Plate heat exchanger with core plate with remarkable flow guide effect

Abstract

The invention relates to the field of engineering thermophysics, and provides a plate heat exchanger with a core plate with a remarkable flow guiding effect, the heat exchanger comprises a heat exchanger fluid inlet, a flow guiding area, a fluid main heat exchange area and a heat exchanger fluid outlet, the flow guiding area comprises a flow guiding groove area and a flow channel area, and the fluid main heat exchange area is arranged in the central area of the heat exchanger. Flow channel areas are arranged on the left side and the right side of the heat exchanger correspondingly. The heat exchanger fluid inlet and the heat exchanger fluid outlet communicate with the flow channel areas through the diversion trench areas. The diversion trench area comprises diversion trench top and bottom optimization areas, and the diversion trench top and bottom optimization areas are located on the top side of a fluid inlet of the heat exchanger and / or located on the top side and the bottom side of a fluid outlet of the heat exchanger. The flow channel area comprises a flow channel lower optimization area which is located on the lower side of the heat exchanger flow channel area. Therefore, the structure of the heat exchanger is improved, and the maximum non-uniform rate and the comprehensive flow non-uniform amplitude of heat exchange fluid flowing through the interior are both reduced. Finally, the purpose of more uniform flow distribution in the flow channel is achieved.

Description

Technical Field

[0001] This invention relates to the field of engineering thermophysics, specifically to widely used plate heat exchanger equipment. Background Technology

[0002] Plate heat exchangers, as compact and efficient heat exchange equipment, are widely used in centralized heating systems due to their advantages such as compact and lightweight structure, good heat transfer effect, large logarithmic mean temperature difference, strong interchangeability, flexible disassembly, convenient maintenance and cleaning, and low operating costs, thus achieving good economic benefits. Detachable plate heat exchangers are assembled from a series of parallel, corrugated thin metal plates, gaskets, clamping plates, clamping bolts, supports, and other components.

[0003] As the most important heat exchange element in plate heat exchangers, corrugated metal plates require a reasonable design structure to achieve better heat transfer, resistance characteristics, and pressure resistance. Typically, molds with different groove or corrugation patterns are manufactured according to user needs, and then plates of 0.5mm to 1.2mm thickness are cold-rolled to form the corresponding groove or corrugated plates. Adjacent plates do not directly contact each other, forming a corrugated curved channel with a flow spacing of approximately 2.5 to 12mm. The corrugation of commonly used plates is divided into two parts: a flow guiding zone, mainly for guiding the fluid to distribute evenly, and a heat exchange zone, mainly for heat exchange. Existing research shows that many plate heat exchangers exhibit significant non-uniformity in fluid flow and heat transfer. This non-uniform flow greatly affects the performance of plate heat exchangers, leading to obvious heat transfer "dead zones" on the opposite side of the inlet and outlet. The uneven distribution of fluid inside the heat exchanger is directly related to the structure of the flow guiding zone; an optimized flow guiding zone can reduce the area of ​​the heat transfer dead zone and ensure the heat transfer performance of the plate heat exchanger. Currently, the flow guiding area of ​​the plate is mainly made into strips or grids by pressing, and the depressions or protrusions formed by pressing play a role in guiding the flow.

[0004] A plate heat exchanger's corrugated plates consist of a fluid inlet, an inlet-side guide channel area, an inlet-side flow channel area, a main heat exchange area, an outlet-side flow channel area, an outlet-side guide channel area, and a fluid outlet. The guide channel area and the flow channel area are collectively referred to as the guide zone. Ensuring a more uniform flow distribution between the plates is crucial for improving the overall performance of the heat exchanger. Diagonal flow and single-sided flow are two common fluid flow patterns in plate heat exchanger plates. In industrial applications, single-sided flow is more commonly used to meet installation requirements. In single-sided flow plate heat exchangers, the uniformity of flow distribution between the heat exchange plates is a key indicator of the plate heat exchanger's performance. Summary of the Invention

[0005] To address the aforementioned problems, a heat exchanger is proposed that achieves more uniform flow distribution within the flow channels by altering the structural distribution of the flow guide groove region and the flow channel region, and by installing sealing strips in the flow channel region and the main heat exchange region. To achieve the above objectives, the technical solution adopted by this invention is as follows.

[0006] The present invention provides a heat exchanger, which includes a heat exchanger fluid inlet, a guide channel region, a flow channel region, a main fluid heat exchange zone, and a heat exchanger fluid outlet. The main fluid heat exchange zone is arranged in the central region of the heat exchanger, and flow channel regions are arranged on the left and right sides of the heat exchanger, respectively. The heat exchanger fluid inlet and the heat exchanger fluid outlet are both connected to the flow channel region through the guide channel region.

[0007] The present invention provides a heat exchanger with an optimized flow guide zone structure, further characterized in that: the heat exchanger flow guide zone region includes a top optimization zone, which is located on the top side of the heat exchanger fluid inlet and / or on the top side of the heat exchanger fluid outlet.

[0008] The present invention provides a heat exchanger with an optimized flow guide zone structure, further characterized in that: the flow guide zone region of the heat exchanger includes a bottom optimization zone, which is located on the bottom side of the fluid inlet of the heat exchanger and / or on the bottom side of the fluid outlet of the heat exchanger.

[0009] The present invention provides a heat exchanger with an optimized flow guide zone structure, further characterized in that: the flow channel region of the heat exchanger includes an optimized flow channel region, which is located at the 11th-14th flow channel position on the lower side of the flow channel region of the heat exchanger.

[0010] The present invention provides a heat exchanger with an optimized flow guide zone structure, further characterized in that: the heat exchanger includes a sealing plate, which penetrates the main heat exchange zone, is arranged parallel to the main flow direction of the fluid, passes through the flow channel region, is arranged parallel to the flow channel in the flow channel region, and is connected to the flow guide groove region.

[0011] Compared with the prior art, the beneficial effects of the present invention are as follows.

[0012] After the fluid flows through the inlet, it flows through the optimized guide channel area, which makes the fluid distribution in the flow channel area more uniform, effectively reducing the heat exchange dead zone in the heat exchange zone and improving the heat exchange efficiency.

[0013] The fluid flows through the optimized flow channel area, making the fluid flow distribution into the main heat exchange zone more uniform, thereby improving the heat exchange efficiency.

[0014] The optimized zone at the bottom of the guide channel increases the distance between the two guide channels, resulting in a lower pressure drop in the fluid inlet guide zone.

[0015] The flow channel optimization zone changes the curvature of the lower flow channel in the flow channel region, resulting in a lower pressure drop when the fluid flows through the guide zone. Attached Figure Description

[0016] The attached figure provides a schematic diagram of the optimized flow channel of the present invention, wherein... Figure 1 This is a schematic diagram of the optimized area at the top of the guide channel in the guide zone 2 of the heat exchanger of the present invention; Figure 2 This is a schematic diagram of the bottom optimization area of ​​the guide channel in the guide zone 2 of the heat exchanger of the present invention; Figure 3 This is a schematic diagram of the optimized lower flow channel in the flow channel region 2 of the heat exchanger of the present invention. Figure 4 A schematic diagram showing the heat exchanger of the present invention with the optimal number of sealing plates added; Figure 5 This is a schematic diagram of the top of the guide groove 21 in the heat exchanger guide zone 2 of the present invention at different angles; Figure 6 This is a schematic diagram showing different spacings at the bottom of the guide grooves in the guide zone 2 of the heat exchanger of the present invention; Figure 7 This is a schematic diagram showing different curvatures of the lower flow channel in the flow channel region 2 of the heat exchanger of the present invention. Figure 8 This is a schematic diagram showing the different positions and numbers of the added sealing plates in the heat exchanger of the present invention; Figure 9 This is an overall schematic diagram of the heat exchanger of the present invention;

[0017] The reference numerals in the accompanying drawings include the following.

[0018] 1. Heat exchanger fluid inlet; 2. Flow guiding zone; 21. Flow guiding channel area; 211. Top optimization zone of the flow guiding channel; 212. Bottom optimization zone of the flow guiding channel; 22. Flow channel area; 221. Flow channel area optimization zone; 3. Main heat exchange zone of the fluid; 4. Heat exchanger fluid outlet; 5. Sealing plate. Wherein, 1 and 4 are the fluid inlet and outlet corresponding to the same pipeline. Detailed Implementation

[0019] To make the objectives, technical solutions, and advantages of this technical solution clearer, the following detailed description, in conjunction with specific embodiments, further illustrates this technical solution. It should be understood that these descriptions are merely exemplary and not intended to limit the scope of this technical solution.

[0020] It should be noted that, unless otherwise specified, the embodiments and features described in the embodiments of this invention can be combined with each other. Regarding the heat exchange medium, the term "fluid" in this application mainly refers to high-temperature media and low-temperature media, indicating differences in heat transfer and heat absorption, rather than differences in the type of substance, to avoid misunderstandings.

[0021] For ease of explanation, the calculation methods for some of the quantities involved are given below. (1) Equivalent diameter De: In the formula, L w —Length of the cross-section where the flow guide zone meets the main heat exchange zone; h—width of the cross-section; b—distance between the two corrugated metal plates. (2) Reynolds number Re: Re = ρD e u / μ (2) (3) Flow deviation The flow module deviation can intuitively represent the non-uniformity of the average flow rate of the 14 small faces after the cross-section where the flow guide zone and the main heat exchange zone are evenly divided by area, and the average flow rate of the entire large cross-section, as shown in the following formula. δ i =(q i -q p ) / q p ×100% (3) In the formula, q i —Flow rate (kg / s) at the i-th cross-section; q p —Average flow rate (kg / s) across the entire cross-section. (4) Maximum non-uniformity ξ=δ max -δ min (4) (5) Flow distribution coefficient The flow distribution coefficient represents the ratio of the flow rate of each small section to the average flow rate of the entire large section, and can indicate the amount of flow rate distributed among the sections. K i =q i / q p (5) (6) Overall flow unevenness amplitude ΔK ξ =∑|(K) i -1.0)| / N (6) In the formula, N represents the number of small cross sections. The calculation of the maximum non-uniformity rate and the amplitude of the overall flow non-uniformity are based on the cross section perpendicular to the main flow direction of the fluid, which is located near the fluid inlet side of the guide zone and the main heat exchange zone. Example 1

[0022] like Figures 1-4As shown, this embodiment proposes a heat exchanger, including a heat exchanger fluid inlet 1, a flow guiding zone 2, a flow guiding groove region 21, a flow channel region 22, a main fluid heat exchange zone 3, and a heat exchanger fluid outlet 4. The main fluid heat exchange zone 3 is arranged in the central region of the heat exchanger, and the flow channel regions 22 are arranged on the left and right sides of the heat exchanger, respectively. The heat exchanger fluid inlet 1 and the heat exchanger fluid outlet 4 are both connected to the flow channel regions 22 through the flow guiding groove region 21.

[0023] In this embodiment, the central part of the heat exchanger is a rectangular main fluid heat exchange zone 3. Flow channel regions 22 are provided on both sides of the main fluid heat exchange zone 3. The flow channel regions 22 are generally isosceles triangles, with the longest side of the bottom of the flow channel region 22 matching the height direction of the main fluid heat exchange zone 3. A guide channel region 21 is formed between the upper side of the flow channel region 22 and the fluid inlet 1 of the heat exchanger. The above structure represents the structure between the fluid inlet 1 and the main fluid heat exchange zone 3. The structure between the main fluid heat exchange zone 3 and the fluid outlet 4 is a mirror image of the structure between the fluid inlet 1 and the main fluid heat exchange zone 3. That is, on one side of this heat exchanger, the heat exchanger is arranged in a mirror image with the center of the main fluid heat exchange zone 3 in the height direction as the symmetrical center.

[0024] In this embodiment, the fluid flows in from the heat exchanger fluid inlet 1, passes through the guide groove 21 area in the guide zone 2 and flows into the flow channel area 22. After being distributed in the flow channel area 22, the fluid flows into the main heat exchange zone 3 and undergoes heat exchange in the main heat exchange zone 3. The fluid flowing out of the main heat exchange zone 3 flows through the flow channel area 22, then flows into the guide groove area 21, and then flows out from the heat exchanger fluid outlet 4.

[0025] like Figure 1 As shown, the guide channel region 21 has several guide channels. Among the guide channels in the guide channel region 21 between the heat exchanger fluid inlet 1 and / or the heat exchanger fluid outlet 4 and the guide channel region 21, the top optimization region 211 of the guide channel is located on the upper side of the heat exchanger fluid inlet 1 and / or the heat exchanger fluid outlet 4 and the main heat exchange zone 3. The extension direction of the guide channel in the top optimization region 211 of the guide channel makes an angle of 60° with the width direction of the heat exchanger. The fluid Re in the guide channel in the top optimization region 211 of the guide channel is between 2488 and 12440, and the flow distribution is relatively uniform. The maximum non-uniformity rate and the comprehensive flow non-uniformity amplitude are 0.572 and 0.131, respectively, which are reduced by 34.9% and 5.7% compared with the original model.

[0026] like Figure 1 As shown, the upper flow channel in the flow channel region 22 of the flow guide zone 2 is shorter, resulting in low resistance and high cross-sectional velocity. By changing the angle of the top flow guide channel of the flow guide channel 21 in the flow guide zone 2 to 60°, the direction of the fluid entering the flow guide zone 2 is changed, causing more of the fluid to flow to the lower side of the flow guide zone 2, thereby improving the uneven fluid distribution phenomenon.

[0027] The maximum non-uniformity rate and the comprehensive flow non-uniformity amplitude under different angles between the extension direction of the guide channel and the width direction of the heat exchanger in the optimization zone 211 at the top of the guide channel are shown in Table 1. Table 1. Statistical table of inlet side index parameters for heat exchange zones of different models Example 2

[0028] like Figure 2 As shown in Example 1, based on the fact that the angle between the extension direction of the guide channel in the top optimization zone 211 of the guide channel and the width direction of the heat exchanger is 60°, in order to allow more fluid to flow to the lower side of the guide zone 2 and further improve the uneven fluid distribution, the area below the fluid inlet 1 and / or the fluid outlet 5 of the heat exchanger is the bottom optimization zone 212 of the guide channel. The interval of the guide channels in the bottom optimization zone 212 of the guide channel is 15mm, the flow distribution is more uniform, and the maximum non-uniformity rate and the comprehensive flow non-uniformity amplitude are 0.522 and 0.122, respectively, which are reduced by 40.5% and 12.23% compared with the original model.

[0029] The maximum non-uniformity rate and the comprehensive flow non-uniformity amplitude of the guide channel at different intervals in the bottom optimization zone 212 of the guide channel are shown in Table 2. Table 2. Statistical table of inlet side index parameters for heat exchange zones of different models Example 3

[0030] like Figure 3 As shown, based on Example 1, the flow channel region 22 has several flow channels. To shorten the length of the 11th-14th flow channels on the lower side of the flow channel region in the guide zone 2, the angle of the 11th-14th flow channels on the lower side is increased to guide more fluid to flow to the lower flow channels and improve the uneven fluid distribution. The three sets of flow channels in the optimized region 221 on the lower side of the flow channel region are straight-through channels, and these channels are parallel to the other flow channels in the flow channel region 22. The flow channel region 22 has 14 flow channels. The maximum non-uniformity rate of the heat exchange fluid and the comprehensive flow non-uniformity amplitude in the flow channel region 22 are 0.397 and 0.100, respectively, which are reduced by 54.8% and 28.1% compared with the original model.

[0031] The maximum non-uniformity rate and comprehensive flow non-uniformity amplitude of the three groups of flow channels in the optimized region 221 on the lower side of the flow channel under different curvatures are shown in Table 3. Example 4

[0032] like Figure 4As shown, to improve the fluid splitting phenomenon between flow channels in the flow channel region 22 of the guide zone 2, the heat exchanger has three sealing plates 5 on its front and / or back sides. These three sealing plates 5 are horizontally arranged within the main fluid heat exchange zone 3, dividing it into four equal areas. Each sealing plate 5 extends obliquely upwards parallel to the flow channel at both ends of the main fluid heat exchange zone 3 to the guide channel region 21. On the same side of the main fluid heat exchange zone 3, each sealing plate 5 is arranged parallel to each other in the flow channel region 22. The best effect was observed with three sealing plates, resulting in a maximum non-uniformity rate and a combined flow non-uniformity amplitude of 0.612 and 0.108, respectively, representing reductions of 30.3% and 22.3% compared to the original model. Table 3. Statistical table of inlet side index parameters for heat exchange zones of different models

[0033] Table 4 shows the maximum non-uniformity rate and the amplitude of the overall flow non-uniformity after installing different numbers of sealing plates at different locations in the corrugated metal guide zone 2 and the main heat exchange zone 3. Table 4. Inlet-side index parameters of heat exchange zones for different models

[0034] This heat exchanger alters its structure through various means, such as changing the angle and length of the upper and lower guide channels at the fluid inlet 1 and fluid outlet 4, and changing the number of seals added between the plates. This greatly reduces the maximum non-uniformity rate and the overall flow non-uniformity amplitude of the internal heat exchange fluid.

[0035] The above content is only a preferred embodiment of the present invention. For those skilled in the art, many changes can be made in the specific implementation and application scope based on the ideas of the present invention. As long as these changes do not depart from the concept of the present invention, they all fall within the protection scope of this patent.

Claims

1. A plate heat exchanger with a core plate having a significant flow-guiding effect, characterized in that: It includes a heat exchanger fluid inlet, a guide channel area, a flow channel area, a main fluid heat exchange zone, and a heat exchanger fluid outlet; the main fluid heat exchange zone is arranged in the central area of ​​the heat exchanger, and the flow channel areas are arranged on the left and right sides of the heat exchanger respectively. The heat exchanger fluid inlet and the heat exchanger fluid outlet are both connected to the flow channel areas through the guide channel area.

2. The guide channel region includes a top optimization area of ​​the guide channel, which is located on the top side of the heat exchanger fluid inlet and / or on the top side of the heat exchanger fluid outlet.

3. The heat exchanger according to claim 1, characterized in that: The angle between the extension direction of the guide channel in the top optimization area of ​​the guide channel and the width direction of the heat exchanger is an acute angle.

4. The heat exchanger according to claim 2, characterized in that: The angle between the extension direction of the guide channel in the top optimization area of ​​the guide channel and the width direction of the heat exchanger is 60°.

5. The heat exchanger according to claim 1, characterized in that: The Reynolds number of the guide channel in the top optimization zone of the guide channel is within a first set value range; the first set value range includes a value range of 2488-12440.

6. The heat exchanger according to claim 1, characterized in that: The guide channel area also includes a guide channel bottom optimization area, which is located on the bottom side of the heat exchanger fluid inlet and / or on the bottom side of the heat exchanger fluid outlet.

7. The heat exchanger according to claim 1, characterized in that: The spacing between the guide channels in the bottom optimization area of ​​the guide channel is a second set value range, which includes a value of 15mm.

8. The heat exchanger according to claim 1, characterized in that: The flow channel region includes several parallel straight channels, which are parallel to each other.

9. The heat exchanger according to claim 1, characterized in that: It includes several sealing plates; the several sealing plates are arranged in the main heat exchange zone of the fluid, dividing the main heat exchange zone of the fluid into areas of equal area, and the several sealing plates extend to the guide groove area.

10. The heat exchanger according to claim 8, characterized in that: The sealing plates are arranged in parallel in the main heat exchange zone of the fluid.

11. The heat exchanger according to claim 1, characterized in that: Change the curvature of the last 11-14 flow channels on the lower left side of the fluid inlet in the guide zone to 180°.

12. A method for improving the efficiency of a heat exchanger, characterized in that: By changing the maximum non-uniformity rate and the overall flow non-uniformity amplitude of the fluid after it flows from the inlet through the guide zone, the flow distribution of the fluid entering the main heat exchange zone is made more uniform, thereby improving the efficiency of the heat exchanger.

13. A thermal management method / structure for a heat exchanger, characterized in that... Heat management: a. The sealing plate runs through the main heat exchange zone, is arranged parallel to the main flow direction of the fluid, and passes through the flow channel area 22, is arranged parallel to the flow channel in the flow channel area, and is connected to the flow guide groove area in the flow guide area; b. The sealing plate according to claim a is made of ordinary rubber material, and its surface is rolled to increase the heat exchange area, thereby increasing heat exchange and scientifically managing heat exchange.

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