CN116625143B - Explosion-proof LNG shell-and-tube heat exchanger - Google Patents
Explosion-proof LNG shell-and-tube heat exchanger Download PDFInfo
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- CN116625143B CN116625143B CN202310485643.9A CN202310485643A CN116625143B CN 116625143 B CN116625143 B CN 116625143B CN 202310485643 A CN202310485643 A CN 202310485643A CN 116625143 B CN116625143 B CN 116625143B
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Classifications
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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
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
- F28D7/163—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing
- F28D7/1638—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing with particular pattern of flow or the heat exchange medium flowing inside the conduits assemblies, e.g. change of flow direction from one conduit assembly to another one
- F28D7/1646—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing with particular pattern of flow or the heat exchange medium flowing inside the conduits assemblies, e.g. change of flow direction from one conduit assembly to another one with particular pattern of flow of the heat exchange medium flowing outside the conduit assemblies, e.g. change of flow direction
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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
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/006—Tubular elements; Assemblies of tubular elements with variable shape, e.g. with modified tube ends, with different geometrical features
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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
- F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
- F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
- F28F13/12—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation
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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
- F28F27/00—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/005—Other auxiliary members within casings, e.g. internal filling means or sealing means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/007—Auxiliary supports for elements
- F28F9/013—Auxiliary supports for elements for tubes or tube-assemblies
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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
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/24—Arrangements for promoting turbulent flow of heat-exchange media, e.g. by plates
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators
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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
- F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
- F28F2250/10—Particular pattern of flow of the heat exchange media
- F28F2250/102—Particular pattern of flow of the heat exchange media with change of flow direction
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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
- F28F2265/00—Safety or protection arrangements; Arrangements for preventing malfunction
- F28F2265/16—Safety or protection arrangements; Arrangements for preventing malfunction for preventing leakage
Abstract
The invention relates to an explosion-proof LNG shell-and-tube heat exchanger, which comprises a heat exchange space of an inner layer and a buffer space of an outer layer. The heat exchange space is formed by axially connecting the end socket and the inner shell of the heat exchanger, the fixed tube plate and the floating tube plate are respectively arranged at two ends of the inner shell of the heat exchanger, the plurality of radial heat exchange tubes are respectively connected with the fixed tube plate and the floating tube plate. The radial heat exchange tube can effectively enhance the heat transfer performance of the shell-and-tube heat exchanger, and the radial and axial sub-flow channels have high elasticity, so that the influence of large thermal stress caused by LNG large-temperature difference low-temperature operation working conditions can be effectively relieved; the floating tube plate and the heat exchange tube supporting mechanism also enhance the running stability under extreme working conditions. The buffer space is composed of a buffer layer outer shell and a heat exchanger inner shell, and gas with high chemical stability is filled in the buffer space to isolate external air and LNG in the heat exchanger. The invention can provide guarantee for the efficient and safe operation of the LNG cold energy utilization process.
Description
Technical Field
The invention relates to a heat exchange device, in particular to a shell-and-tube heat exchanger which is used for improving heat exchange performance, realizing safe explosion prevention and has a radial structural characteristic heat exchange tube bundle and is applied to the field of LNG cold energy utilization.
Background
The heat exchanger is a basic equipment component in the LNG cold energy utilization field, and is also an important precondition for guaranteeing the efficient operation of each energy system in the LNG cold energy utilization field. The shell-and-tube heat exchanger is a preferable scheme applied to the energy system in the field because of high operation reliability, low system energy consumption and low investment cost.
Shell-and-tube heat exchangers generally consist of a tube side header, a tube sheet, a parallel heat exchanger tube bundle, and a shell of the shell side and baffles. Enhanced heat transfer research for shell-and-tube heat exchangers is generally conducted from the view of optimization of heat exchange tube bundles and baffle plate structures, but as known from field cooperative theory, parallel tube bundle arrangement cannot fully utilize space in a shell, and is not an optimal space combination mode. While the baffle structure in the shell pass can play a role in turbulent flow to strengthen heat transfer, the periphery of the tube bundle is easy to generate a leakage flow phenomenon, so that a flow dead zone is formed.
In addition, the unique operation conditions of large temperature difference, high pressure, inflammability and explosiveness exist in the LNG cold energy utilization field, and safety protection is an important technical problem facing the LNG cold energy utilization field of the shell-and-tube heat exchanger. In the low-temperature system starting and large-temperature-difference running process, the shell-and-tube heat exchanger component can generate very large thermal stress, equipment deformation and damage are easy to cause, the safe running of an LNG cold energy utilization energy system is affected, natural gas in the heat exchanger is in a high-pressure working state, and challenges such as working medium leakage exist.
Therefore, the optimization design of the shell-and-tube heat exchanger structure is urgently needed to be developed, so that the flow heat transfer performance in the heat exchanger can be effectively improved, and the safety protection requirement in the LNG cold energy utilization field can be met.
Disclosure of Invention
Aiming at the defects of the prior art, the invention provides an explosion-proof LNG shell-and-tube heat exchanger, which aims to improve the heat exchange effect of the heat exchanger and the safety performance applied to the field of LNG cold energy utilization.
The technical scheme adopted by the invention is as follows:
the application provides an explosion-proof LNG shell and tube heat exchanger, including the heat transfer space and the outer buffer space of inlayer. The heat exchange space consists of a seal head, an inner shell of the heat exchanger, a tube side fluid inlet, a tube side fluid outlet, a shell side fluid inlet, a shell side fluid outlet, a separation partition plate, a fixed tube plate, a radial heat exchange tube, a heat exchange tube supporting mechanism, a floating head tube plate and a floating head cover. The seal heads are respectively arranged at two ends of the inner shell of the heat exchanger and are axially connected with the inner shell of the heat exchanger to form a heat exchange space of the inner layer. The fixed tube plate is arranged on the left side of the inner layer shell of the heat exchanger, and forms a tube box with the sealing head on the left side, and the tube box is divided into an upper part and a lower part by the separation partition plate which is horizontally arranged, and is divided into two tube passes. The tube side fluid inlet and the tube side fluid outlet are respectively arranged at the top and the bottom of the left end socket for tube side fluid circulation. The floating head tube plate and the floating head cover are arranged on the right side of the inner shell of the heat exchanger, and the forming space is used for changing the flow direction of tube side fluid so as to realize tube side switching. Two groups of heat exchange tube bundles are formed by a plurality of radial heat exchange tubes, the two ends of the heat exchange tube bundles are respectively fixed on the fixed tube plate and the floating tube plate as two tube passes, and the floating end can freely move in the axial direction relative to the inner shell of the heat exchanger, so that the thermal stress of the heat exchange tube bundles is reduced. The heat exchange tube bundle is radially connected with the inner shell of the heat exchanger through the heat exchange tube supporting mechanism. The shell side fluid inlet and the shell side fluid outlet are respectively positioned at the left lower side and the right upper side of the inner layer shell of the heat exchanger for shell side fluid circulation.
The buffer space is composed of the inner shell of the heat exchanger, the outer shell of the buffer layer, the supporting structure of the buffer layer, the exhaust pressure release mechanism, the buffer layer pressure sensor and the LNG concentration measuring device of the buffer layer. The inner shell of the heat exchanger and the outer shell of the buffer layer are radially and fixedly connected through the buffer layer supporting structure. The exhaust pressure relief mechanism is arranged at the top of the seal head, the inner shell of the heat exchanger and the outer shell of the buffer layer. The buffer layer LNG concentration measuring device is arranged around the buffer layer outer shell.
And the bottom of the outer shell of the buffer layer is provided with a heat exchanger supporting base for supporting the shell-and-tube heat exchanger.
The radial heat exchange tube is formed by connecting a plurality of runner units with the same structure in series, and the adjacent runner units are connected by a main runner which coincides with the axis of the inner layer shell of the heat exchanger. Each flow channel unit is composed of two layers of N-generation flow channel groups, wherein each layer of N-generation flow channel group is composed of a mother flow channel, N-generation radial radiation sub-flow channels and N-generation axial sub-flow channels (the total circulation number N is an integer greater than or equal to 2).
The 1 st generation radial radiation sub-flow channels are connected with the main flow channel, the connection part is used as a radiation node, M1 st generation radial radiation sub-flow channels (the radiation number M of each generation is an integer greater than or equal to 3) are radially and co-radiated on the plane vertical to the main flow channel, the 1 st generation radial radiation sub-flow channels are distributed at equal intervals along the circumferential direction, and the 1 st generation axial sub-flow channels with equal length extend from the tail end of each 1 st generation radial radiation sub-flow channel along the axial direction of the main flow channel.
When the circulation algebra N is more than or equal to 2 (N is more than or equal to 2), the nth generation radial radiation sub-runners respectively take the tail ends of the nth-1 generation axial sub-runners as radiation nodes, M nth generation radial radiation sub-runners extend out along the radial direction along the plane vertical to the nth-1 generation axial sub-runners, and the nth generation radial radiation sub-runners radiated by the same nth-1 generation axial sub-runner are distributed along the circumferential direction at equal intervals. In addition, at the end of each nth generation radial radiation sub-runner, an nth generation axial sub-runner with equal length extends along the nth-1 generation axial sub-runner.
The diameter of the radial radiation sub-flow channel of the same generation is the same as that of the axial sub-flow channel, and the diameter ratio of the upper sub-flow channel and the lower sub-flow channel is selected to be the optimal value which minimizes the turbulent flow friction resistance, namely (D) n-1 /D n ＝M 3/7 N is more than or equal to 2 and N is more than or equal to N). The length of the radial radiation sub-flow channel of the same generation is the same as that of the axial sub-flow channel, and the length ratio of the upper sub-flow channel and the lower sub-flow channel is the same as the optimal value for minimizing the turbulent flow friction resistance, namely (L) n-1 /L n ＝M 1/7 N is more than or equal to 2 and N is more than or equal to N). Optimum flow channel diameter ratio D n-1 /D n Optimal flow channel length ratio L n-1 /L n The calculation method comprises the following specific steps:
selecting the n-1 generation axial sub-flow channel and the n generation radial radiation sub-flow channel as analysis calculation objects, as shown in fig. 5:
1) And (3) defining the total flow channel volume constraint condition of the analysis and calculation object, as shown in the formula (1).
2) The flow of the tube side fluid in the heat exchange tube bundle is in a turbulent state, and the flow friction pressure drop in the n-1 generation axial sub-flow channel and the n generation radial radiation sub-flow channel can be respectively represented by delta P in the formula (2) n-1 And delta P n And (5) calculating to obtain the product.
3) Taking the total flow friction pressure drop of the analysis object as an optimization target, and properly simplifying the function
The final objective function is represented by equation (3).
4) On the basis, solving the optimal value problem by adopting a Lagrange multiplier method, and establishing a Lagrange
The function is shown as formula (4), wherein lambda is Lagrangian multiplier.
5) By separately aligning L n-1 、L n 、D n-1 、D n And lambda is used for obtaining first-order partial derivatives, and the formulae are 0, and the result is shown as a formula (5).
6) By eliminating lambda from formula (5), the n-1 generation axial sub-flow channel diameter D can be deduced n-1 And the diameter D of the flow passage of the nth generation radial radiating sub- n The optimal ratio of (2) is shown in the formula (6).
7) The flow path diameter D is eliminated by substituting the formula (6) into the formulas (1) and (3), respectively, and the result is shown in the formula (7), wherein C is a constant.
R turb ＝C(M -17 L n-1 +L n ) 72 (7)
8) By adding the spatial distribution constraint condition of the analysis calculation object, a lagrangian function including only the flow path length L can be established as shown in expression (8).
Ψ＝M -17 L n-1 +L n +μL n-1 L n (8)
9) By separately aligning L n-1 、L n The first order bias is obtained and the formulae are 0, and the result is shown in formula (9).
10 Finally, the length L of the nth-1 generation axial sub-runner can be solved n-1 Length L of the radial radiating sub-runner of the nth generation n The optimal ratio of (2) is shown in the formula (10).
The two layers of the N-generation flow channel groups are oppositely arranged and are connected into a whole by the N-th generation axial sub-flow channels to form the flow channel unit.
Tube side fluid is equally distributed from the tube box to the heat exchange tube bundles, passing through all of the flow path units in the axial direction in each of the radial heat exchange tubes. In each flow channel unit, the tube side fluid flows through the mother flow channel, the 1 st generation radial radiation sub-flow channel and the 1 st generation axial sub-flow channel in the first layer of the N generation flow channel group at first, and finally flows to the Nth generation radial radiation sub-flow channel and the Nth generation axial sub-flow channel to finish the flow of the tube side fluid in the first layer of the N generation flow channel group. And then the flow enters the second layer of the N-generation flow passage group, flows through the N-generation axial sub-flow passage and the N-generation radial radiation sub-flow passage in sequence, finally converges at the main flow passage of the N-generation flow passage group, and ends the flow process of tube side fluid in each flow passage unit.
The radial heat exchange tube designed by the common structure in nature is used for effectively enhancing the turbulence development of the tube side fluid and enhancing the heat transfer performance of the tube side fluid, and the optimal diameter ratio and the optimal length ratio of the upper and lower generation sub-channels obtained based on the optimization of the tube side turbulence flow friction resistance also ensure the superior flow characteristic of the tube side. In addition, the radial structure of the heat exchange tube bundle can also improve the disturbance effect of the shell-side fluid and enhance the convection heat exchange in the shell side.
The heat exchange tube supporting mechanism consists of a shell connecting piece, a sliding connecting piece, a supporting spring and a heat exchange tube fixing piece. The top of the shell connecting piece is a curved surface and is fixedly connected with the top or the bottom of the inner shell of the heat exchanger in a welding mode; the inside is hollow structure, is provided with smooth slide rail in the structure bottom surface, has seted up the round hole in center department to be provided with annular limit baffle along circumference at round hole outer fringe circle. The top of the sliding connecting piece is of a disc-shaped sliding structure, the sliding connecting piece is arranged in the shell connecting piece, small-range displacement in the horizontal direction can be achieved through matching with the sliding rail, and the maximum displacement range of the sliding connecting piece is limited by the limiting baffle. The bottom of the sliding block connecting piece is of a cylindrical structure and is arranged in the round hole, so that displacement in a small range along the axial direction of the round hole can be realized. The top of the heat exchange tube fixing piece is of a cylindrical structure, the bottom of the heat exchange tube fixing piece is of a clamp structure and is used for clamping the female runner, and the heat exchange tube fixing piece and the female runner are completely fixed through a pin bolt. The top and the bottom of the supporting spring are respectively fixed with the cylindrical structure at the bottom of the sliding connecting piece and the cylindrical structure at the top of the heat exchange tube fixing piece.
The problem of large thermal stress can be generated in the low-temperature starting and running process in the LNG cold energy utilization field, when the heat exchange tube bundle is affected by the thermal stress to expand or shrink, the sliding block connecting piece can meet the requirement that the heat exchange tube bundle is supported by the free axial displacement of the heat exchange tube bundle, and the stability under the working condition of large-temperature-difference low-temperature running is enhanced.
The buffer layer supporting structure is annular and is coaxially arranged with the inner layer shell and the outer layer shell of the buffer layer, wherein the inner side supporting curved surface is connected with the inner layer shell of the heat exchanger, and the outer side supporting curved surface is connected with the outer layer shell of the buffer layer. The rotary cross section of the buffer layer supporting structure is an I-shaped structure with high bearing capacity, and a plurality of hollow hole grooves are distributed along the circumferential direction of the buffer layer supporting structure at equal intervals.
And nitrogen with high chemical stability is filled in the buffer layer, and inert gases such as helium, argon and the like can also be filled in the buffer layer for isolating external air from LNG in the buffer layer, so that the buffer layer has a flame-retardant effect.
The buffer layer LNG concentration measuring device is used for monitoring the change of LNG concentration in the buffer layer, and the buffer layer LNG concentration measuring device and the remote monitoring equipment jointly form an LNG leakage early warning system.
Setting an upper limit value of the pressure increment and an upper limit value of the pressure in the remote monitoring equipment, and sending an alarm signal when the pressure increment or the pressure in the buffer layer exceeds the corresponding upper limit value within 5 continuous minutes. In addition, the upper limit value of the LNG concentration increment and the upper limit value of the LNG concentration are set in the remote monitoring equipment, and when the LNG concentration increment or the LNG concentration in the buffer layer exceeds the corresponding upper limit value in 5 continuous minutes, an alarm signal is sent out by the remote monitoring equipment.
The exhaust pressure release mechanism consists of an exhaust pressure release mechanism base, a compression spring, a sealing structure and a sealing gasket. The base of the exhaust and pressure relief mechanism comprises a flange plate and a cylinder body, the flange plate is used for fixedly connecting the exhaust and pressure relief mechanism with the inner shell of the heat exchanger and the outer shell of the buffer layer, 2 layers of 12 exhaust round holes are formed in the side face of the cylinder body along the circumferential direction at equal intervals, and an annular limit baffle is arranged at the bottom of the cylinder body along the circumferential direction of the inner wall of the cylinder body. The sealing structure is characterized in that the sealing gasket is arranged in the cylinder body and is sequentially connected with the limiting baffle plate along the axial direction, and the compression spring is arranged between the top of the cylinder body and the sealing structure and is used for sealing the exhaust pressure release mechanism.
When the LNG in the heat exchange space explodes, the pressure in the heat exchange space can rise sharply. At this time, the exhaust pressure release mechanism arranged at the seal head and the inner shell of the heat exchanger can be sprung out, so that the heat exchange space and the buffer space are communicated, and the buffer effect is achieved on the explosion of LNG. And when the pressure in the buffer space also exceeds the pressure-resistant upper limit of the outer shell of the buffer layer, the air-release mechanism arranged at the top of the outer shell of the buffer layer also can spring open and is exploded outwards from the top, so that the harm of explosion to personnel can be greatly reduced.
The beneficial effects of the invention are as follows:
(1) The radial heat exchange tubes are adopted in the flow channels of the tube side fluid LNG, and are composed of the sub-flow channels which are distributed axially and radially, so that the turbulent flow development of the tube side fluid is enhanced, and the heat transfer performance of the tube side fluid is enhanced. The invention optimizes the radial heat exchange tube structure based on the Lagrangian multiplier method by taking the minimum frictional resistance of tube side turbulent flow as a target, obtains the optimal diameter ratio and the optimal length ratio of the upper and lower sub-runners, and realizes the minimum resistance of tube side turbulent flow. In addition, the radial structure also improves the disturbance effect of the shell-side fluid and enhances the convection heat exchange in the shell side.
(2) Unlike common straight heat exchange tube, radial heat exchange tube has radial and axial sub-flow channels, which are perpendicular to each other and are axially spaced along the inner shell of heat exchanger. Because the axial flow passages of each section are distributed on different axes, no direct constraint relation exists between the axial flow passages of each section and the radial flow passages of each section are not radially constrained, so that the radial heat exchange tube can be contracted and expanded in the axial direction and the radial direction. The special structural characteristics enable the radial heat exchange tube to have the characteristics of high strength and high elasticity, and when the radial heat exchange tube operates in the extreme working condition of large temperature difference and low temperature in the LNG cold energy utilization field, the radial heat exchange tube can deform autonomously, so that the influence of thermal stress can be effectively relieved, and safe operation is ensured. On the other hand, the heat exchange tube supporting mechanism can play a supporting role while moving along with the heat exchange tube bundle, so that the stability under the working condition of large temperature difference and low temperature operation is further enhanced.
(3) The buffer layer has a large internal space, can isolate external air from LNG in the heat exchanger by filling gas with high chemical stability, and has a flame-retardant effect. According to the LNG leakage early warning system, whether the leakage condition exists in the heat exchanger can be timely judged by monitoring the pressure change and the LNG concentration change in the buffer layer, so that potential explosion risks of LNG are effectively avoided.
(4) When encountering the extreme condition of LNG explosion, arrange in the exhaust relief valve in the buffer layer and can spring when the explosion is risen, communicate heat transfer space and buffer space on the one hand, play the cushioning effect to the explosion of LNG. On the other hand, the harm of explosion to personnel can be greatly reduced by outwards discharging the explosion from the top of the heat exchanger.
Additional features and advantages of the invention will be set forth in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention.
Drawings
Fig. 1 is a schematic overall structure of an embodiment of the present invention.
Fig. 2 is a schematic structural diagram of a radial heat exchange tube according to an embodiment of the present invention.
FIG. 3 is a side view of a single flow channel unit in the radiant heat exchange tube of FIG. 2
Fig. 4 is a front view of a single flow passage unit in the radial heat exchange tube of fig. 2.
Fig. 5 is a schematic size view of a single flow channel unit.
Fig. 6 is a schematic structural diagram of a heat exchange tube supporting mechanism according to an embodiment of the present invention.
Fig. 7 is a cut-away view of fig. 6.
Fig. 8 is a schematic structural diagram of a buffer layer supporting structure according to an embodiment of the invention.
Fig. 9 is a schematic structural view of a pressure release mechanism according to an embodiment of the present invention.
Fig. 10 is a cut-away view of fig. 9.
In the figure: 1. a seal head; 2. a separation baffle; 3. a tube side fluid inlet; 4. fixing the tube plate; 5. an inner shell of the heat exchanger; 6. a radial heat exchange tube; 7. a heat exchange tube supporting mechanism; 8. a shell side fluid outlet; 9. floating head tube plate; 10. a floating head cover; 11. a tube side fluid outlet; 12. a shell side fluid inlet; 13. a buffer layer outer shell; 14. a buffer layer support structure; 15. a pressure release mechanism; 16. a buffer layer pressure sensor; 17. buffer layer LNG concentration measuring device; 18. a heat exchanger support base; 61. a female runner; 62. a 1 st generation radial radiation sub-runner; 63. the 1 st generation axial sub-flow channel; 64. a 2 nd generation radial radiation sub-runner; 65. the 2 nd generation axial sub-flow passage; 66. a flow channel unit; 67. an N-generation runner group; 71. a housing connection; 72. a sliding connection; 73. a support spring; 74. a heat exchange tube fixing member; 141. an inner support curved surface; 142. an outer support curved surface; 151. a base of the exhaust and pressure relief mechanism; 152. a compression spring; 153. a sealing structure; 154. and a sealing gasket.
Detailed Description
The following describes specific embodiments of the present invention with reference to the drawings.
Referring to fig. 1, the application provides a shell-and-tube heat exchanger in LNG cold energy utilization field, including the heat exchange space of inlayer and the buffer space of outer. The heat exchange space consists of a seal head 1, a heat exchanger inner shell 5, a tube side fluid inlet 3, a tube side fluid outlet 11, a shell side fluid inlet 8, a shell side fluid outlet 12, a separation baffle plate 2, a fixed tube plate 4, a radial heat exchange tube 6, a heat exchange tube supporting mechanism 7, a floating head tube plate 9 and a floating head cover 10. The seal heads 1 are respectively arranged at two ends of the inner shell 5 of the heat exchanger and are axially connected with the inner shell 5 of the heat exchanger to form a heat exchange space of the inner layer. The fixed tube plate 5 is arranged on the left side of the inner shell 5 of the heat exchanger, and forms a tube box with the end socket 1 on the left side, and the tube box is divided into an upper part and a lower part by the horizontal separation plate 2, and is divided into two tube passes. The tube side fluid inlet 3 and the tube side fluid outlet 11 are respectively arranged at the top and the bottom of the left end socket 1 for tube side fluid circulation. The floating head tube plate 9 and the floating head cover 10 are both arranged on the right side of the heat exchanger inner shell 5, and the space formed by the floating head tube plate and the floating head cover is used for changing the flow direction of tube side fluid so as to realize tube side switching. Two groups of heat exchange tube bundles are formed by a plurality of radial heat exchange tubes 6, and as two tube passes, two ends of the heat exchange tube bundles are respectively fixed on the fixed tube plate 5 and the floating tube plate 9, and the floating end can freely move in the axial direction relative to the inner shell 5 of the heat exchanger, so that the thermal stress of the heat exchange tube bundles can be reduced. The heat exchange tube bundle is radially connected with the inner shell 5 of the heat exchanger through the heat exchange tube supporting mechanism 7. The shell side fluid inlet 12 and the shell side fluid outlet 8 are respectively positioned at the left lower side and the right upper side of the inner shell 5 of the heat exchanger and are used for circulating shell side fluid.
The buffer space is composed of the heat exchanger inner shell 5, the buffer layer outer shell 13, the buffer layer supporting structure 14, the exhaust pressure relief mechanism 15, the buffer layer pressure sensor 16 and the buffer layer LNG concentration measuring device 17. The inner shell 5 of the heat exchanger and the outer shell 13 of the buffer layer are fixedly connected in the radial direction by the buffer layer supporting structure 14. The exhaust pressure relief mechanism 15 is arranged at the top of the seal head 1, the inner shell 5 of the heat exchanger and the outer shell 13 of the buffer layer. The buffer layer pressure sensor 16 and the buffer layer LNG concentration measuring device 17 are respectively installed around the buffer layer outer shell 13.
The bottom of the buffer layer outer shell 13 is provided with a heat exchanger supporting base 18 for supporting the shell-and-tube heat exchanger.
Referring to fig. 2, 3 and 4, the radial heat exchange tube 6 is formed by connecting a plurality of flow passage units 66 with the same structure in series, and the adjacent flow passage units 66 are connected by a main flow passage 61 which coincides with the axis of the inner shell 5 of the heat exchanger. Each flow channel unit 66 is further formed by two layers of N-generation flow channel groups 67, wherein each layer of N-generation flow channel groups 67 is further formed by a main flow channel 61, N-generation radial radiation sub-flow channels and N-generation axial sub-flow channels (the total number of circulation algebra N is an integer greater than or equal to 2).
The 1 st generation radial radiation sub-flow channels 62 are connected with the main flow channel 61, and take the connection part as a radiation node, M1 st generation radial radiation sub-flow channels 62 are radiated in the radial direction (the radiation number M of each generation is an integer greater than or equal to 3) on the plane perpendicular to the main flow channel 61, the 1 st generation radial radiation sub-flow channels 62 are distributed at equal intervals along the circumferential direction, and the 1 st generation axial sub-flow channels 63 with equal length extend from the tail end of each 1 st generation radial radiation sub-flow channel 62 along the axial direction of the main flow channel 61.
When the circulation algebra N is more than or equal to 2 (N is more than or equal to 2), the nth generation radial radiation sub-runners respectively take the tail ends of the nth-1 generation axial sub-runners as radiation nodes, M nth generation radial radiation sub-runners extend out along the radial direction along the plane vertical to the nth-1 generation axial sub-runners, and the nth generation radial radiation sub-runners radiated by the same nth-1 generation axial sub-runner are distributed along the circumferential direction at equal intervals. In addition, at the end of each nth generation radial radiation sub-runner, an nth generation axial sub-runner with equal length extends along the nth-1 generation axial sub-runner.
The diameter of the radial radiation sub-flow channel of the same generation is the same as that of the axial sub-flow channel, and the diameter ratio of the upper sub-flow channel and the lower sub-flow channel is selected to be the optimal value which minimizes the turbulent flow friction resistance, namely (D) n-1 /D n ＝M 3/7 N is more than or equal to 2 and N is more than or equal to N). The length of the radial radiation sub-flow channel of the same generation is the same as that of the axial sub-flow channel, the length ratio of the upper sub-flow channel and the lower sub-flow channel is the same as the optimal value for minimizing the turbulent flow friction resistance,namely (L) n-1 /L n ＝M 1/7 ，2≤n≤N)。
Referring to fig. 6 and 7, the heat exchange tube supporting mechanism 7 is composed of a housing connecting member 71, a sliding connecting member 72, a supporting spring 73 and a heat exchange tube fixing member 74. The top of the shell connecting piece 71 is a curved surface and is fixedly connected with the top or the bottom of the inner shell 5 of the heat exchanger in a welding mode; the inside is hollow structure, is provided with smooth slide rail in the structure bottom surface, has seted up the round hole in center department to be provided with annular limit baffle along circumference at round hole outer fringe circle. The top of the sliding connecting piece 72 is in a disc-shaped sliding structure, and is arranged inside the shell connecting piece 71, and small-range displacement in the horizontal direction can be realized by matching with the sliding rail, and the maximum displacement range is limited by the limit baffle. The bottom of the slider connecting piece 72 is in a cylindrical structure and is arranged in the round hole, so that small-range displacement along the axial direction of the round hole can be realized. The heat exchange tube fixing member 74 has a cylindrical structure at the top and a clamp structure at the bottom, and is used for clamping the main flow channel 61, and completely fixing the two members by a pin. The top and bottom of the supporting spring 73 are respectively fixed with the cylindrical structure at the bottom of the sliding connection piece 72 and the cylindrical structure at the top of the heat exchange tube fixing piece 74.
The problem of large thermal stress can be generated in the low-temperature starting and running process in the LNG cold energy utilization field, when the heat exchange tube bundle is affected by the thermal stress to expand or shrink, the sliding block connecting piece 72 can support the heat exchange tube bundle while the heat exchange tube bundle is axially and freely displaced, so that the stability under the large-temperature-difference low-temperature running working condition is enhanced.
Referring to fig. 8, the buffer layer supporting structure 14 is in a ring shape and is coaxially arranged with the inner shell 5 and the outer shell 13 of the buffer layer, wherein the inner supporting curved surface 141 is connected with the inner shell 5 of the heat exchanger, and the outer supporting curved surface 142 is connected with the outer shell 13 of the buffer layer. The rotation cross section of the buffer layer supporting structure 14 is an i-shaped structure with high bearing capacity, and a plurality of hollow holes and grooves are distributed along the circumference of the buffer layer supporting structure 14 at equal intervals.
Referring to fig. 9, the pressure release mechanism 15 is composed of a pressure release mechanism base 151, a compression spring 152, a sealing structure 153, and a sealing gasket 154. The exhaust and pressure relief mechanism base 151 comprises a flange plate and a cylinder body, the flange plate is used for fixedly connecting the exhaust and pressure relief mechanism 15 with the inner shell 5 of the heat exchanger and the outer shell 13 of the buffer layer, 2 layers of 12 exhaust round holes are formed in the side surface of the cylinder body at equal intervals along the circumferential direction, and an annular limit baffle is arranged at the bottom of the cylinder body along the circumferential direction of the inner wall of the cylinder body. The sealing structure 153 and the sealing gasket 154 are disposed in the cylinder and are sequentially connected with the limit baffle along the axial direction, and the compression spring 152 is disposed between the top of the cylinder and the sealing structure 153, and is used for sealing the pressure release mechanism 15.
Those of ordinary skill in the art will appreciate that: the foregoing description is only a preferred embodiment of the present invention, and the present invention is not limited thereto, but it is to be understood that modifications and equivalents of some of the technical features described in the foregoing embodiments may be made by those skilled in the art, although the present invention has been described in detail with reference to the foregoing embodiments. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (6)
1. An explosion-proof LNG shell-and-tube heat exchanger, comprising:
the heat exchange space of the inner layer; the heat exchange space comprises an end socket (1), a heat exchanger inner shell (5), a separation baffle (2), a fixed tube plate (4), radial heat exchange tubes (6), a heat exchange tube supporting mechanism (7), a floating head tube plate (9) and a floating head cover (10); the seal heads (1) are respectively arranged at two ends of the inner shell (5) of the heat exchanger and are axially connected with the inner shell (5) of the heat exchanger; the fixed tube plate (4) is arranged on one side of the inner shell (5) of the heat exchanger, and forms a tube box with the end socket (1) on the side, and the tube box is divided into an upper part and a lower part by the horizontally arranged separation baffle (2) to form two tube passes; the floating head tube plate (9) and the floating head cover (10) are all provided withThe other side of the inner shell (5) of the heat exchanger is provided with a space for changing the flow direction of tube side fluid so as to realize tube side switching; two groups of heat exchange tube bundles are formed by a plurality of radial heat exchange tubes (6) together, and as two tube passes, two ends of the heat exchange tube bundles are respectively fixed on the fixed tube plate (4) and the floating head tube plate (9), and the floating head end can freely move in the axial direction relative to the inner shell (5) of the heat exchanger, so that the thermal stress of the heat exchange tube bundles can be reduced; the heat exchange tube bundle is radially connected with the inner shell (5) of the heat exchanger through the heat exchange tube supporting mechanism (7); a tube side fluid inlet (3), a tube side fluid outlet (11), a shell side fluid inlet (12) and a shell side fluid outlet (8) are arranged on the inner shell (5) of the heat exchanger, the tube side fluid inlet (3) and the tube side fluid outlet (11) are used for circulating tube side fluid LNG, and the shell side fluid inlet (12) and the shell side fluid outlet (8) are used for circulating shell side fluid; the radial heat exchange tube (6) is formed by connecting a plurality of runner units (66) with the same structure in series, and the adjacent runner units (66) are connected by a main runner (61) which is overlapped with the axis of the inner shell (5) of the heat exchanger; each flow passage unit (66) is composed of two layersNA runner group (67) in which each layerNThe runner group (67) is composed of a main runner (61),NRadial radiation sub-runnerNThe substitute shaft is formed by a sub-runner,Nthe 1 st generation radial radiation sub-runner (62) is connected with the main runner (61) by taking an integer greater than or equal to 2, and takes the connection part as a radiation node to radiate along the radial direction on the plane vertical to the main runner (61)MThe 1 st generation radial radiation sub-flow passage (62),Mtaking an integer greater than or equal to 3, wherein the 1 st generation radial radiating sub-channels (62) are distributed at equal intervals along the circumferential direction, and a 1 st generation axial sub-channel (63) with equal length extends out of the tail end of each 1 st generation radial radiating sub-channel (62) along the axial direction of the main channel (61); when the algebra is loopednWhen greater than or equal to 2, the firstnThe radial radiation sub-channels are respectively divided into the firstn-the end of the generation 1 axial sub-flow channel acts as a radiating node, perpendicular to the first said pathn-1 generation axial sub-flow passage plane, extending radiallyMStrip No.nRadial radiation sub-flow passage is replaced, and the same strip is the firstn-each of said first radial sub-channels of generation 1nRadial radiating sub-flow passages are distributed at equal intervals along the circumferential direction; at each of said firstnThe radial radiation sub-runner end is along the firstn-1 generation axial sub-flow passage extending out of the first equal lengthnA substitution shaft sub-runner; the diameter of the radial radiation sub-flow passage of the same generation is the same as that of the axial sub-flow passage, and the former generation sub-flow passageD n And diameter of next generation sub-runnerD n-1 The ratio is selected to be the optimal value with the minimum flow friction resistance, namelyD n-1 /D n =M 3/7 The method comprises the steps of carrying out a first treatment on the surface of the The length of the radial radiation sub-flow passage of the same generation is the same as that of the axial sub-flow passage, and the length of the previous generation sub-flow passageL n And the length of the next generation sub-runnerL n-1 By choosing the optimum value for minimizing the flow friction resistance, i.eL n-1 /L n =M 1/7 The method comprises the steps of carrying out a first treatment on the surface of the Two layersNThe runner groups (67) are arranged in opposite directions and are formed by the firstNThe sub-flow passages are connected into a whole to form the flow passage unit (66);
and a buffer space of the outer layer; the buffer space is positioned between the heat exchanger inner layer shell (5) and the buffer layer outer layer shell (13), and inert gas with high chemical stability is filled in the buffer space and used for isolating outside air and LNG in the buffer space, so that the heat exchanger has a flame-retardant effect.
2. The explosion-proof LNG shell-and-tube heat exchanger according to claim 1, characterized in that a buffer layer support structure (14), a gas venting mechanism (15), a buffer layer pressure sensor (16) and a buffer layer LNG concentration measuring device (17) are arranged between the heat exchanger inner layer shell (5) and the buffer layer outer layer shell (13); the inner shell (5) of the heat exchanger and the outer shell (13) of the buffer layer are radially and fixedly connected through the buffer layer supporting structure (14); the exhaust pressure relief mechanism (15) is arranged at the tops of the seal head (1), the inner shell (5) of the heat exchanger and the outer shell (13) of the buffer layer; the buffer layer pressure sensor (16) and the buffer layer LNG concentration measuring device (17) are respectively arranged around the buffer layer outer layer shell (13); a heat exchanger supporting base (18) is arranged at the bottom of the buffer layer outer shell (13) and used for supporting the shell-and-tube heat exchanger; the buffer layer LNG concentration measuring device (17) is used for monitoring the change of the LNG concentration in the buffer layer, and the buffer layer LNG concentration measuring device (17) and the buffer layer LNG concentration measuring device (16) and the remote monitoring equipment jointly form an LNG leakage early warning system.
3. The explosion-proof LNG shell-and-tube heat exchanger according to claim 2, wherein the heat exchange tube support mechanism (7) is composed of a housing connector (71), a sliding connector (72), a support spring (73) and a heat exchange tube fixing member (74); the top of the shell connecting piece (71) is a curved surface and is fixedly connected with the top or the bottom of the inner shell (5) of the heat exchanger in a welding mode; the inside of the device is a hollow structure, a flat and smooth sliding rail is arranged on the bottom surface of the structure, a round hole is formed in the center of the structure, and an annular limit baffle is arranged on the periphery of the round hole along the circumferential direction; the top of the sliding connecting piece (72) is of a disc-shaped sliding structure, the sliding connecting piece is arranged in the shell connecting piece (71), small-range displacement in the horizontal direction can be realized through matching with the sliding rail, and the maximum displacement range of the sliding connecting piece is limited by the limit baffle; the bottom of the sliding connecting piece (72) is of a cylindrical structure and is arranged in the round hole, so that displacement in a small range along the axial direction of the round hole can be realized; the top of the heat exchange tube fixing piece (74) is of a cylindrical structure, the bottom of the heat exchange tube fixing piece is of a clamp structure and is used for clamping the main flow channel (61), and the heat exchange tube fixing piece and the main flow channel are completely fixed through a pin bolt; the top and the bottom of the supporting spring (73) are respectively fixed with the cylindrical structure at the bottom of the sliding connecting piece (72) and the cylindrical structure at the top of the heat exchange tube fixing piece (74).
4. The explosion-proof LNG shell-and-tube heat exchanger according to claim 2, characterized in that the buffer layer support structure (14) is ring-shaped, coaxially arranged with the heat exchanger inner layer shell (5) and the buffer layer outer layer shell (13), wherein an inner support curved surface (141) is connected with the heat exchanger inner layer shell (5), and an outer support curved surface (142) is connected with the buffer layer outer layer shell (13); the rotary cross section of the buffer layer supporting structure (14) is an I-shaped structure with high bearing capacity, and a plurality of hollow hole grooves are distributed along the circumferential direction of the buffer layer supporting structure (14) at equal intervals.
5. The explosion-proof LNG shell-and-tube heat exchanger according to claim 2, wherein the pressure relief mechanism (15) is constituted by a pressure relief mechanism base (151), a compression spring (152), a sealing structure (153) and a sealing gasket (154); the exhaust and pressure relief mechanism base (151) comprises a flange plate and a cylinder body, the flange plate is used for fixedly connecting the exhaust and pressure relief mechanism (15) with the inner shell (5) of the heat exchanger and the outer shell (13) of the buffer layer, 2 layers of 12 exhaust round holes are formed in the side surface of the cylinder body at equal intervals along the circumferential direction, and an annular limit baffle is arranged at the bottom of the cylinder body along the circumferential direction of the inner wall of the cylinder body; the sealing structure (153) and the sealing gasket (154) are arranged in the cylinder body and are sequentially connected with the limit baffle along the axial direction, and the compression spring (152) is arranged between the top of the cylinder body and the sealing structure (153) and is used for sealing the air discharge and pressure relief mechanism (15).
6. The explosion-proof LNG shell-and-tube heat exchanger according to claim 1, wherein the inert gas is nitrogen, helium or argon.
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Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3400758A (en) * | 1966-05-16 | 1968-09-10 | United Aircraft Prod | Helical baffle means in a tubular heat exchanger |
| CN101435670A (en) * | 2008-12-09 | 2009-05-20 | 华中科技大学 | Longitudinal disturbed flow shell and tube hear exchanger |
| CN101706227A (en) * | 2009-11-27 | 2010-05-12 | 北京化工大学 | Shell-and-tube heat exchanger with un-notched traverse baffles |
| CN101846467A (en) * | 2010-04-28 | 2010-09-29 | 东南大学 | Shell-tube heat exchanger |
| CN202002515U (en) * | 2011-02-24 | 2011-10-05 | 中国石化扬子石油化工有限公司 | Heat exchanger |
| CN102865755A (en) * | 2012-08-03 | 2013-01-09 | 谭新 | Heat exchanger |
| CN105258533A (en) * | 2015-11-17 | 2016-01-20 | 中国科学院上海高等研究院 | Shell-and-tube heat exchanger of fractal structure |
-
2023
- 2023-05-04 CN CN202310485643.9A patent/CN116625143B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3400758A (en) * | 1966-05-16 | 1968-09-10 | United Aircraft Prod | Helical baffle means in a tubular heat exchanger |
| CN101435670A (en) * | 2008-12-09 | 2009-05-20 | 华中科技大学 | Longitudinal disturbed flow shell and tube hear exchanger |
| CN101706227A (en) * | 2009-11-27 | 2010-05-12 | 北京化工大学 | Shell-and-tube heat exchanger with un-notched traverse baffles |
| CN101846467A (en) * | 2010-04-28 | 2010-09-29 | 东南大学 | Shell-tube heat exchanger |
| CN202002515U (en) * | 2011-02-24 | 2011-10-05 | 中国石化扬子石油化工有限公司 | Heat exchanger |
| CN102865755A (en) * | 2012-08-03 | 2013-01-09 | 谭新 | Heat exchanger |
| CN105258533A (en) * | 2015-11-17 | 2016-01-20 | 中国科学院上海高等研究院 | Shell-and-tube heat exchanger of fractal structure |
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