CN112378278A - Self-adaptive non-uniform fin plate bundle for heat exchanger and design method of flow channel of self-adaptive non-uniform fin plate bundle - Google Patents
Self-adaptive non-uniform fin plate bundle for heat exchanger and design method of flow channel of self-adaptive non-uniform fin plate bundle Download PDFInfo
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- CN112378278A CN112378278A CN202011277289.3A CN202011277289A CN112378278A CN 112378278 A CN112378278 A CN 112378278A CN 202011277289 A CN202011277289 A CN 202011277289A CN 112378278 A CN112378278 A CN 112378278A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
- F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
- F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
- F28F3/042—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element
- F28F3/046—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element the deformations being linear, e.g. corrugations
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- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
The invention discloses a self-adaptive non-uniform fin plate bundle for a heat exchanger, which comprises one or more groups of fin base plates which are stacked up and down, wherein cold and hot fluid channels are arranged in the base plates to form an integrated structure, a cold runner is a concave channel-shaped structure body, a plurality of fins are arranged in a groove from dense to sparse in the flow direction, and a plurality of semicircular independent channels are arranged on a hot runner at equal intervals in the vertical direction of the cold runner. And a cover plate in sealing connection is arranged at the upper part of the cold runner. The self-adaptive non-uniform fin plate bundle for the heat exchanger is suitable for heat exchange requirements under various different conditions, is more suitable for thermal hydraulic variation of fluid in the heat exchange process, can effectively enhance the heat transfer characteristic, can effectively improve the hydraulic performance, and has wider application field. The invention also discloses a flow channel design method of the self-adaptive non-uniform fin plate bundle for the heat exchanger.
Description
Technical Field
The invention belongs to the technical field of heat exchangers used in refrigeration, energy, chemical engineering and the like, and particularly relates to a self-adaptive non-uniform fin plate bundle for a heat exchanger and a flow channel design method thereof.
Background
In recent years, with the increase of industrial demand in China, the demand of energy is increasing day by day. Therefore, the development and utilization of clean energy are important measures for dealing with energy crisis all over the world. In the field of energy application, a heat exchanger is used as a key part for improving energy conversion, and the heat transfer of the heat exchanger is strengthened. Improvements in heat transfer technology to improve energy utilization have become important research. The heat exchanger device is widely applied to industries such as petrochemical industry, power electronic technology and the like.
Especially, the fluid with violent physical property change in the heat exchange process like natural gas has important significance for the research of the heat exchanger thereof. In the application of natural gas, liquefied natural gas is gasified by a heat exchanger and then is conveyed to a pipe network. Chemical etching techniques for such heat exchangers have long been monopolized by foreign companies. Therefore, the development of a compact heat exchanger with strong adaptability and good heat exchange performance is a problem which must be solved for the industrial development of China.
Generally, the gasification process of natural gas is carried out under supercritical pressure. The supercritical fluid has: the micro-channel heat exchanger has the physical characteristics of high density, low viscosity, high diffusion speed and the like, pressure loss generated by flow in the micro-channel is much smaller than that of common fluid, and excellent flow and heat exchange performances can be shown. But also has many problems that the physical properties of the natural gas such as density, viscosity, specific heat capacity and the like can fluctuate sharply near a pseudo-critical point in the heat exchange process, so that the research on the supercritical natural gas is much more complicated than that of the conventional fluid; in addition, in the heat exchange process of the supercritical fluid, along with the rise of the temperature, the volume of the supercritical fluid is increased, so that the flow resistance of the supercritical fluid in the heat exchange process can be increased, and the generated pressure drop is larger.
In the prior printed circuit board type heat exchanger, fins in a flow channel are periodically and uniformly arranged, and the arrangement mode cannot effectively adapt to the change of thermophysical properties of fluid in the heat exchange process, so that the heat exchange performance is poor and needs to be further improved.
Disclosure of Invention
The object of the present invention is to adapt the heat exchanger to more complicated environments, in view of the above-mentioned characteristics of the supercritical fluid. A self-adaptive non-uniform fin plate bundle for a heat exchanger and a flow channel design method thereof are provided.
The heat exchanger flow channel designed by the method can effectively adapt to the complex flow of the physical property change of the fluid under different flow states. Has good effects on hydraulic characteristics, heat transfer performance and compactness, and can be widely applied to other places with complicated conditions.
In order to achieve the purpose, the invention adopts the following technical scheme to realize the purpose:
the utility model provides a non-uniform fin board of self-adaptation restraints, includes base plate 1, base plate 1 is concave channel form structure, constitutes the cold runner by dense to sparse dislocation set up a plurality of fins 2 in the flow direction in the recess, and equidistant a plurality of semicircular channel 3 perpendicular with the cold runner of having seted up on base plate 1 of recess lower part, and recess upper portion is equipped with sealing connection's apron 4.
Further preferably, the fins 2 are serpentine fins, airfoil fins or zigzag fins. The serpentine fins are formed by vector displacement of sin reference curves to opposite directions, the offset angle alpha is 10-60 degrees, the ratio of the fin transverse length B1 to the fin width A1 is 1-10, the ratio of the adjacent fin longitudinal spacing C1 to the fin width A1 is not less than 0.2, and the ratio of the adjacent fin transverse spacing D1 to the transverse length B1 is 1-2; the ratio of the transverse length B2 of the wing-shaped fin to the maximum thickness A2 of the wing-shaped fin is 1-10, the ratio of the longitudinal spacing C2 of adjacent fins to the maximum thickness A2 of the fins is not less than 0.2, and the ratio of the transverse spacing D2 of adjacent fins to the transverse length B2 of the adjacent fins is 1-2; the ratio of the transverse length B3 of the zigzag fins to the width A3 of the zigzag fins is 2-15, the ratio of the longitudinal spacing C3 of the adjacent fins to the width A3 of the adjacent fins is not less than 0.2, and the ratio of the transverse spacing D3 of the adjacent fins to the transverse length B3 of the adjacent fins is 1-2. The fin heights H of the serpentine fins, the wing-shaped fins and the sawtooth-shaped fins are all 0.5-2 mm.
Further preferably, the base plate 1 and the cover plate 4 are made of stainless steel, titanium alloy, or aluminum alloy.
In order to achieve the purpose, the invention is realized by adopting another technical scheme.
The heat exchanger comprises the self-adaptive non-uniform fin plate bundle, the fin plate bundle 6 is formed by at least one or more than one fin plate bundle which is overlapped up and down, the peripheries of the fin plate bundle 6 are respectively and hermetically connected with end sockets 5, and a cold fluid inlet channel i is arranged on the end socket 5 at one end of a channelcA cold fluid outlet channel O is arranged on the end socket 5 at the other endc(ii) a A hot fluid inlet channel i is arranged on the end socket 5 at one end of the channel 3hA hot fluid outlet channel O is arranged on the end enclosure 5 at the other endh。
Further preferably, the cold fluid inlet channel icFixed on the side with smaller free flow passage area, the cold fluid outlet passage OcIs fixed on the side with larger area of the free flow passage, and the cold fluid flow passage is gradually enlarged.
Further preferably, the seal head 5 and the cold fluid inlet channel icCold fluid outlet channel OcHot fluid inlet channel ihAnd a hot fluid outlet channel OhThe two cavities are respectively provided with an independent closed cavity, wherein the volume of the inlet cavity is gradually expanded positively, and the volume of the outlet cavity is gradually reduced negatively.
Further preferably, an inlet and outlet pipeline of the heat exchanger is vertically and fixedly connected to the upper surface of the seal head 5.
In order to achieve the above object, the present invention is implemented by using a third technical solution.
A design method of a self-adaptive non-uniform fin plate bundle cold and hot flow passage comprises the following steps:
the first step is as follows: determining the form, specification and size of the inner fins (2) of the cold runner according to the use conditions of the heat exchanger and the pressure, temperature and flow required by the inlet and the outlet of the cold fluid;
the second step is that: according to the flow of cold and hot fluids and keeping the flow velocity at 2-8 m/s, determining the minimum free runner area of the first section of the cold runner and the flow area of the hot runner;
the third step: according to the change of cold fluid density with temperature
The heat exchange temperature zone is segmented;
the fourth step: according to
Determining the area of a free flow channel of each segment;
the fifth step: the final size of the flow channels of each section is determined according to the enthalpy change and the temperature change of the segmented fluid, and the number of the channels (3) of the hot runner is determined.
Compared with the prior art, the invention has the advantages and beneficial effects that:
1. the fin plate bundle is more suitable for severe physical property change in the fluid heat exchange process, so that the heat exchange area is increased while a larger heat transfer coefficient is obtained. And the overall size of the heat exchanger is not changed, and the heat exchanger is more compact.
2. The fin form of the fin plate bundle adopts a snake shape, a wing shape or a sawtooth shape, so that the heat exchanger which is more targeted can be designed according to different design conditions and fluid state changes.
3. Because the flow direction and the chaos degree of the supercritical fluid on the discontinuous fins for heat exchange can change along with the arrangement form of the fins, the fin structure is controlled within a certain proportion range, the heat exchange capacity can be improved, and the service life of the fins is ensured.
4. The reasonable design of the inlet and the outlet can lead the fluid to be more uniformly guided into the heat exchange channel, and can effectively reduce the problems of local overtemperature and the like caused by non-uniform flow.
Drawings
FIG. 1 is a schematic three-dimensional structure of a finned plate bundle of the present invention;
FIG. 2 is a schematic three-dimensional structure of the heat exchanger of the present invention;
FIG. 3 is a schematic diagram of the variation of the size of the free flow channel of the serpentine fin channel of the present invention;
FIG. 4 is a schematic representation of the variation in the size of the free flow channels of an airfoil fin channel of the present invention;
FIG. 5 is a schematic diagram of the variation of the size of the free flow channels of the zigzag finned passage of the present invention;
FIG. 6 is a diagram showing the specific structural dimensions of the serpentine (a), the airfoil (b) and the zigzag (c) fins of the present invention;
FIG. 7 is a schematic diagram of the physical property change and the segmentation design division of the methane heat exchange process of the present invention;
in the figure: 1-base plate, 2-fin, 3-channel, 4-cover plate, 5-end socket and 6-fin plate bundle;
iccold fluid inlet channel, OCCold fluid outlet channel, ihHot fluid inlet channel, Oh-a hot fluid outlet channel.
Detailed Description
In order to make those skilled in the art better understand the technical solution of the present invention, the following detailed description of the embodiments of the present invention will be made clear and fully with reference to the accompanying drawings.
In the present embodiment, a heat exchanger required for LNG vaporization is described as an example.
As shown in fig. 3 and 7, a method for designing a self-adaptive non-uniform fin plate bundle for a heat exchanger and a flow channel thereof comprises the following steps:
the first step is as follows: according to the pressure p, the temperature t and the flow G required by the inlet and outlet channels of the cold fluid, and because the LNG gasification process is carried out at sea, the required heat exchanger is as compact as possible, and the inner fins of the cold channel adopt a serpentine structure;
the second step is that: keeping the flow velocity v at 2-8 m/s according to the flow G of cold and hot fluid through a formula
Thereby determining the minimum free flow area D of the first section of the cold flow passage1And a hot runner flow area B;
the third step: based on the fact that methane is the main component of LNG, the method is as followsOn the variation curve of the methane density along with the temperature, along with the increasing direction of the temperature,
the method comprises the following steps of (1) preparing a first section,
the process comprises the following steps of (1) preparing a second section,
the method comprises the following steps of (1) preparing a III section,
the compound has the structural formula of IV,
the molecular weight of the compound is V,
is VI.
The fourth step: according to
Determining the free flow passage area D of each segment;
the fifth step: according to the enthalpy change delta h and the temperature change delta t of each segmented fluid, the final size of each segment of cold channel is determined by the formula m delta h-Q, Q-K multiplied by A multiplied by delta t, and the number of the hot runner independent channels is determined at the same time. Wherein K is the heat transfer coefficient of each section, and A is the heat transfer area.
Fig. 1 shows that the self-adaptive non-uniform fin plate bundle comprises a base plate 1, wherein cold and hot fluid channels are arranged in the base plate 1 to form an integrated structure, the base plate 1 is a concave channel-shaped structure, a plurality of fins 2 are arranged in a groove from dense to sparse staggered in the flow direction to form a cold runner, a plurality of semicircular channels 3 perpendicular to the cold runner are arranged on the base plate 1 at the lower part of the groove at equal intervals, and a cover plate 4 in sealing connection is arranged at the upper part of the groove.
Fig. 2 shows a heat exchanger comprising an adaptive non-uniform finned plate bundle according to the present invention, wherein the finned plate bundle 6 is composed of at least one or more pieces stacked up and down,seal heads 5 are respectively connected around the fin plate bundles 6 in a sealing way, and a cold fluid inlet channel i is arranged on the seal head 5 at one end of the channelcA cold fluid outlet channel O is arranged on the end socket 5 at the other endc(ii) a A hot fluid inlet channel i is arranged on the end socket 5 at one end of the channel 3hA hot fluid outlet channel O is arranged on the end enclosure 5 at the other endh。
The cold fluid inlet channel icFixed on the side with smaller free flow passage area, the cold fluid outlet passage OcIs fixed on the side with larger area of the free flow passage, and the cold fluid flow passage is gradually enlarged.
The seal head 5 and the cold fluid inlet channel icCold fluid outlet channel OcHot fluid inlet channel ihAnd a hot fluid outlet channel OhThe two cavities are respectively provided with an independent closed cavity, wherein the volume of the inlet cavity is gradually expanded positively, and the volume of the outlet cavity is gradually reduced negatively.
FIG. 6 is a schematic diagram showing the structural dimensions of a fin 2 of the present invention, FIG. 6(a) is a schematic diagram showing the structural dimensions of a serpentine fin, FIG. 6(B) is a schematic diagram showing the structural dimensions of an airfoil fin, and FIG. 6(C) is a schematic diagram showing the structural dimensions of a zigzag fin, wherein the serpentine fin is formed by vector displacement of sin reference curves in opposite directions, the offset angle α is between 10 and 60 °, the ratio of the fin transverse length B1 to the fin width A1 is 1 to 10, the ratio of the fin longitudinal spacing C1 to the fin width A1 is not less than 0.2, and the ratio of the fin transverse spacing D1 to the fin transverse length B1 is 1 to 2. The ratio of the transverse length B2 of the wing-shaped fin to the maximum thickness A2 of the wing-shaped fin is 1-10, the ratio of the longitudinal spacing C2 of adjacent fins to the maximum thickness A2 of the fins is not less than 0.2, and the ratio of the transverse spacing D2 of adjacent fins to the transverse length B2 of the adjacent fins is 1-2. The ratio of the transverse length B3 of the zigzag fins to the width A3 of the zigzag fins is 2-15, the ratio of the longitudinal spacing C3 of the adjacent fins to the width A3 of the adjacent fins is not less than 0.2, and the ratio of the transverse spacing D3 of the adjacent fins to the transverse length B3 of the adjacent fins is 1-2. The fin heights H of the serpentine fins, the wing-shaped fins and the sawtooth-shaped fins are all 0.5-2 mm.
FIG. 3 is a schematic view of the variation of the size of the free flow channel of the serpentine fin channel of the present invention;
FIG. 4 is a schematic view of the change in the size of the free flow channels of an airfoil fin channel of the present invention;
FIG. 5 is a schematic diagram showing the variation of the size of the free flow channel of the zigzag finned channel of the present invention.
Referring to fig. 3 to 6, the fins 2 in the cold fluid channel can take various forms, such as serpentine fins, airfoil fins or zigzag fins or even combinations thereof. In addition, the areas of the free flow passages of the sections in the cold fluid channel are different and gradually increase along with the flowing direction of the cold fluid.
The working process of the heat exchanger provided by the invention is as follows: cold fluid from cold fluid inlet channel icFlows into the fin plate bundle 6 through the expansion cavity in the seal head 5 and flows into the cold fluid outlet channel OcFlows out of the heat exchanger through the shrinkage cavity in the seal head 5. Hot fluid from hot fluid inlet channel ihFlows into the fin plate bundle 6 through the expansion cavity in the seal head 5 and flows into a hot fluid outlet channel OhFlows out of the heat exchanger through the shrinkage cavity in the seal head 5. The cold and hot fluids exchange heat within the finned plate bundle 6.
It is to be understood that the described embodiments are merely exemplary of the invention, and not restrictive of the full scope of the invention. Based on the embodiments of the present invention, those skilled in the art will appreciate that any changes, substitutions, modifications, etc. to the embodiments of the present invention may be made without departing from the spirit and scope of the present invention as set forth in the appended claims.
Claims (8)
1. The utility model provides a non-uniform fin board of self-adaptation restraints, includes base plate (1), its characterized in that, base plate (1) is concave channel form structure, constitutes the cold runner by close to sparse dislocation set up a plurality of fins (2) in the flow direction in the recess, and equidistant a plurality of semicircular channel (3) perpendicular with the cold runner of having seted up on base plate (1) of recess lower part, and recess upper portion is equipped with sealing connection's apron (4).
2. An adaptive non-uniform fin plate pack according to claim 1, wherein the fins (2) are serpentine fins or airfoil fins or zigzag fins.
3. The adaptive non-uniform fin plate bundle according to claim 1, characterized in that the base plate (1) and the cover plate (4) are made of stainless steel, titanium alloy or aluminum alloy.
4. A heat exchanger comprising a self-adaptive non-uniform fin plate bundle as claimed in any one of claims 1 to 3, wherein the fin plate bundle (6) is composed of at least one or more stacked fin plates, end sockets (5) are respectively connected to the periphery of the fin plate bundle (6) in a sealing manner, and a cold fluid inlet channel i is arranged on the end socket (5) at one end of the channelcA cold fluid outlet channel O is arranged on the end socket (5) at the other endc(ii) a A hot fluid inlet flow passage i is arranged on the seal head (5) at one end of the flow passage (3)hA hot fluid outlet channel O is arranged on the end socket (5) at the other endh。
5. The heat exchanger of claim 4, wherein the cold fluid inlet channel icFixed on the side with smaller free flow passage area, the cold fluid outlet passage OcIs fixed on the side with larger area of the free flow passage, and the cold fluid flow passage is gradually enlarged.
6. Heat exchanger according to claim 4, wherein the head (5) is connected to the cold fluid inlet channel icCold fluid outlet channel OcHot fluid inlet channel ihAnd a hot fluid outlet channel OhThe two cavities are respectively provided with an independent closed cavity, wherein the volume of the inlet cavity is gradually expanded positively, and the volume of the outlet cavity is gradually reduced negatively.
7. The heat exchanger according to claim 4, characterized in that the inlet and outlet pipes of the heat exchanger are vertically and fixedly connected to the upper surface of the end socket (5).
8. A design method of a cold and hot flow passage of a self-adaptive non-uniform fin plate bundle as claimed in any one of claims 1 to 3, comprising the following steps:
the first step is as follows: determining the form, specification and size of the inner fins (2) of the cold runner according to the use conditions of the heat exchanger and the pressure, temperature and flow required by the inlet and the outlet of the cold fluid;
the second step is that: according to the flow of cold and hot fluids and keeping the flow velocity at 2-8 m/s, determining the minimum free runner area of the first section of the cold runner and the flow area of the hot runner;
the third step: according to the change of cold fluid density with temperature
The heat exchange temperature zone is segmented;
the fourth step: according to
Determining the area of a free flow channel of each segment;
the fifth step: the final size of the flow channels of each section is determined according to the enthalpy change and the temperature change of the segmented fluid, and the number of the channels (3) of the hot runner is determined.
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| CN113271039A (en) * | 2021-04-19 | 2021-08-17 | 江苏大学 | Parameter determination method for temperature of thermoelectric generator and non-equidistant heat transfer structure of thermoelectric generator |
| CN113670099A (en) * | 2021-07-02 | 2021-11-19 | 广州华工机动车检测技术有限公司 | Liquid cooling plate structure of power battery |
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| WO2022205765A1 (en) * | 2021-03-31 | 2022-10-06 | 西安热工研究院有限公司 | Compact heat exchanger and asymmetric airfoil heat exchange plate thereof |
| CN116605076A (en) * | 2023-07-10 | 2023-08-18 | 毫厘机电(苏州)有限公司 | High-power charging station cooling system |
| EP4253898A1 (en) * | 2022-04-01 | 2023-10-04 | Hamilton Sundstrand Corporation | Varying topology heat sinks |
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Application publication date: 20210219 |