | 2022-05-27 | 浙江意动科技股份有限公司 | Spiral plate type heat regenerator |
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| CA579273A (en) * | 1959-07-07 | V. Bergstrom Eric | Process and apparatus for hydrocarbon conversion | |
| CN102735089A (en) * | 2011-04-02 | 2012-10-17 | 珠海格力节能环保制冷技术研究中心有限公司 | Heat transfer pipe, and heat and mass transfer equipment having heat transfer pipe |
| CN104501627A (en) * | 2014-12-24 | 2015-04-08 | 高台县聚合热力有限责任公司 | Spiral flat heat exchange unit and spiral flat heat exchanger |
| CN109520101A (en) * | 2018-11-14 | 2019-03-26 | 清华大学 | Heat-recovering fresh air system and working method |
| CN111637492A (en) * | 2020-06-01 | 2020-09-08 | 深圳意动航空科技有限公司 | Heat exchanger and miniature gas turbine |
| CN215637328U (en) * | 2021-04-28 | 2022-01-25 | 浙江意动科技股份有限公司 | Heat exchanger for gas turbine |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114543119A (en) * | 2022-02-28 | 2022-05-27 | 浙江意动科技股份有限公司 | Spiral plate type heat regenerator |
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