CN213515186U - Heat exchanger - Google Patents
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- CN213515186U CN213515186U CN202022008301.2U CN202022008301U CN213515186U CN 213515186 U CN213515186 U CN 213515186U CN 202022008301 U CN202022008301 U CN 202022008301U CN 213515186 U CN213515186 U CN 213515186U
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Abstract
The application discloses heat exchanger includes: the heat exchange tube is provided with a non-circular cross section, and comprises a spiral groove which is inwards concave from the outer surface of the tube wall and has a uniform pitch on the tube wall in the middle of two ends of the hollow tube body along the longitudinal direction, so as to generate disturbance on fluid media flowing through the heat exchange tube in use; the side surfaces of the heat exchange tubes in the height direction are arranged towards the incident flow direction of the second fluid medium, and any two adjacent heat exchange tubes are arranged in a mirror symmetry mode by taking the longitudinal direction as a symmetry axis. According to the heat exchanger of this application through the cross sectional shape who changes current heat exchange tube, reinforcing flow velocity and torrent degree in the heat exchange tube, reduce the outer flow resistance of pipe, further improve the heat transfer performance of heat exchange tube to improve the heat exchange efficiency of heat exchanger.
Description
Technical Field
The utility model relates to an industry heat exchanger fields such as oil refining, chemical industry, specifically, relate to a heat exchanger.
Background
In the field of heat exchangers, the traditional round tube type heat exchanger has the advantages of firm structure, large operation elasticity and wide application, and plays an important role in the field of heat exchangers at present. However, the traditional round tube heat exchanger has significant defects in the aspects of heat exchange efficiency, equipment structure compactness, metal consumption and the like. A non-circular cross section heat transfer tube heat exchanger that appears in recent years, for example plate tube heat exchanger has heat exchange efficiency height, compact structure, the convenient advantage of maintenance for traditional tube heat exchanger, can guarantee moreover that the medium is zero to leak.
However, the heat transfer is enhanced only by changing the arrangement of the heat exchange tubes with the non-circular cross sections of the heat exchanger and changing the longitudinal shape of the heat exchange tubes with the non-circular cross sections, so that the heat exchange efficiency of the heat exchanger is improved, and the improvement of the efficiency of the heat exchanger is greatly limited. Therefore, the development of the heat exchanger with high heat exchange efficiency has important significance.
SUMMERY OF THE UTILITY MODEL
It is an object of the present invention to provide a heat exchanger to at least partially alleviate the above problems.
According to the utility model discloses a heat exchanger, include:
a housing comprising a housing inlet and a housing outlet; and
a heat exchange tube disposed within the housing, the heat exchange tube including a hollow tube body extending in a longitudinal direction and an inlet and an outlet at both ends of the hollow tube body, the inlet and the outlet being open on the housing, the hollow tube body of the heat exchange tube having a non-circular cross section at least at a portion intermediate the both ends of the hollow tube body, the non-circular cross section having a width greater than a height, at least one end portion of the non-circular cross section in the width direction being shaped as a smooth curve and being smoothly connected to a side in the width direction, and a spiral groove having a uniform pitch inwardly recessed from an outer surface of the tube wall on the tube wall intermediate the both ends of the hollow tube body in the longitudinal direction to generate disturbance to a fluid medium inside and outside the tube flowing therethrough in use;
wherein the inlet, the outlet and the hollow tube body of the heat exchange tube form a first fluid medium channel, the shell inlet, the shell outlet and the gap in the shell form a second fluid medium channel, the first fluid medium channel and the second fluid medium channel are isolated in a sealing way and are arranged in a way that the first fluid medium in the first fluid medium channel and the second fluid medium in the second fluid medium channel can exchange heat through the tube wall of the heat exchange tube,
the side surfaces of the heat exchange tubes in the height direction are arranged towards the incident flow direction of the second fluid medium, and any two adjacent heat exchange tubes are arranged in a mirror symmetry mode by taking the longitudinal direction as a symmetry axis.
Preferably, at least one end of the heat exchange tube is shaped as an elliptical end or a circular arc end, and the width-to-height ratio W/H of the non-circular cross section is not less than 10.
Preferably, at least one of the width-direction side edges of the non-circular cross section includes a straight line portion or a curved line portion, and the side edge and the end portion in the width direction constitute a shape of the non-circular cross section.
Preferably, the width-direction side edges of the non-circular cross section are parallel straight line segments or mirror-symmetrical curved line segments.
Preferably, the shape of the non-circular cross-section is a streamlined shape.
Preferably, the width-direction side edges of the non-circular cross section are non-parallel straight line segments.
Preferably, the curved section is a wavy curved section.
Preferably, the portion of each of the grooves that spirals on the wide side of the wall of the hollow tubular body that includes the width is a straight groove or a curved groove with a uniform groove width, or a curved groove with a groove width that varies in the direction of extension of the groove.
Preferably, both side walls of the curved groove along the extension direction of the groove, in which the groove width varies in the extension direction of the groove, include a curved wall and a straight wall.
Preferably, the portion of the groove on the wide side of the heat exchange tube forms an angle with the longitudinal axis, the angle is in the range of 0 to 90 degrees, and the pitch S of the helix is greater than or equal to the width V of the groove.
Preferably, the heat exchange tubes are arranged in an array in the housing, the array comprising M rows and Y columns, M.gtoreq.1, Y.gtoreq.2, the wide side of the heat exchange tubes comprising the width is along the flow direction of the second fluid medium, the narrow side of the heat exchange tubes comprising the height near the second inlet is arranged to face the inflow direction of the second fluid medium, and the end of the non-circular cross-section in the width direction end which is more favorable for reducing the fluid resistance is selected to face the inflow direction of the second fluid medium.
Preferably, the shell inlet and the shell outlet are arranged opposite to each other, and the flow direction of the second medium is vertical to the flow direction of the first medium; or the shell inlet and the shell outlet are arranged in a staggered mode, and the flowing direction of the second medium is at least partially parallel to and opposite to the flowing direction of the first medium.
Preferably, the heat exchange tube is provided with support members spaced apart in a longitudinal direction thereof for supporting the heat exchange tube to prevent the heat exchange tube from being thermally deformed or shaken by an air flow, the support members being sized and positioned so as not to obstruct the flow of the fluid.
Preferably, the shell comprises two opposite tube plates, mounting holes corresponding to the cross section of the end of the heat exchange tube are formed in the tube plates, and two ends of the heat exchange tube are respectively connected with the mounting holes of the tube plates in a sealing mode.
Preferably, the heat exchanger further comprises an expansion joint arranged around the outer side of at least one tube plate, and the tube plate is hermetically connected with the shell through the expansion joint so as to adapt to thermal expansion and contraction of the heat exchange tube.
To sum up, according to the utility model discloses a heat exchange tube and heat exchanger are through the cross sectional shape who changes current heat exchange tube, and the velocity of flow and torrent degree, reduction outside of tubes flow resistance in the reinforcing heat exchange tube further improve the heat transfer performance of heat exchange tube to improve the heat exchange tube and use the heat exchange efficiency of its heat exchanger.
Drawings
Other features, objects and advantages of the invention will become more apparent upon reading of the detailed description of non-limiting embodiments made with reference to the following drawings:
figure 1 is a cross-sectional view of one end of a heat exchange tube according to a first embodiment of the present invention;
figure 2 is a cross-sectional view of one end of a heat exchange tube according to a second embodiment of the present invention;
figure 3 is a cross-sectional view of one end of a heat exchange tube according to a third embodiment of the present invention;
figure 4 is a schematic view of a heat exchange tube according to a fourth embodiment of the present invention;
figure 5 is a schematic view of a heat exchange tube according to a fifth embodiment of the present invention;
fig. 6 is a schematic front view of a heat exchanger according to a first embodiment of the present invention;
fig. 7 is a schematic front view of a heat exchanger according to a second embodiment of the present invention;
FIG. 8 is a top cross-sectional view of the heat exchanger shown in FIG. 7, showing a support structural detail;
FIG. 9 is a top cross-sectional view of the heat exchanger shown in FIG. 7 showing additional support structural details.
Detailed Description
The present application will be described in further detail with reference to the following drawings and examples. It is to be understood that the specific embodiments described herein are merely illustrative of the relevant invention and are not limiting of the invention. It should be noted that, for convenience of description, only the portions related to the present invention are shown in the drawings.
In the present invention, the terms "upper", "lower", "left", "right", "front", "rear", "top", "bottom", "inner", "outer", "middle", "vertical", "horizontal", "lateral", "longitudinal", "axial", and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings. These terms are used primarily to better describe the invention and its embodiments, and are not intended to limit the indicated devices, elements or components to a particular orientation or to be constructed and operated in a particular orientation.
The utility model discloses a heat exchanger is often applied to the heat exchange tube, when specifically using, flows through a fluid heat transfer medium in the heat exchange tube, flows through another fluid heat transfer medium outside the heat exchange tube, and two kinds of fluid heat transfer media realize the heat exchange through the heat exchange effect of the pipe wall of heat exchange tube. The utility model discloses an idea is, through the cross sectional shape who changes current heat exchange tube, flow velocity and torrent degree in the reinforcing heat exchange tube, reduction outside of tubes flow resistance further improve the heat transfer performance of heat exchange tube to improve the heat exchange tube and use the heat exchange efficiency of its heat exchanger.
The utility model provides a heat exchange tube includes the cavity body that extends along longitudinal direction and the import and the export at cavity body both ends, and the inside of cavity body is used for through first fluid medium, and the outside of cavity body is used for through second fluid medium, and the heat exchange tube is including setting up import and the export at cavity body both ends. The utility model discloses a hollow pipe body of heat exchange tube has non-circular cross section at least in the middle part in both ends, and this non-circular cross section's width is greater than the height, and at least one tip along width direction takes shape to smooth curve to with width direction's side smooth connection. The ends of the hollow tube may sometimes take a circular cross-section for ease of installation.
At least one end part of the non-circular cross section of the heat exchange tube along the width direction is formed into a smooth curve and is smoothly connected with the side edge of the width direction, and the flow resistance of the heat exchange tube can be at least reduced by the flow-facing arrangement. If both ends of the non-circular cross section of the heat exchange tube are smoothly connected with the side edges in the width direction and one end part is arranged in an upstream manner, the upstream resistance of the upstream end part of the heat exchange tube can be reduced, and the wake vortex at the back of the end part opposite to the upstream end part can be reduced, so that the abrasion of the heat exchange tube is reduced, the heat transfer is enhanced, and the heat exchange efficiency of the heat exchange tube is improved.
For convenience of description, an extending direction of a width of the non-circular cross section is referred to as a width direction, and an extending direction of a height of the non-circular cross section is referred to as a height direction. The side of the heat exchange tube defined by the width and length is called a wide side, and the side defined by the height and length is called a narrow side.
Preferably, the aspect ratio W/H of the non-circular cross section of the heat exchange tube of the present invention is not less than 10, where the aspect ratio refers to the ratio of the extension distance of the non-circular cross section in the width direction to the extension distance of the non-circular cross section in the height direction. The wide sides of the non-circular cross-section of the heat exchange tubes resemble the plates in plate heat exchangers and have a high heat transfer performance close to that of plate heat exchangers. Compared with the circular tube with the same circumference, although the volume flow rate in the tube is the same as Re, the average flow speed in the tube is improved due to the reduction of the cross section and the equivalent diameter, the turbulence degree of the fluid is increased, and the scouring effect on the fluid boundary layer is enhanced due to the improvement of the flow speed, so that the heat transfer is enhanced. The larger the W/H, the closer the cross section is to the shape of a flow channel of the plate heat exchanger, the more the first fluid medium in the heat exchange tube with the non-circular cross section is similar to the laminar flow of the plate heat exchanger, the smaller the cross section area is, the larger the internal flow velocity under the same volume flow is, and the more obvious the strengthening effect on heat transfer is.
A specific embodiment of the non-circular cross-section in the present invention is described below with simultaneous reference to fig. 1 to 3.
The non-circular cross-section 103 shown in fig. 1 is configured such that the width-direction side edges 105 are mutually parallel straight line segments, the two end portions 104 are in an elliptical or streamlined shape, and the end portions 104 are smoothly connected with the parallel side edges 105. The non-circular cross section has a regular shape and plane symmetry, is simple in structure and convenient to manufacture, and the two streamlined ends are beneficial to reducing flow resistance.
Both ends 104 of the non-circular cross section shown in fig. 1 are shaped as smooth curves, or only one of the ends may be shaped as a smooth curve, and both sides in fig. 1 may be shaped as parallel straight segments, or only one side may be a straight segment and the other side may be a curved segment, for example, the whole may be shaped as a streamline shape of a circular arc curve of a straight side with a small end and a large end. Such variations are also within the scope of the present invention.
Fig. 2 is a cross-sectional view of one end of a heat exchange tube according to a second embodiment of the present invention, and as can be seen from fig. 2, both end portions 204 are formed in an oval shape or streamline shape, and both side edges 205 are provided as straight line segments but are not parallel to each other. The non-circular cross section 203 is of a streamline shape similar to a drop shape as a whole, has a regular shape and plane symmetry, is simple in structure and convenient to manufacture, and the streamline shape is beneficial to reducing flow resistance. A straight section side of the non-circular cross-section of fig. 2 may also be curved, and such variations are within the scope of the present invention.
Fig. 3 is a cross-sectional view of one end of a heat exchange tube according to a third embodiment of the present invention, and it can be seen from fig. 3 that two end portions 304 are shaped like a circle, two sides 305 are provided as mirror-symmetrical curve segments, and the curve segments shown in fig. 3 are wavy curve segments, which may also be curve segments presenting an approximate sine function or cosine function. Further arrangements of the ends and sides will not be discussed further herein due to space limitations. Preferably, at least one end is shaped as a circular arc end to reduce flow resistance.
To sum up, the utility model provides a heat exchange tube's non-circular cross section's mode of setting is not limited to the shape that above-mentioned figure 1 to 3 show, can also be other shapes such as spindle shape, snakelike, can be greater than the height through non-circular cross section's width, and along at least one tip of width direction shaping for smooth curve and with two characteristics of width direction's side smooth connection realize strengthening heat transfer and reduce the purpose of flow resistance can.
The above is the description that goes on heat exchange tube cavity body non-circular cross section's structure, because at the heat transfer in-process, not only the cavity body non-circular cross section's of heat exchange tube structure is influential to the heat exchange efficiency, and the external structure of cavity body also has the effect of making up the light and heavy to the heat exchange efficiency, and is following to the utility model discloses a the external structure of the cavity body of heat exchange tube describes and explains.
In the heat exchange process, the second fluid medium flowing outside the heat exchange tube and the first fluid medium flowing inside the heat exchange tube exchange heat through the tube wall of the heat exchange tube, the tube wall of the heat exchange tube is generally smooth surface, so that the thermal resistance generated by the surface boundary layer of the heat exchange element cannot be overcome, and the surface strengthening is difficult to perform so as to further improve the heat exchange performance. In order to solve this problem to a certain extent at least, according to the utility model discloses, provide and set up the vortex structure on the pipe wall of heat exchange tube, come the intraductal outer fluid production disturbance of geminate transistors, play the effect of destroying fluid boundary layer, further strengthen the heat transfer effect from this. This is described in further detail below by means of the embodiment shown in fig. 4 and 5.
Fig. 4 is a schematic view of a heat exchange tube according to a fourth embodiment of the present invention. The heat exchange tube is generally designated 401. In fig. 4, the hollow tube body 402 of the heat exchange tube 401 is shown to include a concave groove 407 recessed inward from the outer surface of the tube wall 406 on the tube wall 406 midway between both ends in the longitudinal direction. The concave groove 407 is a spiral groove having a uniform pitch around the outer surface of the tube wall 406 of the hollow tube body 402, and a portion of each spiral of the spiral groove on the wide side including the width of the tube wall 406 of the hollow tube body 402 is a straight line groove having a uniform groove width. The spiral pitch S is more than or equal to the width V of the groove of the non-circular section high-efficiency heat exchange tube, the width V of the groove section of the groove is more than or equal to 0.5mm and less than or equal to 25mm, the height h of the groove 407 is more than or equal to 0.2mm and less than or equal to 10mm, the projection of the groove 407 on the surface where the long edge of the section of the heat exchange tube is positioned is a straight line, and the included angle between the straight line and the axis of the heat exchange tube.
The purpose of the concave grooves 407 shown in fig. 4 is to enable the concave grooves 407 to generate disturbance to the second fluid medium when the second fluid medium arranged outside the heat exchange tube flows outside the heat exchange tube, the concave grooves 407 limit the flow of the second fluid medium at the outer surface near the tube wall 406, the concave grooves 407 simultaneously guide the fluid to swirl along the grooves, so that the thickness of the boundary layer is reduced, axial vortices are generated by the fluid at the concave grooves 407, and the disturbance of the fluid in the boundary layer and the separation of the boundary layer are caused, thereby accelerating the heat transfer of the first fluid medium from the outer surface of the tube wall 406 to the second fluid medium. Meanwhile, the arrangement of the grooves can increase the heat exchange area to a certain extent. Thereby further improving the heat exchange efficiency of the heat exchange tube.
When the section length-width ratio of the non-circular cross section heat exchange tube is large, the strength and the pressure bearing capacity of the non-circular cross section heat exchange tube are greatly reduced, and the arranged grooves 407 are also equivalent to ribs, so that the strength and the pressure bearing capacity of the non-circular cross section heat exchange tube can be greatly improved.
Fig. 5 is a schematic view of a heat exchange tube according to a fifth embodiment of the present invention. A heat exchange tube is generally indicated at 501. Like parts of the fifth embodiment shown in fig. 5 and the fourth embodiment shown in fig. 4 bear like reference numerals, with only the first digit on the left being incremented by 1 for the sake of distinction. The fifth embodiment is different from the fourth embodiment in that the groove width of the groove 507 varies in the extending direction of the groove 507 as a curved groove. Two side walls of the curved groove along the extending direction of the groove 507 comprise an arc wall 508 and a straight wall 509, the arc wall 508 and the straight wall 509 are arranged in a staggered mode, the arc wall 508 and the straight wall 509 on the two side walls of the same groove 507 are correspondingly arranged, and the arc wall 508 is oppositely arranged in a bracket shape.
The groove of the present invention is not limited to the grooves 407 and 507 shown in the embodiments of fig. 4 and 5, and may be grooves of other forms, for example, the positions of the arc wall 508 and the straight wall 509 of the same groove 507 in fig. 5 may be staggered, the arc wall 508 may be arranged in the same direction, rather than being arranged in a bracket shape, the arc wall 508 may also be a wall of any curve shape, the groove 507 may also be a non-spiral groove, such as a plurality of grooves that are not communicated with each other, or a plurality of grooves that are intersected into a mesh shape, etc., as long as the disturbance of fluid medium and the heat transfer enhancement can be promoted.
The parts of the fifth embodiment that are similar to the parts of the fourth embodiment will not be described in detail.
It is right above the description that the structure of heat exchange tube and principle go on in the utility model provides a, in concrete implementation, the heat exchange tube carries out work as the part of heat exchanger, and is following right the utility model provides a heat exchanger and principle carry out detailed description.
The utility model provides a heat exchanger includes the casing and sets up the above-mentioned heat exchange tube in the casing. The housing includes a housing inlet for the second fluid medium to enter therein and a housing outlet for the second fluid medium to exit the housing, the inlet and outlet of the heat exchange tubes being open at the housing. Therefore, the inlet, the outlet and the hollow tube body of the heat exchange tube form a first fluid medium channel for passing a first fluid medium, the shell inlet, the shell outlet and the shell inner gap form a second fluid medium channel, the first fluid medium channel and the second fluid medium channel are sealed and isolated, and the first fluid medium in the first fluid medium channel and the second fluid medium in the second fluid medium channel can exchange heat through the tube wall of the heat exchange tube. Therefore, the first fluid medium and the second fluid medium cannot leak mutually during work, and the first fluid medium and the second fluid medium can exchange heat through the tube wall of the heat exchange tube.
According to the utility model discloses a heat exchanger is because adopt before the heat exchange tube, the heat exchange efficiency of heat exchange tube improves, therefore the heat exchange efficiency of heat exchanger also corresponding improvement, furthermore, when adopting the heat exchange tube including spiral groove, through setting up adjacent heat exchange tube set spiral groove mirror symmetry and arranging, between adjacent heat exchange tube, the fluid produces the continuous change of velocity of flow and flow direction, improve the degree of turbulence in flow field, and be close to the partial fluid of wall and flow along groove circumference, another partial fluid is favorable to attenuate fluid boundary layer when flowing along the axial in the same direction as the wall, the wholeness ability of heat exchanger has further been improved.
Fig. 6 is a schematic front view of a heat exchanger according to a first embodiment of the present invention, with the side of the housing facing the view removed for clarity of illustration to show the internal heat exchange tubes. The heat exchanger is generally indicated at 612, the housing inlet 614 and the housing outlet 615 are oppositely disposed, and the heat exchange tubes 601 are arranged in an array in the housing, the array of heat exchange tubes includes M rows and Y columns, M ≧ 1, Y ≧ 2, in this embodiment, the heat exchange tubes 601 are shown as 4 rows. The axial extension direction of the heat exchange tube 601 is perpendicular to the connecting direction of the shell inlet 614 and the shell outlet 615, that is, the flow direction of the first fluid medium in the heat exchange tube 601 is perpendicular to the flow direction of the second fluid medium outside the heat exchange tube 601, and the heat exchanger 612 is an interleaved flow heat exchanger.
Furthermore, the narrow side 611 of the heat exchanger tube 601 is arranged in the flow direction, and the direction of extent of the wide side 610 of the heat exchanger tube 601 coincides with the flow direction of the second fluid medium flowing in from the housing inlet 614 and flowing out from the housing outlet 615, for optimum reduction of the flow resistance, it is possible to choose an end in which the flow resistance of the second fluid medium is advantageously reduced to face the inflow direction of the second fluid medium, for example, if the form of the heat exchanger tube of the second embodiment described in fig. 2 is chosen, the smaller end of the drop-shaped non-circular cross section is directed in the inflow direction of the second fluid medium, as in fig. 6 at the housing inlet 614. Therefore, the heat exchanger according to the embodiment can reduce the fluid resistance of the second fluid medium and the wake vortex of the heat exchange tube in the width direction of the cross section, increase the flow velocity of the first fluid medium, enhance the heat transfer effect and reduce the abrasion of the heat exchange tube.
As also shown in fig. 6, any two adjacent heat exchange tubes 601 are arranged in mirror symmetry with the grooves 607 on the wide side 610 as the symmetry axis in the longitudinal direction, so that the grooves 607 on the adjacent heat exchange tubes 601 are substantially communicated with each other, the fluid is guided to swirl along the grooves, the thickness of the boundary layer is reduced, and the fluid passing through the grooves 607 is subjected to axial vortex, so that the fluid in the boundary layer is disturbed and the boundary layer is separated, thereby accelerating the heat transfer from the outer surface of the tube wall 606 to the second fluid medium, and simultaneously changing the flow speed and the flow direction of the second fluid medium, generating turbulence and promoting the heat transfer.
The left and right sides of the heat exchanger shell shown in fig. 6 are also provided with tube plates 617, and the tube plates 617 are provided with tube holes matching the cross-sectional shapes of the heat exchange tubes 601. The two ends of the heat exchange tube 601 are hermetically connected with the two tube plates 617 respectively. The connection mode can adopt welding, expansion joint, bonding or sealing material filling connection and the like, and the combination of the connection modes. Preferably, welding and bonding are used.
When the heat exchange tube 601 is used specifically, due to the effects of expansion with heat and contraction with cold, the heat exchange tube 601 can expand and contract, in order to adapt to the expansion deformation, an expansion joint (not shown in the figure) is further arranged around the outer side of at least one tube plate 617, the tube plate 617 is connected with the shell in a sealing mode through the expansion joint, when the heat exchange tube 601 extends or shortens, the heat exchange tube 601 drives the tube plate 617 to move, and due to the existence of the expansion joint, the tube plate 617 cannot be separated from the shell. The telescopic joint can set up in the rubber seal ring all around in the tube sheet 617 outside, when the tube sheet 617 removed, the rubber seal ring can take place elastic deformation and follow the motion of tube sheet 617, guarantee tube sheet 617 and casing sealing connection simultaneously, the telescopic joint also can be a plurality of metal ring that set up all around in the tube sheet 617 outside that closely cup joint, when the tube sheet 617, during the removal, metal ring relative slip each other, make whole telescopic joint extension or shorten, thereby make the telescopic joint follow the motion of tube sheet 617 and guarantee tube sheet 617 and casing sealing connection, more the mode of setting no longer redundantly describes.
In practical use, the heat exchange tubes 601 will be shaken by the impact of the second fluid medium, and will also be weakened to generate thermal deformation under the high temperature action of the second fluid medium, so in order to avoid the above problem, a support member 616 is further disposed between the heat exchange tubes 601 transversely to the heat exchange tubes 601 between the tube plates 617, and a specific implementation form of the support member 616 will be described in detail with reference to fig. 8 to 9.
Fig. 7 is a schematic view of a heat exchanger according to a seventh embodiment of the present invention, with the side of the housing shown removed to show the internal heat exchange tubes for clarity of illustration. Fig. 7 is a front view, generally indicated at 712, showing a counter flow heat exchanger. As can be seen in fig. 7, the heat exchanger 712 comprises a housing comprising a housing inlet 714 arranged below and a housing outlet 715 arranged above the housing, the housing inlet 714 and the housing outlet 715 not being directly opposite each other, but being offset from each other, unlike what is shown in fig. 6. The axial extension direction of the heat exchange tube 701 shown in fig. 7 is arranged in the vertical direction, and the first fluid medium flows in the heat exchange tube 701 from top to bottom. From the perspective of fig. 7, when the second fluid medium flows from the lower left to the upper right, the flow direction of at least a portion in the middle is from the bottom to the top, and the flow direction of the first fluid medium in the heat exchange tube 701 is from the top to the bottom, so that the flow directions of the first fluid medium and the second fluid medium are at least partially parallel and opposite to each other, and when the flow directions of the first fluid medium and the second fluid medium are set to be opposite, a larger temperature difference can be realized between the first fluid medium and the second fluid medium with respect to the same flow direction, and a larger heat exchange efficiency is obtained.
As can be seen in fig. 7, the narrow sides 711 of the heat exchange tubes 701 are arranged facing the flow direction, and in order to optimally reduce the flow resistance, the end portions which are favorable for reducing the flow resistance of the second fluid medium are selected to face the inflow direction of the second fluid medium, for example, the heat exchange tube form of the second embodiment is selected, the larger end portion of the non-circular cross section of the drop shape is oriented to the inflow direction of the second fluid medium, and the overall streamline shape of the drop-shaped cross section is like a drop-shaped submarine, so that the fluid around the heat exchange tubes 701 is smooth and uniform, the flow resistance and wake vortex of the second fluid medium are reduced, and the abrasion of the heat exchange tubes 701 is reduced.
The heat exchanger 712 shown in fig. 7 also includes a telescopic joint (not shown) the construction of which is the same as that described in relation to the embodiment shown in fig. 6 and will not be described in detail here.
Fig. 8 and 9 are top cross-sectional views of the heat exchanger 712 according to the embodiment of the present invention shown in fig. 7, the cross-section being a section parallel to the horizontal plane in fig. 7. In fig. 8 and 9, the heat exchange tubes 701 are arranged in the housing in an array including M rows and Y columns, the extending direction of the columns in fig. 8 is perpendicular to the width direction of the cross section of the heat exchange tubes 801, and the direction of the rows is parallel to the width direction of the cross section of the heat exchange tubes 801, while referring to fig. 7, it can be understood that in the present embodiment, the heat exchange tubes 801 are arranged in 11 rows and 8 columns. The number of rows and columns of heat exchange tubes 701 in fig. 7-9 is exemplary.
Referring to fig. 8, the supporting member 716 is implemented as a supporting structure formed by bending a short length of a metal sheet substantially similar to the cross section of the heat exchange pipe.
Referring to fig. 9, the supporting member 716' is implemented as a net structure connected with short-length metal tubes having a section substantially similar to that of the heat exchange tubes.
The supports 716 and 716' are generally sized and positioned so as not to impede the flow of fluid. The support members are not limited to the forms of the support members 716 and 716' shown in fig. 8 and 9, and any other structure capable of supporting the heat exchange pipe without blocking the flow of the fluid medium is also possible.
The above description is only a preferred embodiment of the application and is illustrative of the principles of the technology employed. It will be understood by those skilled in the art that the scope of the present invention is not limited to the specific combination of the above-mentioned features, but also covers other embodiments formed by any combination of the above-mentioned features or their equivalents without departing from the spirit of the present invention. For example, the above features may be replaced with (but not limited to) features having similar functions disclosed in the present application.
Claims (15)
1. A heat exchanger, comprising:
a housing comprising a housing inlet and a housing outlet; and
a heat exchange tube disposed within the housing, the heat exchange tube including a hollow tube body extending in a longitudinal direction and an inlet and an outlet at both ends of the hollow tube body, the inlet and the outlet being open on the housing, the hollow tube body of the heat exchange tube having a non-circular cross section at least at a portion intermediate the both ends of the hollow tube body, the non-circular cross section having a width greater than a height, at least one end portion of the non-circular cross section in the width direction being shaped as a smooth curve and being smoothly connected to a side in the width direction, and a spiral groove having a uniform pitch inwardly recessed from an outer surface of the tube wall on the tube wall intermediate the both ends of the hollow tube body in the longitudinal direction to generate disturbance to a fluid medium inside and outside the tube flowing therethrough in use;
wherein the inlet, the outlet and the hollow tube body of the heat exchange tube form a first fluid medium channel, the shell inlet, the shell outlet and the gap in the shell form a second fluid medium channel, the first fluid medium channel and the second fluid medium channel are isolated in a sealing way and are arranged in a way that the first fluid medium in the first fluid medium channel and the second fluid medium in the second fluid medium channel can exchange heat through the tube wall of the heat exchange tube,
the side surfaces of the heat exchange tubes in the height direction are arranged towards the incident flow direction of the second fluid medium, and any two adjacent heat exchange tubes are arranged in a mirror symmetry mode by taking the longitudinal direction as a symmetry axis.
2. The heat exchanger according to claim 1, wherein at least one end portion of the heat exchange tube is shaped as an elliptical end portion or a circular arc end portion, and the non-circular cross section has an aspect ratio W/H of not less than 10.
3. The heat exchanger according to claim 2, wherein at least one of width-direction side edges of the non-circular cross section includes a straight line portion or a curved line portion, and the side edge and an end portion in the width direction constitute a shape of the non-circular cross section.
4. A heat exchanger according to claim 3, wherein the width-wise sides of the non-circular cross-section are parallel straight sections or mirror-symmetrical curved sections.
5. The heat exchanger of claim 3, wherein the non-circular cross-sectional shape is a streamlined shape.
6. The heat exchanger of claim 5, wherein the width-wise sides of the non-circular cross-section are non-parallel straight segments.
7. The heat exchanger of claim 4, wherein the curved segment is a wavy curved segment.
8. The heat exchanger according to claim 1, wherein a portion of each spiral of the groove on the wide side including the width of the tube wall of the hollow tube body is a straight groove or a curved groove having a uniform groove width, or a curved groove having a groove width varying in an extending direction of the groove.
9. The heat exchanger according to claim 8, wherein two side walls of the curved groove, along the extension direction of the groove, in which the groove width varies in the extension direction, include a circular arc wall and a straight wall.
10. A heat exchanger according to claim 8 or 9, wherein the portion of the groove on the wide side of the heat exchange tube is at an angle to the longitudinal axis, the angle being in the range 0 to 90 degrees and the pitch S of the helix being equal to or greater than the width V of the groove.
11. The heat exchanger according to any one of claims 1 to 9, wherein the heat exchange tubes are arranged in an array in the housing, the array comprising M rows and Y columns, M ≧ 1, Y ≧ 2, the wide side of the heat exchange tube including the width along the flow direction of the second fluid medium, the narrow side of the heat exchange tube including the height near the second inlet is set to face the inflow direction of the second fluid medium, and one of the ends in the width direction of the non-circular cross-section which is more favorable for reducing the fluid resistance faces the inflow direction of the second fluid medium is selected.
12. The heat exchanger according to any one of claims 1 to 9, wherein the shell inlet and the shell outlet are arranged facing each other, and the second medium flow direction is perpendicular to the first medium flow direction; or the shell inlet and the shell outlet are arranged in a staggered mode, and the flowing direction of the second medium is at least partially parallel to and opposite to the flowing direction of the first medium.
13. A heat exchanger according to any one of claims 1 to 9, wherein supports are provided at intervals in the longitudinal direction of the heat exchange tube for supporting the heat exchange tube against thermal deformation or shaking under the action of the air flow, the supports being sized and positioned so as not to obstruct the flow of the fluid.
14. The heat exchanger according to any one of claims 1 to 9, wherein the shell comprises two oppositely arranged tube plates, mounting holes corresponding to the cross-sectional shapes of the end parts of the heat exchange tubes are formed in the tube plates, and the two ends of the heat exchange tubes are respectively connected with the mounting holes of the tube plates in a sealing manner.
15. The heat exchanger of claim 14, further comprising a telescopic joint disposed around the outside of at least one of the tube sheets, wherein the tube sheet is sealingly connected to the shell via the telescopic joint to accommodate thermal expansion and contraction of the heat exchange tube.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202022008301.2U CN213515186U (en) | 2020-09-15 | 2020-09-15 | Heat exchanger |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202022008301.2U CN213515186U (en) | 2020-09-15 | 2020-09-15 | Heat exchanger |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113497248A (en) * | 2021-06-30 | 2021-10-12 | 上海杰宁新能源科技发展有限公司 | Heat exchange device applied to hydrogen fuel cell |
| CN115031564A (en) * | 2022-05-23 | 2022-09-09 | 哈尔滨理工大学 | Multistage phase change heat storage water tank and system of terrace-shaped additional groove |
-
2020
- 2020-09-15 CN CN202022008301.2U patent/CN213515186U/en active Active
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113497248A (en) * | 2021-06-30 | 2021-10-12 | 上海杰宁新能源科技发展有限公司 | Heat exchange device applied to hydrogen fuel cell |
| CN115031564A (en) * | 2022-05-23 | 2022-09-09 | 哈尔滨理工大学 | Multistage phase change heat storage water tank and system of terrace-shaped additional groove |
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Effective date of registration: 20230201 Address after: 1302, Floor 3, Building 1, Yinkun Science Park, No. 6, Fenghua Road, Luoyang Area, Luoyang Free Trade Pilot Zone, Henan Province, 471000 Patentee after: LUOYANG MINGYUAN PETROCHEMICAL INDUSTRY TECHNOLOGY Co.,Ltd. Patentee after: SINOPEC GUANGZHOU ENGINEERING Co.,Ltd. Address before: 1302, Floor 3, Building 1, Yinkun Science Park, No. 6, Fenghua Road, Luoyang Area, Luoyang Free Trade Pilot Zone, Henan Province, 471000 Patentee before: LUOYANG MINGYUAN PETROCHEMICAL INDUSTRY TECHNOLOGY Co.,Ltd. |