CN112539668A - Heat exchanger and manufacturing method thereof - Google Patents
Heat exchanger and manufacturing method thereof Download PDFInfo
- Publication number
- CN112539668A CN112539668A CN202011377883.XA CN202011377883A CN112539668A CN 112539668 A CN112539668 A CN 112539668A CN 202011377883 A CN202011377883 A CN 202011377883A CN 112539668 A CN112539668 A CN 112539668A
- Authority
- CN
- China
- Prior art keywords
- plate
- baffle plate
- heat exchanger
- pattern plate
- baffle
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Images
Classifications
-
- 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
-
- 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
-
- 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
Abstract
The invention discloses a heat exchanger, which comprises: a barrel; a first end cap and a second end cap; the heat exchange inner core comprises a first pattern plate, a second pattern plate, at least one baffle plate and a tube bundle, wherein two end parts of the tube bundle are respectively fixed with the first pattern plate and the second pattern plate in a sealing way, and the middle part of the tube bundle penetrates through the baffle plate; the tube bundle comprises at least: the first area is positioned between the first pattern plate and the baffle plate adjacent to the first pattern plate; the second area is positioned between the second pattern plate and the baffle plate adjacent to the second pattern plate; the hollow tube in at least one of the first region and the second region extends obliquely. In the heat exchanger, in the first area and/or the second area, the clearance between the periphery of the tube bundle and the inner wall of the cylinder is increased, the flow resistance of shell-side fluid is reduced, and the heat exchange rate is accelerated; meanwhile, the size of the gap between the adjacent hollow tubes is increased, the flowing turbulence degree is further improved, and the quick heat exchange is facilitated. The invention also provides a manufacturing method of the heat exchanger, which has simple steps and good reliability of the heat exchanger.
Description
Technical Field
The invention belongs to the technical field of heat exchange devices, and particularly relates to a heat exchanger and a manufacturing method thereof.
Background
US3417812 discloses a heat exchanger comprising a shell, a tube bundle located inside the shell and two end caps sealingly fixed to the two ends of the shell, the end caps being provided with an inlet tube and an outlet tube, respectively, for the inflow and outflow of the fluid inside the tubes, and the shell being provided on each side with an inlet tube and an outlet tube, respectively, for the inflow and outflow of the fluid outside the tubes.
Wherein, many hollow tubes constitute the tube bank, and the both ends of tube bank are sealed at first to be fixed in two end plates, and inside inserting the casing again with the end plate together, two end plates are sealed respectively and are fixed in the both ends of casing, and the tube bank is straight to extend between two end plates. Therefore, in the whole length range of the tube bundle, the distance between the peripheries of the adjacent hollow tubes is always equal to the distance between the peripheries of the end parts of the adjacent hollow tubes which are fixed in the end plates in a sealing mode, and the shapes of gaps between the peripheries of the adjacent hollow tubes are uniform.
The heat exchanger disclosed in US3228456 is similar to the heat exchanger disclosed in US3417812 in that the tube bundle extends straight between two end plates.
In the heat exchangers provided by the above two us patents, since the hollow tubes extend straightly in the whole length range, the size and shape of the gap between the adjacent hollow tubes are always regular and uniform, so that the flow uniformity of the fluid flowing inside the shell and around the hollow tubes, i.e. the shell-side fluid, is relatively high, the turbulence degree is low, and the heat exchange rate of the heat exchanger is relatively low. And because the tube bank is straight and extended in the shell, the length of the tube bank is equal to that of the shell, and the heat exchange area can not be increased under the condition of not increasing the size of the shell. In addition, in the heat exchanger, since the gap between the outer peripheries of the adjacent hollow tubes is small, the flow resistance of the fluid flowing through the gap is large, and the flow rate and the heat exchange rate are further reduced.
Therefore, it is desirable to provide a new heat exchanger, which can increase the size of the gap between the peripheries of adjacent hollow tubes and the nonuniformity of the size without increasing the size of the cylinder, and make the shape of the gap irregular, so as to solve the problem of low heat exchange efficiency of the existing heat exchanger due to low turbulence degree of the shell-side fluid, and increase the heat exchange area of the heat exchanger to a certain extent.
Disclosure of Invention
In order to overcome the disadvantages of the prior art, the present invention provides a heat exchanger capable of increasing a heat exchange rate and increasing a heat exchange area of the heat exchanger to some extent by providing a partial region of a tube bundle to extend obliquely without increasing the size of a cylinder. Meanwhile, a manufacturing method of the heat exchanger is also provided.
The technical scheme adopted by the invention for solving the technical problems is as follows: a heat exchanger, comprising:
the cylinder body is provided with two open ends and at least two joints on the side wall;
the first end cover and the second end cover are respectively fixed at two ends of the cylinder in a sealing way and are respectively provided with at least one joint;
the heat exchange inner core comprises a first pattern plate, a second pattern plate, at least one baffle plate and a tube bundle, wherein the baffle plate is positioned between the first pattern plate and the second pattern plate, the tube bundle is formed by a plurality of hollow tubes, two end parts of the tube bundle are respectively and hermetically fixed with the first pattern plate and the second pattern plate, the middle part of the tube bundle penetrates through the baffle plate, a first positioning hole penetrated by the hollow tubes is formed in the baffle plate, and a second positioning hole penetrated by the hollow tubes is formed in the first pattern plate and the second pattern plate;
the maximum value of the outer diameters of the second flower plate and the baffle plate is smaller than the minimum value of the inner diameter of the cylinder;
the tube bundle comprising at least:
the first area is positioned between the first pattern plate and the baffle plate adjacent to the first pattern plate;
the second area is positioned between the second pattern plate and the baffle plate adjacent to the second pattern plate;
the hollow tube in at least one of the first region and the second region extends obliquely.
In the heat exchanger provided by the invention, the middle part of the tube bundle penetrates through the baffle plate, the tube bundle is positioned in at least one of a first area between the first pattern plate and the adjacent baffle plate and a hollow tube positioned in at least one of a second area between the second pattern plate and the adjacent baffle plate, and the hollow tube obliquely extends, the clearance between the periphery of the tube bundle and the inner wall of the cylinder in the first area and/or the second area is increased, so that the flow of shell-side fluid from an inlet to an area opposite to the inlet is facilitated, the flow of shell-side fluid from an area opposite to an outlet to the outlet is facilitated, and the heat exchange rate is; meanwhile, the size and the shape of a gap between adjacent hollow tubes are increased and irregular, and when shell-side fluid flows through, the flowing turbulence degree is improved, so that the heat exchange efficiency and the heat exchange rate are both improved; in addition, when the turbulence degree of the shell-side fluid passing through at least one of the first area and the second area is improved, the problems of slow fluid flow and low heat exchange efficiency in the area near the sealing connection part of the end part of the cylinder and the first flower plate and/or the second flower plate can be relieved to a certain extent.
Further, the length of the middle part of the tube bundle between the first flower plate and the second flower plate is 1.05-1.2 times of the length of the cylinder, and the inclination angle of the hollow tube in the first area and/or the second area is 2-8 degrees.
The length of the middle part of the tube bundle between the first pattern plate and the second pattern plate is 1.05-1.2 times of the length of the cylinder, namely the length of the area actually playing a heat exchange role in the tube bundle is larger than the length of the cylinder and is 1.05-1.2 times of the latter, so that the heat exchange area can be increased to a certain extent, and the phenomenon that a plurality of hollow tubes are wound together in the cylinder due to the overlong tube bundle is avoided, extra resistance is generated on shell-side fluid, and the condition that a faster heat exchange rate can be provided is ensured. The inclination angle of the hollow pipe in the first area and/or the second area is 2-8 degrees, namely the inclination extension angle of the hollow pipe is not more than 8 degrees, so that the hollow pipe can be prevented from being excessively bent and damaged.
Furthermore, the central axes of the first flower plate, the second flower plate and the baffle plate are mutually overlapped, and the hole interval of the first positioning hole is larger than or smaller than that of the second positioning hole.
The positions of first card, second card and baffling board are just right, the hole interval of the first locating hole of baffling board is greater than the hole interval of the second locating hole of first card and/or second card, the interval of adjacent hollow tube is greater than the interval that the tube bank is located adjacent hollow tube in the tip of first card and second card in the mid portion of tube bank, can fully separate the hollow tube of the mid portion of tube bank, the size in space between the adjacent hollow tube of increase, the flow resistance of shell side fluid wherein reduces, the velocity of flow increases, thereby heat transfer rate improves.
Or the hole spacing of the second positioning holes of the first flower plate and/or the second flower plate is larger than that of the first positioning holes of the baffle plate, so that the gap size of the periphery of the adjacent hollow pipe in the two end parts of the pipe bundle is increased, the flow resistance of the shell-side fluid in the sealing connection area of the first flower plate and/or the second flower plate and the two end parts of the cylinder body is reduced, the flow speed is increased, and the heat exchange rate is improved.
Furthermore, the baffle plates at least comprise a first baffle plate adjacent to the first flower plate and a second baffle plate adjacent to the second flower plate, and the hollow pipes in the first area and the second area extend obliquely.
The number of the baffles is at least two, the hollow tubes in the first area and the second area of the tube bundle extend obliquely, gaps between the adjacent hollow tubes are uneven in size and irregular in shape, and the two obliquely extending areas extend to cross the areas near the first flower plate and the second flower plate, so that the turbulence degree of the shell-side fluid in the areas of the heat exchanger close to the first flower plate and the second flower plate can be improved, the flow of the shell-side fluid near the first flower plate and the second flower plate can be disturbed additionally, and the heat exchange rate in the areas can be accelerated.
Furthermore, the hole spacing of the first positioning holes of the first baffle plate and the second baffle plate is the same and is 1.3-1.6 times of the hole spacing of the second positioning holes of the first flower plate and the second flower plate.
The hole interval of the first positioning hole of the baffle plate is 1.3-1.6 times of the hole interval of the second positioning hole of the first pattern plate and the second pattern plate, and in the first area and the second area of the tube bundle, the hollow tubes are inclined and extended, so that the size of the first baffle plate and the size of the second baffle plate are not too large, and the heat exchange inner core can be rapidly inserted into the barrel in the assembling process of the heat exchanger.
Further, the tube bundle includes an intermediate region between the first and second baffle plates, the first and second regions having an overall length of at least 60% of the overall length of the tube bundle.
When the length of the hollow pipe corresponding to the first area and the second area is more than 60% of the total length of the pipe bundle, the turbulence degree of the shell-side fluid in the area with enough width is improved, and the area close to the first flower plate and the second flower plate is ensured not to form a flowing dead angle.
Furthermore, in the first area and the second area, the inclination angle of the hollow pipe positioned at the outer ring is larger than that of the hollow pipe positioned at the adjacent inner ring.
Between first card and first baffling board and between second card and the second baffling board, the angle of inclination that the hollow tube slope of outer lane extended is greater than the angle of inclination that the hollow tube slope of adjacent inner circle extended, further improves two regions of tube bank, and the inhomogeneous and the irregular degree of shape of the size of the space between the adjacent hollow tube increases the perturbation effect to shell side fluid, improves the torrent degree, further accelerates heat transfer rate.
Further, the inner diameter of the first positioning hole of the first baffle plate and the first positioning hole of the second baffle plate are larger than the outer diameter of the hollow pipe; the outer ring hollow pipe sleeve of the pipe bundle is provided with a first protective sleeve and a second protective sleeve, the first protective sleeve extends from the tail end of the first pattern plate and penetrates through the first baffle plate, and the second protective sleeve extends from the tail end of the second pattern plate and penetrates through the second baffle plate.
The internal diameter of the first locating hole of first baffling board and second baffling board is greater than the external diameter of hollow tube, make things convenient for the hollow tube to pass the hole of first baffling board and second baffling board, only pass this moment, do not form the fixed action, the setting of first protective sheath and second protective sheath can be avoided under the fluidic percussion action of shell side, the hollow tube of outer lane forms the great rocking of range in the first locating hole of first baffling board and second baffling board, effectively avoid producing the friction between the outer wall of hollow tube and first locating hole inner wall, the hollow tube formation guard action to the outer lane.
Furthermore, the first protective sleeve and the second protective sleeve respectively form interference fit with the first positioning hole of the first baffle plate and the first positioning hole of the second baffle plate.
First protective sheath and second protective sheath form interference fit with the first locating hole of first baffling board and second baffling board respectively, avoid first protective sheath and second protective sheath to remove at will to ensure that two outermost circles of hollow tubes pass the first locating hole's of first baffling board and second baffling board regional inside first and second protective sheath all the time.
Further, the central axes of the first baffle plate and the second baffle plate are not coincident; the hollow tube in the middle region extends obliquely or spirally.
The hollow pipe extends obliquely or spirally corresponding to the middle area between the first baffle plate and the second baffle plate, so that the turbulence degree of the shell-side fluid is improved and the heat exchange rate is accelerated in the middle area inside the cylinder.
Furthermore, the baffle plates are arch baffle plates, openings for fluid circulation are formed in circle-lacking areas of the arch baffle plates, and the openings of the adjacent baffle plates are arranged in a staggered mode.
The arch baffle plate can increase the width of a flow channel of shell pass fluid in the cylinder, reduce the flow resistance of the shell pass fluid and accelerate the heat exchange rate; the opening of the first baffle plate and the opening of the second baffle plate are arranged in a staggered mode, so that the flow of the shell pass fluid forms an S shape, the disturbance of the flow of the shell pass fluid is increased, the turbulence degree of the shell pass fluid is improved, and the heat exchange efficiency is improved.
Further, the present invention also provides a method of manufacturing the heat exchanger, which includes the steps of:
(1) a plurality of hollow pipes forming the pipe bundle penetrate through the first positioning holes of the baffle plate, and two end parts of the hollow pipes are respectively fixed to the second positioning holes of the first pattern plate and the second pattern plate in a sealing manner, so that a heat exchange inner core is manufactured;
(2) the second end of the heat exchange inner core extends into the first end of the cylinder body and extends out of the second end of the cylinder body, the first flower plate and the first end cover of the heat exchange inner core are simultaneously and hermetically fixed to the first end of the cylinder body, and the second flower plate and the second end cover of the heat exchange inner core are simultaneously and hermetically fixed to the second end of the cylinder body;
in the heat exchange inner core, the maximum value of the outer diameters of the second flower plate and the baffle plate is smaller than the minimum value of the inner diameter of the cylinder;
the tube bundle comprising at least:
the first area is positioned between the first pattern plate and the baffle plate adjacent to the first pattern plate;
the second area is positioned between the second pattern plate and the baffle plate adjacent to the second pattern plate;
the hollow tube in at least one of the first region and the second region extends obliquely.
The manufacturing method of the heat exchanger provided by the invention comprises the following steps of firstly, providing an integrated heat exchange inner core, then, extending the heat exchange inner core into a cylinder body, and hermetically fixing the corresponding pattern plate and the end cover to the corresponding end part of the cylinder body; the maximum value of the outer diameters of the second pattern plate and the baffle plate is smaller than the minimum value of the inner diameter of the cylinder, so that the heat exchange inner core can conveniently extend into the cylinder, and the heat exchanger can be conveniently manufactured. In the manufacturing method, the assembly operation of the components is convenient, the process is simple, and after the assembly is completed, the reliability of the heat exchanger is good, and the use by customers is convenient.
The invention has the beneficial effects that: at least one of the area of the tube bundle between the first flower plate and the adjacent baffle plate and the area of the tube bundle between the second flower plate and the adjacent baffle plate extends obliquely, so that in at least one of the area between the first flower plate and the adjacent baffle plate and the area between the second flower plate and the adjacent baffle plate, the clearance between the tube bundle and the inner wall of the cylinder is increased, the flowing of shell-side fluid from an inlet to the area opposite to the inlet is facilitated, the flowing of shell-side fluid from the area opposite to the outlet is facilitated, and the heat exchange rate is increased; meanwhile, in at least one of the areas, the size of the gap between the adjacent hollow tubes becomes uneven, the shape becomes irregular, and when the shell-side fluid flows through the gap, the flowing turbulence degree is improved, so that the heat exchange rate and the heat exchange efficiency are improved; in addition, in the area near the sealing connection between the end part of the cylinder and the first flower plate and/or the second flower plate, the flow speed of the shell-side fluid is usually lower, the residence time of the shell-side fluid in the two areas is longer, and the heat exchange rate of the fluid in the area is obviously lower than that in the middle area of the heat exchanger; when the turbulence degree of the shell pass fluid passing through at least one of the area between the first flower plate and the adjacent baffle plate and the area between the second flower plate and the adjacent baffle plate is improved, an additional disturbance effect can be caused to the fluid flow in the area near the sealing connection part of the end part of the cylinder and the first flower plate and/or the second flower plate, and the problems that the shell pass fluid in the area flows too slowly and the heat exchange efficiency is low are solved.
Drawings
Fig. 1 is a perspective view of a heat exchanger according to the present invention.
Fig. 2 is a perspective view of the heat exchange core of the present invention with the tube bundle removed.
Fig. 3 is a sectional view of a heat exchange core of a first structure provided by the invention.
Fig. 4 is an enlarged view of a structure in fig. 3.
Fig. 5 is an enlarged view of the structure at B in fig. 3.
Fig. 6 is a sectional view of a heat exchange core in a second structure according to the present invention.
FIG. 7 is a top view of a first deck provided by the present invention.
FIG. 8 is a top view of a baffle provided by the present invention.
Fig. 9 is a schematic diagram of the structure of the middle area of the tube bundle of the heat exchange core in the third structure provided by the invention.
The heat exchanger comprises a barrel body 1, a barrel body 11, a joint on the outer wall of the barrel body 21, a first end cover 22, a second end cover 211, a joint on the first end cover 221, a joint on the second end cover 3, a heat exchange inner core 30, a hollow pipe 31, a pipe bundle 311, a first area of the pipe bundle 312, a second area of the pipe bundle 313, a middle area of the pipe bundle 313, a first protective sleeve 32, a second protective sleeve 33, a first pattern plate 4, a second positioning hole 42, a second pattern plate 5, a baffle plate 6, an opening 60, a first baffle plate 61, a first baffle plate 611, a second baffle plate 62, a second baffle plate 621, a first positioning hole 63.
Detailed Description
In order to make the technical solutions of the present invention better understood, the technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
As shown in fig. 1 to 9, a heat exchanger includes a hollow cylinder 1, a first end cap 21 and a second end cap 22 hermetically fixed to both ends of the cylinder 1, and a heat exchange core 3 internally installed in the cylinder 1.
The two ends of the cylinder body 1 are opened to form a first end and a second end, the side wall of the cylinder body 1 is provided with at least two joints 11, the first end cover 21 is fixed at the first end of the cylinder body 1, the second end cover 22 is fixed at the second end of the cylinder body 1 in a sealing way, the first end cover 21 is provided with at least one joint 211, and the second end cover 22 is provided with at least one joint 221.
In this embodiment, the side wall of the cylinder 1 has four joints, and each two joints are located at two opposite sides of the cylinder 1, wherein two joints located at two ends of the cylinder 1 are used as an inlet and an outlet of the shell-side heat exchange fluid, and two joints located at the other two ends are used as outlets of the condensed gas and the liquid. Of course, the discharge ports for condensed gas and liquid are provided, as the case may be.
The heat exchange inner core 3 comprises a first flower plate 4 and a second flower plate 5, at least one baffle plate 6 positioned between the first flower plate 4 and the second flower plate 5, and a tube bundle 31 composed of a plurality of hollow tubes 30, wherein two end parts of the tube bundle 31 are respectively fixed in a sealing way in a plurality of holes of the first flower plate 4 and the second flower plate 5, and the middle part of the tube bundle 31 passes through the baffle plate 6 with a plurality of holes. Wherein, the maximum value of the outer diameters of the second flower plate 5 and the baffle plate 6 is smaller than the minimum value of the inner diameter of the cylinder 1, so that the heat exchange inner core 3 can rapidly extend into the cylinder 1.
The first and second flower plates 4 and 5 are both disc structures, and a plurality of openings for the hollow tube 30 to pass through are formed inside, and the material of the openings is fluorine-containing resin. The heat exchange inner core 3 is hermetically fixed between the first end of the cylinder 1 and the first end cover 21 and between the second end of the cylinder 1 and the second end cover 22 through the first spline 4 and the second spline 5, and the specific sealing connection mode may be a sealing connection mode through a flange and a gasket or a welding mode.
The number of the baffle plates 6 may be one or two or more, and the number of the baffle plates 6 is two for the example, that is, the baffle plates 6 include a first baffle plate 61 disposed adjacent to the first faceplate 4, and a second baffle plate 62 disposed adjacent to the second faceplate 5. Accordingly, the maximum value of the outer diameters of the first baffle 61, the second baffle 62 and the second spline 5 is smaller than the minimum value of the inner diameter of 1 cylinder.
As shown in fig. 3, the tube bundle 31 comprises at least a first zone 311 between the first flower 4 and the baffle 6 adjacent thereto, i.e. the first baffle 61, and a second zone 312 between the second flower 5 and the baffle 6 adjacent thereto, i.e. the second baffle 62; hollow tubes 30 in first region 311 extend obliquely, or hollow tubes 30 in second region 312 extend obliquely, as shown in fig. 6; or hollow tubes 30 in both first region 311 and second region 312 extend obliquely as shown in fig. 3.
At least one of the first region 311 and the second region 312 of the tube bundle 31 extends obliquely, which makes the gap between the tube bundle 31 and the inner wall of the cylinder 1 increase in at least one of the regions between the first spline 4 and the first baffle 61 and between the second spline 5 and the second baffle 62, facilitating the flow of the shell-side fluid from the inlet to the region opposite to the inlet, and facilitating the flow of the shell-side fluid from the region opposite to the outlet, and accelerating the heat exchange rate.
At the same time, in at least one of the first region 311 and the second region 312, the size of the gap between the adjacent hollow tubes 30 is also uneven, the shape thereof is irregular, and the degree of turbulence of the flow is increased when the shell-side fluid flows therethrough, so that the heat exchange rate and the heat exchange efficiency are both increased.
In addition, in the region near the sealing connection of the end of the cylinder 1 with the first and second flower plates 4 and 5, i.e., the space between the outer peripheries of the first and second regions 311 and 312 and the inner wall of the end of the cylinder 1, the flow velocity of the shell-side fluid will generally be relatively low, and the residence time of the shell-side fluid in these two regions will be relatively long, i.e., so-called dead flow zones are formed, and the heat exchange rate of the fluid in this region will be significantly less than that in the middle region of the heat exchanger. When the turbulence degree of the shell-side fluid passing through the area is increased, an additional disturbance effect can be caused to the fluid flow in the area near the sealing connection part of the end part of the cylinder body 1 and the first flower plate 4 and/or the second flower plate 5, and the problems that the shell-side fluid flows too slowly and the heat exchange efficiency is low in the two areas are solved.
As shown in fig. 8, a plurality of first positioning holes 63 through which hollow tubes 30 pass are formed on baffle plate 6; as shown in fig. 7, a plurality of second positioning holes 42 through which hollow tubes 30 pass are formed in first flower plate 4, and correspondingly, a plurality of second positioning holes 42 through which hollow tubes 30 pass are also formed in second flower plate 5.
Incidentally, the first positioning hole 63 refers to a hole of the first baffle plate 61 and the second baffle plate 62 through which the hollow tube 30 passes, and the second positioning hole 42 refers to a hole of the first flower plate 4 and the second flower plate 5 through which the hollow tube 30 passes. The holes in first baffle plate 61, second baffle plate 62, first flower plate 4, and second flower plate 5 through which hollow tube 30 does not pass are not referred to as first or second positioning holes 63 or 42.
In this embodiment, all the holes of the first baffle plate 61, the second baffle plate 62, the first flower plate 4 and the second flower plate 5 are penetrated by the hollow tube 30, and thus, all the holes of each form the corresponding first positioning hole 63 or the second positioning hole 42.
When the hole pitch of the first positioning holes 63 is greater than the hole pitch of the second positioning holes 42, the hollow tubes 30 are obliquely extended in the first region 311 and the second region 312, and the gap between the peripheries of the adjacent hollow tubes 30 is larger in the region of the tube bundle 31 close to the first baffle plate 61 and the second baffle plate 62; when the hole pitch of the first positioning holes 63 is smaller than the hole pitch of the second positioning holes 42, the hollow tubes 30 realize an oblique extension in the other direction in the first region 311 and the second region 312, and the clearance between the peripheries of the adjacent hollow tubes 30 is larger in the region where the tube bundle 31 is close to the first flower plate 4 and the second flower plate 5.
In the structure, the central axes of the first flower plate 4, the second flower plate 5 and the baffle plate 6 are coincident, and the hole pitches of the first positioning holes 63 of the first baffle plate 61 and the second baffle plate 62 are the same; the hole pitches of the second positioning holes 42 of the first flower plate 4 and the second flower plate 5 are the same; and the hole pitch of the first positioning holes 63 is 1.3 to 1.6 times the hole pitch of the second positioning holes 42. Hole pitch refers to the distance between the centers of adjacent holes.
In other embodiments, the first baffle plate 61 and the second baffle plate 62 may not only have the first positioning hole 63, but also have holes 611 and 621 that are not penetrated by the hollow tube 30; similarly, first and second flower plates 4 and 5 may have holes through which hollow tube 30 does not pass, in addition to second positioning hole 42. In this case, the openings of the first baffle 61, the second baffle 62, the first flower 4 and the second flower 5 may be arranged in the same array, and the intervals may be equal.
In this case, in order to realize the oblique extension of the tube bundle 31 or the hollow tubes 30, the hollow tubes 30 do not pass through every hole of all the holes of the baffle plate 6, but the hollow tubes 30 pass through every other hole or holes, leaving a hole vacant in the middle, and only the hole through which the hollow tube 30 passes is called the first positioning hole 63 of the present invention. Similarly, the hollow tube 30 does not pass through every hole, but the hollow tube 30 passes through every other hole or every several holes, leaving a hole in the middle, and only the hole through which the hollow tube 30 passes is called the second positioning hole 42 in the present invention.
The length of hollow tube 30 at the outer circumference is greater than the length of hollow tube 30 at the adjacent inner circumference, and the inclination angle of hollow tube 30 at the outer circumference in first region 311 and second region 312 of tube bundle 31 is greater than the inclination angle of hollow tube 30 at the adjacent inner circumference, which is the angle of the extending direction of hollow tube 30 with respect to the central axis of cylinder 1.
Because the length of the hollow tube 30 of the outer ring is greater than that of the hollow tube 30 of the adjacent inner ring, the heat exchange area can be increased to a certain extent and the heat exchange rate can be increased under the condition of not increasing the size of the cylinder body 1; between the first spline 4 and the first baffle 61 and between the second spline 5 and the second baffle 62, the inclined angle of the inclined extension of the hollow tube 30 of the outer ring is larger than the inclined angle of the inclined extension of the hollow tube 30 of the adjacent inner ring, so that the irregular degree of the shape of the gap between the adjacent hollow tubes 30 in the two inclined extension areas of the tube bundle 31 is further improved, the disturbance effect on the shell-side fluid is increased, the turbulence degree is improved, and the heat exchange rate is further accelerated.
In some of these embodiments, the length of the intermediate portion of the tube bundle 31 between the first and second flower plates 4, 5 is 1.05-1.2 times the length of the cylinder 1, and the angle of inclination of the hollow tubes 30 in the first region 311 and/or the second region 312 is 2-8 °.
The length of the middle part of the tube bundle 31 between the first flower plate 4 and the second flower plate 5 is 1.05-1.2 times of the length of the cylinder 1, namely the length of the area actually playing a heat exchange role in the tube bundle 31 is larger than the length of the cylinder 1 and is 1.05-1.2 times of the length of the latter, so that the heat exchange area can be increased to a certain extent, and the phenomenon that a plurality of hollow tubes 30 are wound together in the cylinder 1 because the tube bundle 31 is too long is avoided, additional resistance is generated on shell fluid, and a faster heat exchange rate can be provided. While the angle of inclination of hollow tube 30 in first region 311 and/or second region 312 is 2-8 °, i.e., the angle of inclination of hollow tube 30 is not greater than 8 °, which prevents hollow tube 30 from being excessively bent and damaged.
To facilitate the hollow tube 30 to pass through the first positioning holes 63 of the first and second baffle plates 61 and 62, the inner diameter of the first positioning holes 63 of the first and second baffle plates 61 and 62 is larger than the outer diameter of the hollow tube 30, and the hollow tube 30 passes through only the first positioning holes 63 of the first and second baffle plates 61 and 62 without being fixed. Because the length of outer lane hollow tube 30 is greater than the length of adjacent inner circle hollow tube 30, consequently, hollow tube 30 of outer lane can form the great shake of range in first locating hole 63 of first baffle 61 and second baffle 62 under the impact of shell side fluid, and the in-process of rocking, produces certain degree friction effect between the outer wall of hollow tube 30 and the inner wall of first locating hole 63 to this friction effect can be carried on continuously, so after lasting a period, hollow tube 30's outer wall can receive more serious friction damage.
In order to solve this problem, as shown in fig. 4 and 5, a first protective sleeve 32 and a second protective sleeve 33 are respectively sleeved on the outer peripheries of the two ends of the two layers of hollow pipes 30 at the outermost ring, the first protective sleeve 32 extends from the end of the first spline 4 and passes through the first baffle 61, and the second protective sleeve 33 extends from the end of the second spline 5 and passes through the second baffle 62. The first and second protective sleeves 32 and 33 form an interference fit with the first positioning holes 63 of the first and second baffles 61 and 62 to prevent the first and second baffles from moving freely, so as to ensure that the areas of the two outermost rings of hollow tubes 30 passing through the first positioning holes 63 of the first and second baffles 61 and 62 are always located inside the first and second protective sleeves 32 and 33.
The tube bundle 31 further includes an intermediate region 313 between the first and second baffle plates 61, 62, the total length of the first and second regions 311, 312 being at least 60% of the total length of the tube bundle 31. The hollow tubes 30 in the central region 313 may extend straight or obliquely, and when they extend obliquely, the central axes of the first and second baffle plates 61, 62 do not coincide. Of course, as shown in fig. 9, hollow tube 30 in intermediate region 313 may also extend helically. When the number of baffles 6 is one, the middle region 313 does not exist.
The baffle plates 6 are arch baffle plates, and the circular area of the baffle plates is provided with openings 60 for the circulation of fluid, namely the first baffle plate 61 and the second baffle plate 62 have the same structure, and after the installation is finished, the openings 60 of the adjacent baffle plates 6 are arranged in a staggered mode. The arch baffle 6 can increase the width of a flow channel of the shell-side fluid in the cylinder 1, reduce the flow resistance of the shell-side fluid and accelerate the heat exchange rate; the openings of the first baffle plate 61 and the second baffle plate 62 are arranged in a staggered manner, so that the flow of the shell-side fluid forms an S shape, the disturbance to the flow of the shell-side fluid is increased, the turbulence degree of the shell-side fluid is improved, and the heat exchange efficiency is improved.
In addition, the invention also provides a manufacturing method of the heat exchanger, which comprises the following steps:
(1) a plurality of hollow tubes 30 forming the tube bundle 31 pass through the first positioning holes 63 of the baffle plate 6, and the two end parts of the hollow tubes are respectively fixed to the second positioning holes 42 of the first flower plate 4 and the second flower plate 5 in a sealing manner, so as to prepare a heat exchange inner core 3;
(2) the second end of the heat exchange inner core 3 extends into the first end of the cylinder 1 and extends out of the second end of the cylinder 1, the first flower plate 4 and the first end cover 21 of the heat exchange inner core 3 are simultaneously and hermetically fixed to the first end of the cylinder 1, and the second flower plate 5 and the second end cover 22 of the heat exchange inner core 3 are simultaneously and hermetically fixed to the second end of the cylinder 1.
In this embodiment, baffle 6 includes first baffle plate 61 and second baffle plate 62, with hollow tube 30 passing through first locator hole 63. A first faceplate 4 and a first end cap 21, and a second faceplate 5 and a second end cap 22.
In the heat exchange inner core 3, the maximum value of the outer diameters of the second pattern plate 5 and the baffle plate 6 is smaller than the minimum value of the inner diameter of the cylinder 1, so that the heat exchange inner core 3 can conveniently extend into the cylinder 1. In the heat exchange core 3, the tube bundle 31 includes at least: a first region 311 located between the first spline 4 and the baffle plate 6 adjacent thereto, i.e., the first baffle plate 61; a second area 312 between the second baffle plate 5 and the baffle plate 6 adjacent thereto, i.e., the second baffle plate 62; hollow tube 30 in at least one of first region 311 and second region 312 extends obliquely. In the present embodiment, hollow tubes 30 in both first region 311 and second region 312 extend obliquely.
In the manufacturing method of the heat exchanger provided by the invention, firstly, the integrated heat exchange inner core 3 is provided, then the heat exchange inner core 3 extends into the cylinder 1, and the corresponding flower plates 4 and 5 and the end covers 21 and 22 are hermetically fixed to the corresponding ends of the cylinder 1. In the manufacturing method, the assembly operation of the components is convenient, the process is simple, and after the assembly is completed, the reliability of the heat exchanger is good, and the use by customers is convenient.
The foregoing detailed description is intended to illustrate and not limit the invention, which is intended to be within the spirit and scope of the appended claims, and any changes and modifications that fall within the true spirit and scope of the invention are intended to be covered by the following claims.
Claims (12)
1. A heat exchanger, comprising a heat exchanger having a heat exchanger,
the cylinder body is provided with two open ends and at least two joints on the side wall;
the first end cover and the second end cover are respectively fixed at two ends of the cylinder in a sealing way and are respectively provided with at least one joint;
the heat exchange inner core comprises a first pattern plate, a second pattern plate, at least one baffle plate and a tube bundle, wherein the baffle plate is positioned between the first pattern plate and the second pattern plate, the tube bundle is formed by a plurality of hollow tubes, two end parts of the tube bundle are respectively and hermetically fixed with the first pattern plate and the second pattern plate, the middle part of the tube bundle penetrates through the baffle plate, a first positioning hole penetrated by the hollow tubes is formed in the baffle plate, and a second positioning hole penetrated by the hollow tubes is formed in the first pattern plate and the second pattern plate;
the maximum value of the outer diameters of the second flower plate and the baffle plate is smaller than the minimum value of the inner diameter of the cylinder;
characterized in that the tube bundle comprises at least,
the first area is positioned between the first pattern plate and the baffle plate adjacent to the first pattern plate;
the second area is positioned between the second pattern plate and the baffle plate adjacent to the second pattern plate;
the hollow tube in at least one of the first region and the second region extends obliquely.
2. The heat exchanger according to claim 1, wherein the length of the middle portion of the tube bundle between the first and second flower plates is 1.05-1.2 times the length of the cylinder, and the angle of inclination of the hollow tubes in the first and/or second region is 2-8 °.
3. The heat exchanger as claimed in claim 1 or 2, wherein the first and second spline plates and the baffle plate have center axes coincident with each other, and the first positioning holes have a hole pitch larger or smaller than that of the second positioning holes.
4. A heat exchanger according to claim 1 or 2, wherein the baffles comprise at least a first baffle adjacent to the first flower and a second baffle adjacent to the second flower, the hollow tubes in both the first and second regions extending obliquely.
5. The heat exchanger of claim 4, wherein the first baffle plate and the second baffle plate have the same hole pitch of the first positioning holes, which is 1.3 to 1.6 times the hole pitch of the second positioning holes of the first and second flower plates.
6. The heat exchanger of claim 4, wherein the tube bundle further comprises an intermediate region between the first and second baffle plates, the first and second regions having a combined length of at least 60% of the total length of the tube bundle.
7. The heat exchanger according to claim 4, wherein in the first and second regions, the inclination angle of the hollow tube at the outer ring is larger than that of the hollow tube at the adjacent inner ring.
8. The heat exchanger of claim 4, wherein the first positioning holes of the first and second baffle plates have an inner diameter greater than an outer diameter of the hollow tubes; the outer ring hollow pipe sleeve of the pipe bundle is provided with a first protective sleeve and a second protective sleeve, the first protective sleeve extends from the tail end of the first pattern plate and penetrates through the first baffle plate, and the second protective sleeve extends from the tail end of the second pattern plate and penetrates through the second baffle plate.
9. The heat exchanger of claim 8, wherein the first and second protective sleeves form an interference fit with the first locator holes of the first and second baffle plates, respectively.
10. The heat exchanger of claim 6, wherein the central axes of the first and second baffle plates are not coincident; the hollow tube in the middle region extends obliquely or spirally.
11. The heat exchanger of claim 1, wherein the baffles are arcuate baffles, the circular cutout areas of which are provided with openings for fluid flow, and the openings of adjacent baffles are offset.
12. A method of manufacturing a heat exchanger according to any preceding claim, comprising the steps of:
a plurality of hollow pipes forming the pipe bundle penetrate through the first positioning holes of the baffle plate, and two end parts of the hollow pipes are respectively fixed to the second positioning holes of the first pattern plate and the second pattern plate in a sealing manner, so that a heat exchange inner core is manufactured;
the second end of the heat exchange inner core extends into the first end of the cylinder body and extends out of the second end of the cylinder body, the first flower plate and the first end cover of the heat exchange inner core are simultaneously and hermetically fixed to the first end of the cylinder body, and the second flower plate and the second end cover of the heat exchange inner core are simultaneously and hermetically fixed to the second end of the cylinder body;
in the heat exchange inner core, the maximum value of the outer diameters of the second flower plate and the baffle plate is smaller than the minimum value of the inner diameter of the cylinder;
the tube bundle comprising at least:
the first area is positioned between the first pattern plate and the baffle plate adjacent to the first pattern plate;
the second area is positioned between the second pattern plate and the baffle plate adjacent to the second pattern plate;
the hollow tube in at least one of the first region and the second region extends obliquely.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011377883.XA CN112539668A (en) | 2020-11-30 | 2020-11-30 | Heat exchanger and manufacturing method thereof |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011377883.XA CN112539668A (en) | 2020-11-30 | 2020-11-30 | Heat exchanger and manufacturing method thereof |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN112539668A true CN112539668A (en) | 2021-03-23 |
Family
ID=75016566
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202011377883.XA Pending CN112539668A (en) | 2020-11-30 | 2020-11-30 | Heat exchanger and manufacturing method thereof |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN112539668A (en) |
Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1155694A (en) * | 1965-02-13 | 1969-06-18 | Svenska Carbon Black Aktiebola | Improvements relating to Coolers for Mixtures of Gases and Solid Particles |
| CN103968688A (en) * | 2014-05-19 | 2014-08-06 | 南京工业大学 | Shell-and-tube heat exchanger and method for machining plate holes in shell-and-tube heat exchanger |
| CN104034188A (en) * | 2014-05-19 | 2014-09-10 | 陈勤 | Heat exchanger and heat exchange enhancement method |
| CN104501626A (en) * | 2014-12-26 | 2015-04-08 | 新奥科技发展有限公司 | Shell and tube heat exchanger |
| CN107270741A (en) * | 2017-08-06 | 2017-10-20 | 郑州大学 | Multiple flow reduced pipe wound tube heat exchanger |
| CN108225051A (en) * | 2018-01-15 | 2018-06-29 | 南京工业大学 | A kind of wrap-round tubular heat exchanger with endless tube air deflector and inside lining sleeve device |
| CN109520329A (en) * | 2017-09-19 | 2019-03-26 | 浙江盾安机械有限公司 | Heat exchanger |
| CN208920911U (en) * | 2018-08-14 | 2019-05-31 | 镇江旭世机械设备有限公司 | A kind of energy-efficient wound tube heat exchanger of poor methanol |
| CN211695982U (en) * | 2020-01-09 | 2020-10-16 | 贵州永红航空机械有限责任公司 | Small-sized tube type heat exchanger |
-
2020
- 2020-11-30 CN CN202011377883.XA patent/CN112539668A/en active Pending
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1155694A (en) * | 1965-02-13 | 1969-06-18 | Svenska Carbon Black Aktiebola | Improvements relating to Coolers for Mixtures of Gases and Solid Particles |
| CN103968688A (en) * | 2014-05-19 | 2014-08-06 | 南京工业大学 | Shell-and-tube heat exchanger and method for machining plate holes in shell-and-tube heat exchanger |
| CN104034188A (en) * | 2014-05-19 | 2014-09-10 | 陈勤 | Heat exchanger and heat exchange enhancement method |
| CN104501626A (en) * | 2014-12-26 | 2015-04-08 | 新奥科技发展有限公司 | Shell and tube heat exchanger |
| CN107270741A (en) * | 2017-08-06 | 2017-10-20 | 郑州大学 | Multiple flow reduced pipe wound tube heat exchanger |
| CN109520329A (en) * | 2017-09-19 | 2019-03-26 | 浙江盾安机械有限公司 | Heat exchanger |
| CN108225051A (en) * | 2018-01-15 | 2018-06-29 | 南京工业大学 | A kind of wrap-round tubular heat exchanger with endless tube air deflector and inside lining sleeve device |
| CN208920911U (en) * | 2018-08-14 | 2019-05-31 | 镇江旭世机械设备有限公司 | A kind of energy-efficient wound tube heat exchanger of poor methanol |
| CN211695982U (en) * | 2020-01-09 | 2020-10-16 | 贵州永红航空机械有限责任公司 | Small-sized tube type heat exchanger |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JP4401388B2 (en) | Heat exchanger | |
| US4286366A (en) | Method for the construction of a baffled heat exchanger | |
| US5642778A (en) | Rod baffle heat exchangers | |
| US20140262172A1 (en) | Tube bundle for shell-and-tube heat exchanger and a method of use | |
| US20140262171A1 (en) | Tube bundle for shell-and-tube heat exchanger and method of constructing same | |
| US5553665A (en) | Rod baffle heat exchangers utilizing dual support strip | |
| TWI776162B (en) | Helically baffled heat exchanger and method of assembling a heat exchanger | |
| CN112539668A (en) | Heat exchanger and manufacturing method thereof | |
| EP0002823B1 (en) | Tube bundle assembly and process for its construction | |
| JPH0275805A (en) | Axial symmetry aslant flow once-through boiler | |
| CN104567485B (en) | A kind of tubular heat exchanger | |
| US5411080A (en) | Baffle rings for retrofit of existing shell-and-tube heat exchangers | |
| CN212133386U (en) | Collecting and distributing type shell and tube heat exchanger | |
| CN104501626B (en) | A kind of tubular heat exchanger | |
| CN217818279U (en) | Tubular heat exchanger | |
| JPS5847676B2 (en) | Genshiroyounenriyoyouso | |
| CN215413300U (en) | Heat exchange equipment | |
| CN212988105U (en) | U-shaped guide plate heat exchanger | |
| CN220304333U (en) | Tube type graphite heat exchanger with high heat exchange efficiency | |
| CN108895864A (en) | Baffle plate component and shell-and-tube heat exchanger including this component | |
| CN108827042B (en) | Finned tube fluidized bed heat collector | |
| CN212620276U (en) | Heat exchange device | |
| JPH03207993A (en) | Multitube type heat exchanger | |
| JPS5937576Y2 (en) | Shell-and-tube heat exchanger | |
| JPS5952197A (en) | Heat exchanger |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| RJ01 | Rejection of invention patent application after publication |
Application publication date: 20210323 |
|
| RJ01 | Rejection of invention patent application after publication |