CN218480949U - Heat exchanger core and printed circuit board type heat exchanger comprising same - Google Patents

Abstract

The utility model provides a heat exchanger core body and a printed circuit board type heat exchanger including the core body. The heat exchanger core includes a first plate and a second plate, a first working medium channel is formed between the first plate and the second plate, and the first plate faces the second The lower surface of the plate forms a part of the first working medium channel, and the upper surface of the second plate facing the first plate forms another part of the first working medium channel. The utility model obtains the working medium channel by arranging a part of the working medium channel on two different plates, and then combining the two different plates, which makes the inside of the working medium channel easier to clean and reduces the possibility of channel blockage .

Description

Heat exchanger core and printed circuit board heat exchanger including same

technical field

The utility model relates to a core body of a heat exchanger, in particular to a core body of the heat exchanger suitable for high-viscosity and low-velocity fluid and a printed circuit board type heat exchanger including the core body of the heat exchanger.

Background technique

The printed circuit board heat exchanger is a compact plate heat exchanger formed by splicing multi-layer microchannel plates using diffusion welding technology. Its core heat exchange component is a heat exchange core with a porous structure with a channel diameter of about 1-2mm. Body, with high compactness, high pressure resistance, high temperature resistance, corrosion resistance and high stability and safety, has been widely used in chemical industry, refrigeration and air conditioning, oil and gas and other fields, but the diameter of the fluid channel is small ( About 1-2mm), the technical problem of channel blockage cannot be avoided. This problem is even more difficult to overcome for molten salt working fluid, because molten salt may carry suspended matter after long-term service, which is more likely to cause blockage of microchannels. On the one hand, such a large number of fluid channels leads to a low flow rate of molten salt in a single channel. At the same time, in order to avoid clogging of molten salt, the flow area needs to be increased, which makes the originally low molten salt The flow rate will become lower, and the reduction in flow rate will result in a decrease in the heat transfer coefficient of the molten salt and a greatly reduced heat transfer capability of the heat exchanger. On the other hand, for high-viscosity fluids, compared with traditional working fluids, the Prandtl number is higher, and there is a thinner thermal viscous bottom layer near the wall, and the heat transfer process of the fluid to the outside of the tube is greatly hindered at low flow rates. .

Utility model content

The technical problem to be solved by the utility model is to overcome the defect that the channel of the core body of the heat exchanger is easily blocked in the prior art, and to provide a heat exchanger that is easy to clean, has low channel blockage rate, better heat transfer performance, and wider application range. Heat exchanger core.

The utility model solves the problems of the technologies described above through the following technical solutions:

A heat exchanger core, which includes a first plate and a second plate, a first working medium channel is formed between the first plate and the second plate, and the first plate faces the The lower surface of the second plate forms a part of the first working medium channel, and the upper surface of the second plate facing the first plate forms another part of the first working medium channel.

In this solution, the above-mentioned structure is adopted, and a part of the first working medium channel is respectively set on the lower surface of the first plate and the upper surface of the second plate, and the first working medium channel is located between the lower surface of the first plate and the upper surface of the second plate. Formed between the upper surfaces of the two plates, by setting a part of the first working medium channel on different plates, and then combining two different plates to form the first working medium channel, this combination forms the first working medium channel , By separating the two plates, the inner wall of the channel can be effectively cleaned, which makes the cleaning of the channel more convenient and reduces the clogging rate of the working medium channel.

Preferably, the lower surface of the first plate or the upper surface of the second plate forms a part of the first working medium channel by etching or machining, and the first plate and the The second sheet is joined by diffusion welding.

In this solution, the above-mentioned structure is used to form a part of the working medium channel by etching or machining, which can meet the requirements of forming a part of the first working medium channel on the first plate and the second plate, and can be arbitrary according to requirements. Change, less costly.

Preferably, the cross-sectional shape of the first working medium channel is rhombus, polygon, rectangle, circle, semi-ellipse or ellipse.

In this solution, by adopting the above-mentioned structure, different working requirements can be met by setting the cross section of the first working medium channel into different shapes.

Preferably, the inner wall of the first working medium channel is provided with a plurality of radially inwardly protruding annular protrusions, and the plurality of annular protrusions are arranged along the extending direction of the working medium channel.

In this solution, the above-mentioned structure is adopted, and the annular protrusion is provided on the inner wall of the first working medium channel, which enhances the radial turbulence of the fluid, and at the same time increases the scouring of the wall surface by the fluid.

Preferably, the heat exchanger core further includes a third plate, the third plate is arranged above the second plate, and a second plate is formed between the third plate and the second plate. Two working medium channels, the upper surface of the third plate facing the second plate forms a part of the second working medium channel, the second plate facing the lower surface of the third plate Another part of the second working medium channel is formed.

In this solution, by adopting the above structure, by arranging a part of the working medium channel on the upper and lower surfaces of the second plate, the working medium channel on the upper surface of the second plate and the working medium channel on the lower surface can overlap in the vertical direction, In this way, the core body of the heat exchanger can form more channels of working fluid under the same volume, which improves the compactness of the core body of the heat exchanger.

Preferably, the horizontal arrangement of the first working medium channel and the second working medium channel is sequential, staggered or obliquely intersecting.

Preferably, the flow shape of the first working medium channel is a stripe type, a fin type, a corrugation type or a spiral groove type.

In this solution, adopting the above-mentioned structure can make the distribution of cores more flexible and reasonably match various application scenarios.

Preferably, a plurality of the first working medium channels are arranged in parallel and equidistant.

In this solution, the above-mentioned structure is adopted, so that the fluid can pass through the working medium channel uniformly, and the mutual influence between the two channels is avoided.

Preferably, the first working medium channel includes a high temperature working medium channel and a low temperature working medium channel; there is at least one low temperature single channel between two adjacent high temperature single channels, or at least one high temperature single channel between two low temperature channels.

In this solution, the above-mentioned structure is adopted to better improve the heat exchange effect of the heat exchanger core.

The utility model also provides a printed circuit board heat exchanger, and the printed circuit board heat exchanger includes at least one heat exchanger core as described above.

The positive progressive effect of the present utility model is:

(1) Effectively improve channel blockage, prevent dirt formation, and reduce pollution risk. On the one hand, due to the combined flow channel formed by the symmetrical connection of the plates, the cross-section can be made larger, and the molten salt is less likely to be blocked. On the other hand, due to the periodic change of the section of the tube-fin channel, the fluid in the tube is always in a regular disturbance state, which increases the radial flow of the fluid in the tube, promotes the turbulent flow intensity of the high-viscosity fluid, and makes the fluid impurities, etc. The distribution is more uniform, which not only makes it difficult for foreign particles to attach in the fluid channels, but also radically reduces the possibility of fouling of the heat exchanger.

(2) Enhance heat transfer performance. Due to the inwardly expanding annular protrusions on the inner wall of the tube-fin channel, the high-viscosity fluid is affected by the protrusions to form an axial vortex when flowing in the tube, which improves the turbulent flow intensity of the fluid and increases the disturbance of the fluid boundary layer. It is conducive to the thinning of the boundary layer thickness, and is conducive to the reduction of the thermal resistance of the boundary layer and the transfer of heat through the boundary layer, which greatly improves the heat transfer coefficient. When the vortex passes through a protrusion and is about to disappear, the fluid will flow through the next inner wall protrusion, so that the axial vortex is continuously generated in this way, so that the fluid maintains a continuous and stable strengthening effect in the tube-fin channel. Compared with the smooth wall channel structure, the heat transfer coefficient of the tube-fin structure flow channel for high-viscosity fluid provided by the utility model can be increased by 2.3-2.8 times at low flow velocity (Re<2300).

(3) Higher compactness. Different from the traditional PCHE single-sided etching channel, the structural plate is etched on both sides, and the hot and cold channels are combined by two-sided channels, which saves the thickness of the partition of the traditional plate, reduces the core volume to a certain extent, and improves the equipment. At the same time, compared with the traditional PCHE core structure with the same thickness and tube spacing, the PCHE core structure also increases the heat transfer area.

(4) The distribution of cores is more flexible and can reasonably match various application scenarios. It can flexibly assemble different flow channel forms (such as: horizontal grain type, fin type, corrugated type, spiral groove type, etc.), and can also freely combine different flow channel cross-sectional shapes (triangular, trapezoidal, rectangular, semicircular, any of semi-ellipse, ellipse or profile). At the same time, in order to match different working fluid characteristics and different heat transfer requirements, parameters can be flexibly set, such as: channel number ratio, diameter ratio, plate arrangement form, flow channel stacking method, etc.

(5) A wide range of applications, the form of the combined flow channel and the resulting large heat transfer wall between the hot and cold channels, on the one hand, can reduce thermal stress and mechanical stress, on the other hand, it is more suitable for large temperature differences, Severe working conditions such as large pressure difference. This is not only suitable for high-temperature application scenarios such as molten salt reactors and molten salt heat storage, but also has good application prospects for comprehensive utilization of new energy such as solar thermal power generation, advanced Brayton cycle power generation, and high-temperature hydrogen production.

(6) Better economic performance and safety stability, because the manufacturing technology of this structure is relatively simpler than that of airfoil and S-shaped plates, and the manufacturing cost can be reduced accordingly; in addition, due to the anti-blocking, anti-scaling and anti-fouling Strong capacity greatly reduces the risk of high-viscosity fluid blockage, corresponding maintenance costs are reduced, and equipment failure rates are also reduced, which provides a strong guarantee for the safe and stable operation of fourth-generation reactors, power generation and energy storage systems.

Description of drawings

Fig. 1 is a schematic cross-sectional structure diagram of a heat exchanger core in a preferred embodiment of the present invention.

Fig. 2 is a schematic perspective view of the three-dimensional structure of the heat exchanger core in a preferred embodiment of the present invention.

Fig. 3A is a schematic diagram of an axial cross-sectional structure of a first working medium channel of a stripe type in a preferred embodiment of the present invention.

Fig. 3B is a schematic diagram of an axial cross-sectional structure of a fin-shaped first working medium channel in a preferred embodiment of the present invention.

Fig. 3C is a schematic diagram of an axial cross-sectional structure of a corrugated first working medium channel in a preferred embodiment of the present invention.

Fig. 3D is a schematic diagram of the axial cross-sectional structure of the first working medium channel of the spiral groove type in a preferred embodiment of the present invention.

Fig. 4A is a schematic cross-sectional view of a diamond-shaped first working medium channel in a preferred embodiment of the present invention.

Fig. 4B is a schematic cross-sectional view of a polygonal first working medium channel in a preferred embodiment of the present invention.

Fig. 4C is a schematic cross-sectional view of a rectangular first working medium channel in a preferred embodiment of the present invention.

Fig. 4D is a schematic cross-sectional view of a circular first working medium channel in a preferred embodiment of the present invention.

Fig. 4E is a schematic cross-sectional view of a semi-elliptical first working medium channel in a preferred embodiment of the present invention.

Fig. 4F is a schematic cross-sectional view of an elliptical first working medium channel in a preferred embodiment of the present invention.

Explanation of reference signs:

Heat exchanger core 100

First plate 110

Second plate 120

The first working medium channel 130

Annular protrusion 131

third plate 140

Second working medium channel 150

Detailed ways

The utility model is further illustrated below by means of examples, but the utility model is not limited to the scope of the examples.

As shown in Figure 1 and Figure 2, this embodiment provides a heat exchanger core 100, the heat exchanger core 100 includes a first plate 110 and a second plate 120, the first plate 110 and the second plate 120 A first working medium channel 130 is formed between the second plates 120, the lower surface of the first plate 110 facing the second plate 120 forms a part of the first working medium channel 130, and the second The upper surface of the plate 120 facing the first plate 110 forms another part of the first working medium channel 130 . The lower surface of the first plate 110 or the upper surface of the second plate 120 forms a part of the first working medium channel 130 by etching or machining, and the first plate 110 and the The second plate 120 is connected by diffusion welding.

Specifically, the heat exchanger is mainly two fluids with different temperatures flowing in the space separated by the wall, through the heat conduction of the wall and the convection of the fluid on the surface of the wall, heat exchange is performed between the two fluids. Among them, the heat exchange core 100 having a porous structure with a channel diameter of about 1-2 mm is the core component of the heat exchanger. Since the channel diameter is only 1-2 mm, it will inevitably cause channel blockage, especially for molten salt working fluids. is insurmountable. In the present utility model, the upper surface of the first plate 110 and the lower surface of the second plate 120 are processed by etching or machining to form a part of the first working medium channel 130, and then the first plate 110 is The connection with the second plate 120 by diffusion welding technology, then a part of the working medium channel formed by the upper surface of the first plate 110 and the lower surface of the second plate 120 forms the first working medium channel 130, which can be passed through Disassemble the plate to achieve a better cleaning effect on the working medium channel and reduce the channel blockage rate of the working medium channel. At the same time, the combination of the first plate 110 and the second plate 120 to form the first working medium channel 130 also reduces thermal stress and mechanical stress, so that the heat exchanger core 100 can be applied to severe conditions such as large temperature difference and large pressure difference. harsh working conditions. The diameter of the first working fluid channel 130 is not limited to a specific size, and its diameter can be adjusted according to the working requirements. In this embodiment, each plate only forms half of the first working medium channel, but the utility model is not limited thereto, and the technicians of the utility model can form the first working fluid channel on the first plate as required. One-third, one-fourth, etc. of the working medium channel.

In this embodiment, the cross-sectional shape of the first working fluid channel 130 is a rhombus, polygon, rectangle, circle, semi-ellipse or ellipse, and Figures 4A, 4B, 4C, 4D, 4E, and 4F represent rhombus, polygon , rectangular, circular, semi-elliptical and elliptical cross-sectional views of the first working medium channel 130, by adjusting the cross-sectional shape of the working medium channel, the heat exchanger core can match various application scenarios, so that the entire core body Allocation is also more flexible.

In this embodiment, the heat exchanger core 100 further includes a third plate 140, the third plate 140 is arranged above the first plate 110, the third plate 140 and the first plate 110 forms a second working medium channel 150, the lower surface of the third plate 140 facing the first plate 110 forms a part of the second working medium channel 150, the first plate 110 faces Another part of the second working medium channel 150 is formed on the upper surface of the third plate 140 . As shown in Fig. 1 and Fig. 2, only a core body composed of three plates is illustrated, but the utility model is not limited thereto. The core body of the present utility model can comprise more than three plates, and a plurality of plates are superimposed on each other in the manner shown in FIG. A part of the channel of the working fluid is formed to form a complete core, and the upper surface of the uppermost plate and the lower surface of the lowermost plate do not need to etch channels. By forming a part corresponding to the channel on the upper and lower surfaces of each plate of the plate in the middle, such as the second plate 120, etc., more working medium channels can be formed under the same volume, which improves the efficiency of the equipment. The compactness also increases the heat transfer area. At the same time, the connection between such plates is relatively simple, and the manufacturing cost is correspondingly reduced. In addition to the linear structure shown in Figure 2, the working medium channel can also be a Z-shaped, S-shaped or streamlined structure.

In this embodiment, as shown in FIG. 2 , the inner wall of the first working medium channel 130 is provided with a plurality of annular protrusions 131 protruding radially inward, and the plurality of annular protrusions 131 are along the The extension direction of the working medium channel is set. For example, annular projections 131 are provided in each working medium channel in the first working medium channel 130, and these annular projections 131 make the high-viscosity fluid flow in the working medium channel affected by the projections to form an axial vortex, The turbulence intensity of the fluid is improved, and the disturbance of the fluid boundary layer is increased, which is not only beneficial to the thinning of the boundary layer thickness, but also beneficial to the reduction of the thermal resistance of the boundary layer and the transfer of heat through the boundary layer, which greatly improves the heat transfer coefficient. When the vortex passes through a protrusion and is about to disappear, the fluid will flow through the next annular protrusion 131 , so that the axial vortex is continuously generated in such a reciprocating manner, so that the fluid maintains a continuous and stable strengthening effect in the working medium channel. The existence of the ring-shaped protrusion will enhance the radial turbulence capacity in the working medium channel, and the anti-scale and anti-fouling capabilities in the working medium channel will also be correspondingly enhanced, the risk of fluid blockage will be correspondingly reduced, and the failure rate of the equipment will be reduced accordingly. It will also be reduced, which enhances the economic performance and safety and stability of the heat exchanger core 100 .

In this embodiment, the flow shape of the first working fluid channel 130 is a ribbed, finned, corrugated or spiral fluted. Since many annular protrusions 131 are arranged along the extending direction of the working medium channel, and the annular protrusions 131 protrude toward the inner surface of the working medium channel, a concave-convex structure will be formed on the outer surface of the working medium channel, The different aspect ratios of the ring-shaped protrusions will form the flow channel forms of stripes, fins, corrugations or spiral grooves as shown in Figures 3A, 3B, 3C and 3D. These ring-shaped protrusions protrude inward, and then fins are formed on the outer surface of the working fluid passage, specifically, the fins are formed because the ring-shaped protrusions 131 protrude inward. The working medium channel has fins, which can further improve the heat exchange efficiency, and at the same time, the anti-blocking and anti-fouling ability is also stronger. In this embodiment, according to different working conditions, the fin type, that is, the aspect ratio of the annular protrusion, can be flexibly adjusted to meet different working condition requirements.

In this embodiment, a plurality of the first working medium channels 130 are arranged in parallel and equidistant, and the horizontal arrangement of the first working medium channels 130 and the second working medium channels 150 is sequence, staggered column or slanted cross. The central axes of the second working medium channel 150 and the first working medium channel 130 are in two different planes, and the mutual arrangement of the second working medium channel 150 and the first working medium channel 130 has no influence on the passage of fluid, so The first working medium channel 130 and the second working medium channel 150 can be parallel to each other in the horizontal direction, that is, a sequential arrangement as shown in Figure 2 is formed, and the first working medium channel 130 and the second working medium channel 150 can also be Instead of being arranged in one direction, the first working medium channel 130 and the second working medium channel 150 may intersect each other in the horizontal direction, that is, form an obliquely intersecting arrangement. In addition, the first working medium channel 130 and the second working medium channel The mass channels 150 neither cross each other nor parallel to each other in the horizontal direction, that is, form a staggered arrangement.

The first plate 110 forms part of one or more working medium channels. In this embodiment, the first plate 110 forms part of multiple first working medium channels 130 and second working medium channels 150 . A plurality of the first working medium channels 130 are arranged in parallel and equidistant. Specifically, the first plate 110 does not only form a part of a working medium channel, and the second plate 120 also not only forms another part of a working medium channel, thus the first plate 110 and the second plate 120 connection will form a plurality of the first working medium channel 130 as shown in Figure 1 and Figure 2, the first working medium channel 130 and the first working medium channel formed between the first plate 110 and the second plate 120 The distances between the mass channels 130 are equal.

In this embodiment, the first working medium channel 130 includes a high temperature working medium channel and a low temperature working medium channel; there is at least one low temperature single channel between two adjacent high temperature single channels, or there is at least one high temperature single channel between two low temperature channels. single channel. By dividing the working medium channel into a high temperature working medium channel and a low temperature working medium channel, the heat exchange effect of the heat exchanger core is better improved. The quantity ratio of the high-temperature working medium channel and the low-temperature working medium channel can be adjusted according to different work requirements. Setting the high-temperature working medium channel and the low-temperature working medium channel improves the efficiency of heat exchange, but it does not limit the fluid passing through the high-temperature working medium channel and the low-temperature working medium channel, that is, both the high-temperature working medium channel and the low-temperature working medium channel can pass through high-temperature fluid and cryogenic fluid. In addition, the diameter ratio of the working fluid channel is not limited, and the diameter ratio of the working fluid channel can be adjusted differently under different working conditions.

It should be understood by those skilled in the art that this embodiment only illustrates the situation of three plates superimposed, but the utility model is not limited thereto, and the number of plates in the utility model can be set according to actual needs.

This embodiment also provides a printed circuit board heat exchanger, and the printed circuit board includes the above-mentioned heat exchanger core.

In describing the present invention, it should be understood that the terms "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top" , "bottom", "inner", "outer" and other indicated orientations or positional relationships are based on the orientations or positional relationships shown in the drawings, and are only for the convenience of describing the utility model and simplifying the description, rather than indicating or implying Any device or element must have a specific orientation, be constructed and operate in a specific orientation, and thus should not be construed as limiting the invention.

Although the specific implementation of the utility model has been described above, those skilled in the art should understand that this is only an example, and the protection scope of the utility model is defined by the appended claims. Those skilled in the art can make various changes or modifications to these embodiments without departing from the principle and essence of the present utility model, but these changes and modifications all fall within the protection scope of the present utility model.

Claims (10)

1. The heat exchanger core is characterized by comprising a first plate and a second plate, wherein a first working medium channel is formed between the first plate and the second plate, the lower surface of the first plate facing the second plate forms one part of the first working medium channel, and the upper surface of the second plate facing the first plate forms the other part of the first working medium channel.

2. The heat exchanger core of claim 1, wherein the lower surface of the first plate or the upper surface of the second plate forms a portion of the first working fluid passage by etching or machining, and the first plate and the second plate are joined by diffusion welding.

3. The heat exchanger core of claim 1, wherein the cross-sectional shape of the first working fluid passage is diamond-shaped, polygonal, rectangular, circular, semi-elliptical, or elliptical.

4. The heat exchanger core according to claim 1, wherein the inner wall of the first working medium channel is provided with a plurality of annular projections projecting radially inwards, and the plurality of annular projections are arranged along the extension direction of the working medium channel.

5. The heat exchanger core of claim 1, further comprising a third plate disposed above the second plate, wherein a second working medium passage is formed between the third plate and the second plate, wherein an upper surface of the third plate facing the second plate forms a portion of the second working medium passage, and a lower surface of the second plate facing the third plate forms another portion of the second working medium passage.

6. The heat exchanger core of claim 5, wherein the first working medium passages and the second working medium passages are arranged in a sequential, staggered or oblique crossing manner in the horizontal direction.

7. The heat exchanger core according to claim 1, wherein the flow pattern of the first working fluid channel is a cross-hatched pattern, a finned pattern, a corrugated pattern or a spiral-grooved pattern.

8. The heat exchanger core of claim 1, wherein a plurality of said first working fluid passages are arranged in parallel and equidistant.

9. The heat exchanger core of claim 1, wherein the first working fluid passage comprises a high temperature working fluid passage and a low temperature working fluid passage; at least one low-temperature working medium channel is arranged between two adjacent high-temperature working medium channels, or at least one high-temperature working medium channel is arranged between two low-temperature working medium channels.

10. A printed circuit board heat exchanger, characterized in that the printed circuit board comprises a heat exchanger core according to any of claims 1-9.

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