CN218764766U - Heat pipe type heat exchanger - Google Patents

Abstract

The utility model discloses a heat pipe type heat exchanger, include: the shell is provided with a cooling cavity and a smoke cavity which are separated; the heat pipe groups are sequentially arranged in the flowing direction of the flue gas, each heat pipe comprises a heat absorption section and a heat release section, the heat absorption section is located in the flue gas cavity, the heat release section is located in the cooling cavity, the section, perpendicular to the axial direction, of the heat absorption section is oval, the heat absorption section is provided with a first long axis direction, the end part of the heat absorption section in the first long axis direction is a long axis end part, and the first long axis direction is parallel to the flowing direction of the flue gas; in the same heat pipe set, the end parts of two adjacent long shafts of two adjacent heat absorption sections are connected through a connecting plate. The heat pipe type heat exchanger is high in structural stability, not prone to dust accumulation and capable of being conveniently cleaned.

Description

Heat pipe type heat exchanger

Technical Field

The utility model relates to a heat exchanger technical field, concretely relates to heat pipe type heat exchanger.

Background

The heat pipe type heat exchanger is commonly used in flue systems of coal-fired power plants, steel plants, coking plants and the like, and is used for recycling the waste heat of flue gas. However, the flue environment is relatively complex, and the specific expression is that the dust content is relatively large, and part of dust has great viscosity, if a large amount of dust is accumulated on the heat exchanger, the heat exchange efficiency of the heat exchanger is affected, the flow of flue gas is affected, and even the corrosion of the heat exchanger is caused.

SUMMERY OF THE UTILITY MODEL

The utility model aims at providing a heat pipe type heat exchanger, its structural stability is high, is difficult for the deposition, and can conveniently blow the clearance.

In order to solve the technical problem, the utility model provides a heat pipe type heat exchanger, include: the shell is provided with a cooling cavity and a smoke cavity which are separated; the heat pipe groups are sequentially arranged in the flowing direction of the flue gas, each heat pipe comprises a heat absorption section and a heat release section, the heat absorption section is located in the flue gas cavity, the heat release section is located in the cooling cavity, the section, perpendicular to the axial direction, of the heat absorption section is oval, the heat absorption section is provided with a first long axis direction, the end part of the heat absorption section in the first long axis direction is a long axis end part, and the first long axis direction is parallel to the flowing direction of the flue gas; in the same heat pipe group, the end parts of two adjacent long shafts of two adjacent heat absorption sections are connected through a connecting plate.

The utility model provides a heat pipe type heat exchanger compares and has following technical advantage in prior art:

1) The heat absorption section is an elliptical tube, and the first long axis direction of the heat absorption section can be consistent with the flow direction of the flue gas, so that the whole heat absorption section is in a streamline design, the outer wall surface of the heat absorption section is not easy to accumulate dust, the heat exchange efficiency of the heat absorption section is favorably ensured, the projection area (the flow blocking area of the flue gas) of the heat absorption section in the flow direction of the flue gas is relatively small, and the air flow flows through the heat absorption section of the heat exchange tube set smoothly, so that the flow resistance of the flue gas can be reduced, and the energy consumption of a fan is favorably reduced;

2) The arrangement of the connecting plate can improve the structural stability of the heat pipe set and is beneficial to increasing the heat exchange area;

3) The arrangement of the connecting plate is also beneficial to inhibiting the wake vortex phenomenon of the leeward side of the heat absorption section at the upstream side in the two adjacent heat absorption sections, so that the flow distribution of the air flow between the heat exchange tube groups can be relatively uniform, the obvious air flow compression-expansion process is avoided, the high-speed area can be basically eliminated, and the scouring of the dust-containing air flow on the heat tubes can be further reduced; importantly, because the wake vortex phenomenon is well inhibited, even if part of ammonium bisulfate or ammonium chloride and other dust are adhered to the surface of the heat pipe, when compressed air or steam is adopted for blowing, the resistance of the compressed air or the steam between the heat pipe sets can be relatively small, and the compressed air or the steam can well blow through the space between the heat pipe sets, so that the surface of the heat pipe can be blown and cleaned conveniently, and the surface of the heat pipe can be kept clean for a relatively long time;

4) The arrangement of the connecting plate can also guide the air flow of the windward side of the downstream side heat absorption section in the two adjacent heat absorption sections, so that the flue gas can flow to the windward side of the downstream side heat absorption section more smoothly, and the wind resistance is favorably reduced.

Optionally, in the first long axis direction, the thickness of the connecting plate gradually increases from the middle region to the two end regions.

Optionally, the connecting plate is provided with balancing holes.

Optionally, in the same heat pipe set, a plurality of connecting plates are arranged between two adjacent heat absorbing sections, and each connecting plate is arranged at intervals in the axial direction of the heat absorbing section.

Optionally, a baffle is connected to each of the long shaft ends of the same heat pipe set, the most upstream and/or the most downstream of the long shaft ends.

Optionally, in the first long axis direction, the thickness of the flow guide plate gradually increases in a direction approaching the corresponding heat absorbing section.

Optionally, one heat absorbing section is provided with a plurality of baffles, and the baffles are arranged at intervals in the axial direction of the heat absorbing section.

Optionally, a cooling pipe is sleeved on the outer side of each heat release section, and a cooling medium is introduced into the cooling pipe.

Optionally, the heat releasing section and the cooling pipe are circular in cross section perpendicular to the axial direction.

Optionally, the cooling cavity includes a plurality of heat exchange chambers that are communicated with each other, a plurality of the heat release sections are arranged in each of the heat exchange chambers, and a cooling medium is introduced into each of the heat exchange chambers.

Optionally, the section of the heat releasing section perpendicular to the axial direction is also elliptical, and the heat releasing section has a second major axis direction, which is parallel to the flow direction of the cooling medium in the heat exchange chamber.

Optionally, each of the heat radiating sections is configured with a heat radiating fin.

Drawings

Fig. 1 is a schematic structural diagram of an embodiment of a heat pipe type heat exchanger provided by the present invention;

FIG. 2 isbase:Sub>A schematic view of the structure of FIG. 1 in the direction A-A;

FIG. 3 is a schematic view of the construction of the heat pipe set of FIG. 2;

FIG. 4 is a schematic structural view of the variant of FIG. 2;

FIG. 5 is a schematic view of the structure of FIG. 1 in the direction B-B;

fig. 6 is a schematic structural diagram of another embodiment of the heat pipe type heat exchanger according to the present invention;

FIG. 7 is a schematic view of the structure of FIG. 6 in the direction C-C;

FIG. 8 is a schematic structural view of the variant of FIG. 7;

fig. 9 is a schematic structural diagram of another embodiment of the heat pipe heat exchanger according to the present invention.

The reference numerals are explained below:

1 shell, 11 cooling side shell part, 111 cooling cavity, 111a heat exchange chamber, 111b inlet chamber, 111c outlet chamber, 111d reversing chamber, 112 inlet pipe, 113 outlet pipe, 12 smoke side shell part, 121 smoke cavity, 13 heat insulation section shell part and 131 heat insulation chamber;

2 heat pipe set, 21 heat pipes, 211 heat absorption section, 211a long shaft end, 212 heat release section, 22 connecting plate, 221 balance hole, 23 guide plate and 24 heat dissipation fin;

3, cooling the pipe;

4, communicating pipes;

5 a first partition plate;

6 a second separator.

Detailed Description

In order to make those skilled in the art better understand the technical solution of the present invention, the present invention is further described in detail with reference to the accompanying drawings and specific embodiments.

In the embodiments of the present invention, the terms "first" and "second" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature.

In the description of the embodiments of the present invention, it should be noted that the terms "mounted," "connected," and "connected" are to be construed broadly unless otherwise explicitly specified or limited, and for example, "connected" may or may not be detachably connected; may be directly connected or may be indirectly connected through an intermediate.

The directional terms used in the embodiments of the present invention, such as "upper", "lower", "inner", "outer", etc., are only directions referring to the drawings, and therefore, the directional terms used are intended to better and more clearly illustrate and understand the embodiments of the present invention, rather than to indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus, should not be construed as limiting the embodiments of the present invention. Further, unless stated otherwise herein, "a plurality" as referred to herein means two or more; and the use of "a number" when referring to the number of certain elements does not indicate a quantitative relationship between such elements.

In the description of the embodiments of the present invention, the terms "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such process, method, article, or apparatus. Without further limitation, an element defined by the phrase "comprising a … …" does not exclude the presence of another identical element in a process, method, article, or apparatus that comprises the element.

In the embodiment of the present invention, "and/or" is only an association relationship describing an associated object, and indicates that three relationships may exist, for example, a and/or B, and may indicate: a exists alone, A and B exist simultaneously, and B exists alone. In addition, the character "/" herein generally indicates that the former and latter related objects are in an "or" relationship.

Example one

Referring to fig. 1 to 5, fig. 1 isbase:Sub>A schematic structural diagram of an embodiment ofbase:Sub>A heat pipe type heat exchanger according to the present invention, fig. 2 isbase:Sub>A schematic structural diagram of fig. 1 inbase:Sub>A directionbase:Sub>A-base:Sub>A, fig. 3 isbase:Sub>A schematic structural diagram ofbase:Sub>A heat pipe group in fig. 2, fig. 4 isbase:Sub>A schematic structural diagram ofbase:Sub>A modification of fig. 2, and fig. 5 isbase:Sub>A schematic structural diagram of fig. 1 inbase:Sub>A direction B-B.

The utility model provides a heat pipe type heat exchanger, including casing 1 and a plurality of heat pipe group 2.

Referring to fig. 1, the casing 1 includes a cooling-side casing portion 11, a flue-gas-side casing portion 12, and a heat-insulating section casing portion 13, which are connected. Wherein, a cooling cavity 111 is formed in the cooling side shell part 11, and a cooling medium is introduced into the cooling cavity 111; a smoke cavity 121 is formed in the smoke side shell part 12, and smoke is introduced into the smoke cavity 121; the bottom plates of the heat insulation section shell part 13 and the cooling side shell part 11 and the top plate of the smoke side shell part 12 can enclose a heat insulation chamber 131, so that the cooling cavity 111 and the smoke cavity 121 can be isolated, and the top plate of the smoke side shell part 12 can be prevented from being corroded due to acid generated by smoke cooling.

The shapes of the cooling side shell portion 11, the flue gas side shell portion 12 and the heat insulating section shell portion 13 are not limited herein, and can be determined in combination with actual use requirements.

Each heat pipe set 2 comprises a plurality of heat pipes 21 which are sequentially arranged in the flowing direction of the flue gas, each heat pipe 21 comprises a heat absorption section 211 and a heat release section 212, and each heat pipe 21 is inserted in the heat insulation chamber 131. After the installation is completed, the heat absorbing section 211 is disposed in the flue gas chamber 121 and the heat releasing section 212 is disposed in the cooling chamber 111. The heat pipe 21 has a nearly zero leakage characteristic, and the cooling medium in the cooling cavity 111 can be basically prevented from leaking into the flue gas cavity 121 through indirect heat exchange.

The heat pipe 21 is filled with a working medium which can generate phase change, and in the flue gas cavity 121, the liquid working medium in the heat absorption section 211 can absorb the heat of the flue gas, so as to be gasified, thereby forming a gaseous working medium. The gaseous working medium can flow to the heat release section 212 and can release heat in the cooling cavity 111 to reform a liquid working medium, and then the liquid working medium can flow to the heat absorption section 211 to complete the working medium circulation. In the process of working medium circulation, the heat of the flue gas in the flue gas cavity 121 can be brought into the cooling cavity 111, the temperature of the flue gas can be reduced, the temperature of a cooling medium in the cooling cavity 111 can be increased, and the cooling and waste heat recovery of the flue gas can be realized.

With reference to fig. 2, a cross section of the heat absorbing section 211 perpendicular to the axial direction is an ellipse, the heat absorbing section 211 has a first major axis direction, and an end of the heat absorbing section 211 in the first major axis direction is a major axis end 211a, it should be understood that each heat absorbing section 211 includes two major axis ends 211a, respectively a windward end and a leeward end; the first long axis direction is parallel to the flow direction of the flue gas. Due to the arrangement, the whole heat absorption section 211 is in a streamline design, and the outer wall surface of the heat absorption section 211 is not easy to accumulate dust, so that the heat exchange efficiency of the heat absorption section 211 is ensured; in addition, the projection area (the flow resistance area to the flue gas) of the heat absorption section 211 in the flue gas flowing direction is relatively small, the flow resistance of the flue gas can be reduced, and the reduction of the energy consumption of the fan is facilitated.

Further, as shown in fig. 2 and 3, in the same heat pipe set 2, two adjacent long axis ends 211a of two adjacent heat absorbing sections 211 may be connected through a connecting plate 22; that is, in two adjacent heat absorption sections 211, the leeward end of the upstream heat absorption section 211 and the windward end of the adjacent downstream heat absorption section 211 can be connected by the connection plate 22.

By adopting the scheme, on one hand, the structural stability of the heat pipe set 2 can be improved, and the heat exchange area is increased; on the other hand, the arrangement of the connecting plate 22 is also beneficial to inhibiting the wake vortex phenomenon of the leeward side of the upstream side heat absorption section 211 in the two adjacent heat absorption sections 211, so that the flow distribution of the air flow between the heat exchange tube groups 2 can be relatively uniform, no obvious air flow compression-expansion process exists, a high-speed area can be basically eliminated, and the scouring of the dust-containing air flow on the heat tubes 21 can be further reduced; importantly, because the wake vortex phenomenon is well suppressed, even if part of dust such as ammonium bisulfate or ammonium chloride adheres to the surface of the heat pipe 21, when compressed air or steam is used for purging, the resistance of the compressed air or steam between the heat pipe sets 2 can be relatively small, and the compressed air or steam can well blow through the space between the heat pipe sets 2, so that the surface of the heat pipe 21 can be purged and cleaned conveniently, and the surface of the heat pipe 21 can be kept clean for a relatively long time.

In addition, the arrangement of the connecting plate 22 can also guide the airflow on the windward side of the downstream side heat absorption section 211 in the two adjacent heat absorption sections 211, so that the flue gas can flow to the windward side of the downstream side heat absorption section 211 more smoothly, and the wind resistance can be reduced.

Here, the embodiment of the present invention does not limit the structural form of the connecting plate 22, and in practical applications, those skilled in the art can set the connecting plate according to specific needs as long as the requirement of use can be satisfied.

In the embodiment of the drawings, as shown in fig. 3 and 4, the thickness of the connection plate 22 gradually increases from the middle region to the two end regions in the first long axis direction, that is, the connection plate 22 may adopt a structure form that the middle is thin and the two ends are thick. Therefore, on one hand, the characteristic that the heat flow of the section of the connecting plate 22 is gradually increased in the first long axis direction and the direction close to the corresponding heat absorption section 211 can be adapted, so that the heat exchange efficiency is favorably improved; on the other hand, the contact area between the connecting plate 22 and the heat absorbing section 211 can be increased, so that the heat resistance of the welding seam is reduced, and the connecting plate 22 is not easy to generate stress deformation after the welding is finished; meanwhile, the structural design in this form is also more favorable for forming a streamline structure between two adjacent heat absorbing sections 211.

It should be understood that the above description regarding the thickness of the connection plate 22 refers specifically to the dimension in the up-down direction in fig. 3/4.

Taking the orientation and position relationship shown in fig. 3 and 4 as an example, the thickness of the connecting plate 22 can be gradually changed by adjusting the structure of the upper wall and/or the lower wall of the connecting plate 22. Taking the above wall surface as an example, the upper wall surface may include two symmetrically arranged inclined surfaces, and both the two inclined surfaces may form an included angle with the first long axis direction; alternatively, the upper wall surface may include two smooth curved surfaces, such as an arc-shaped surface, which are symmetrically arranged.

In fact, it is also possible to use a constant thickness design for the connection plate 22, in addition to the above-described design with a gradually changing thickness.

With continued reference to fig. 1, the connecting plate 22 may further be provided with a balance hole 221 for balancing the pressure on both sides (in the thickness direction) of the connecting plate 22, so as to improve the operation stability of the heat pipe set 2 in the flue gas chamber 121 and facilitate the uniformity of the airflow distribution in the flue gas chamber 121.

Here, the embodiment of the present invention does not limit the number, shape and arrangement of the balance holes 221, and in practical applications, those skilled in the art may adjust the balance holes according to specific needs as long as the requirements of use can be met. In the embodiment of the drawings, as shown in fig. 1, the connecting plate 22 may be provided with a plurality of balancing holes 221, and each balancing hole 221 may be arranged at intervals in the extending direction (i.e., axial direction) of the heat absorbing section 211; the distance between the balance holes 221 may be 0.4m to 0.6m, or may be other values; each balance hole 221 may be a circular hole, a square hole, or a hole of another shape.

In some alternative embodiments, in the same heat pipe set 2, a plurality of connection plates 22 may be disposed between two adjacent heat absorption sections 211, and each connection plate 22 may be spaced in the axial direction of the heat absorption section 211. Thus, the axial dimension of each connecting plate 22 can be relatively small, the welding deformation is small, and the reliable connection between the connecting plate 22 and the heat absorbing section 211 can be easily ensured; moreover, the gap between two axially adjacent connecting plates 22 can also be used for balancing the pressure on the two sides of the connecting plates 22, so as to facilitate the improvement of the uniformity of airflow distribution in the flue gas chamber 121.

The length of the single connecting plate 22 is not limited herein, and in practical applications, a person skilled in the art may configure the connecting plate according to specific needs as long as the connecting plate can meet the requirements of use. For example, the length of the webs 22 may be between 1m and 1.5m, and the gap between two webs 22 may be approximately 1cm.

Further, of the long axis ends 211a of the same heat pipe group 2, the most upstream and/or the most downstream long axis end 211a may be connected with a baffle 23.

As shown in fig. 3, the guide plate 23 is connected to both the most upstream long axis end 211a and the most downstream long axis end 211 a. Therefore, the whole heat exchange group 2 can form a streamline structure of the guide plate 23+ the heat absorption section 211+ the connecting plate 22+ the heat absorption section 211+ the guide plate 23, so that the wind resistance can be greatly reduced, and the possibility of accumulating dust and the like on the surface of the heat exchange group 2 is reduced. Of the two guide plates 23, the most upstream guide plate 23 (the right guide plate 23) can increase the heat exchange area and guide the flue gas to the windward side of the most upstream heat absorption section 211, so as to realize the diversion and the guiding of the flue gas; the most downstream flow guide plate 23 (the left flow guide plate 23) can increase the heat exchange area, and can effectively inhibit the wake vortex phenomenon of the most downstream heat absorption section 211, so as to reduce the washing of the air flow to the heat absorption section 211, and can improve the permeability of the space between the heat pipe sets 2, so as to facilitate the purging of the surface of the heat absorption section 211.

In the first long axis direction, the thickness of the baffle 23 gradually increases in a direction approaching the corresponding heat absorbing section 211. Therefore, on one hand, the characteristic that the heat flow is gradually increased in the first long axis direction and the direction close to the corresponding heat absorption section 211 can be adapted, so that the heat exchange efficiency is favorably improved; on the other hand, the contact area between the guide plate 23 and the heat absorption section 211 can be increased, so that the heat resistance of the welding seam can be reduced, and the guide plate 23 is not easy to generate stress deformation after the welding is finished; meanwhile, the structural design in this form is also more favorable for forming a streamline structure in cooperation with the heat absorbing section 211.

Taking the orientation and position relationship in fig. 3 as an example, the gradual change of the thickness of the baffle 23 may be adjusted by the structural form of the upper wall surface and/or the lower wall surface of the baffle 23. Taking the above wall surface as an example, the upper wall surface may be an inclined surface disposed at an angle to the first long axis direction; alternatively, the upper wall surface may be a smooth curved surface, such as a curved surface.

It should be understood that the above-mentioned solution regarding the gradual thickness arrangement of the baffle 23 is only an exemplary illustration of the structure form of the baffle 23 of the embodiment of the present invention, and in a specific practice, the above-mentioned baffle 23 may actually adopt other structure forms, for example, the baffle 23 may also adopt an equal thickness design.

In some alternative embodiments, one heat absorbing section 211 may be configured with a plurality of baffles 23, and the baffles 23 may be spaced apart in the axial direction of the heat absorbing section 211. In this way, the axial dimension of each guide plate 23 can be relatively small, the welding deformation is small, and the reliable connection between the guide plate 23 and the heat absorption section 211 can be easily ensured; moreover, the gap between two axially adjacent guide plates 23 can also be used for balancing the pressure on the two sides of the guide plates 23, so as to facilitate the improvement of the uniformity of airflow distribution in the flue gas chamber 121.

The length of the single baffle 23 is not limited herein, and in practical applications, those skilled in the art can configure the baffle according to specific needs as long as the baffle can meet the requirements of use. For example, a single baffle 23 may be between 1m and 1.5m in length, and the gap between two baffles 23 may be approximately 1cm.

The number of heat pipes 21 included in each heat pipe set 2 is not limited herein, and in particular practice, the skilled person can adjust the number according to specific needs. In the embodiment of the figures, the heat pipe set 2 comprises two heat pipes 21, so that the size of each heat pipe set 2 in the flow direction of the flue gas can be relatively small, and the gap between two adjacent heat pipe sets 2 in the flow direction of the flue gas can also realize the pressure balance between the two sides of the heat pipe set 2 and facilitate the distribution of the flue gas in the flue gas cavity 121. Of course, the heat pipe set 2 may also include three or more heat pipes 21, which are all possible solutions in particular practice.

As shown in fig. 5, a plurality of cooling pipes 3 may be disposed in the cooling chamber 111, the cooling pipes 3 may be fitted around the heat radiating sections 212 in a one-to-one correspondence, and a cooling medium may be introduced between the cooling pipes 3 and the heat radiating sections 212 to exchange heat with the heat radiating sections 212. The cooling medium may specifically be water or the like.

In the scheme, the heat exchange of the cooling cavity 111 only occurs in the space between the cooling pipe 3 and the heat release section 212, and the airflow in other areas of the cooling cavity 111 does not flow, so that the heat dissipation loss in the cooling cavity 111 can be reduced, and the waste heat of the flue gas can be better recovered.

In practical application, the scheme is mainly applied to the situation that the pressure of the cooling medium is large, for example, the pressure of the cooling medium is more than 1 MPa.

The heat releasing section 212 may have a similar structure to the heat absorbing section 211, i.e., the heat releasing section 212 may be an elliptical tube, which is actually formed by pressing a circular tube. Alternatively, the heat releasing section 212 may be a circular tube, i.e. the heat releasing section 212 may not be pressed, so that the forming process of the heat pipe 21 may be relatively simple; in this case, the entire heat pipe 21 may further have a transition section between the heat absorbing section 211 and the heat releasing section 212, and the transition section may be disposed in the heat insulating section casing 13.

In the embodiment of the drawings, as shown in fig. 5, the sections of the heat releasing section 212 and the cooling pipe 3 perpendicular to the axial direction are both circular, and in this case, the heat exchange efficiency between the cooling medium and the heat releasing section 212 may be relatively high. Of course, the cross-sectional shape of the cooling pipe 3 is not limited to a circular shape, and other shapes of pipes, such as a square pipe, an oval pipe, etc., may be adopted.

The communicating pipe 4 can be disposed between the adjacent front and rear cooling pipes 3 to realize the communication of the cooling medium in each cooling pipe 3, and to facilitate the simplification of the pipe structure.

It should be emphasized, the embodiment of the present invention does not limit the application scenario of the heat pipe heat exchanger, and in practical application, those skilled in the art can set according to specific needs, as long as the cooling treatment and waste heat recovery for the flue gas can be satisfied. For example, the heat pipe type heat exchanger may be disposed on a flue between an outlet of the boiler air preheater and the dust remover, or may be disposed on a flue between the dust remover and the desulfurization apparatus.

Example two

Referring to fig. 6 to 8, fig. 6 is a schematic structural diagram of another embodiment of the heat pipe type heat exchanger according to the present invention, fig. 7 is a schematic structural diagram of fig. 6 in a direction C-C, and fig. 8 is a schematic structural diagram of a modification of fig. 7.

As shown in fig. 6, the present invention further provides another heat pipe type heat exchanger, compared to the first embodiment, the present embodiment mainly adjusts the structural form of the cooling cavity 111 and the heat releasing section 212, and the rest is consistent with the first embodiment, and repeated descriptions are not provided herein.

As shown in fig. 7 and 8, the cooling cavity 111 may be provided with a plurality of first partition plates 5, the first partition plates 5 may divide the interior of the cooling cavity 111 into a plurality of heat exchange chambers 111a, the heat exchange chambers 111a may be communicated, each heat exchange chamber 111a may be provided with a plurality of heat release sections 212, and each heat exchange chamber 111a may be filled with a cooling medium.

In the present embodiment, the flow of the cooling medium in each heat exchange chamber 111a is used to realize the heat exchange with the heat release section 212, which is different from the first embodiment. In practical applications, this solution is mainly used for the case of small pressure of the cooling medium, for example, the pressure of the cooling medium may be below 1 MPa.

In some alternative embodiments, the cross section of the heat release section 212 perpendicular to the axial direction may also be an ellipse, and thus, the heat release section 212 may have a second major axis direction, and the second major axis direction and the flow direction of the cooling medium in the heat exchange chamber 111a may be parallel. In this way, the flow resistance area of the heat release section 212 to the cooling medium can be smaller, the flow resistance of the cooling medium can be smaller, the heat exchange effect can be better, and the power for driving the cooling medium to flow can be smaller, which is beneficial to reducing the energy consumption of the pump.

The cooling cavity 111 may be divided into a plurality of flow paths according to the flow speed of the cooling medium in the cooling cavity 111, and the specific number of flow paths is not limited herein. As shown in fig. 7, the three-flow-path structure includes an inlet chamber 111b, an outlet chamber 111c and two direction-changing chambers 111d separated by the second partition plate 6, the inlet chamber 111b is connected to an inlet pipe 112, the outlet chamber 111c is connected to an outlet pipe 113, and the cooling medium entering from the inlet pipe 112 can be discharged from the outlet pipe 113 after being turned twice. As shown in fig. 8, in a two-pass structure including an inlet chamber 111b, an outlet chamber 111c and a direction change chamber 111d partitioned by the second partition plate 6, the inlet chamber 111b is connected to an inlet pipe 112, the outlet chamber 111c is connected to an outlet pipe 113, and a cooling medium introduced from the inlet pipe 112 can be discharged from the outlet pipe 113 after being once turned.

EXAMPLE III

Referring to fig. 9, fig. 9 is a schematic structural diagram of another embodiment of the heat pipe type heat exchanger according to the present invention.

As shown in fig. 9, the present invention further provides a heat pipe type heat exchanger, compared to the first embodiment, the present embodiment mainly adjusts the structural form of the cooling cavity 111 and the heat releasing section 212, and the rest of the embodiments are consistent with the first embodiment, and repeated description is not provided herein.

In the present embodiment, each heat releasing section 212 may be configured with a heat dissipating fin 24 to increase the heat exchanging area through the heat dissipating fin 24, thereby improving the heat exchanging efficiency; the heat dissipation fins 24 may be spiral steel fins, integrally rolled aluminum fins, or wound aluminum fins.

In this embodiment, air may be used for heat exchange in the cooling cavity 111, and the flow direction of the flue gas in the flue gas cavity 121 may be opposite to the flow direction of the air in the cooling cavity 111, so that the heat exchange effect can be further improved.

The foregoing is only a preferred embodiment of the present invention, and it should be noted that, for those skilled in the art, a plurality of improvements and decorations can be made without departing from the principle of the present invention, and these improvements and decorations should also be regarded as the protection scope of the present invention.

Claims (12)

1. A heat pipe type heat exchanger, comprising:

the device comprises a shell (1), wherein the shell (1) is provided with a cooling cavity (111) and a smoke cavity (121) which are isolated;

the heat pipe heat exchanger comprises a plurality of heat pipe sets (2), each heat pipe set (2) comprises a plurality of heat pipes (21) which are sequentially arranged in the flowing direction of smoke, each heat pipe (21) comprises a heat absorption section (211) and a heat release section (212), the heat absorption section (211) is located in a smoke cavity (121), the heat release section (212) is located in a cooling cavity (111), the cross section, perpendicular to the axial direction, of the heat absorption section (211) is oval, the heat absorption section (211) is provided with a first long axis direction, the end part, in the first long axis direction, of the heat absorption section (211) is a long axis end part (211 a), and the first long axis direction is parallel to the flowing direction of the smoke;

in the same heat pipe set (2), the end parts (211 a) of the long shafts of two adjacent heat absorbing sections (211) are connected through a connecting plate (22).

2. The heat pipe type heat exchanger as defined in claim 1, wherein the thickness of the connection plate (22) increases gradually from a middle area to both end areas in the first long axis direction.

3. The heat pipe type heat exchanger as defined in claim 1, wherein the connection plate (22) is provided with balancing holes (221).

4. The heat pipe type heat exchanger as defined in claim 1, wherein a plurality of the connecting plates (22) are arranged between adjacent heat absorbing sections (211) in the same heat pipe group (2), and the connecting plates (22) are arranged at intervals in an axial direction of the heat absorbing sections (211).

5. The heat pipe type heat exchanger as defined in claim 1, wherein a baffle (23) is connected to the most upstream and/or the most downstream of the major axis ends (211 a) of the same heat pipe group (2).

6. The heat pipe heat exchanger as defined in claim 5, wherein the thickness of the flow guide plate (23) in the direction of the first long axis increases gradually in a direction approaching the respective heat absorbing section (211).

7. The heat pipe type heat exchanger as defined in claim 5, wherein one heat absorbing section (211) is provided with a plurality of the baffles (23), the baffles (23) being arranged at intervals in an axial direction of the heat absorbing section (211).

8. The heatpipe type heat exchanger according to any one of claims 1-7, wherein a cooling pipe (3) is sleeved outside each heat releasing section (212), and a cooling medium is introduced into the cooling pipe (3).

9. The heat pipe heat exchanger according to claim 8, characterized in that the heat radiating section (212) and the cooling pipe (3) are circular in cross-section perpendicular to the axial direction.

10. The heat pipe type heat exchanger as defined in any one of claims 1-7, wherein the cooling chamber (111) comprises a plurality of interconnected heat exchange chambers (111 a), each heat exchange chamber (111 a) having a plurality of heat radiating sections (212) disposed therein, each heat exchange chamber (111 a) having a cooling medium communicated therein.

11. The heat pipe type heat exchanger as defined in claim 10, wherein the heat radiating section (212) is also elliptical in cross-section perpendicular to the axial direction, the heat radiating section (212) having a second major axis direction, the second major axis direction being parallel to the flow direction of the cooling medium in the heat exchange chamber (111 a).

12. The heat pipe type heat exchanger as defined in any one of claims 1-7, wherein each heat radiating section (212) is configured with heat radiating fins (24).

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