CN115265243A - Heat exchanger and composite set - Google Patents

Abstract

The invention discloses a heat exchanger and a combined device, wherein the heat exchanger comprises: the heat exchanger body comprises a cold runner and a hot runner, the cold runner is in contact with the hot runner, the flow directions of the fluids of the cold runner and the hot runner are opposite, the flow cross-sectional area of a hot flow outlet of the hot runner is smaller than that of a hot flow inlet of the hot runner, and the flow cross-sectional area of a cold flow outlet of the cold runner is smaller than that of a cold flow inlet of the cold runner; the heat of the hot runner is transferred to the cold runner, and the temperature of the cold runner is increased after the cold runner absorbs the heat of the hot runner, so that the heat exchange between the hot runner and the cold runner is effectively realized; the airflow direction through the cold runner is opposite to that of the hot runner, so that the heat flow direction is opposite to that of the cold flow in the heat exchange process, and counter flow is formed.

Description

Heat exchanger and composite set

Technical Field

The invention relates to the technical field of heat exchange, in particular to a heat exchanger and a combined device.

Background

A heat exchanger, also known as a heat exchanger, is used to transfer heat from a hot fluid to a cold fluid to reduce energy loss, and is an industrial application of convective heat transfer and thermal heat transfer. In the existing heat energy recovery process, hot fluid and cold fluid are generally respectively sent to a heat exchange device, after entering the heat exchange device, the heat of the hot fluid can be transferred to the cold fluid, and the temperature of the cold fluid rises after absorbing the heat transferred by the hot fluid, so that the heat energy recovery is completed, and the cyclic utilization of the heat energy is realized. At present, in the mainstream heat exchanger on the market, cold fluid and hot fluid exchange heat in a staggered mode, two flow channels form 90 degrees, the flow channels are crossed to cause uneven heat exchange, the cold and hot heat exchange time is short, and the heat exchange efficiency of the heat exchanger is low.

Disclosure of Invention

The embodiment of the application provides a heat exchanger, has solved the technical problem that the heat exchange efficiency of heat exchanger is low among the prior art, has realized improving the heat exchange efficiency of heat exchanger.

In order to achieve the purpose, the invention adopts the following technical scheme:

a heat exchanger, comprising:

the heat exchanger body comprises a cold runner and a hot runner, wherein the cold runner is in contact with the hot runner, the flow direction of the fluid of the cold runner is opposite to that of the fluid of the hot runner, the flow cross-sectional area of a heat flow outlet of the hot runner is smaller than that of a heat flow inlet of the hot runner, and the flow cross-sectional area of a cold flow outlet of the cold runner is smaller than that of a cold flow inlet of the cold runner.

Furthermore, a first included angle is formed between the heat flow inlet and the cold flow outlet, and a second included angle is formed between the heat flow outlet and the cold flow inlet.

Furthermore, the contact surface of the hot runner and the cold runner is an inclined surface or an arc surface.

Further, the hot runner is located above the cold runner, and the inclined surface is inclined from the cold runner toward the hot runner.

Further, a brazing layer is arranged between the hot runner and the cold runner.

Furthermore, adjacent two be provided with the hot flow water conservancy diversion strip between the hot flow import, adjacent two be provided with the cold flow water conservancy diversion strip between the cold flow import.

Further, a fin body is arranged in the cold runner and/or the hot runner.

Furthermore, a plurality of grooves with alternate concave and convex are formed in the fin body along the x-axis direction.

Further, the grooves are arranged in a straight shape or a corrugated shape.

Another object of the present invention is to: the combined device comprises a device body, wherein the device body comprises two heat exchange areas which are symmetrically arranged, a first outlet and a second outlet are respectively arranged at two ends of the device body, heat flow outlets of the two heat exchange areas are respectively communicated with the first outlet, cold flow outlets of the two heat exchange areas are respectively communicated with the second outlet, and at least one of the two heat exchange areas is the heat exchanger in the specification.

Compared with the prior art, the invention has the following beneficial effects:

a heat exchanger is used by matching a cold runner and a hot runner, the cold runner is in contact with the hot runner, the heat of the hot runner is transferred to the cold runner, the temperature of the cold runner rises after the cold runner absorbs the heat of the hot runner, the heat exchange between the hot runner and the cold runner is effectively realized, the heat recovery is completed, the cyclic utilization of the heat energy is realized, and the energy consumption is reduced; the flow direction of the air flow passing through the cold runner is opposite to that of the air flow passing through the hot runner, so that the transport direction of the hot flow is opposite to that of the cold flow in the heat exchange process, and counter flow is formed; the flow cross-sectional area of the heat flow outlet of the hot runner is smaller than that of the hot flow inlet of the hot runner, the flow cross-sectional area of the cold flow outlet of the cold runner is smaller than that of the cold flow inlet of the cold runner, the time of the hot fluid passing through the hot runner and the time of the cold fluid passing through the cold runner are effectively reduced, the residence time of the cold fluid in the cold runner is further prolonged, and the residence time of the hot fluid in the hot runner is prolonged, so that the cold fluid and the hot fluid can fully exchange heat, and the heat exchange effect of the heat exchanger is effectively improved.

Additional aspects and advantages of the invention will be set forth in part in the description which follows and, in part, will be obvious from the description, or may be learned by practice of the invention.

Drawings

In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to these drawings without creative efforts.

FIG. 1 is a schematic structural diagram of the present invention.

Fig. 2 is a schematic cross-sectional view of the heat exchanger body according to the present invention.

Fig. 3 is a schematic structural diagram at a in fig. 2.

Fig. 4 is a schematic structural diagram at E in fig. 2.

FIG. 5 is a cross-sectional schematic view of a hot runner according to the present invention.

Fig. 6 is a schematic cross-sectional view of a cold runner according to the present invention.

FIG. 7 is a schematic view showing the structure of the gas-liquid separating apparatus of the present invention.

FIG. 8 is a schematic view of a hot runner according to the present invention.

FIG. 9 is a schematic view of a manifold assembly according to the present invention.

FIG. 10 is a schematic view of the eating piece body of the present invention.

Fig. 11 is a schematic structural view at B in fig. 10.

FIG. 12 is a second schematic view of the eating piece body of the present invention.

Fig. 13 is a schematic view of the structure at C in fig. 12.

FIG. 14 is a third schematic view of the eating piece body of the present invention.

Fig. 15 is a schematic view of the structure at D in fig. 14.

FIG. 16 is a fourth schematic view of the eating piece body of the present invention.

FIG. 17 is a schematic view of the stacked structure of the fin bodies of the present invention.

FIG. 18 is a schematic structural diagram of the device body of the present invention.

FIG. 19 is another schematic structural diagram of the device body of the present invention.

Reference numerals:

1. a heat exchanger body; 11. a hot runner; 11a, a heat flow inlet; 11b, a heat flow outlet; 12. a cold runner; 12a, a cold flow inlet; 12b, a cold flow outlet; 13. a contact surface; 14. a heat flow guide strip; 15. cold flow guide strips; 16. installing a flange;

2. a gas-liquid separation device; 21. a manifold; 211. a confluence groove; 212. a buffer section; 22. a collecting pipe;

3. a first included angle;

4. a second included angle;

5. a fin body; 51a, a straight portion; 51b, an arc portion; 52. a trench; 53. a boss portion; 54. a recessed portion;

6. a device body; 61. a heat exchange zone; 62. a first outlet; 63. a second outlet.

Detailed Description

In order to make the objects, technical solutions and advantages of the embodiments of the present application clearer, the technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the drawings in the embodiments of the present application, and it is obvious that the described embodiments are some embodiments of the present application, but not all 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 application.

Unless defined otherwise, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this application belongs; the terminology used in the description of the application herein is for the purpose of describing particular embodiments only and is not intended to be limiting of the application.

The terms "comprising" and "having," and any variations thereof, in the description and claims of this application and in the description of the figures are intended to cover, but not exclude, other things. The word "a" or "an" does not exclude a plurality.

Reference herein to "an embodiment" means that a particular feature, structure, or characteristic described in connection with the embodiment can be included in at least one embodiment of the application. The appearances of the phrase "an embodiment" in various places in the specification are not necessarily all referring to the same embodiment, nor are separate or alternative embodiments mutually exclusive of other embodiments. It is explicitly and implicitly understood by one skilled in the art that the embodiments described herein can be combined with other embodiments.

The directional terms appearing in the following description are directions shown in the drawings, and do not limit the specific structure of the battery cell of the present application. For example, in the description of the present application, the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," "circumferential," and the like are used in an orientation or positional relationship indicated based on the orientation or positional relationship shown in the drawings for the convenience of description and simplicity of description only, and do not indicate or imply that the device or element being referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore should not be considered as limiting the present application.

Further, expressions of directions indicated for explaining the operation and configuration of each member of the heat exchanger of the present embodiment, such as the x-axis direction, the y-axis direction, and the z-axis direction, are not absolute but relative, and although these indications are appropriate when each member of the heat exchanger is in the position shown in the drawings, when the position is changed, the directions should be interpreted differently to correspond to the changes.

Furthermore, the terms "first," "second," and the like in the description and claims of the present application or in the above-described drawings are used for distinguishing between different objects and not necessarily for describing a particular sequential order, and may explicitly or implicitly include one or more of the features.

In the description of the present application, unless otherwise specified, "plurality" means two or more (including two), and similarly, "plural groups" means two or more (including two).

In the description of the present application, it should be noted that, unless explicitly stated or limited otherwise, the terms "mounted," "connected" and "connected" should be interpreted broadly, for example, the mechanical structures "connected" or "connected" may refer to physical connections, for example, the physical connections may be fixed connections, for example, fixed connections by fasteners, such as screws, bolts or other fasteners; the physical connection can also be a detachable connection, such as a mutual clamping or clamping connection; the physical connection may also be an integral connection, for example, a connection made by welding, gluing or integrally forming the connection. "connected" or "coupling" of circuit structures may mean not only physical coupling but also electrical or signal coupling, for example, direct coupling, i.e., physical coupling, or indirect coupling via at least one element therebetween, as long as electrical communication is achieved, or communication between the two elements; signal connection may refer to signal connection through a medium, such as radio waves, in addition to signal connection through circuitry. The specific meaning of the above terms in this application will be understood to be a specific case for those of ordinary skill in the art.

Referring to fig. 1 to 6, a heat exchanger provided in an embodiment of the present application includes a heat exchanger body 1, the heat exchanger body 1 includes a cold runner 12 and a hot runner 11, the cold runner 12 contacts the hot runner 11, a flow direction of a fluid of the cold runner 12 is opposite to a flow direction of a fluid of the hot runner 11, a flow cross-sectional area of a hot outlet 11a of the hot runner 11 is smaller than a flow cross-sectional area of a hot inlet 11a of the hot runner 11, and a flow cross-sectional area of a cold outlet 12b of the cold runner 12 is smaller than a flow cross-sectional area of a cold inlet 12a of the cold runner.

Compared with the prior art, the heat exchanger provided by the embodiment of the application is used by matching the cold runner 12 and the hot runner 11, the cold runner 12 is in contact with the hot runner 11, the heat of the hot runner 11 is transferred to the cold runner 12, the temperature of the cold runner 12 rises after absorbing the heat of the hot runner 11, the heat exchange between the hot runner 11 and the cold runner 12 is effectively realized, the heat energy recovery is completed, the cyclic utilization of the heat energy is realized, and the energy consumption is reduced; the airflow direction of the cold runner 12 is opposite to that of the hot runner 11, so that the heat flow and the cold flow are opposite in transportation direction in the heat exchange process, and counter flow is formed; the flow cross-sectional area of the heat flow outlet 11b through the hot runner 11 is smaller than that of the inlet of the hot runner 11, the flow cross-sectional area of the cold flow outlet 12b of the cold runner 12 is smaller than that of the cold flow inlet 12a, the time of the hot fluid passing through the hot runner 11 and the time of the cold fluid passing through the cold runner 12 are effectively slowed down, the residence time of the cold fluid in the cold runner 12 is further prolonged, the residence time of the hot fluid in the hot runner 11 is prolonged, the cold fluid and the hot fluid can fully exchange heat, and the heat exchange effect of the heat exchanger is effectively improved.

In some embodiments, a plurality of cold runners 12 and hot runners 11 may be provided, and a plurality of cold runners 12 and a plurality of hot runners 11 are alternately stacked in sequence, so that it is effective to sufficiently contact the cold fluid in the cold runner 12 with the hot fluid in the hot runner 11, thereby improving the heat exchange efficiency.

In some embodiments, a braze layer is disposed between the hot runner 11 and the cold runner 12.

The hot runner 11 and the cold runner 12 are welded by brazing; through adopting the brazing welding between hot runner 11 and the cold runner 12, effectual connection hot runner 11 and cold runner 12 can weld the heat exchanger wholly through brazing, and the stress and the deformation that arouse are less, guarantee the dimensional accuracy of weldment easily to prevent hot runner 11 and cold runner 12 the problem of deformation from appearing in the course of working.

It should be noted that the hot runner 11 and the cold runner 12 may also be welded or spliced, and may be set according to actual requirements during processing.

In some embodiments, referring to fig. 2 to 4, a first included angle 3 is formed between the hot fluid inlet 11a and the cold fluid outlet 12b, and a second included angle 4 is formed between the hot fluid outlet 11b and the cold fluid inlet 12 a; the cold fluid inlet 12a, the cold fluid outlet 12b, the hot fluid inlet 11a and the hot fluid outlet 11b are used in a matched manner, the cold fluid inlet 12a is arranged at one end of the cold runner 12, the cold fluid outlet 12b is arranged at the other end of the cold runner 12, the cold fluid inlet 12a and the cold fluid outlet 12b are communicated with the cold runner 12, the cold fluid enters the cold runner 12 through the cold fluid inlet 12a and is then discharged through the cold fluid outlet 12b, the hot fluid inlet 11a is arranged at one end of the hot runner 11, the hot fluid outlet 11b is arranged at the other end of the hot runner 11, the hot fluid inlet 11a and the hot fluid outlet 11b are communicated with the hot runner 11, the hot fluid enters the hot runner 11 through the hot fluid inlet 11a and is then discharged through the hot fluid outlet 11b, and the circulation of the cold runner 12 and the hot runner 11 is effectively realized. Through the setting of first contained angle 3, second contained angle 4, be formed with first contained angle 3 between heat flow inlet 11a and the cold flow export 12b, be formed with second contained angle 4 between heat flow export 11b and the cold flow import 12a, the effectual air current flow direction who makes hot runner 11 and cold flow 12 is opposite.

Specifically, the first included angle 3 and the second included angle 4 are symmetrically arranged, so that pressure drop generated in the cold runner 12 and the hot runner 11 is effectively reduced, and energy consumption is reduced.

Specifically, the angle of first contained angle 3 and second contained angle 4 is 60 ~ 150 degrees, the contained angle of first contained angle 3 and the contained angle of second contained angle 4 are big more, hot runner 11 is big more with cold runner 12's contact surface 13 volume, thereby increase hot-fluid and cold fluidic heat transfer area, on the contrary, the contained angle of first contained angle 3 and the contained angle of second contained angle 4 are little, hot runner 11 is little with cold runner 12's contact surface 13 volume, thereby reduce hot-fluid and cold fluidic heat transfer area, therefore, in this scope, can guarantee hot runner 11 and cold runner 12's contact surface 13 volume, still can prevent that the area of heat exchanger is too big.

Optionally, the angle between the first included angle 3 and the second included angle 4 is 60 to 70 degrees, 70 to 80 degrees, 80 to 90 degrees, 90 to 100 degrees, 100 to 110 degrees, 110 to 120 degrees, 120 to 130 degrees, 130 to 140 degrees or 140 to 150 degrees, and when the device is used, the selection can be performed according to actual requirements.

In some embodiments, referring to fig. 7-9, the contact surface 13 of the hot runner 11 and the cold runner 12 is an inclined surface or an arc surface.

In some embodiments, the hot runner 11 is located above the cold runner 12, with the inclined surface sloping from the cold runner 12 towards the hot runner 11.

The contact surface 13 of the hot runner 11 and the cold runner 12 is an inclined surface or an arc surface, and the contact surface 13 is a plane, so that the area of the contact surface 13 of the hot runner 11 and the cold runner 12 is effectively increased, meanwhile, the inclined surface is inclined in the direction of the hot outlet 11b of the hot runner 11, the effective hot runner 11 is contracted in the direction from the hot inlet 11a to the hot outlet 11b, the cold runner 12 is contracted in the direction from the cold inlet 12a to the cold outlet 12b, so that the sizes of the hot inlet 11a and the cold inlet 12a are enlarged, the hot fluid can conveniently enter the hot runner 11 and the cold fluid can conveniently enter the cold runner 12, the sizes of the hot outlet 11b and the cold outlet 12b are reduced, the discharge speed of the cold fluid in the cold runner 12b and the discharge speed of the hot fluid in the hot runner 11b are effectively reduced, the residence time of the hot fluid in the cold runner 12 is further prolonged, and the residence time of the hot fluid in the hot runner 11 is further, so that the cold fluid and the hot fluid can fully exchange heat with the hot fluid, and the effect of the heat exchanger can be effectively improved.

Specifically, the inclination angle of the inclined plane is 15 to 75 degrees, optionally, the inclination angle of the inclined plane is 15 to 25 degrees, 25 to 35 degrees, 35 to 45 degrees, 45 to 55 degrees, 55 to 65 degrees or 65 to 75 degrees, and when the inclined plane is used, the inclination angle can be selected according to actual requirements.

In some embodiments, referring to fig. 3 to 4, a hot flow guide strip 14 is disposed between two adjacent hot flow inlets 11a, and a cold flow guide strip 15 is disposed between two adjacent cold flow inlets 12 a. Through the setting of heat flow gib 14, cold flow gib 15, when effectual hot-fluid passes through hot fluid inlet 11a and gets into hot runner 11, the cold fluid leads when getting into cold runner 12 through cold fluid inlet 12a to reduce the resistance of hot-fluid, cold fluid, effectual improvement heat exchange rate.

It should be noted that the cross-sectional shape of the hot flow guide strip 14 and the cross-sectional shape of the cold flow guide strip 15 may be set according to actual requirements, such as V-shape, circular arc, triangle, etc.

In some embodiments, referring to fig. 10-17, the fin body 5 is disposed within the cold runner 12 and/or the hot runner 11. Through the arrangement of the fin body 5, the fin body 5 is arranged in the cold runner 12 and/or the hot runner 11, and the fin body 5 is used for assisting the cold runner 12 in transporting cold fluid and assisting the hot runner 11 in transporting hot fluid.

In some embodiments, referring to fig. 10-11, the fin body 5 has a plurality of grooves 52 disposed along the x-axis. Through the setting of slot 52, fin body 5 is provided with a plurality of unsmooth alternate slots 52 along the direction of x axle, and slot 52 is used for transporting hot-fluid or cold fluid, and after hot-fluid got into hot runner 11 from hot fluid import 11a, cold-fluid got into cold runner 12 from cold fluid import 12a, cold-fluid or hot-fluid dispersed through a plurality of slots 52 to improve the heat transfer effect of hot-fluid and cold-fluid.

In some embodiments, referring to fig. 10-13, the grooves 52 are arranged in a straight or corrugated configuration. Through the shape setting of slot 52, slot 52 is straight form or corrugate, compares with straight form, sets up slot 52 into the corrugate, when slot 52 transports hot-fluid or cold fluid, has certain vortex effect to hot-fluid or cold fluid, increases the dwell time of hot-fluid or cold fluid in fin body 5 to improve heat transfer effect.

In some embodiments, referring to fig. 14 to 15, one side of each trench 52 is provided with a plurality of protrusions 53 arranged at equal intervals, and the other side of each trench 52 is correspondingly provided with a plurality of recesses 54 arranged at equal intervals. The cooperation through bellying 53, depressed part 54 is used, when slot 52 transports hot-fluid or cold fluid, has certain vortex effect to hot-fluid or cold fluid, increases the dwell time of hot-fluid or cold fluid in fin body 5 to improve heat transfer effect.

The cross-sectional shape of the groove 52, the cross-sectional shape of the convex portion 53, and the cross-sectional shape of the concave portion 54 are one of a triangle, a square, a trapezoid, a pentagon, a hexagon, a circle, and an ellipse.

It should be noted that the number and the size of the grooves 52, the protruding portions 53 and the recessed portions 54 can be set according to actual requirements, and the distance between two adjacent grooves 52, two adjacent protruding portions 53 and two adjacent recessed portions 54 can also be set according to actual requirements.

It should be noted that the fin body 5 is manufactured by an extrusion molding process, and then is bent by a mold to form the arc-shaped portion 51b, so that the manufacturing process is simple, and the mass production of the fin body 5 is facilitated.

It should be noted that, the fin body 5 may also be arranged in a windowing manner or an organ manner, and when the fin body 5 is arranged in the organ manner, the fin body 5 is manufactured by adopting an extrusion process, so that a plurality of flow channels are formed in the fin body 5; when the fin body 5 is set to be the windowing type, an opening is formed between two adjacent circulation channels in the fin body 5, so that the circulation speed of heat flow or cold flow in the circulation channels is delayed, and the heat exchange effect is effectively improved.

In some embodiments, the fin body 5 includes a straight portion 51a and two arc portions 51b, the two arc portions 51b are provided at both ends of the straight portion 51a, respectively, and the two arc portions 51b are integrally formed with the straight portion 51 a; through straight portion 51a, arc portion 51 b's cooperation is used, arc portion 51b is provided with two, two arc portions 51b set up respectively in straight portion 51 a's both ends, arc portion 51b has certain vortex effect to hot-fluid or cold fluid, increase the dwell time of hot-fluid or cold fluid in fin body 5, and simultaneously, arc portion 51b and straight portion 51a integrated into one piece, effectual messenger fin body 5 is streamlined, thereby reduce the pressure drop that produces in cold runner 12 and the hot runner 11, reduce the energy consumption.

In some embodiments, mounting flanges 16 are provided at both ends of the hot runner 11 and both ends of the cold runner 12; through the arrangement of the mounting flanges 16, the mounting flanges 16 are arranged at the two ends of the hot runner 11 and the two ends of the cold runner 12, so that the fixation of the hot flow inlet 11a, the hot flow outlet 11b, the cold flow inlet 12a and the cold flow outlet 12b is effectively enhanced, and the heat exchanger is convenient to assemble with exhaust equipment or exhaust equipment.

Referring to fig. 1 to 6, the heat exchanger according to the embodiment of the present application further includes a gas-liquid separation device 2; the gas-liquid separation device 2 is partially disposed at the bottom of the hot runner 11. Through the setting of gas-liquid separation device 2, gas-liquid separation device 2 part sets up in hot runner 11, and in the heat transfer process, high-temperature gas has the comdenstion water to separate out at the in-process of cooling down easily, and the comdenstion water that separates out can be discharged through gas-liquid separation device 2. By arranging the gas-liquid separation device 2 at the bottom of the hot runner 11, condensed water is easy to separate out in the cooling process of high-temperature gas, and the separated condensed water sinks to the bottom of the hot runner 11 because the density of water is higher than that of gas, and is discharged out of the hot runner 11 through the gas-liquid separation device 2, so that gas-liquid separation is realized.

In some embodiments, the gas-liquid separation device 2 includes a manifold 21 and a header 22, the manifold 21 is disposed in the hot runner 11, the header 22 is disposed on the heat exchanger body 1 along the z-axis direction, one end of the manifold 21 close to the hot flow outlet 11b is communicated with the hot runner 11, and the other end of the manifold 21 close to the hot flow inlet 11a is communicated with the header 22. The manifold 21 and the collecting pipe 22 are used in a matched manner, one end of the manifold 21, which is close to the heat flow outlet 11b, is communicated with the hot runner 11, the other end of the manifold 21, which is close to the heat flow inlet 11a, is communicated with the collecting pipe 22, when high-temperature gas is cooled to separate out condensed water, the condensed water enters the manifold 21 from the hot runner 11 and is discharged from the manifold 21 through the collecting pipe 22, the separated condensed water is effectively collected and converged, meanwhile, the inclined surface inclines upwards along the direction of the heat flow outlet 11b of the hot runner 11, and in the process that the condensed water enters the collecting pipe 22 from the manifold 21, the condensed water flows along the direction of the heat flow outlet 11b of the hot runner 11 to the heat flow inlet 11a, so that the condensed water flows back, the heat is effectively exchanged with hot fluid in the hot runner 11 by using the returned condensed water, the working efficiency of the heat exchanger can be effectively improved due to the large specific heat capacity of water, and the separated condensed water is recycled, and resources are saved.

In some embodiments, referring to fig. 9, a manifold slot 211 is disposed at the top of the manifold 21 along the y-axis, and the manifold slot 211 communicates the manifold 21 and the hot runner 11. Through the setting of converging groove 211, the top of manifold 21 is provided with converging groove 211 along the y axle direction, and converging groove 211 communicates manifold 21 and hot runner 11, and the comdenstion water that precipitates can get into manifold 21 from hot runner 11 through converging groove 211, and the effectual comdenstion water that precipitates is collected, converges.

In some embodiments, a plurality of flow-converging grooves 211 may be provided, and the plurality of flow-converging grooves 211 are arranged at intervals on the top of the manifold 21 along the x-axis direction, so as to effectively improve the capability of collecting and converging precipitated condensed water.

Specifically, the shape of the cross-sectional area of the bus bar 211 is one of a triangle, a trapezoid, a square, a pentagon, a hexagon, a circle and an ellipse, and the bus bar can be set according to actual requirements during use.

It should be noted that the size and the number of the bus bars 211 may be set according to actual requirements.

It should be noted that, in order to prevent the condensed water from remaining in the hot runner 11 during the collecting and converging processes, and flowing from the hot flow outlet 11b of the hot runner 11 to the hot flow inlet 11a, and then being discharged from the hot flow inlet 11a, so as to perform the hot fluid entering the hot runner 11 from the hot flow inlet 11a, a blocking block may be disposed at the hot flow inlet 11a of the hot runner 11, or an inclined portion of the hot runner 11 at the hot flow inlet 11a may be disposed, and a converging groove 211 may be disposed at the front side of the blocking block or at the lowest point of the inclined portion, so that the condensed water can effectively flow into the collecting chamber 21 through the converging groove 211 before being discharged from the hot flow inlet 11 a.

In order to prevent condensed water from accumulating at the other end of the manifold 21 close to the heat flow inlet 11a of the hot runner 11, a convex hull is arranged at the other end of the manifold 21 close to the heat flow inlet 11a of the hot runner 11, and the accumulated condensed water is assisted by the convex hull to enter the collecting pipe 22 from the manifold 21.

It should be noted that the size and number of the headers 22 may be set according to actual requirements.

In some embodiments, a buffer portion 212 is provided in the manifold 21 at the confluence groove 211, and the buffer layer communicates the manifold 21 and the confluence groove 211. By the arrangement of the buffer part 212, the buffer part 212 is positioned at the confluence groove 211 in the manifold 21, the buffer part 212 is communicated with the manifold 21 and the confluence groove 211, and when condensed water enters the manifold 21 from the confluence groove 211, the condensed water can be buffered by the buffer part 212, so that the condensed water is prevented from carrying part of gas to enter the manifold 21.

It should be noted that the gas-liquid separation filler is arranged in the buffer portion 212, the gas-liquid separation filler includes a filling module formed by winding prismatic metal filaments and a wavy fine mesh woven by metal filaments, the filling module is arranged above the wavy fine mesh, and the condensed water achieves separation, buffering and condensation re-separation multi-frequency separation effects under the action of the gas-liquid separation filler, so that the condensed water is prevented from entering the manifold 21 along with part of gas.

According to the heat exchange method of the heat exchanger provided by the embodiment of the application, the cold fluid passes through the cold runner 12, the hot fluid passes through the hot runner 11, the flow directions of the cold fluid and the hot fluid are opposite, and the cold fluid and the hot fluid exchange heat. By the method, heat exchange is carried out on the hot fluid and the cold fluid, the heat of the hot fluid is transferred to the cold fluid, the temperature of the cold fluid is increased after the cold fluid absorbs the heat of the hot fluid, and then the temperature of the hot fluid at the hot fluid outlet 11b of the hot fluid channel 11 is reduced.

Referring to fig. 18 to 19, some embodiments of the present disclosure provide a combined device, which includes a device body, the device body includes two heat exchange areas symmetrically disposed, two ends of the device body are respectively provided with a first outlet and a second outlet, heat outlets of the two heat exchange areas are respectively communicated with the first outlet, cold outlets of the two heat exchange areas are respectively communicated with the second outlet, and at least one of the two heat exchange areas is a heat exchanger in the foregoing description.

Different from the prior art, the utility model provides a composite set, cooperation through the heat transfer district of two symmetry settings is used, the heat exchange efficiency of effectual improvement device body, and simultaneously, the hot fluid export of two heat transfer districts and the first export intercommunication of the one end of device body, the effectual hot-fluid with in two heat transfer districts converges to first export and discharges, the cold flow export of two heat transfer districts and the second export intercommunication of the other end of device body, the effectual cold fluid with in two heat transfer districts converges to the second export and discharges, be convenient for after the heat exchange to the centralized processing of the hot-fluid and the cold fluid in two heat transfer districts, and then improve composite set's work efficiency.

The hot runner 11 described above can introduce the following media:

1. pure gas, which enters the hot runner 11 for heat exchange from the hot fluid inlet 11a, and gas is discharged from the hot fluid outlet 11 b.

2. And a gas mixture which enters the hot runner 11 from the hot flow inlet 11a for heat exchange, and is discharged from the hot flow outlet 11 b.

3. And the gas-liquid mixture enters the hot runner 11 from the hot flow inlet 11a for heat exchange, and in the process of heat exchange, when the physical property of a certain substance in the gas-liquid mixture is cooled to the condensation point (condensation temperature), separation can be realized, the separated condensed water is discharged from the collecting cavity 21 and the collecting pipe 22, and other parts which are still gaseous are discharged from the hot flow outlet 11 b.

It will be evident to those skilled in the art that the invention is not limited to the details of the foregoing illustrative embodiments, and that the present invention may be embodied in other specific forms without departing from the spirit or essential attributes thereof. The present embodiments are therefore to be considered in all respects as illustrative and not restrictive, the scope of the invention being indicated by the appended claims rather than by the foregoing description, and all changes which come within the meaning and range of equivalency of the claims are therefore intended to be embraced therein.

Claims (10)

1. A heat exchanger, comprising:

heat exchanger body (1), including cold runner (12), hot runner (11), cold runner (12) with hot runner (11) contact, cold runner (12) with the fluid flow direction of hot runner (11) is opposite, the flow cross-sectional area of hot fluid outlet (11 b) of hot runner (11) is less than the flow cross-sectional area of its hot fluid import (11 a), the flow cross-sectional area of cold fluid outlet (12 b) of cold runner (12) is less than the flow cross-sectional area of its cold fluid import (12 a).

2. A heat exchanger according to claim 1, characterized in that a first angle (3) is formed between the hot fluid inlet (11 a) and the cold fluid outlet (12 b), and a second angle (4) is formed between the hot fluid outlet (11 b) and the cold fluid inlet (12 a).

3. A heat exchanger according to claim 1, characterised in that the contact surfaces (13) of the hot runner (11) and the cold runner (12) are inclined or curved.

4. A heat exchanger according to claim 3, wherein the hot runner (11) is located above the cold runner (12), the inclined surface being inclined from the cold runner (12) towards the hot runner (11).

5. A heat exchanger according to claim 1, characterised in that a brazing layer is provided between the hot runner (11) and the cold runner (12).

6. A heat exchanger according to claim 1, characterized in that a hot flow guide strip (14) is arranged between two adjacent hot flow inlets (11 a), and a cold flow guide strip (15) is arranged between two adjacent cold flow inlets (12 a).

7. Heat exchanger according to any of claims 1 to 6, wherein fin bodies (5) are provided in the cold runner (12) and/or in the hot runner (11).

8. A heat exchanger according to claim 7, characterised in that the fin body (5) is provided with a plurality of alternating concave and convex grooves (52) along its width.

9. A heat exchanger according to claim 8, characterised in that the grooves (52) are arranged in a straight or corrugated manner.

10. A combined device, characterized by comprising a device body, wherein the device body (6) comprises two heat exchange areas (61) which are symmetrically arranged, a first outlet (62) and a second outlet (63) are respectively arranged at two ends of the device body, hot flow outlets of the two heat exchange areas (61) are respectively communicated with the first outlet (62), cold flow outlets of the two heat exchange areas (61) are respectively communicated with the second outlet (63), and at least one of the two heat exchange areas (61) is the heat exchanger according to any one of claims 1 to 9.

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