Patent Application
20110017436
1. Field of the Invention
The present invention relates to a plate type heat exchanger, and more particularly, to a plate type heat exchanger, capable of simply and rapidly fabricating a heat transfer assembly to improve workability by bending a pair of heat transfer plates, by welding a pair of heat transfer plates into a heat transfer cell, and by stacking and welding the heat transfer cells in multiple layers, preventing the flaw of welding caused by downward sagging of the heat transfer plate when the welding is performed, reducing the total number of constituent parts and thus production costs, and improving assemblability.
2. Description of the Related Art
In general, heat exchangers are fluid-to-fluid heat recovery apparatuses that recover heat included in gases discharged to the outside in industrial facilities such as air-conditioning facilities and then supply the recovered heat to productive facilities or interiors of buildings.
These heat exchangers are classified into a plate type heat exchanger, heat pipe type heat exchanger, disc type heat exchanger, etc. according to the type of a heat exchange module that is an internal core part.
In other words, the plate type heat exchanger is designed to perform heat transfer (heat exchange) between a high-temperature fluid and a low-temperature fluid without a physical contact.
Among these heat exchangers, the plate type heat exchanger recovers heat by arranging a plurality of heat transfer plates in parallel to each other at predetermined intervals, adopting a gap between every two neighboring heat transfer plates as a channel through which a fluid flows in one direction, and alternately supplying a high-temperature fluid and a low-temperature fluid to the respective channels so as to perform heat transfer (heat exchange) through the respective heat transfer plates.
One example of the plate type heat exchanger is disclosed in Korean Patent Publication No. 1993-7002655 (Sep. 9, 1993). According to the plate type heat exchanger of this document, a rigid parallelepiped shaped core is installed in a frame, and the core is formed of a plurality of thin parallel plates that define alternating passages for two different fluid flows. Each of the thin parallel plates is connected to its adjacent plate by parallel bars along side edges thereof, wherein each bar is of stronger construction than each plate. The frame includes a pair of spaced parallel plates and transverse structural connectors. Seal means are provided both between vertical corners and transverse corners of the core and the adjacent surfaces of the frame defined by the pair of plates and by the structural connectors.
However, in this related art, the plurality of thin parallel plates constituting the core are welded so as to define the fluid passages, i.e. gas flow passages, crossing each other by the horizontal bars. For this reason, when a worker individually welds the parallel plates, a high precision of welding is required, which increases a working burden of the worker. Further, when the parallel plates are disposed and welded in a horizontal direction, the parallel plates sagging downwards due to their weights cause the flaw of welding.
Further, the fluids flowing to the different passages of the core collide with the horizontal bar installed at the inlet of the passage, so that vortex and resistance of the fluid take place outside the inlet of the passage. For this reason, a contact area between the plate as the heat transfer member and the fluid is relatively reduced, and thus heat exchange efficiency is reduced.
Further, the total number of parts constituting the conventional plate type heat exchanger is much, and thus processes of welding or joining these parts are very complicated, which increases production costs and reduces workability.
Embodiments of the present invention provide a plate type heat exchanger capable of simply and rapidly fabricating a heat transfer assembly to improve workability by bending a pair of heat transfer plates, by welding the pair of heat transfer plates into a heat transfer cell, and by stacking and welding the heat transfer cells in multiple layers, of preventing the flaw of welding caused by downward sagging of the heat transfer plate when the welding is performed, minimizing turbulence at an inlet into which a fluid flows to improve heat exchange efficiency, reducing the total number of constituent parts and thus production costs, and improving assemblability.
According to an aspect of the present invention, the heat exchanger includes a heat transfer assembly including a plurality of heat transfer cells stacked in multiple layers, each of the heat transfer cells including a pair of heat transfer plates, wherein each of the heat transfer plates has a pair of first flanges bent from a heat transfer area shaped of a quadrilateral panel in one direction and a pair of second flanges bent from the heat transfer area in a direction opposite the bending direction of the first flanges; wherein each of the heat transfer cells has weld lines formed along one of the first and second flanges of the heat transfer plates disposed so as to be opposite to each other in a minor image, an internal passage between the weld lines, and external recesses outside the heat transfer areas so as to intersect with the internal passage at a right angle; wherein the heat transfer assembly has first fluid passages, each of which is formed by the internal passage, and second fluid passages between the heat transfer cells to intersect with the first fluid passage at a right angle so as to exchange heat with the first fluid passages; a framework having a plurality of support beams connected between a pair of sealing panels facing opposite outer faces of the heat transfer assembly; and an elastic support having first elastic members installed between the sealing panels and the heat transfer assembly and second elastic members installed between the support beams and the heat transfer assembly, absorbing thermal expansion of the heat transfer assembly, and preventing fluids from leaking out.
In an exemplary embodiment of the present invention, each of the heat transfer cells may have the weld lines along the first flanges of the heat transfer plates that are opposite to and in contact with each other in the minor image, and the internal passage formed between the heat transfer plates that are opposite to each other so as to be parallel to the weld lines and having an inlet and an outlet defined by the second flanges that are opposite to and spaced apart from each other.
In another exemplary embodiment of the present invention, each of the heat transfer cells may have first slopes that are inclined toward the weld lines among the first flanges, the first or second heat transfer area, and the second flanges at a predetermined angle, and second slopes that are inclined toward the inlet and the outlet of the internal passage between the second flanges and the first or second heat transfer area at a predetermined angle so as to define the external recesses.
In another exemplary embodiment of the present invention, the heat transfer assembly may be configured so that the second flanges of the neighboring heat transfer cells which intersect with the internal passages at the right angle are in surface contact with each other, and that the first flanges of the neighboring heat transfer cells are spaced apart from each other, and includes end plates contacting the second flanges and the weld lines at opposite left-hand and right-hand ends of the first flanges.
In another exemplary embodiment of the present invention, each of the heat transfer cells may have the weld lines along the second flanges of the heat transfer plates that are opposite to and in contact with each other in the mirror image, and the internal passage formed between the heat transfer plates that are opposite to each other so as to be parallel to the weld lines and having an inlet and an outlet defined by the first flanges that are opposite to and spaced apart from each other.
In another exemplary embodiment of the present invention, each of the heat transfer cells may have first slopes that are inclined toward the inlet and the outlet of the internal passage among the first flanges, the first or second heat transfer area, and the second flanges at a predetermined angle at a predetermined angle so as to define the external recesses, second slopes that are inclined toward the weld lines between the second flanges and the heat transfer area at a predetermined angle, and end plates contacting the second flanges and the weld lines at opposite left-hand and right-hand ends of the first flanges.
In another exemplary embodiment of the present invention, the heat transfer assembly may be configured so that the second flanges of the neighboring heat transfer cells which intersect with the internal passages at the right angle are in surface contact with each other, and that the first flanges of the neighboring heat transfer cells are spaced apart from each other, and is sealed at opposite left-hand and right-hand ends of the second flanges by the end plates.
In another exemplary embodiment of the present invention, one of the heat transfer plates may include a spacer set, a height of which is equal to or less than an interval between the neighboring heat transfer areas.
In another exemplary embodiment of the present invention, the spacer set may include a plurality of stud spacers, a lower end of each of which is welded to one of the heat transfer areas so as to intersect with one of the heat transfer areas at a right angle.
In another exemplary embodiment of the present invention, the spacer set may include a plurality of strip spacers, a lower end of each of which is welded to one of the heat transfer areas so as to intersect with one of the heat transfer areas at a right angle, and each of which extends in a flow direction of the fluid at a predetermined length.
In another exemplary embodiment of the present invention, the spacer set may include a plurality of stud spacers, a lower end of each of which is welded to one of the heat transfer area so as to intersect with one of the heat transfer areas at a right angle, and a plurality of strip spacers, a lower end of each of which is welded to one of the heat transfer areas so as to intersect with one of the heat transfer areas at a right angle and each of which extends in a flow direction of the fluid at a predetermined length.
In another exemplary embodiment of the present invention, the sealing panels may include sealing plates facing the outer faces of the heat transfer assembly, reinforcing plates installed on outer surfaces of the sealing plates in a lattice shape, and fastening holes formed in corners of the sealing plates and fastened to ends of the support beams by fastening members.
In another exemplary embodiment of the present invention, each of the sealing plates may include a glass coating layer on an inner surface thereof.
In another exemplary embodiment of the present invention, the sealing panels and the support beams may be coupled with a plurality of joint quadrilateral frames so as to be disposed at inlets and outlets of the first and second fluid passages.
In another exemplary embodiment of the present invention, the first elastic members may include plates having a predetermined length, bonded and fixed to inner surfaces of the sealing panels in contact with leading ends thereof and to the outer face of the heat transfer assembly in contact with trailing ends thereof, and having a contractile section having a curved cross section between the leading and trailing ends thereof.
In another exemplary embodiment of the present invention, each of the second elastic members may be an elastic plate, which has a predetermined length, which is bonded and fixed to a first lateral face of each of the support beams in contact with a leading end thereof and to the outer face of the heat transfer assembly in contact with a trailing end thereof, and which has a corrugated section between the leading and trailing ends thereof.
In another exemplary embodiment of the present invention, the elastic support may further include stoppers, each of which has a predetermined length, is fixed to a second lateral face of each of the support beams, which is perpendicular to the first lateral face of each of the support beams on which the second elastic members are installed, and is opposite to an outer edge of the heat transfer assembly.
In another exemplary embodiment of the present invention, the heat transfer assembly may include planar cover members spaced apart from and parallel to the heat transfer plates at a predetermined interval, so as to define another fluid passage between the heat transfer plates, through which, of the first and second fluids having different temperatures, one having a relatively low temperature flows.
In another exemplary embodiment of the present invention, the cover members may be installed on corners of the heat transfer plate where the inlet of the fluid passage through which the fluid having the relatively low temperature flows encounters with the outlet of the fluid passage through which the fluid having a relatively high temperature flows in a triangular shape.
According to the exemplary embodiments of the present invention, the heat transfer cell is fabricated by welding a pair of heat transfer plates disposed so as to be opposite to each other in a mirror image to thereby form weld lines along one of first and second flanges of the heat transfer plates disposed so as to be opposite to each other in a mirror image, an internal passage between the weld lines, and external recesses outside the heat transfer areas so as to intersect with the internal passage at a right angle. The heat transfer assembly is fabricated by stacking a plurality of heat transfer cells in multiple layers to thereby form first fluid passages, each of which serves as the internal passage, and second fluid passages between the heat transfer cells so as to intersect with the first fluid passages at a right angle and to exchange heat with the first fluid passages. The elastic support is installed between the sealing panels facing opposite outer faces of the heat transfer assembly and the heat transfer assembly and between the support beams provided between the sealing panels and the heat transfer assembly, thereby absorbing thermal expansion of the heat transfer assembly and preventing fluids from leaking out. Thereby, the heat exchanger can simply and rapidly fabricated, prevent the flaw of welding when welding is performed, reducing a burden of the welding to improve workability, reducing the total number of constituent parts and thus production costs, and improving assemblability.
Further, the heat exchanger can minimize turbulence and resistance of the fluid occurring at the inlets of the fluid passages of the heat transfer assembly, and thereby stably maintain contact between the fluid and the heat transfer plate as the heat transfer member to improve heat exchange efficiency.
The above and other aspects, features and other advantages of the present invention will be more clearly understood from the following detailed description taken in conjunction with the accompanying drawings, in which:
Exemplary embodiments of the present invention will now be described in greater detail with reference to the accompanying drawings.
As illustrated in
In
Here, one of the first and second fluid includes air having an atmospheric temperature, and the other fluid includes waste gas, exhaust gas, or the like that is discharged from any industrial field and has a relatively higher temperature.
As illustrated in
In detail, the heat transfer plate 110 or 120 of the heat transfer cell 130 includes a heat transfer area 111 or 121 shaped of a substantially quadrilateral panel, a pair of first flanges 112 and 113, or 122 and 123 bent from opposite upper and lower edges of the heat transfer area 111 or 121 in one direction when viewed from
Here, the first flanges 112 and 113, and 122 and 123 and the second flanges 114 and 115, and 124 and 125 are bent from the heat transfer areas 111 and 121 perpendicular to each other.
First slopes 116 and 117, or 126 and 127 are inclined toward the weld lines S1 among the first flanges 112 and 113, or 122 and 123, the heat transfer area 111 or 121, and the second flanges 114 and 115, or 124 and 125 at a predetermined angle, and thus smoothly converts a flow of the fluid so as to inhibit the fluid, which flows in a direction perpendicular to the weld lines S1, from generating vortex at an inlet of each external passage.
Further, second slopes 118 and 119, or 128 and 129 are inclined toward the inlet 131 and the outlet 132 of the internal passage P1 between the second flanges 114 and 115, or 124 and 125 and the heat transfer area 111 or 121 at a predetermined angle so as to define the external recesses 101 and 102 between the second flanges 114 and 115, or 124 and 125 with a predetermined width.
At this time, the weld lines Si are formed by seam welding faying surfaces of the first flanges 112 and 122, and 133 and 123 of the heat transfer plates 110 and 120 facing each other in a mirror image, and the inlet 131 and the outlet 132 of the internal passage P1 are formed by the second flanges 114 and 124, and 115 and 125 which are opposite to and spaced apart from each other.
First, as illustrated in
Subsequently, as illustrated in
In this state, the first flanges 112 and 122, and 133 and 123 come into surface contact with each other, and then are welded along the outer ends thereof. As a result, as illustrated in
As illustrated in
In detail, the heat transfer plate 110a or 120a of the heat transfer cell 130a includes a heat transfer area 111a or 121a shaped of a quadrilateral panel, a pair of first flanges 112a and 113a, or 122a and 123a bent from opposite upper and lower edges of the heat transfer area 111a or 121a in one direction, and a pair of second flanges 114a and 115a, or 124a and 125a bent from opposite left-hand and right-hand edges of the heat transfer area 111a or 121a in the direction that is perpendicular and opposite to the bending direction of the first flanges 112a and 113a, or 122a and 123a. The heat transfer cell 130a includes weld lines S1 along the first flanges 112a and 122a, and 113a and 123a that are opposite to and in contact with each other on the left-hand and right-hand sides of
Here, the first flanges 112a and 113a, and 122a and 123a and the second flanges 114a and 115a, and 124a and 125a are bent from the heat transfer areas 111a and 121a in the direction that is perpendicular and opposite to each other.
First slopes 116a and 117a, or 126a and 127a are inclined toward an inlet and an outlet of the internal passage P2 among the first flanges 112a and 113a, or 122a and 123a, the heat transfer area 111a or 121a, and the second flanges 114a and 115a, or 124a and 125a at a predetermined angle so as to form external recesses 101a and 102a between the first flanges 112a and 113a, and 122a and 123a with a predetermined width.
Further, second slopes 118a and 119a, or 128a and 129a are inclined toward the weld lines S2 between the second flanges 114a and 115a, or 124a and 125a and the heat transfer area 111a or 121a at a predetermined angle.
At this time, the weld lines S2 are formed by seam welding faying surfaces of the first flanges 114a and 124a, and 115a and 125a of the heat transfer plates 110a and 120a facing each other in a mirror image, and the inlet and the outlet of the internal passage P2 are formed by the first flanges 112a and 122a, or 113a and 123a which are opposite to and spaced apart from each other.
First, as illustrated in
Subsequently, as illustrated in
In this state, the second flanges 114a and 124a, and 115a and 125a come into surface contact with each other, and then are welded along the outer ends thereof. As a result, as illustrated in
As illustrated in
This heat transfer assembly 100 is designed to form a passage having a predetermined size such that a fluid can freely flow between two neighboring ones of the heat transfer cells 130, thereby forming a first fluid passage F1 through which a first fluid flows one side to the other side.
Here, a second fluid passage F2 intersects with the first fluid passage F1, which is formed as an internal passage P1 in each heat transfer cell 130, at a right angle. Thus, a second fluid flowing through the second fluid passage F2 flows through the heat transfer assembly 100 without being mixed with the first fluid, so that the first and second fluids having different temperatures can exchange heat with each other.
In detail, when the heat transfer cells 130, each of which has the weld lines Si of the first flanges 112 and 122, and 113 and 123, are stacked in a vertical direction as in
Thus, the first flanges 112 and 122, and 113 and 123 are provided with end plates 103 and 104 at left-hand and right-hand ends thereof which connect the first flanges 112 and 122, and 113 and 123 of the neighboring heat transfer cell 130 and are in contact with the weld lines S1. Thereby, an inlet and an outlet of the second fluid passage F2 are defined between the heat transfer cell 130 and its neighboring heat transfer cell 130.
As illustrated in
This heat transfer assembly 100a is designed to form a passage having a predetermined size such that a fluid can freely flow between two neighboring ones of the heat transfer cells 130a, thereby forming a first fluid passage F1 through which a first fluid flows one side to the other side.
Here, the first fluid passage F1 intersects with a second fluid passage F2, which is formed as an internal passage P2 in each heat transfer cell 130a, at a right angle. Thus, the first fluid flowing through the first fluid passage F1 flows through the heat transfer assembly 100a without being mixed with a second fluid, so that the first and second fluids having different temperatures can exchange heat with each other.
In detail, when the heat transfer cells 130a, each of which has the weld lines S2 of the second flanges 114a and 124a, and 115a and 125a are stacked in a vertical direction as in
As illustrated in
The heat transfer plates 110 and 120, or 110a and 120a disposed in a horizontal direction are subjected to sagging at the central regions thereof due to their own weights in the process of fabricating the heat transfer assembly 100 or 100a by stacking the heat transfer cells 130 or 130a in a vertical direction and by welding the flanges of the heat transfer cells 130 or 130a which are in contact with each other. At this time, the spacer set 160 is contacted with and supported on heat transfer area 121 or 111, or 121a or 111a of the neighboring heat transfer plates 120 or 110, or 120a or 110a at an upper end thereof, thereby preventing excessive sagging of the heat transfer plate and maintaining the interval between the heat transfer areas of the heat transfer plates 110 and 120, or 110a and 120a as a design value.
In addition, the spacer set 160 increases an internal surface area of the heat transfer area, so that it can increase heat exchange efficiency between first and second fluids.
Accordingly, the process of welding the flanges of the heat transfer cells 130 or 130a staked in a vertical direction in order to assemble the heat transfer assembly 100 or 100a can be more precisely performed without a flaw.
As illustrated in
Here, the support stud 162 is shown to have, but not limited to, a cylindrical shape. Thus, the support stud 162 may have an oval cross section or an angled cross section.
As illustrated in
Finally, as illustrated in
Here, the stud spacers 163, which are selectively installed on either an upper surface, i.e. a front surface, or a lower surface, i.e. a rear surface, of the heat transfer area 111 or 111a, or 121 or 121a when viewed from the figure, are arranged to have, but not limited to, a matrix array in order to constantly maintain spacing between the neighboring stud spacers.
Specifically, in the process of fabricating the heat transfer assembly 100 or 100a, the heat transfer cells 130 made up of the heat transfer plates 110 and 120, or 110a and 120a are horizontally disposed and welded to each other. @ At this time, in consideration of the downward sagging that occurs on a central region of each heat transfer area, the interval between the neighboring stud spacers 163 on the central region of each heat transfer area may be set to be narrower than that on an edge region of each heat transfer area.
Further, the interval between the neighboring strip spacers 164 is, in one embodiment, set in such a manner that the central region of each heat transfer area is narrower than the edge region of each heat transfer area.
As illustrated in
As illustrated in
In one embodiment, the sealing plates 141a and 142a facing the heat transfer assembly 100 or 100a are provided with glass coating layers 141d and 142d on inner surfaces thereof which have a predetermined thickness so as to inhibit thermal deformation and corrosion to the maximum extent.
The support beams 143, 144, 145 and 146 are support members that connect and support the sealing panels 141 and 142 disposed so as to face the heat transfer assembly 100 or 100a with the heat transfer assembly 100 or 100a in between and that have a predetermined length.
As illustrated in
Each of the support beams 143, 144, 145 and 146 is provided with reinforcing ribs 148 at regular intervals in a lengthwise direction.
Meanwhile, the sealing panels 141 and 142 and the support beams 143, 144, 145 and 146 are coupled with joint quadrilateral frames 149 having a plurality of fastening holes 149a so as to be disposed at the inlets and outlets of the first and second fluid passages F1 and F2.
A plurality of heat exchangers 200 can be continuously connected to each other in a direction of the first or second fluid passage by the joint quadrilateral frames 149.
As illustrated in
As illustrated in
Here, the trailing ends 151c of the first elastic members 151 are contacted with and welded to the flanges of the outermost heat transfer cells 130 or 130a of the heat transfer assembly 100 or 100a.
As illustrated in
Meanwhile, the heat transfer assembly 100 or 100a may be provided with planar cover members 131, each of which forms a separate fluid passage between the neighboring heat transfer plates so as to prevent moisture from being generated by a temperature difference between the heat transfer plates 110 and 120, or 110a and 120a when the first and second fluids having different temperatures exchange heat with each other.
Each cover member 131 is installed parallel to the heat transfer plates, which define the passage through which the fluid having a relatively low temperature flows, by means of a plurality of spacing pins 131a thereof.
Further, the cover members 131 are installed on the corners of the heat transfer plates at which the inlet of the fluid passage F1 through which a room-temperature fluid such as air in the atmosphere flows encounters with the outlet of the fluid passage F2 through which the fluid having a relatively high temperature flows.
While the present invention has been shown and described in connection with the exemplary embodiments, it will be apparent to those skilled in the art that modifications and variations can be made without departing from the spirit and scope of the invention as defined by the appended claims.
