A plate heat exchanger with asymmetric channels
By setting grooves on the first plate valley of the plate heat exchanger, asymmetric channels are formed and welding area is increased, the problem of difficult to take into account both the heat exchange performance and the pressure bearing effect is solved, and more efficient heat exchange and stronger pressure bearing capacity are achieved.
Patent Information
- Application Number
- CN202010206928.0
- Authority / Receiving Office
- CN · China
- Patent Type
- Patents(China)
- Current Assignee / Owner
- Filing Date
- 2020-03-23
- Publication Date
- 2025-04-25
- Estimated Expiration
- 2040-03-23
Smart Images
Figure CN111271996B_ABST
Abstract
Description
Technical Field
[0001] The invention relates to the technical field of heat exchangers, in particular to a plate heat exchanger with an asymmetric channel. Background Art
[0002] The brazed plate heat exchanger is a high-efficiency heat exchanger made of a series of corrugated metal sheets stacked and brazed. Channels are formed between the various plates, and heat is exchanged through the plates. Compared with conventional shell and tube heat exchangers, its heat transfer coefficient is much higher under the same flow resistance and pump power consumption, and it has a tendency to replace shell and tube heat exchangers within the applicable range.
[0003] The heat transfer performance and pressure bearing performance of the brazed plate heat exchanger are two important technical indicators of the product. Under the premise of ensuring the customer's design conditions, the heat transfer performance of the heat exchanger should be improved as much as possible and the pressure bearing effect of the heat exchanger should be guaranteed. For traditional brazed plate heat exchangers, if it is equal height corrugation, the number of welding points on the upper and lower sides of the plate is the same, which can ensure the pressure bearing capacity, but in the case of traditional equal height corrugation, the volume of each channel is also the same, which does not contribute to improving the heat transfer effect; if it is a traditional high and low corrugated plate, although it can form an asymmetric channel, it can improve the heat transfer effect, but due to the different number of welding points on the upper and lower sides of the plate, it is easy to cause the pressure bearing effect of the side with fewer welding points to deteriorate. It can be seen that the welding effect between the plates of the traditional brazed plate heat exchanger is often inversely proportional to the heat transfer performance of the plate, and the two cannot be taken into account at the same time. Moreover, the pressure bearing performance of the traditional brazed plate heat exchanger usually only depends on the front and rear end plates and the reinforcement plate arrangement. Under the premise of seeking to improve the heat transfer performance of the heat exchanger, considering how to ensure the pressure bearing effect from the structure of the heat exchanger plate itself is a feasible research direction. Summary of the invention
[0004] In order to solve the problem that the heat exchange performance and pressure bearing effect of the existing plate heat exchanger cannot be taken into account at the same time, the present invention provides a plate heat exchanger with an asymmetric channel. The heat exchanger forms asymmetric channels with different volumes on both sides of the second plate by arranging a number of evenly distributed grooves on the valley of the first plate, thereby increasing the heat exchange performance. The arrangement of the grooves makes the ridge of the second plate located between two adjacent grooves, and the inclined surfaces on both sides of the ridge and the inclined surfaces on both sides of the grooves that contact each other effectively increase the welding area, enhance the pressure bearing effect of the heat exchanger, and take both the heat exchange performance and the pressure bearing effect into account.
[0005] The technical solution adopted by the present invention to solve its technical problem is:
[0006] A plate heat exchanger with an asymmetric channel includes a plurality of heat exchange plates stacked to form a heat exchange channel, wherein the heat exchange plates are first plates and second plates alternately arranged, wherein the first plates and the second plates both include a main panel and a surrounding baffle, wherein the main panel is provided with a plurality of ridges, and valleys are formed between adjacent ridges, and a plurality of grooves are evenly distributed on the valleys of the first plate, so that asymmetric channels with different volumes are formed on both sides of the second plate.
[0007] Preferably, the ridge of the second plate is arranged between two adjacent grooves on the first plate, so that the top of the ridge of the second plate contacts the bottom of the valley of the first plate, and the upper ends of both sides of the ridge of the second plate contact the side surfaces of the groove of the first plate, and the contact portion forms a welding point.
[0008] Preferably, the ridges are arranged in a herringbone shape from the central axis of the first plate or the second plate to both sides.
[0009] Preferably, the second plate is rotated 180° relative to the first plate.
[0010] Preferably, the valleys of the first plate have grooves at the central axis, and the remaining grooves are evenly arranged from the groove at the central axis to both sides.
[0011] Preferably, the height of the ridge is 1.1-8 times the depth of the groove.
[0012] Preferably, the height of the ridge is 2-4 times the depth of the groove.
[0013] Preferably, the four corners of the main panel are provided with four corner holes, and no grooves are provided on the valleys of the first plate near the corner holes.
[0014] Preferably, the width of the portion of the main panel of the first plate where no grooves are provided is w1, and the width of the portion where grooves are provided is w2, and w2 is 8-12 times of w1.
[0015] The beneficial effects of the present invention are:
[0016] (1) The heat exchanger of the present invention forms asymmetric channels with different volumes on both sides of the second plate by arranging a number of evenly distributed grooves on the valley of the first plate. The flow pressure drop of the medium in the channel with a smaller volume is increased, and the turbulence of the medium is significantly improved, thereby enhancing the heat transfer effect of the medium inside the heat exchanger and significantly improving the heat exchange performance.
[0017] (2) The arrangement of the grooves in the present invention enables the ridge of the second plate to be clamped between two adjacent grooves on the first plate. On a conventional plate without grooves, welding can only be performed at the contact surface between the top of the ridge of the second plate and the bottom of the valley of the first plate, and the welding area is relatively small. In addition to the contact surface between the top of the ridge and the bottom of the valley, the present invention effectively increases the contact area between the inclined surfaces on both sides of the ridge and the inclined surfaces on both sides of the groove. That is, without changing the number of welding points, the contact area of each welding point is effectively increased, the force bearing capacity of each welding point is increased, and the overall pressure bearing capacity of the heat exchanger is improved. That is, the present invention takes both heat exchange performance and pressure bearing effect into consideration;
[0018] (3) The first plate of the present invention does not have grooves on the valleys near the corner holes. In the portion where the grooves are not provided, the channel has a larger volume, which can allow the medium to be quickly diverted, ensuring that the medium is quickly and evenly distributed, which is conducive to a more even circulation of the medium in the entire channel, further improving the heat exchange performance and ensuring long-term heat exchange stability. BRIEF DESCRIPTION OF THE DRAWINGS
[0019] The present invention is further described below in conjunction with the accompanying drawings and embodiments.
[0020] Figure 1 It is a schematic diagram of the arrangement of the heat exchange plates of the present invention;
[0021] Figure 2 is a front view of a plate group consisting of a first plate, a second plate and a first plate stacked in sequence;
[0022] Figure 3 is along Figure 2 Sectional view of line AA (view omitted);
[0023] Figure 4 is along Figure 2 Sectional view of the midline BB (view omitted);
[0024] Figure 5 yes Figure 2 Enlarged view of part C;
[0025] Figure 6 is the main view of the second plate (omitted view);
[0026] In the figure: 1. first plate; 2. second plate; 3. main panel; 31. ridge; 32. valley; 321. groove; 33. corner hole; 4. baffle. DETAILED DESCRIPTION
[0027] The present invention will now be described in further detail with reference to the accompanying drawings. These drawings are simplified schematic diagrams, which only illustrate the basic structure of the present invention in a schematic manner, and therefore only show the components related to the present invention.
[0028] A plate heat exchanger with asymmetric channels, such as Figure 1 , Figure 2 , Figure 3 , Figure 5 and Figure 6 As shown, it includes a plurality of heat exchange plates stacked to form a heat exchange channel, the heat exchange plates are first plates 1 and second plates 2 arranged alternately, the first plates 1 and the second plates 2 both include a main panel 3 and a surrounding baffle 4, the main panel 3 is provided with a plurality of ridges 31, and valleys 32 are formed between adjacent ridges 31, and a plurality of grooves 321 are evenly distributed on the valleys 32 of the first plate 1, so that asymmetric channels with different volumes are formed on both sides of the second plate 2. Figure 3 As shown in the portion with the groove 321 on the right side, the volume of the channel formed on the second plate 2 is significantly smaller than the channel formed below. In the asymmetric channels formed on both sides of the second plate, the flow pressure drop of the medium in the channel with a smaller volume increases, and the turbulence of the medium is significantly improved, thereby enhancing the heat transfer effect of the medium inside the heat exchanger and significantly improving the heat exchange performance. In general, the refrigerant flows in the channel with a smaller volume.
[0029] In a specific embodiment, Figure 4 As shown, the ridge 31 of the second plate 2 is clamped between two adjacent grooves 321 on the first plate 1, so that the top of the ridge 31 of the second plate 2 contacts the bottom of the valley 32 of the first plate 1, and the upper ends of both sides of the ridge 31 of the second plate 2 contact the side surfaces of the groove 321 of the first plate 1, and a welding point is formed at the contact position.
[0030] On traditional plates without grooves, welding can only be performed on the contact surface between the top of the ridge of the second plate and the bottom of the valley of the first plate, and the welding area is relatively small. In addition to the contact surface between the top of the ridge and the bottom of the valley, the present invention effectively increases the contact area at the inclined surfaces on both sides of the ridge and the inclined surfaces on the side of the groove. That is, without changing the number of welding points, the contact area of each welding point is effectively increased, the force bearing capacity of each welding point is increased, and the overall pressure bearing capacity of the heat exchanger is improved. At the same time, since the number of welding points remains unchanged, the heat exchange area is not affected. That is, the present invention takes into account both heat exchange performance and pressure bearing effect.
[0031] In a specific embodiment, Figure 1 As shown, the ridges 31 are arranged in a herringbone shape from the central axis of the first plate 1 or the second plate 2 to both sides.
[0032] In a specific embodiment, Figure 1 As shown, the second plate 2 is rotated 180° relative to the first plate 1 .
[0033] In a specific embodiment, Figure 2As shown, the valleys 32 of the first plate 1 all have a groove 321 at the center axis position, and the remaining grooves 321 are evenly arranged from the groove 321 at the center axis position to both sides.
[0034] In a specific implementation, the height of the ridge 31 is 1.1-8 times the depth of the groove 321. In a specific implementation, the depth of the groove 321 can be adjusted according to actual needs, as long as the channel is not blocked.
[0035] In a specific embodiment, the height of the ridge 31 is 2-4 times the depth of the groove 321. When the height of the ridge 31 is 2-4 times the depth of the groove 321, better heat exchange and pressure bearing effects can be obtained. In specific embodiments, 2 times, 2.5 times, 3 times, 3.5 times, 4 times, etc. can be selected.
[0036] In a specific embodiment, Figure 2 As shown, the four corners of the main panel 3 have four corner holes 33 , and the part of the valley 32 on the first plate 1 close to the corner holes 33 is not provided with a groove 321 .
[0037] like Figure 3 As shown, the first plate has no grooves on the concave part near the corner hole. For the channel above the second plate 2: the part without grooves ( Figure 3 The left side of the center, where the volumes of the channels are equal) is larger than the grooved portion ( Figure 3 The volume of the channel formed by the rightmost part (the upper channel volume is smaller than the lower channel volume) should be large. The larger channel volume of the part without groove can make the medium flow quickly, ensure the medium is distributed quickly and evenly, and facilitate the medium to flow more evenly in the whole channel, further improve the heat exchange performance, and ensure long-term heat exchange stability.
[0038] In a specific embodiment, the width of the portion of the main panel 3 of the first plate 1 where the groove 321 is not provided is w1, and the width of the portion where the groove 321 is provided is w2, wherein w2 is 8-12 times of w1. Figure 2 As shown, w1 is only the width of the part without grooves on one side, not the total width of all the parts without grooves on a plate. The part without grooves can quickly guide and evenly distribute the incoming medium. After the medium completes heat exchange in the main heat exchange area with the groove part in the middle, it flows into the part without grooves again, evenly gathers the medium together, and finally flows to the outlet. The medium undergoes two even distributions in the whole process, which is conducive to a more even and smooth flow of the medium in the channel, which is conducive to improving the heat exchange performance and ensuring long-term heat exchange stability.
[0039] Based on the above ideal embodiments of the present invention, the relevant staff can make various changes and modifications without departing from the technical concept of the present invention through the above description. The technical scope of the present invention is not limited to the contents of the specification, and its technical scope must be determined according to the scope of the claims.
Claims
1. A plate heat exchanger with an asymmetric channel, comprising a plurality of heat exchange plates stacked to form a heat exchange channel, wherein the heat exchange plates are first plates (1) and second plates (2) arranged alternately, wherein the first plates (1) and the second plates (2) each comprise a main panel (3) and a surrounding baffle (4), wherein the main panel (3) is provided with a plurality of ridges (31), and valleys (32) are formed between adjacent ridges (31), wherein: A plurality of grooves (321) are evenly distributed on the valley (32) of the first plate (1), so that asymmetric channels with different volumes are formed on both sides of the second plate (2); The ridge (31) of the second plate (2) is clamped between two adjacent grooves (321) on the first plate (1), so that the top of the ridge (31) of the second plate (2) contacts the bottom of the valley (32) of the first plate (1), and the upper ends of both sides of the ridge (31) of the second plate (2) contact the side surfaces of the groove (321) of the first plate (1), and a welding point is formed at the contact position; The ridges (31) are arranged in a herringbone shape from the central axis of the first plate (1) or the second plate (2) to both sides.
2. The plate heat exchanger with asymmetric channels according to claim 1, characterized in that: The second plate (2) is rotated 180 degrees relative to the first plate (1).
3. The plate heat exchanger with asymmetric channels according to claim 1, characterized in that: The valleys (32) of the first plate (1) all have grooves (321) at the central axis position, and the remaining grooves (321) are evenly arranged from the groove (321) at the central axis position to both sides.
4. The plate heat exchanger with asymmetric channels according to claim 1, characterized in that: The height of the ridge (31) is 1.1-8 times the depth of the groove (321).
5. The plate heat exchanger with asymmetric channels according to claim 4, characterized in that: The height of the ridge (31) is 2-4 times the depth of the groove (321).
6. The plate heat exchanger with asymmetric channels according to claim 1, characterized in that: The main panel (3) has four corner holes (33) at its four corners, and no grooves (321) are provided on the concave valleys (32) of the first plate (1) close to the corner holes (33).
7. The plate heat exchanger with asymmetric channels according to claim 6, characterized in that: The width of the portion of the main panel (3) of the first plate (1) where the groove (321) is not provided is w1, and the width of the portion where the groove (321) is provided is w2, wherein w2 is 8 to 12 times of w1.
Citation Information
Patent Citations
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CN206488672U
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