CN114279253B - Heat Exchanger - Google Patents
Heat Exchanger Download PDFInfo
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- CN114279253B CN114279253B CN202111677987.7A CN202111677987A CN114279253B CN 114279253 B CN114279253 B CN 114279253B CN 202111677987 A CN202111677987 A CN 202111677987A CN 114279253 B CN114279253 B CN 114279253B
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Abstract
The application provides a heat exchanger, comprising: the shell, both ends of the shell are provided with end covers; the rotating shaft is rotatably arranged on the end cover in a penetrating manner; the impeller set is arranged on the rotating shaft and positioned in the shell, and the impeller set rotates to enable the rotating shaft to rotate; the air inlet and the air outlet are arranged on the side wall of the shell and are respectively positioned at two ends of the shell; the first cooling pipe is connected to the impeller set and positioned in the shell, and can rotate along with the impeller set; the second cooling pipe is arranged on the outer wall of the shell, and the first cooling pipe is communicated with the second cooling pipe. The technical scheme of the application effectively solves the problems of low heat exchange efficiency and difficult treatment of heat exchange of high-temperature high-dust fluid in the related technology.
Description
Technical Field
The application relates to the technical field of heat exchange, in particular to a heat exchanger.
Background
Because of the high temperature and high pressure effect in the coal gasification field, a large amount of high temperature and high pressure gas contained in gas produced from a gasification furnace during gasification enters the ground and enters a gas purification process flow, the high temperature gas with a large amount of sensible heat can be recycled, and the gas with high temperature and high pressure of 400 ℃ and high pressure of 10MPa contains hydrogen (H) 2 ) Carbon monoxide (CO), carbon dioxide (CO) 2 ) And the characteristics of sulfur-containing coal ash dust, the sensible heat in the coal gas can only be used for obtaining recovered heat through indirect heat energy absorption.
In the related art, heat is absorbed by the medium in the pipeline, and the temperature of the heat absorbing medium is further increased by the heat in the gas, but the mode is a conventional double-loop fixed heat exchange mode, and the high-temperature fluid and the low-temperature fluid exchange heat in the fixed circulation wall pipe in the fixed circulation loop, so that the heat exchange efficiency is low, and the heat exchange of the high-temperature and high-dust fluid is difficult to process.
Disclosure of Invention
The application mainly aims to provide a heat exchanger for solving the problems that the heat exchange efficiency in the related art is low and the heat exchange of high-temperature high-dust fluid is difficult to treat.
In order to achieve the above object, the present application provides a heat exchanger comprising: the shell, both ends of the shell are provided with end covers; the rotating shaft is rotatably arranged on the end cover in a penetrating manner; the impeller set is arranged on the rotating shaft and positioned in the shell, and the impeller set rotates to enable the rotating shaft to rotate; the air inlet and the air outlet are arranged on the side wall of the shell and are respectively positioned at two ends of the shell; the first cooling pipe is connected to the impeller set and positioned in the shell, and can rotate along with the impeller set; the second cooling pipe is arranged on the outer wall of the shell, and the first cooling pipe is communicated with the second cooling pipe.
Further, the liquid inlet of the first cooling pipe is positioned at the first end of the rotating shaft, and the liquid outlet of the first cooling pipe is positioned at the second end of the rotating shaft; the liquid inlet of second cooling tube is located the second end of axis of rotation, and the liquid outlet of second cooling tube is located the first end of axis of rotation, and the liquid outlet of second cooling tube communicates with the liquid inlet of first cooling tube.
Further, a first communication hole communicated with the outside is formed in the end part of the first end of the rotating shaft, a second communication hole communicated with the outside is formed in the end part of the second end of the rotating shaft, a third communication hole and a fourth communication hole are formed in the side wall of the rotating shaft, the third communication hole is communicated with the first communication hole, and the fourth communication hole is communicated with the second communication hole; the heat exchanger further comprises a first connecting pipe, a second connecting pipe and a third connecting pipe, wherein the first connecting pipe is connected between the liquid inlet of the first cooling pipe and the third communication hole, the second connecting pipe is connected between the liquid outlet of the first cooling pipe and the fourth communication hole, and the third connecting pipe is connected between the first communication hole and the liquid outlet of the second cooling pipe.
Further, the first communication hole and the second communication hole are axial holes, the third communication hole and the fourth communication hole are radial holes, the axis of the rotating shaft is collinear with the axis of the shell, and the air inlet and the air outlet are symmetrically arranged relative to the center of the shell.
Further, the impeller group includes a plurality of first impellers arranged in the axial direction of the rotating shaft, each of the first impellers including a plurality of first blades arranged in the circumferential direction of the rotating shaft, and a plurality of second impellers, each of the second impellers including one of the second blades, one of the plurality of first impellers being disposed adjacent to the air intake.
Further, the number of the first impellers is two, the two first impellers are respectively arranged at the air inlet and the air outlet, and the plurality of the second impellers are arranged between the two first impellers.
Further, a first included angle a is formed between the second blades of two adjacent second impellers, wherein the first included angle a is between 60 degrees and 120 degrees.
Further, the air inlet is obliquely arranged relative to the rotating shaft, and a second included angle b is formed between the air inlet and the rotating shaft, wherein the second included angle b is between 60 degrees and 75 degrees.
Further, the heat exchanger further comprises a driving motor, the driving motor is in driving connection with the rotating shaft, and a flywheel device is arranged between the driving motor and the rotating shaft.
Further, the first cooling pipe comprises a first pipe, a second pipe, a third pipe and a fourth pipe which are nested, the first pipe, the second pipe, the third pipe and the fourth pipe are spiral pipes, and the first pipe, the second pipe, the third pipe and the fourth pipe are connected with the impeller set.
Further, a first rotary joint is arranged between the third connecting pipe and the first connecting hole, and a second rotary joint is arranged between the second connecting hole and the external pipeline.
Further, the heat exchanger further comprises bearing assemblies, the bearing assemblies are arranged at two ends of the rotating shaft, and sealing elements are arranged at the joints of the rotating shaft and the end parts of the end covers.
Further, the air inlet is positioned at the top of the shell, the air outlet is positioned at the bottom of the shell, and a third included angle c is formed between the air outlet and the axis of the shell, wherein the third included angle c is between 60 degrees and 75 degrees.
By applying the technical scheme of the application, the two ends of the shell are provided with the end covers, the rotating shaft is rotatably arranged in the shell, and the two ends of the rotating shaft are connected with the end covers. The impeller set is arranged on the rotating shaft and positioned in the shell, and the impeller set rotates to enable the rotating shaft to rotate. The air inlet and the air outlet are arranged on the side wall of the shell and are positioned at two ends of the shell, the first cooling pipe is connected to the impeller set and is positioned in the shell, and the first cooling pipe can rotate along with the impeller set. The second cooling pipe is arranged on the outer wall of the shell, and the first cooling pipe is communicated with the second cooling pipe. Through foretell setting, high temperature gas enters into the casing through the air inlet to with impeller group contact, with blowing impeller group, make it rotate, at pivoted in-process, because first cooling tube sets up on the impeller group, make first cooling tube also rotate like this, make first cooling tube can better with high temperature gas contact like this, and then can improve the efficiency of heat transfer effectively. The medium of heat exchange is advanced to the second cooling tube, the medium enters the first cooling tube through the second cooling tube, the second cooling tube can absorb the heat on the shell, the heat exchange efficiency is further improved, and as the temperature of the heat absorbing medium in the second cooling tube is lower than that of the heat absorbing medium in the first cooling tube, the medium is equivalent to preheating in the second cooling tube, when the heat absorbing medium enters the first cooling tube, high-temperature high-pressure gas directly acts on the rotating first cooling tube, so that the temperature of the heat absorbing medium in the first cooling tube is gradually increased to obtain higher temperature, and finally the high-temperature medium is discharged through the first cooling tube to perform subsequent steps (such as power generation), so that the temperature of the medium for performing the subsequent steps can be ensured to be kept at higher level. Meanwhile, due to the rotation effect of the rotating shaft and the impeller set, high-temperature and high-pressure gas flows to the gas outlet in the rotation of the shell, dust in stirring gas flow in the rotation of the impeller set cannot stay in the shell, and the dust is screwed out from the gas outlet along with the high-pressure gas flow. Therefore, the technical scheme of the application effectively solves the problems of lower heat exchange efficiency and difficult treatment of heat exchange of high-temperature high-dust fluid in the related technology.
Drawings
The accompanying drawings, which are included to provide a further understanding of the application and are incorporated in and constitute a part of this specification, illustrate embodiments of the application and together with the description serve to explain the application. In the drawings:
fig. 1 shows a schematic cross-sectional view of an embodiment of a heat exchanger according to the application;
FIG. 2 shows a schematic cross-sectional view of the heat exchanger of FIG. 1 for mounting an impeller assembly;
FIG. 3 shows a schematic cross-sectional view of the housing and impeller set of the heat exchanger of FIG. 1;
FIG. 4 shows a schematic cross-sectional view of the housing of the heat exchanger of FIG. 1;
FIG. 5 shows a schematic side view of the heat exchanger of FIG. 1;
FIG. 6 shows a schematic view of the structure of a first cooling tube of the heat exchanger of FIG. 1;
FIG. 7 shows a schematic side view of the first cooling tube of FIG. 6;
fig. 8 shows a schematic structural view of a second cooling tube of the heat exchanger of fig. 1.
Wherein the above figures include the following reference numerals:
10. a housing; 11. an end cap; 20. a rotating shaft; 21. a first communication hole; 22. a second communication hole; 23. a third communication hole; 24. a fourth communication hole; 30. an impeller set; 31. a first impeller; 311. a first blade; 32. a second impeller; 321. a second blade; 41. an air inlet; 42. an air outlet; 50. a first cooling tube; 51. a first tube; 52. a second tube; 53. a third tube; 54. a fourth pipe; 60. a second cooling tube; 71. a first connection pipe; 72. a second connection pipe; 73. and a third connection pipe.
Detailed Description
The following description of the embodiments of the present application will be made clearly and completely with reference to the accompanying drawings, in which it is apparent that the embodiments described are only some embodiments of the present application, but not all embodiments. The following description of at least one exemplary embodiment is merely exemplary in nature and is in no way intended to limit the application, its application, or uses. All other embodiments, which can be made by those skilled in the art based on the embodiments of the application without making any inventive effort, are intended to be within the scope of the application.
It is noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of exemplary embodiments according to the present application. As used herein, the singular is also intended to include the plural unless the context clearly indicates otherwise, and furthermore, it is to be understood that the terms "comprises" and/or "comprising" when used in this specification are taken to specify the presence of stated features, steps, operations, devices, components, and/or combinations thereof.
The relative arrangement of the components and steps, numerical expressions and numerical values set forth in these embodiments do not limit the scope of the present application unless it is specifically stated otherwise. Meanwhile, it should be understood that the sizes of the respective parts shown in the drawings are not drawn in actual scale for convenience of description. Techniques, methods, and apparatus known to one of ordinary skill in the relevant art may not be discussed in detail, but should be considered part of the authorization specification where appropriate. In all examples shown and discussed herein, any specific values should be construed as merely illustrative, and not a limitation. Thus, other examples of the exemplary embodiments may have different values. It should be noted that: like reference numerals and letters denote like items in the following figures, and thus once an item is defined in one figure, no further discussion thereof is necessary in subsequent figures.
As shown in fig. 1 to 5, in the present embodiment, the heat exchanger includes: the casing 10, the rotation shaft 20, the impeller assembly 30, the air inlet 41, the air outlet 42, the first cooling pipe 50, and the second cooling pipe 60. End caps 11 are provided at both ends of the housing 10. The rotating shaft 20 is rotatably inserted through the end cover 11. The impeller assembly 30 is disposed on the rotation shaft 20 and within the housing 10, and the impeller assembly 30 rotates to rotate the rotation shaft 20. The air inlet 41 and the air outlet 42 are provided on the side wall of the housing 10 and are located at both ends of the housing 10, respectively. The first cooling tube 50 is connected to the impeller assembly 30 and is located inside the casing 10, and the first cooling tube 50 can rotate with the impeller assembly 30. The second cooling pipe 60 is provided on the outer wall of the housing 10, and the first cooling pipe 50 and the second cooling pipe 60 communicate.
By applying the technical scheme of the embodiment, the two ends of the shell 10 are provided with the end covers 11, the rotating shaft 20 is rotatably arranged in the shell 10, and the two ends of the rotating shaft 20 are connected with the end covers 11. The impeller assembly 30 is disposed on the rotation shaft 20 and inside the casing 10, and the impeller assembly 30 rotates to rotate the rotation shaft 20. The air inlet 41 and the air outlet 42 are provided on the side wall of the housing 10 at both ends of the housing 10, and the first cooling pipe 50 is connected to the impeller assembly 30 and located inside the housing 10, and the first cooling pipe 50 can rotate with the impeller assembly 30. The second cooling pipe 60 is provided on the outer wall of the housing 10, and the first cooling pipe 50 and the second cooling pipe 60 communicate. Through the above arrangement, the high temperature gas enters the housing 10 through the gas inlet 41 and contacts with the impeller assembly 30 to blow the impeller assembly 30 to rotate, and in the rotating process, the first cooling tube 50 is arranged on the impeller assembly 30, so that the first cooling tube 50 also rotates, and the first cooling tube 50 can better contact with the high temperature gas in the rotating stirring process, so that the heat exchange efficiency can be effectively improved. The heat absorbing medium of heat exchange enters the second cooling tube 60 and then enters the first cooling tube 50 through the second cooling tube 60, the second cooling tube 60 can absorb heat on the shell 10 to be preheated, heat exchange efficiency is further improved, and as the temperature of the medium in the second cooling tube 60 is lower than that of the medium in the first cooling tube 50, the medium is preheated in the second cooling tube 60, when the medium enters the first cooling tube 50, high-temperature high-pressure gas directly acts on the rotating first cooling tube 50, so that the temperature of the heat absorbing medium in the first cooling tube 50 is gradually increased to be kept at a higher temperature, finally the medium is discharged through the first cooling tube 50 to perform subsequent steps (such as power generation), and the temperature of the medium for performing the subsequent steps can be ensured to be kept at a higher level. Meanwhile, due to the rotation action of the rotating shaft 20 and the impeller set 30, high-temperature and high-pressure gas flows to the gas outlet 42 in the rotation of the shell, dust in the stirring gas flow in the rotation of the impeller set blades cannot stay and accumulate in the shell, and the dust is rotated out of the gas outlet along with the high-pressure gas flow. Therefore, the technical scheme of the embodiment effectively solves the problems of low heat exchange efficiency and difficult treatment of heat exchange of high-temperature high-dust fluid in the related technology.
The high-temperature gas is high-pressure gas with a high temperature of 400 ℃ and a high pressure of 10 MPa.
The air inlet 41 enters the housing 10 from the circumferential edge of the housing 10 from top to bottom at the rear side of the rotation shaft 20 to form a rotational flow, and the air outlet 42 flows out horizontally from the circumferential edge of the housing 10 from inside to outside at the lower side of the rotation shaft 20.
The rotation of the first cooling pipe 50 and the impeller set 30 in the shell 10 breaks up the shape of the original cyclone gas flow to generate vortex flow so as to enable the high-temperature gas flow to form irregular unstable vortex turbulence flow, so that collision interaction between the gas and the first cooling pipe 50 is increased, and spiral vortex cyclone flow is formed in the shell 10 so as to increase contact between the first cooling pipe 50 and the rotating gas, and heat exchange efficiency is improved. Meanwhile, the impeller set 30 rotates to play a blowing role, so that the problem of high-temperature and high-pressure gas sensible heat efficient recovery with high coal ash content is solved, and the cleaning role of gas dust is also solved. Outside the inlet and outlet positions of the heat exchange pipelines at the left side and the right side of the rotary first cooling pipe 50 are connected with the fluid interfaces of the rotary shaft 20, a three-blade impeller (first blade 311) is respectively arranged, the left side corresponds to the high-temperature high-pressure gas inlet 41, the first blade 311 forms an included angle of 45 degrees with gas inlet air flow, the air flow directly blows the first blade 311 to rotate so as to drive the first cooling pipe 50 to rotate, meanwhile, the three-blade impeller forms a rotary guiding function on the gas air flow, so that the gas passes through and rotates out of an air outlet in the rotation of the shell 10, the three-blade impeller (first blade 311) arranged at the right side corresponds to the gas outlet 42, and the three-blade impeller in the rotation blows the gas dust at the tail end in the shell 10 to flow out of the heat exchanger. A single blade (a second blade 321) penetrating through a main shaft is arranged between pitches of a 3 rd spiral right tube from the left side of the heat exchanger, the second blade 321 is fixedly positioned and fixed with the rotating shaft 20, meanwhile, the second blade 321 is tightly attached to the first cooling tube 50 and welded together, a second blade 321 is sequentially arranged at intervals of three spirals backwards, the orientation of each second blade 321 corresponds to the upper and lower directions of the previous second blade 321, and a spiral staggered installation rotating direction is formed from left to right front and back blades.
As shown in fig. 1 to 8, in the present embodiment, the liquid inlet of the first cooling tube 50 is located at the first end of the rotating shaft 20, and the liquid outlet of the first cooling tube 50 is located at the second end of the rotating shaft 20; the liquid inlet of the second cooling pipe 60 is located at the second end of the rotating shaft 20, the liquid outlet of the second cooling pipe 60 is located at the first end of the rotating shaft 20, and the liquid outlet of the second cooling pipe 60 is communicated with the liquid inlet of the first cooling pipe 50. The above arrangement enables the first cooling pipe 50 and the second cooling pipe 60 to communicate, thereby effectively realizing the flow of the medium in the first cooling pipe 50 and the second cooling pipe 60. The first cooling pipe 50 and the second cooling pipe 60 form a circulation line by a rotary joint mounted at a first end of the rotary shaft 20.
As shown in fig. 1 to 8, in the present embodiment, the end of the first end of the rotation shaft 20 is provided with a first communication hole 21 communicating with the outside, the end of the second end of the rotation shaft 20 is provided with a second communication hole 22 communicating with the outside, a third communication hole 23 and a fourth communication hole 24 are provided on the side wall of the rotation shaft 20, the third communication hole 23 communicates with the first communication hole 21, and the fourth communication hole 24 communicates with the second communication hole 22; the heat exchanger further includes a first connection pipe 71, a second connection pipe 72, and a third connection pipe 73, the first connection pipe 71 being connected between the liquid inlet of the first cooling pipe 50 and the third communication hole 23, the second connection pipe 72 being connected between the liquid outlet of the first cooling pipe 50 and the fourth communication hole 24, the third connection pipe 73 being connected between the first communication hole 21 and the liquid outlet of the second cooling pipe 60. The first communication hole 21, the second communication hole 22, the third communication hole 23, and the fourth communication hole 24 are provided on the rotation shaft 20, that is, the rotation shaft 20 is drilled, and the first cooling pipe 50 and the first communication hole 21 are communicated through the first connection pipe 71 and the second connection pipe 72, so that the rotation of the first cooling pipe 50 can be effectively realized and the first cooling pipe 50 does not have a pipe folding condition. Specifically, the first connection pipe 71 is connected between the liquid inlet of the first cooling pipe 50 and the third communication hole 23, and the second connection pipe 72 is connected between the liquid outlet of the first cooling pipe 50 and the fourth communication hole 24. Meanwhile, since the third connection pipe 73 is connected to the liquid outlets of the first and second communication holes 21 and 60, the first and second cooling pipes 50 and 60 are effectively conducted.
As shown in fig. 1 to 8, in the present embodiment, the first communication hole 21 and the second communication hole 22 are axial holes, the third communication hole 23 and the fourth communication hole 24 are radial holes, the axis of the rotation shaft 20 is collinear with the axis of the housing 10, and the air inlet 41 and the air outlet 42 are disposed symmetrically with respect to the center of the housing 10. The arrangement mode is simple, and the device can be effectively matched with related structures.
The impeller assembly 30 includes a plurality of first impellers 31 and a plurality of second impellers 32 arranged in the axial direction of the rotating shaft 20, each first impeller 31 including a plurality of first blades 311 arranged in the circumferential direction of the rotating shaft 20, each second impeller 32 including one second blade 321, one of the plurality of first impellers 31 being disposed adjacent to the air intake 41. The plurality of first impellers 31 and the plurality of second impellers 32 are arranged to effect rotation. Specifically, the first impeller 31 includes a plurality of first blades 311, the second impeller 32 includes a second blade 321, and one of the plurality of first impellers 31 is disposed adjacent to the air inlet 41 in such a manner that the high-temperature gas can contact the first blades 311 at a first time, thereby blowing the first blades 311. The second impeller 32 is provided with only one second blade 321 in order to reduce the overall weight, thereby making the rotation of the rotation shaft easier.
As shown in fig. 1 to 8, in the present embodiment, there are two first impellers 31, two first impellers 31 are provided at an air inlet 41 and an air outlet 42, respectively, and a plurality of second impellers 32 are provided between the two first impellers 31. The above arrangement can effectively ensure the blowing of the high-temperature gas to the impeller assembly 30, and can smoothly be discharged through the gas outlet under the action of the first vane 311.
In an embodiment not shown in the figures, only one first impeller is provided, the rest being provided with a plurality of second impellers, which also enables the rotation of the rotating shaft.
As shown in fig. 1 to 8, in the present embodiment, the second blades 321 of the adjacent two second impellers 32 have a first included angle a therebetween, wherein the first included angle a is between 60 ° and 120 °. The above arrangement is to ensure that the plurality of second impellers 32 are arranged to make the overall quality of the rotating shaft 20 more uniform, so that the plurality of second blades 321 are prevented from being positioned on the same side, and thus the situation that rotation cannot occur easily occurs, and therefore, in order to avoid the above situation, the second blades 321 of the adjacent second impellers 32 are required to be arranged in a staggered manner. Specifically, in the present embodiment, the first included angle a is 90 °, that is, 360 ° is enclosed by the second blades of the adjacent four second impellers 32. This ensures uniform overall quality.
As shown in fig. 1 to 8, in the present embodiment, the air inlet 41 is disposed obliquely with respect to the rotation shaft 20, and a second angle b is formed between the air inlet 41 and the rotation shaft 20, wherein the second angle b is between 60 ° and 75 °. The above-described inclined arrangement of the inlet port 41 is to facilitate the direct blowing of the high-temperature gas onto the first vane 311. Specifically, in the present embodiment, the second included angle b is 75 °.
As shown in fig. 1 to 8, in the present embodiment, the heat exchanger further includes a driving motor, which is drivingly connected to the rotating shaft 20, and a flywheel device is provided between the driving motor and the rotating shaft 20. The driving motor is provided to blow against the high temperature gas in the initial stage, and the impeller assembly 30 rotates slowly or hardly, so that the driving motor is required to drive the rotating shaft to rotate to increase the rotating speed. The flywheel means accelerates the rotation speed when the high pressure gas drives the impeller assembly 30 and the first cooling pipe 50 to rotate. The flywheel device is mounted on the shaft 20 between the swivel joint and the shaft cover.
As shown in fig. 1 to 8, in the present embodiment, the first cooling pipe 50 includes a first pipe 51, a second pipe 52, a third pipe 53, and a fourth pipe 54 that are nested, and each of the first pipe 51, the second pipe 52, the third pipe 53, and the fourth pipe 54 is a spiral pipe, and each of the first pipe 51, the second pipe 52, the third pipe 53, and the fourth pipe 54 is connected to the impeller assembly 30. The arrangement of the first pipe 51, the second pipe 52, the third pipe 53 and the fourth pipe 54 can effectively improve the heat exchange efficiency, and ensure that a large amount of medium can be contacted with high-temperature gas in the same time.
As shown in fig. 1 to 8, in the present embodiment, a first rotary joint is provided between the third connection pipe 73 and the first communication hole 21, and a second rotary joint is provided between the second communication hole 22 and the external pipe. The first rotary joint and the second rotary joint can realize one-side rotation, one side is fixed, the sealing effect is good, and the high-temperature heat absorption medium can be prevented from overflowing through the rotary joint.
As shown in fig. 1 to 8, in the present embodiment, the heat exchanger further includes bearing assemblies provided at both ends of the rotation shaft 20, and a sealing member is provided at the junction of the rotation shaft 20 and the end of the end cover 11. The sealing member is provided to further improve the overall sealing effect and ensure that high temperature and high pressure gas can not escape from the housing 10.
As shown in fig. 1 to 8, in the present embodiment, the air inlet 41 is located at the top circumferential shell side of the housing 10, the air outlet 42 is located at the bottom circumferential shell side of the housing 10, and a third included angle c is formed between the air outlet 42 and the axis of the housing 10, wherein the third included angle c is between 60 ° and 75 °. The above-mentioned angle is set to facilitate the outflow of the high-temperature gas, and specifically, in this embodiment, the third included angle c is 75 °.
The heat exchanger of this embodiment has two sets of coil heat exchange pipelines (a first cooling pipe 50 and a second cooling pipe 60) inside and outside, the second cooling pipe 60 is circularly fixed on the shell 10, the first cooling pipe 50 is formed by multi-level circular rotating moving coil pipes with different diameters in a stacked manner at intervals, the space between the stacked pipes is 1-time pipe diameter space, the pitch between the spiral pipes is coiled according to the pipe diameter by taking the axial width of the impeller group 30 supporting the first cooling pipe 50 as a basis, the impeller group 30 similar to a paddle is integrally installed with the rotating shaft 20, the stacked first cooling pipe 50 forms a complete rotating body with the rotating shaft 20 through a second vane 321 which is distributed at intervals, the rotating shaft 20 is fixed with two ports of the shell 10 through a high-temperature rotating joint installed at two ports, the first cooling pipe 50 realizes the rotation of the first cooling pipe 50 and keeps the communicating butt joint of the first cooling pipe 50 and the second cooling pipe 60, the inlet of the cooling liquid second cooling pipe 60 enters the first cooling pipe 50, the tail end of the second cooling pipe 60 is connected with the rotating joint, the cooling heat exchange heat of the absorbing shell 10 enters the first cooling pipe 50, and the sensible heat of a working medium is directly absorbed by the second cooling medium and absorbs the sensible heat of gas, and the heat of the gas is directly absorbed by the rotating joint.
A bearing assembly is arranged around the shaft hole of the end cover 11 through holes between the rotating shaft 20 and the end covers 11 at the two ends of the shell 10, the first cooling pipe 50 is fixed with the bearing of the bearing assembly, the contact surfaces of the rotating shaft 20 and the supporting plate of the end cover 11 are sealed internally and externally by adopting high-temperature and high-pressure sealant, a hole gap between the rotating shaft 20 and the end cover 11 of the high-temperature and high-speed rotating oil seal-sealing secondary seal is arranged at the outer side of the shell 10, the pressure bearing of the internal sealant is 35MPa/650 ℃, and the pressure bearing of the external high-temperature and high-speed rotating sealing secondary seal is 27MPa/300 ℃.
The working conditions of the first cooling tube 50 and the second cooling tube 60 of the heat exchanger of the embodiment are different, so that heat exchange efficiency is improved by selecting heat exchange pipelines made of different materials according to characteristics of coal gas, the vortex turbulence heat exchanger maintains the advantages of the existing shell-and-tube heat exchanger, namely, the advantages of high pressure bearing and simple structure, and the impeller set 30 rotates along with the coal gas flow to cause the coal gas flow in the heat exchanger to form harmonic oscillation vortex turbulence aiming at the characteristic that coal gas contains coal ash, thereby accelerating the opposite flushing area and contact time of sensible heat of the coal gas and the first cooling tube 50 and improving heat exchange efficiency. The first cooling pipe 50 and the impeller set 30 rotate and accelerate the centrifugal force of the gas in the heat exchanger, and the gas flow is not smooth due to the accumulation of coal ash, so that the high-temperature and high-pressure gas flow is designed, the air inlet 41 is a side cut in between the axes of the shell 10 at one side of the rotating shaft 20 or a vortex flow direction with an included angle of 45-60 degrees at the side, the gas naturally forms a vortex shape along the inner wall of the shell 10 in the entering shell 10, and the air outlet 42 is positioned at the side outside the central axis of the port of the shell 10 or forms an included angle of 90 degrees with the inlet and outlet ports of the gas at the centrifugal outlet of 45-60 degrees at the shell. The heat exchanger can be vertically arranged or horizontally arranged, and the coal gas outlet is arranged at the bottom of the heat exchanger in any arrangement mode, so that coal ash emission is facilitated;
the first cooling pipes 50 are welded together in the impeller set 30 in a staggered manner along the axis by 120 degrees, independent single second blades 321 are separated by a blade axial length, sine waves oscillate when waves are formed when air flows are caused to rotate between the staggered blades, 120 degrees are distributed between every two second blades 321, the second blades 321 are fixed with the rotating shaft 20 through bayonet pins, the second blades 321 support and centralize the first cooling pipes 50 to form an integrated multi-pipeline conical structure with the rotating shaft 20, the second blades 321 and the first blades 311 form a 60-degree deflection inclination angle with the rotating shaft 20, the deflection inclination angle enables the blades to form a 60-degree included angle with the high-temperature high-pressure air inlet angle on the shell 10, 45-degree included angle is formed between the air flows and the blades, so that when the high-pressure air causes thrust to the first cooling pipes 50 and is not at right angles, the first blades 311 are arranged at the left side near the air inlet 41, the high-pressure air flows push the impeller set 30 to rotate when the high-temperature air flows enter the heat exchanger, thereby forming shear type exchange between the air and the first cooling pipes 50 in the shell 10, the air flows axially enter the shell 10, the high-temperature air flows form a spiral heat exchange channel, the air flows exchange efficiency is improved, the air flows and the air flows are blown out of the impeller set, and the air flows are cooled by the impeller set is accelerated, and the air flows are cooled by the air flow and the impeller set is cooled by the centrifugal heat exchange device is accelerated, and the air is cooled by the air flow and the air flow is simultaneously.
The heat exchanger of the embodiment is heat exchange equipment which is independently suitable for high-temperature high-pressure high-dust fluid environments, and can be used for heat exchange of any type of high-dust fluid or combined use. The test pressure is not less than 15MPa.
The second cooling tube 60 of the heat exchanger of the embodiment is welded with the housing 10 to form a spiral structure and is in contact with the atmosphere, copper tubes are selected to be used for manufacturing the second cooling tube 60 for improving heat exchange efficiency, and heat insulation materials are wound outside the second cooling tube 60 to reduce heat dissipation. For the first cooling pipe 50 in the heat exchanger to work in the environment of high temperature, high pressure, dust and sulfur-containing corrosion, copper pipes and stainless steel pipes can be adopted, or carbon steel pipes can be processed into heat exchange pipes in containers, the carbon steel pipes are low in cost and higher in impact strength than copper pipes and stainless steel pipes, the heat conductivity coefficient is equivalent to that of the stainless steel pipes, and the carbon steel pipes or the stainless steel pipes can be selected for the rotating spiral coil pipes in the actual working conditions of high temperature, high pressure coal gas.
Among the materials of which the first cooling tube 50 is made, the heat conductivity of copper tubes is the best, and the heat conductivity of copper tubes of different thicknesses are slightly different. The heat conductivity coefficient of the stainless steel tube is lower than that of the carbon steel tube, but the water quantity of carbon elements in the carbon steel tube can prevent heat transfer, and the heat conductivity coefficients of the three tubes are respectively: copper pipe: λ= 379.14W/(m.°c); stainless steel tube: λ=10 to 30W/(m.°c), carbon steel pipe: 1.0% carbon is 29W/(m. Degree.C.) and 0.5% carbon is 31W/(m. Degree.C.).
The advantages of copper pipe, stainless steel pipe and carbon steel pipe are as follows:
the highest heat exchange coefficient of the copper pipe also represents stronger heat conduction capacity, but in actual use, the wear-resistant impact and hardness of the copper pipe are weaker than those of a stainless steel pipe, so that the thickness of the copper pipe cannot be lower than 0.8 thickness according to the use condition, the thickness of the copper pipe cannot be lower than 1 thickness when the temperature is high, the copper pipe is possibly damaged due to impact of high-temperature high-pressure dust gas, and the thickness of the copper pipe is required to be thickened to be not lower than 1.2mm.
The heat conductivity of the stainless steel tube is far less than that of the copper tube, but the hardness and impact resistance of the stainless steel tube are better than those of the copper tube, so that the thickness of the stainless steel tube can be properly reduced in the same environment, the wall thickness is reduced, and the heat exchange efficiency can be balanced with the copper tube. The stainless steel tube has good high temperature resistance, and can reach 1000-1200 ℃. The 304 stainless steel has excellent stainless corrosion resistance and better intergranular corrosion resistance, and also has good corrosion resistance to alkaline solution and most of organic acid and inorganic acid.
The carbon steel pipe has the heat conductivity coefficient of purity, and the heat transfer value of carbon is very low, so that the heat exchange rate of heat can be caused to a certain extent. And the higher the carbon content is, the corrosion and impact resistance of the carbon steel pipe are affected, and the corrosion resistance and the service life of the carbon steel pipe are also affected even if the surface treatment is performed in a high-temperature high-pressure high-dust environment. The weight of the carbon steel tube is heavier than that of the steel tube and the stainless steel tube, and the weight can influence the rotating speed during rotation so as to reduce the heat exchange efficiency.
The heat exchange/transfer coefficient is calculated as follows:
the heat exchange/transfer coefficient refers to the heat transferred per unit time through a unit area in watts/(square meter·degree) under the condition of stable heat transfer, wherein the temperature difference of air at two sides of the enclosure structure is 1 degree (K or ℃).
And a heat conduction calculation formula: rc=δ/λ, wherein: rc-thermal resistance, m 2 .K/w。
The heat transfer coefficient k=1/rc=λ/δ, λ—the heat conductivity coefficient W/(m.°c). Delta-pipe wall thickness m, when the pipe wall thickness m is constant and lambda is unchanged, the smaller the pipe wall of the delta pipe is according to the formula, the smaller the Rc heat conduction resistance is, the larger the heat exchange coefficient is, the smaller the object heat conduction resistance is, the material heat conduction coefficient is fixed under certain conditions, and the larger the heat exchange coefficient is, the higher the heat exchange efficiency is. This reduces the difference in overall heat transfer coefficients of the stainless steel tube and copper tube. The outer wall of the stainless steel tube is smoother and finer than the outer wall of the copper tube, so that scale is not easy to form, and the stainless steel tube has certain advantages in use.
The heat exchange parameter table and the corrosion resistance parameter table are as follows:
engineering properties of stainless steel pipe and copper pipe
| Pipe material | Copper pipe | Nickel copper pipe | 304/316 stainless steel pipe |
| Density t/m3 | 8.4 | 8.9 | 8 |
| Yield strength MPa | 120 | 140 | 280-350 |
| Tensile strength MPa | 330 | 390 | 550-659 |
| Elongation percentage% | 60 | 43 | 30-60 |
| Modulus of elasticity MPa | 13.3 | 15.4 | 20 |
| Coefficient of thermal expansion 10-6 | 16 | 16 | 17 |
| Thermal conductivity w/mk | 100 | 30 | 13 |
Corrosion resistance of stainless steel pipe and copper pipe
| Corrosion species | Copper pipe | Nickel copper pipe | 304/316 stainless steel pipe |
| General corrosion of | 2 | 4 | 5 |
| Impact corrosion | 2 | 5 | 6 |
| Pitting corrosion (running state) | 4 | 5 | 4 |
| Pitting (accumulation state) | 2 | 4 | 2 |
| High-speed impact | 3 | 5 | 6 |
| Inlet impingement | 2 | 4 | 6 |
| Steam hot spot corrosion | 2 | 4 | 6 |
| Ammonia etching | 2 | 5 | 6 |
In a closed cooling tower and an evaporative condenser under the condition of normal heat exchange-free pressure air, the heat conductivity coefficient of a copper pipe is highest, and the heat conductivity coefficient of a stainless steel pipe is lowest, but the heat conductivity coefficients of two materials can be adjusted by controlling the wall thickness; in the comparison of the heat conducting performance of the copper pipe and the stainless steel heat exchange pipe, the heat conducting coefficient of the copper pipe is 100W/m.K, the heat conducting coefficient of the stainless steel pipe is 13W/m.K, and the overall heat conducting coefficient is influenced by the stainless steel pipe. However, the wall thickness of the stainless steel tube can be thinned to 0.5-0.8 mm, and the yield strength is still very high, while the wall thickness of the copper tube cannot be lower than 1.2mm due to strength, erosive wear and other reasons, and the wall thickness is expressed in the formula Rc=delta/lambda: rc-thermal resistance, m.K/w.lambda-thermal conductivity, W/(m.K). Delta-when the tube wall thickness m is selected and lambda is unchanged, the smaller the tube wall thickness delta is, the smaller the Rc heat conduction resistance is, and the larger the heat transfer coefficient is, so that the difference between the overall heat transfer coefficients of the stainless steel tube and the copper tube can be reduced. Because the inner and outer walls of the copper pipe are coarser than stainless steel, scaling is easy. However, the stainless steel tube has a more compact and fine surface structure than the copper tube, is not easy to generate scale, has certain advantages compared with the copper tube in use, is used for a long time, and has better use economy as the overall heat exchange coefficient of the stainless steel tube is reduced more slowly than the copper tube along with the increase of the scale.
According to the heat exchange analysis of materials, the steel tube, the stainless steel tube and the carbon steel tube can be applied to the practice of the first cooling tube in the heat exchanger, the cooling liquid is first selected by high-temperature heat conduction oil, the first cooling tube is selected by the stainless steel tube or the thin-wall carbon steel tube, and the second cooling tube is first selected by the copper tube. The total heat exchange of the first cooling pipe of the heat exchanger of the embodiment is equal to the sum of heat exchange of each stage of coil pipes when the multi-layer coil pipes are used for heat exchange of coal gas, the increase of the number of stages of the spiral coil pipes increases the contact area of the convection coal gas, and the vortex turbulence also improves the collision between the coal gas and the heat exchange coil pipes, so that the heat exchange efficiency is improved.
The heat recovery heat value and temperature detection unit is designed and installed on an outlet pipeline of the low-temperature heat conducting medium of the heat exchanger, the detection unit sends data to the heat recovery control module according to the outlet parameter setting of the heat exchange medium, and the heat recovery control module regulates and controls the pressure and flow parameters of the heat exchange medium, so that the heat exchange medium can provide heat energy supply for the subsequent ORC power generation and carbon dioxide CO2 stripping device in a stable temperature range.
In the description of the present application, it should be understood that the azimuth or positional relationships indicated by the azimuth terms such as "front, rear, upper, lower, left, right", "lateral, vertical, horizontal", and "top, bottom", etc., are generally based on the azimuth or positional relationships shown in the drawings, merely to facilitate description of the present application and simplify the description, and these azimuth terms do not indicate and imply that the apparatus or elements referred to must have a specific azimuth or be constructed and operated in a specific azimuth, and thus should not be construed as limiting the scope of protection of the present application; the orientation word "inner and outer" refers to inner and outer relative to the contour of the respective component itself.
Spatially relative terms, such as "above … …," "above … …," "upper surface at … …," "above," and the like, may be used herein for ease of description to describe one device or feature's spatial location relative to another device or feature as illustrated in the figures. It will be understood that the spatially relative terms are intended to encompass different orientations in use or operation in addition to the orientation depicted in the figures. For example, if the device in the figures is turned over, elements described as "above" or "over" other devices or structures would then be oriented "below" or "beneath" the other devices or structures. Thus, the exemplary term "above … …" may include both orientations of "above … …" and "below … …". The device may also be positioned in other different ways (rotated 90 degrees or at other orientations) and the spatially relative descriptors used herein interpreted accordingly.
In addition, the terms "first", "second", etc. are used to define the components, and are only for convenience of distinguishing the corresponding components, and the terms have no special meaning unless otherwise stated, and therefore should not be construed as limiting the scope of the present application.
The above description is only of the preferred embodiments of the present application and is not intended to limit the present application, but various modifications and variations can be made to the present application by those skilled in the art. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present application should be included in the protection scope of the present application.
Claims (8)
1. A heat exchanger, comprising:
the shell (10), two ends of the shell (10) are provided with end covers (11);
the rotating shaft (20) is rotatably arranged on the end cover (11) in a penetrating manner;
an impeller set (30) disposed on the rotation shaft (20) and located within the housing (10), the impeller set (30) rotating to rotate the rotation shaft (20);
the air inlet (41) and the air outlet (42) are arranged on the side wall of the shell (10) and are respectively positioned at two ends of the shell (10);
a first cooling tube (50) connected to the impeller assembly (30) and located inside the housing (10), the first cooling tube (50) being rotatable with the impeller assembly (30);
a second cooling pipe (60) provided on the outer wall of the housing (10), the first cooling pipe (50) being in communication with the second cooling pipe (60);
the liquid inlet of the first cooling pipe (50) is positioned at the first end of the rotating shaft (20), and the liquid outlet of the first cooling pipe (50) is positioned at the second end of the rotating shaft (20); the liquid inlet of the second cooling pipe (60) is positioned at the second end of the rotating shaft (20), the liquid outlet of the second cooling pipe (60) is positioned at the first end of the rotating shaft (20), and the liquid outlet of the second cooling pipe (60) is communicated with the liquid inlet of the first cooling pipe (50);
a first communication hole (21) communicated with the outside is formed in the end part of the first end of the rotating shaft (20), a second communication hole (22) communicated with the outside is formed in the end part of the second end of the rotating shaft (20), a third communication hole (23) and a fourth communication hole (24) are formed in the side wall of the rotating shaft (20), the third communication hole (23) is communicated with the first communication hole (21), and the fourth communication hole (24) is communicated with the second communication hole (22); the heat exchanger further comprises a first connecting pipe (71), a second connecting pipe (72) and a third connecting pipe (73), wherein the first connecting pipe (71) is connected between a liquid inlet of the first cooling pipe (50) and the third communication hole (23), the second connecting pipe (72) is connected between a liquid outlet of the first cooling pipe (50) and the fourth communication hole (24), and the third connecting pipe (73) is connected between the first communication hole (21) and a liquid outlet of the second cooling pipe (60);
-the impeller assembly (30) comprises a plurality of first impellers (31) and a plurality of second impellers (32) arranged in the axial direction of the rotation shaft (20), each of the first impellers (31) comprising a plurality of first blades (311) arranged in the circumferential direction of the rotation shaft (20), each of the second impellers (32) comprising one second blade (321), one of the plurality of first impellers (31) being arranged adjacent to the air inlet (41);
the number of the first impellers (31) is two, the two first impellers (31) are respectively arranged at the air inlet (41) and the air outlet (42), and the plurality of the second impellers (32) are arranged between the two first impellers (31);
the first cooling pipe (50) comprises a first pipe (51), a second pipe (52), a third pipe (53) and a fourth pipe (54) which are arranged in a nested mode, wherein the first pipe (51), the second pipe (52), the third pipe (53) and the fourth pipe (54) are spiral pipes, and the first pipe (51), the second pipe (52), the third pipe (53) and the fourth pipe (54) are connected with the impeller set (30).
2. The heat exchanger according to claim 1, wherein the first communication hole (21) and the second communication hole (22) are axial holes, the third communication hole (23) and the fourth communication hole (24) are radial holes, the axis of the rotation shaft (20) is collinear with the axis of the housing (10), and the air inlet (41) and the air outlet (42) are disposed symmetrically with respect to the center of the housing (10).
3. The heat exchanger according to claim 1, wherein the second blades (321) of two adjacent second impellers (32) have a first angle a therebetween, wherein the first angle a is between 60 ° and 120 °.
4. The heat exchanger according to claim 1, wherein the air inlet (41) is arranged obliquely with respect to the rotational axis (20), the air inlet (41) and the rotational axis (20) having a second angle b therebetween, wherein the second angle b is between 60 ° and 75 °.
5. The heat exchanger according to claim 1, further comprising a drive motor, which is drivingly connected to the rotation shaft (20), wherein a flywheel device is arranged between the drive motor and the rotation shaft (20).
6. The heat exchanger according to claim 1, wherein a first swivel joint is provided between the third connection pipe (73) and the first communication hole (21), and a second swivel joint is provided between the second communication hole (22) and an external pipe.
7. The heat exchanger according to claim 1, further comprising bearing assemblies provided at both ends of the rotating shaft (20), a seal being provided at the junction of the rotating shaft (20) and the end of the end cap (11).
8. The heat exchanger according to claim 1, wherein the air inlet (41) is located at the top of the housing (10), the air outlet (42) is located at the bottom of the housing (10), and a third angle c is formed between the air outlet (42) and the axis of the housing (10), wherein the third angle c is between 60 ° and 75 °.
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| CN116105507B (en) * | 2022-12-06 | 2023-08-15 | 南京华电节能环保股份有限公司 | Coke oven flue waste gas waste heat recovery mechanism |
| CN117433327B (en) * | 2023-12-20 | 2024-03-08 | 宝鸡宏顺达钛业有限公司 | Tube type condenser |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201964782U (en) * | 2010-12-31 | 2011-09-07 | 邹岳明 | Converter with high-temperature heat recovery and utilization effect |
| CN104501623A (en) * | 2014-12-15 | 2015-04-08 | 刘坚 | Barrel-shaped component for cooling and heating |
| CN205332851U (en) * | 2015-10-24 | 2016-06-22 | 湖南长海现代实验室设备有限公司 | Coil type heat exchanger |
| ITUB20156040A1 (en) * | 2015-12-01 | 2017-06-01 | Simm Toscana S R L | COOLER FOR GRANULAR SOLIDS |
| CN108534569A (en) * | 2018-04-20 | 2018-09-14 | 杨艺 | A kind of efficient heat exchanger |
| CN108571836A (en) * | 2018-05-22 | 2018-09-25 | 河北旺源管业有限公司 | A kind of permeable sewage geothermal source ductwork type heat exchange heat pump system |
| CN109386994A (en) * | 2017-08-03 | 2019-02-26 | 沈阳天洁环保新能源有限公司 | Efficient rotary pipe type heat transfer evaporator and heat-exchange method |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20100051233A1 (en) * | 2008-09-02 | 2010-03-04 | Preston Whitney | Heat-transferring, hollow-flight screw conveyor |
| US8578733B2 (en) * | 2009-01-21 | 2013-11-12 | Appollo Wind Technologies Llc | Turbo-compressor-condenser-expander |
-
2021
- 2021-12-31 CN CN202111677987.7A patent/CN114279253B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201964782U (en) * | 2010-12-31 | 2011-09-07 | 邹岳明 | Converter with high-temperature heat recovery and utilization effect |
| CN104501623A (en) * | 2014-12-15 | 2015-04-08 | 刘坚 | Barrel-shaped component for cooling and heating |
| CN205332851U (en) * | 2015-10-24 | 2016-06-22 | 湖南长海现代实验室设备有限公司 | Coil type heat exchanger |
| ITUB20156040A1 (en) * | 2015-12-01 | 2017-06-01 | Simm Toscana S R L | COOLER FOR GRANULAR SOLIDS |
| CN109386994A (en) * | 2017-08-03 | 2019-02-26 | 沈阳天洁环保新能源有限公司 | Efficient rotary pipe type heat transfer evaporator and heat-exchange method |
| CN108534569A (en) * | 2018-04-20 | 2018-09-14 | 杨艺 | A kind of efficient heat exchanger |
| CN108571836A (en) * | 2018-05-22 | 2018-09-25 | 河北旺源管业有限公司 | A kind of permeable sewage geothermal source ductwork type heat exchange heat pump system |
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