Compact heat exchanger

Abstract

The application provides a compact heat exchanger, which comprises a plurality of heat exchange plates stacked in a first direction, a first working fluid channel and a second working fluid channel formed between each two adjacent heat exchange plates and arranged alternately in the first direction, a first working fluid inlet pipe connected with the first working fluid channels, and a second working fluid inlet pipe connected with the second working fluid channels, wherein the extending direction of the first working fluid inlet pipe is the same as the extending direction of the inlet of the first working fluid channel, and the second working fluid inlet pipe is connected with the inlet of the second working fluid channel in a cross type. The compact heat exchanger can be used as a condenser or an evaporator. When used as an evaporator, the compact heat exchanger has a good flow uniformity effect for working fluid in a two-phase inlet condition.

Description

Technical Field

[0001] This invention relates to a heat exchanger, and more particularly to a compact heat exchanger with small volume and large heat exchange capacity. Background Technology

[0002] Existing compact heat exchangers include multiple stacked heat exchange plates, with working fluid channels formed between adjacent layers. These working fluid channels include first and second working fluid channels spaced apart from each other, and typically one of the first and second working fluids is a refrigerant. However, both the first and second working fluids move in one direction throughout their entry and exit from the heat exchanger. Especially when the heat exchanger is used as an evaporator, if the uniformity of the gas-liquid two-phase refrigerant entering the heat exchanger is poor, uneven heat transfer can easily occur within the multiple working fluid channels, reducing the evaporator's heat transfer performance.

[0003] In view of this, it is necessary to improve the existing compact heat exchangers to solve the above problems. Summary of the Invention

[0004] The purpose of this invention is to provide a compact heat exchanger with improved heat exchange performance.

[0005] To achieve the above-mentioned objective, the present invention provides a compact heat exchanger, comprising a plurality of heat exchange plates stacked sequentially along a first direction, a first working fluid channel and a second working fluid channel formed between each pair of adjacent heat exchange plates and alternately arranged along the first direction, a first working fluid inlet pipe connected to the plurality of first working fluid channels, and a second working fluid inlet pipe connected to the plurality of second working fluid channels. The extension direction of the first working fluid inlet pipe is the same as the extension direction at the inlet of the first working fluid channel, and the second working fluid inlet pipe is cross-connected to the inlet of the second working fluid channel.

[0006] As a further improvement of the present invention, the heat exchange plate has a first recess on each side that communicates with the first working fluid channel. The compact heat exchanger also includes a connecting plate disposed in the first recess and a distribution cavity formed between the connecting plate and the inlet of the working fluid channel. The first working fluid inlet pipe passes through the connecting plate to communicate with the distribution cavity.

[0007] As a further improvement of the present invention, the heat exchange plate also has a second recess formed by further recessing from the two inner walls opposite to the first recess, and the connecting plate is disposed in the second recess.

[0008] As a further improvement of the present invention, the heat exchange plate also has a through hole for communicating with the second working fluid channel, and the second working fluid inlet pipe is connected to the through hole.

[0009] As a further improvement of the present invention, the compact heat exchanger also includes a second working fluid outlet pipe connected to the through hole, and the second working fluid inlet pipe and the second working fluid outlet pipe are arranged on the same side.

[0010] As a further improvement of the present invention, the inner diameters of the first working fluid inlet pipe and the second working fluid outlet pipe are different.

[0011] As a further improvement of the present invention, the inlet and outlet sizes of the first working fluid channel are different. As a further improvement of the present invention, the through holes are arranged diagonally on both sides of the heat exchange plate, and the inlet of the first working fluid channel and the inlet of the second working fluid channel are not located on the same side.

[0012] As a further improvement of the present invention, the first working fluid inlet pipe does not protrude into the working fluid distribution cavity.

[0013] As a further improvement of the present invention, the heat exchange plate includes a first heat exchange plate and a second heat exchange plate stacked sequentially at intervals in the vertical direction, and the compact heat exchanger further includes a sequence identification structure to prevent incorrect stacking order of the first heat exchange plate and the second heat exchange plate, wherein the sequence identification structure is a notch recessed from one side of the first heat exchange plate or the second heat exchange plate.

[0014] The beneficial effects of this invention are as follows: In the compact heat exchanger of this invention, the extension direction of the first working fluid inlet pipe is the same as the extension direction of the inlet of the first working fluid channel, and the second working fluid inlet pipe is cross-connected to the inlet of the second working fluid channel. Therefore, the first and second working fluid inlets can not only be evenly distributed around the heat exchanger, improving space utilization, but also, when the second working fluid enters the second working fluid channel through the second working fluid inlet pipe, it needs to make a bend, thereby increasing the turbulence of the second working fluid, making the second working fluid more uniform, and thus improving the heat exchange performance with the first working fluid. Attached Figure Description

[0015] Figure 1 This is a three-dimensional schematic diagram of the compact heat exchanger of the present invention.

[0016] Figure 2 This is an exploded perspective view of the compact heat exchanger of the present invention.

[0017] Figure 3 This is a three-dimensional schematic diagram of a portion of the heat exchange plates, with the second heat exchange plate located on the upper side.

[0018] Figure 4 yes Figure 3 Top view.

[0019] Figure 5yes Figure 3 3D exploded view.

[0020] Figure 6 This is a three-dimensional schematic diagram of a portion of the heat exchange plates, with the first heat exchange plate located on the upper side.

[0021] Figure 7 yes Figure 6 Top view.

[0022] Figure 8 yes Figure 6 3D exploded view.

[0023] Figure 9 yes Figure 4 A cross-sectional view along the AA direction.

[0024] Figure 10 yes Figure 9 Cross-sectional view.

[0025] Figure 11 yes Figure 9 Cross-sectional view of the guide section installed at the end of the heat exchange plate.

[0026] Figure 12 This is a cross-sectional view of the second embodiment with misaligned heat exchanger plate end faces.

[0027] Figure 13 This is a cross-sectional view of the third embodiment with misaligned heat exchanger plate end faces.

[0028] Figure 14 This is a cross-sectional view of the fourth embodiment with misaligned heat exchanger plate end faces.

[0029] Figure 15 This is a cross-sectional view of the fifth embodiment with misaligned heat exchanger plate end faces. Detailed Implementation

[0030] The present invention will now be described in detail with reference to the embodiments shown in the accompanying drawings. However, these embodiments do not limit the present invention, and any structural, methodological, or functional modifications made by those skilled in the art based on these embodiments are included within the scope of protection of the present invention.

[0031] Please refer to Figures 1 to 15The illustration shows an embodiment of the compact heat exchanger of the present invention. The compact heat exchanger is manufactured using a combination of stamping and atomic diffusion welding processes. Specifically, the compact heat exchanger includes multiple heat exchange plates stacked along a first direction and a working fluid channel formed between adjacent heat exchange plates. The heat exchange plates include a first heat exchange plate 1 and a second heat exchange plate 2 arranged sequentially at intervals. The first heat exchange plate 1 includes a first gasket 11 and a first heat exchange plate 12 stacked together. The second heat exchange plate 2 includes a second gasket 21 and a second heat exchange plate 22 stacked together. The heat exchange plates and gaskets are first stamped, and then, after the heat exchange plates and gaskets are stacked, they are fixed together using atomic diffusion welding to form the compact heat exchanger.

[0032] In this embodiment, the first direction is described using the vertical direction as an example. Of course, in other embodiments, the first direction can also be other directions. The first gasket 11 is stacked on the first heat exchange plate 12 to form the first heat exchange plate 1 for the flow of the first working fluid, and the second gasket 21 is stacked on the second heat exchange plate 22 to form the second heat exchange plate 2 for the flow of the second working fluid. Thus, the first heat exchange plate 1 and the second heat exchange plate 2 are stacked alternately to form the compact heat exchanger. Of course, the heat exchange plate can also be stacked on top of the gasket to form the heat exchange plate.

[0033] The first heat exchange plate 1 includes a first A-side and a first B-side, and the second heat exchange plate 2 includes a second A-side and a second B-side. The first A-side and the first B-side are the upper and lower surfaces of the first heat exchange plate 1, and the second A-side and the second B-side are the lower and upper surfaces of the second heat exchange plate 2. The first heat exchange plate 1 and the second heat exchange plate 2 are stacked alternately with their first A-side and second A-side facing each other, forming a first working fluid channel 13 for the flow of a first working fluid between the first A-side and the second A-side; and a second working fluid channel 23 for the flow of a second working fluid is formed between the first B-side and the second B-side.

[0034] Since the heat exchange plates and gaskets are both made by stamping, this application has many advantages over traditional etching processes, such as simple process, high output and low cost, and can be widely used in equipment with heat exchange in various fields.

[0035] In this embodiment, the first and second working fluids are illustrated using water and refrigerant as examples, respectively. However, in other embodiments, the heat exchange is not limited to water and refrigerant; other two working fluids can also be used. For ease of explanation, the first heat exchange plate 12 is referred to as a water layer heat exchange plate, the second heat exchange plate 22 as a refrigerant layer heat exchange plate, the first gasket 11 as a water layer gasket, the second gasket 21 as a refrigerant layer gasket, the first heat exchange plate 1 as a water layer heat exchange plate, the second heat exchange plate 2 as a refrigerant layer heat exchange plate, the first working fluid channel 13 as a water channel, and the second working fluid channel 23 as a refrigerant channel. Taking a set of water layer heat exchange plates and refrigerant layer heat exchange plates as an example, i.e., a four-layer structure, the first layer is a refrigerant layer gasket, the second layer is a refrigerant layer heat exchange plate, the third layer is a water layer gasket, the fourth layer is a water layer heat exchange plate, and so on.

[0036] like Figures 6 to 8 As shown, in this embodiment, each water layer heat exchange plate includes a water layer heat exchange plate and a pair of water layer gaskets disposed opposite each other on both sides of the water layer heat exchange plate. Therefore, the positions at the other two ends of the water layer heat exchange plate where the water layer gaskets are not disposed form the water inlet and the water outlet, respectively. The water layer gaskets are disposed on the front and rear sides, while the water inlet and outlet are located on the left and right sides. Of course, the positions of the water layer gaskets, the water inlet, and the water outlet can also be interchanged.

[0037] The refrigerant layer gasket is a ring-shaped structure disposed around the refrigerant layer heat exchange plate. Alternatively, similar to the water layer gasket, two gaskets can be disposed on opposite sides of the refrigerant layer heat exchange plate. The refrigerant inlet and outlet can be located on the same side as the water inlet and outlet, thus forming a co-current or counter-current flow with the water layer. The refrigerant inlet and outlet can also be located on the left and right sides, thus forming a direct-current flow with the water layer. The above configuration can be tailored to the specific product.

[0038] In this embodiment, the outer contours of the water layer heat exchanger and the refrigerant layer heat exchanger are centrally symmetrical. Therefore, the two oppositely arranged water layer gaskets have identical structures, which facilitates stamping production, eliminates the need to produce two different shapes of water layer gaskets, improves production efficiency, reduces production costs, and simplifies assembly. Of course, the outer contour patterns of the water layer heat exchanger and the refrigerant layer heat exchanger can also be other symmetrical patterns.

[0039] Both the water layer heat exchange plate and the refrigerant layer heat exchange plate have a first recess 14 and a second recess 15 connected to the first recess 14 on both sides. The second recess 15 is formed by further recessing from the two inner walls of the first recess 14, which are arranged opposite to each other. That is, the water layer heat exchange plate, the refrigerant layer gasket, and the refrigerant layer heat exchange plate all have the first recess 14 and the second recess 15 on both sides. Since the water layer gasket is located on the front and rear sides, the water layer gasket does not have the first recess 14, but it has the second recess 15.

[0040] The second recess 15 is located on the outer side, and its width in the front-to-back direction is greater than that of the first recess 14. The depth of the second recess 15 in the left-to-right direction is less than that of the first recess 14. Furthermore, the width of the first recess 14 and the second recess 15 on one side is greater than the width of the first recess 14 and the second recess 15 on the other side.

[0041] like Figure 1 and Figure 2 As shown, the compact heat exchanger further includes a connecting plate 3 disposed on the inlet and outlet sides, and a first working fluid pipe 4 connected to the connecting plate 3. The connecting plate 3 has a connecting hole 31 that mates with the first working fluid pipe 4. The connecting plate 3 is fixed to the inner wall of the second recess 15 by welding. Alternatively, the connecting plate 3 and the inner wall of the second recess 15 can be fixed by adhesive or screws. In this embodiment, the first working fluid pipe 4 includes a first working fluid inlet pipe and a first working fluid outlet pipe, which is the connecting pipe for water flow. A working fluid distribution cavity 28 is formed between the connecting plate 3 and the water channel inlet, and between the connecting plate 3 and the water channel outlet. The end of the connecting pipe is located within the connecting hole 31 and fixed to the inner wall of the connecting hole 31, and / or, the connecting pipe passes through the connecting hole 31 and the end of the connecting pipe is fixed to the side of the connecting plate 3 facing the heat exchange plate.

[0042] In this embodiment, the end of the connecting pipe is located inside the connecting hole 31 and fixed to the inner wall of the connecting hole 31. That is, the connecting pipe does not extend into the working fluid distribution chamber 28, thereby ensuring sufficient space at the inlet and outlet ends to ensure that water can smoothly enter the water channel. Similarly, sufficient space is also left at the outlet end to ensure that water can smoothly flow out of the compact heat exchanger. Since the connecting pipe is located inside the connecting hole 31, it will not become a resistance to the flow of water in the working fluid distribution chamber 28. The connecting pipe also has a stop part 41 that cooperates with the wall surface of the connecting plate 3 facing away from the heat exchange plate to prevent the connecting pipe from being over-installed, thereby effectively preventing the connecting pipe from extending into the working fluid distribution chamber 28 during installation.

[0043] The inner walls of the connecting pipe and the connecting hole 31 are fixed together by welding. On the one hand, this welding position is located inside the compact heat exchanger, ensuring the integrity of the compact heat exchanger and improving its aesthetics. On the other hand, it saves space on the outer wall of the connecting plate 3 facing away from the heat exchange plate for the connecting pipe and the connecting hole 31. Therefore, more space can be provided on the outside of the compact heat exchanger to design and install more components. When the components meet the requirements, the overall structure can be further reduced, achieving a compact design, which is beneficial for the heat exchanger to form a miniaturized assembly with other structures. Furthermore, since the depth of the second recess 15 is less than the depth of the first recess 14, the thickness of the connecting plate 3 is smaller, meaning the mass of the connecting plate 3 is also relatively small, having little impact on the overall mass of the compact heat exchanger, which is beneficial for the lightweight design of the heat exchanger.

[0044] Of course, in other embodiments, the connecting pipe may also protrude from the inner wall of the connecting plate 3 facing the heat exchange plate, that is, the portion of the connecting pipe protruding from the wall of the connecting plate 3 facing the heat exchange plate is located within the working fluid distribution cavity 28. Therefore, the connecting pipe and the inner wall of the connecting plate 3 can also be welded, thereby improving the fixing effect of the connecting plate 3 and the connecting pipe. Furthermore, since the depth of the first recess 14 is relatively large, the space of the working fluid distribution cavity 28 is also relatively large, which can also ensure smooth water flow.

[0045] In this embodiment, since the inlet and outlet of the water heat exchange plate are respectively located on the left and right sides opposite to each other, the water flows in one direction in the water channel without changing direction or turning. Therefore, the water can flow stably in the water channel, thereby ensuring the stability of the overall heat exchange.

[0046] In this embodiment, the two heat exchange plates surrounding the working fluid channel have a first end 16 and a second end 24 surrounding the inlet of the working fluid channel, and at least a portion of the first end 16 and at least a portion of the second end 24 are offset along the extension direction of the working fluid channel.

[0047] like Figure 9 and Figure 10As shown, specifically, the first end 16 is the end of the water layer heat exchange plate, and the second end 24 can be the end of the refrigerant layer gasket and / or the refrigerant layer heat exchange plate. In this embodiment, the water layer heat exchange plate protrudes beyond the refrigerant layer gasket and the refrigerant layer heat exchange plate along the water channel direction, and there are refrigerant layer gaskets and refrigerant layer heat exchange plates between adjacent water layer heat exchange plates. Therefore, when observing the five-layer structure of water layer heat exchange plate, refrigerant layer gasket, refrigerant layer heat exchange plate, water layer gasket, and water layer heat exchange plate as a group, the size of the water channel inlet is the height between adjacent water layer heat exchange plates, while the height of the water channel is the height between the refrigerant layer heat exchange plate and the water layer heat exchange plate. Obviously, the former height is greater than the latter height, which is beneficial for water to enter the water channel, improves the stability of the heat exchanger, and thus improves the heat exchange performance.

[0048] like Figure 9 and 10 As shown, in addition to ensuring a more continuous and stable flow of water into the water channel, the refrigerant layer heat exchanger plate protrudes beyond the refrigerant layer gasket along the water channel direction. Furthermore, the refrigerant layer heat exchanger plate has a positioning portion 26 protruding away from the water layer heat exchanger plate, which is integrally formed by stamping the refrigerant layer heat exchanger plate. Therefore, after stacking, the water layer heat exchanger plate and the refrigerant layer heat exchanger plate form a stepped structure, and the water channel gradually narrows from the inlet inwards, thereby ensuring smooth water flow.

[0049] like Figure 12 As shown, the present invention also provides a second embodiment with misaligned heat exchange plate end faces. Specifically, the refrigerant layer gasket can also protrude from the refrigerant layer heat exchange plate along the water channel direction, and the refrigerant layer heat exchange plate does not need to be provided with positioning part 26, thus forming the above-mentioned stepped structure.

[0050] like Figure 13 As shown, the present invention also provides a third embodiment with misaligned heat exchanger plate end faces, wherein the ends of the refrigerant layer gasket and the refrigerant layer heat exchange plate can also be flush in the vertical direction. Alternatively, the refrigerant layer heat exchange plate protrudes from the refrigerant layer gasket in the direction of the water channel, but does not have the positioning part 26.

[0051] like Figure 14 As shown, in addition to the above embodiments, the present invention also provides a fourth embodiment with misaligned heat exchanger plate end faces. Specifically, the refrigerant layer gasket can also protrude beyond the water layer heat exchange plate along the water channel direction, including two cases: the refrigerant layer gasket protruding beyond the refrigerant layer heat exchange plate and the refrigerant layer heat exchange plate protruding beyond the refrigerant layer gasket. When observing a five-layer structure consisting of a refrigerant layer gasket, a refrigerant layer heat exchange plate, a water layer gasket, a water layer heat exchange plate, and a refrigerant layer gasket as a group, in the first case, there is a refrigerant layer heat exchange plate, a water layer gasket, and a water layer heat exchange plate between two adjacent refrigerant layer gaskets. Therefore, after stacking, the water channel inlet is funnel-shaped, which can ensure smooth water flow.

[0052] like Figure 15As shown, in the second case, the present invention also provides a fifth embodiment with misaligned heat exchange plate end faces. Specifically, when the refrigerant layer heat exchange plate, water layer gasket, water layer heat exchange plate and refrigerant layer gasket are observed as a group, the stacked structure is similar to the above-mentioned structure where the water layer heat exchange plate protrudes from the refrigerant layer gasket and refrigerant layer heat exchange plate along the water channel direction.

[0053] like Figure 11 As shown, to further reduce flow resistance, the first end 16 and the second end 24 also have guide portions 17. The guide portions 17 have guide ramps 18 on their upper and / or lower sides, and the guide ramps 18 are either planar or arc-shaped. That is, the water layer heat exchange plate, the refrigerant gasket, and the refrigerant heat exchange plate also have guide portions 17 disposed at their ends. When the guide ramps 18 are arc-shaped, they include both concave and convex arc surfaces. Therefore, combining the staggered stacked plates and the guide portions 17 can greatly reduce flow resistance. Of course, the staggered stacked plates and the guide portions 17 can also be selected as one of them depending on the actual situation.

[0054] In this embodiment, the misalignment distance between each pair of the water layer heat exchange plate, the refrigerant layer gasket, and the refrigerant layer heat exchange plate is within the range of 0.2-0.7mm, preferably 0.5mm. Therefore, the small misalignment distance not only ensures that the compact heat exchanger has a small volume, but also reduces the flow resistance and facilitates the entry of water into the water layer channel.

[0055] In this embodiment, the water layer heat exchange plate, refrigerant layer heat exchange plate, water layer gasket, and refrigerant layer gasket also have through holes 25 extending vertically. The through holes 25 are located on the front and rear sides, and are diagonally arranged. In other words, if the inlet and outlet are located on the left and right sides, the through holes 25 are located on the front and rear sides, with the front through holes 25 located on the left or right, and the rear through holes 25 located on the right or left. Each water layer gasket has only one through hole 25, and when the water layer heat exchange plate and the refrigerant layer heat exchange plate are stacked, the through holes 25 form a channel for the refrigerant to enter and exit. Of course, when the inlet and outlet are located on the front and rear sides, the through holes 25 are located on the left and right sides.

[0056] The compact heat exchanger is connected to the second working fluid pipe 5 on its upper and lower sides, respectively. The second working fluid pipe 5 includes a second working fluid inlet pipe and a second working fluid outlet pipe. In this embodiment, the second working fluid pipe 5 is the refrigerant pipe. Therefore, the inlet of the refrigerant pipe and the refrigerant channel are arranged in a cross configuration. That is, the refrigerant flows into the refrigerant channel first in the vertical direction, then flows horizontally along the refrigerant channel, and finally flows out of the compact heat exchanger in the vertical direction. In this embodiment, the second working fluid pipe 5 is perpendicular to the second working fluid channel 23. Therefore, when the refrigerant enters the refrigerant layer heat exchange plate, it undergoes a bend, thereby increasing the refrigerant turbulence, ensuring thorough mixing of the refrigerant gas and liquid phases, preventing the refrigerant from separating into gas and liquid phases within the refrigerant layer channel, ensuring uniform refrigerant temperature, and improving heat exchange stability.

[0057] Furthermore, because the connecting pipes are positioned on opposite sides in the horizontal direction, while the refrigerant pipes are positioned on the top and bottom sides, the space around the compact heat exchanger is fully utilized, avoiding excessive local piping density and facilitating pipe design, installation, and maintenance. Moreover, the positions of the water inlet and outlet are opposite to those of the refrigerant inlet and outlet. For example, in this embodiment, assuming the water inlet is on the left and the outlet on the right, the refrigerant inlet is on the right and the refrigerant outlet is on the left. The water flows from left to right, while the overall refrigerant flow is from right to left. Therefore, the water and refrigerant form a counter-flow design, maximizing heat exchange performance. In other embodiments, the water inlet and outlet are located on the front and rear sides, respectively, while the refrigerant inlet and outlet are located on the rear and front sides, respectively. Alternatively, the water inlet and refrigerant inlet, and the water outlet and refrigerant outlet, can be located on the same side.

[0058] In this embodiment, the two through holes 25 located diagonally opposite each other have different outer diameters. When the compact heat exchanger is used as a condenser (e.g.) Figure 1 As shown in the diagram, the larger through-hole 25 serves as the refrigerant inlet, while the smaller through-hole 25 serves as the refrigerant inlet when the compact heat exchanger is used as an evaporator. Taking the condenser as an example: for the condenser, the inlet carries gaseous high-pressure, high-temperature refrigerant, while the outlet carries liquid high-pressure refrigerant. The density difference between the gaseous and liquid refrigerants is significant. To ensure a certain refrigerant flow rate and control the refrigerant velocity within a certain range, it is necessary to select a thicker pipe for the high-pressure gas pipe and a thinner liquid pipe, which is the condenser outlet pipe, when designing the high-pressure gas pipe.

[0059] In the through-holes 25 on the same side, the inner diameter of the through-hole 25 of the water layer heat exchanger is different from that of the through-hole 25 of the refrigerant layer heat exchanger. Furthermore, near the refrigerant inlet and outlet, the inner walls of the through-holes 25 of the water layer heat exchanger and the refrigerant layer heat exchanger are not aligned, i.e., they are misaligned. This ensures that the refrigerant flows smoothly into the refrigerant channel. See the above-described misaligned inlet and outlet structure for details. In this embodiment, the inner diameter of the through-hole 25 of the water layer heat exchanger is larger than that of the through-hole 25 of the refrigerant layer heat exchanger; however, the reverse arrangement is also possible.

[0060] In this embodiment, the thickness of the water layer gasket, water layer heat exchange plate, refrigerant layer gasket, and refrigerant layer heat exchange plate is consistent and not greater than 0.1 mm. Therefore, the thickness of the flow channels in the water layer and refrigerant layer is also not greater than 0.1 mm, and preferably 0.1 mm. This not only ensures stable stamping manufacturing but also significantly improves the heat exchange effect. When the space height is smaller, it is equivalent to dividing the water and refrigerant into smaller structures, thereby increasing the heat exchange area and improving the heat exchange effect. Therefore, when the stacking height of the compact heat exchanger is constant, the more stacked layers there are, i.e., the smaller the space height of the water layer and refrigerant layer, the better the heat exchange effect. Furthermore, although the increased number of layers increases the contact area between the water and refrigerant and the heat exchange plate, which to some extent increases flow loss, the smaller overall size of the compact heat exchanger, i.e., the shorter length of the water channel and refrigerant channel, correspondingly reduces flow loss. These two factors balance each other, thus ensuring a significant improvement in heat exchange effect while minimizing flow loss.

[0061] The water layer gasket and the refrigerant layer gasket not only increase the structural strength, but more importantly, they form the boundary wall between the water layer heat exchange plate and the refrigerant layer heat exchange plate, thereby preventing water and refrigerant leakage and ensuring the normal flow of water and refrigerant.

[0062] To ensure efficient and orderly stacking of the water layer gasket, water layer heat exchange plate, refrigerant layer gasket, and refrigerant layer heat exchange plate, all four components are perforated. The compact heat exchanger also includes base plates 6 at the top and bottom ends, and positioning posts on the bottom base plate 6. In this embodiment, the perforations are located at the four corners. During assembly, the four components are sequentially inserted into the bottom base plate 6. After stacking, the upper base plate 6 is inserted into the positioning posts, and finally, atomic diffusion welding is performed to complete the fabrication of the compact heat exchanger. The base plate 6 has a sealing portion 61 that mates with the wall surface of the connecting plate 3 near the heat exchange plate to seal the connection plate 3 and the heat exchange plate, thereby reducing the risk of working fluid leakage between the connecting plate 3 and the base plate 6.

[0063] However, for ease of insertion, the outer diameter of the positioning post must be smaller than the inner diameter of the perforation. Therefore, misalignment of the above four components is likely to occur. To ensure precise alignment between the water layer gasket and the water layer heat exchange plate, and between the refrigerant layer gasket and the refrigerant layer heat exchange plate, the water layer heat exchange plate and the refrigerant layer heat exchange plate are also provided with the aforementioned protruding positioning portion 26. The water layer gasket and the refrigerant layer gasket each have a limiting portion 27 that cooperates with the positioning portion 26.

[0064] By setting the positioning part 26 and the limiting part 27, accurate positioning is ensured. At the same time, the accurate positioning prevents the gasket from shifting outward, thus ensuring the welding area between the gasket and the heat exchange plate during atomic diffusion welding, improving the welding effect. It also prevents the gasket from shifting inward, thus preventing the width of the water channel and the refrigerant channel from shrinking, ensuring the heat exchange effect.

[0065] In this embodiment, the positioning part 26 on the water layer heat exchange plate is disposed around the through hole 25 and is formed by stamping and protruding from the inner wall of the through hole 25. The limiting part 27 of the water layer gasket is a notch that continues to be recessed outward from the through hole 25. The notch is connected to the through hole 25. Therefore, the inner diameter of the through hole 25 and the notch of the water layer gasket is slightly larger than the inner diameter of the through hole 25 of the water layer heat exchange plate, thereby realizing that the notch of the water layer gasket is sleeved on the outside of the positioning part 26 for positioning.

[0066] Since the through hole 25 is circular, and the positioning part 26 of the water layer heat exchange plate is formed by stamping around the inner wall of the through hole 25, the through hole 25 and the positioning part 26 are not circular as a whole, and the through hole 25 and the notch are also not circular as a whole. When the water layer gasket is installed on the water layer heat exchange plate, the connection between the notch and the through hole 25 forms a stop structure, thereby preventing the water layer gasket from rotating, and thus achieving precise positioning of the water layer gasket and the water layer heat exchange plate.

[0067] By utilizing the through hole 25 to set the positioning part 26 and the limiting part 27, on the one hand, the structure of the through hole 25 itself is fully utilized, the mold design is modified less, it is easy to stamp and form, and the manufacturing is simple. On the other hand, the heat exchange area 9 of the water heat exchange plate is increased as much as possible, thereby improving the heat exchange effect. The positioning portions 26 on the refrigerant heat exchange plate protrude from their opposite sides and are integrally formed by stamping. In this embodiment, the positioning portions 26 are located at the edge of the refrigerant heat exchange plate and are formed by stamping around the inner wall of the first recess 14. The limiting portions 27 of the refrigerant gasket are their opposite sides. That is, the refrigerant gasket is held between the positioning portions 26 on both sides. This not only ensures the accurate positioning of the refrigerant gasket, but also only requires the dimensions of the two sides of the refrigerant gasket to be designed to be slightly smaller, without the need for structural design, which greatly reduces production costs. Of course, in other embodiments, the above two positioning portion 26 structures can also be interchanged, and positioning can also be achieved by setting grooves and protrusions.

[0068] In this embodiment, the positioning part 26 of the refrigerant heat exchange plate is disposed on the left and right sides. Therefore, in addition to the above-mentioned precise alignment, the height of the water inlet and outlet in the vertical direction can be increased, thereby ensuring that water can enter the water channel more easily.

[0069] The above describes the positioning of the heat exchange plates and gaskets between each heat exchange plate. From another perspective, if we consider the water layer heat exchange plates and the refrigerant layer gaskets as one heat exchange plate, and the refrigerant layer heat exchange plates and the water layer gaskets as another heat exchange plate, then the positioning part 26 and the limiting part 27 are used to position adjacent heat exchange plates relative to each other. Furthermore, the structure of the positioning part 26 and the limiting part 27 remains unchanged; only the positioning part 26 of the heat exchange plate protrudes from the heat exchange plate in a direction away from the gasket.

[0070] The compact heat exchanger also has a sequence identification structure 7 that ensures the orderly stacking of water layer gaskets, water layer heat exchange plates, refrigerant layer gaskets, and refrigerant layer heat exchange plates. In this embodiment, the sequence identification structure 7 is a notch provided on the refrigerant heat exchange plates and the refrigerant layer gaskets. The notch is formed by recesses on both sides of the refrigerant heat exchange plates and the refrigerant layer gaskets. The water layer heat exchange plate gaskets and the water layer gaskets do not have the notch. Thus, when stacked, the refrigerant heat exchange plates have notches, while the water layer heat exchange plates do not have notches, which facilitates the identification of whether there is a stacking error.

[0071] The notches on the water layer heat exchanger and the refrigerant heat exchanger are located on the front and rear sides. Since no pipes or connecting plates 3 are needed on the front and rear sides, direct stamping is convenient. In other embodiments, the notches can also be located on the water layer gasket and the water layer heat exchanger, or on the water layer gasket and the refrigerant layer gasket, or on the water layer heat exchanger and the refrigerant layer heat exchanger. Alternatively, the sequence identification structure 7 can be a structure protruding from the edges of the water layer heat exchanger, the refrigerant heat exchanger, the water layer gasket, and the refrigerant layer gasket.

[0072] The water-layer heat exchange plate has a transition zone 8 and a heat exchange zone 9 for water flow along the direction from the inlet to the outlet. In this embodiment, the water-layer heat exchange plate has two transition zones 8 respectively disposed on the left and right sides of the heat exchange zone 9. The water-layer heat exchange plate has a plurality of first protrusions 81 forming the transition zone 8 and a plurality of second protrusions 91 forming the heat exchange zone 9. The arrangement density of the first protrusions 81 is less than the arrangement density of the second protrusions 91, thereby facilitating water flow in and out of the transition zone 8 and allowing sufficient water agitation in the heat exchange zone 9. This not only increases the heat exchange area but also improves the heat exchange time, thereby enhancing the heat exchange effect. In this embodiment, to further enhance the heat exchange effect, the transition zone 8 is also provided with a plurality of second protrusions 91.

[0073] Similarly, the refrigerant heat exchange plate also has a transition zone 8 and a heat exchange zone 9 for refrigerant flow along the refrigerant inlet to outlet direction. However, since the refrigerant inlet and outlet are diagonally arranged, the transition zone 8 is also diagonally arranged. Likewise, the refrigerant heat exchange plate also has multiple first protrusions 81 forming the transition zone 8 and multiple second protrusions 91 forming the heat exchange zone 9.

[0074] In this embodiment, the first protrusion 81 and the second protrusion 91 are both unidirectional protrusions formed by stamping. The protrusion height of the first protrusion 81 and the second protrusion 91 is no greater than 0.1mm, preferably 0.1mm. That is, the protrusion height of the first protrusion 81 and the second protrusion 91 is consistent with the thickness of the water layer gasket, the water layer heat exchange plate, the refrigerant layer gasket, and the refrigerant layer heat exchange plate. In other words, the flow channel height is the protrusion height. Therefore, the gasket and the protrusion are of the same height, which facilitates the stable connection and fixation between adjacent layers during atomic diffusion welding.

[0075] Furthermore, the first protrusion 81 and the second protrusion 91 of the water layer heat exchange plate and the refrigerant layer heat exchange plate are arranged in the same direction. It should be noted that since the first protrusion 81 and the second protrusion 91 are produced by stamping, compared with the protrusions formed by traditional etching, the first protrusion 81 and the second protrusion 91 of this application have a hollow structure inside, while traditional etching has a solid structure. Therefore, the compact heat exchanger of this application requires less production material, has a lower cost, and is lighter in weight, making it easier to install and disassemble, and applicable to a wider range of scenarios.

[0076] In this embodiment, the first protrusion 81 is shaped like a convex lens or a capsule. The first protrusion 81 has drainage portions on both sides, which are positioned towards the water channel inlet and outlet, thereby reducing flow resistance and making it easier for water to flow into or out of the heat exchange zone 9, ensuring smooth water inflow and outflow. Of course, the first protrusion 81 can also be teardrop-shaped, elliptical, or other shapes. The second protrusion 91 is circular.

[0077] Therefore, the second protrusion 91 can also effectively reduce flow resistance. Multiple first protrusions 81 and multiple second protrusions 91 are arranged in multiple rows in the left-right direction, and adjacent rows of first protrusions 81 are staggered. Similarly, adjacent rows of second protrusions 91 are also staggered. Therefore, the first protrusions 81 and second protrusions 91 in the next row can further disperse the water or refrigerant flowing through the previous row, thereby strengthening the turbulence of water and refrigerant in the flow channel, increasing the heat exchange area, and enhancing the heat exchange effect.

[0078] Furthermore, the first protrusions 81 of the water layer heat exchange plates are arranged radially, i.e., in a trumpet shape. Taking the first protrusion 81 on the left as an example: the first protrusion 81 in the rear half is gradually inclined backward from left to right, and the first protrusion 81 in the front half is gradually inclined forward from left to right. Therefore, the overall arrangement is trumpet-shaped, which allows water to be directed to both ends during water intake, avoiding concentration in the middle, making full use of the space within the water channel, resulting in more uniform heat exchange and thus improving the heat exchange effect. Similarly, the first protrusions 81 of the refrigerant layer heat exchange plates are also arranged radially.

[0079] In this embodiment, both the first protrusion 81 and the second protrusion 91 are unidirectional protrusions and extend in the same direction. At the same time, the second protrusion 91 of the water layer heat exchange plate and the second protrusion 91 of the refrigerant heat exchange plate are eccentrically arranged, that is, the centers of the second protrusion 91 of the water layer heat exchange plate and the second protrusion 91 of the refrigerant heat exchange plate are at different positions in the vertical direction, but they have a common part that intersects in the vertical direction. Therefore, part of the second protrusion 91 of the lower refrigerant heat exchange plate abuts against the bottom surface of the upper water layer heat exchange plate, and the other part faces the cavity of the second protrusion 91 of the water layer heat exchange plate. This allows the second protrusions 91 of adjacent water layer heat exchange plates and refrigerant heat exchange plates to provide common support during atomic diffusion welding, which greatly reduces the risk of extrusion deformation between the water layer heat exchange plate and the refrigerant heat exchange plate.

[0080] In this embodiment, within the heat exchange zone 9, the distance between adjacent second protrusions 91 in each row along the left-right direction ranges from 0.5mm to 1.5mm, preferably 1mm. Similarly, the distance between adjacent second protrusions 91 in each column along the front-back direction also ranges from 0.5mm to 1.5mm, preferably 1mm. Furthermore, the diameter of the second protrusion 91 is no greater than 0.5mm, preferably 0.5mm. Therefore, the vertical distance between adjacent rows along the front-back direction is 0mm, and the vertical distance between adjacent columns along the left-right direction is also 0mm. Additionally, adjacent rows or columns of second protrusions 91 are staggered by a distance of 1mm.

[0081] Therefore, by rationally arranging the second protrusions 91, a sufficient number of second protrusions 91 can be ensured. This not only effectively reduces the risk of damaging the heat exchange fins during stamping but also ensures sufficient turbulence of water or refrigerant within the flow channel, thereby improving heat exchange performance. Simultaneously, a greater number of second protrusions 91 can be set within the limited heat exchange area 9, which also facilitates stamping and forming, thereby increasing the heat exchange area and improving the heat exchange effect.

[0082] The distance between two adjacent rows or columns of second protrusions 91 is 1 mm, which is the channel width. The gasket thickness (i.e., channel thickness or protrusion height) is 0.1 mm. According to the hydraulic diameter formula: d = 4 * ab / 2 (a + b), where a is the channel width and b is the channel thickness, we get d = 0.18, indicating a relatively small hydraulic diameter. When the hydraulic diameter is small, it can be understood that the arrangement density of the second protrusions 91 is greater, with more second protrusions 91 for the same length, thus significantly increasing the heat exchange area and improving the heat exchange effect.

[0083] From another perspective: when the arrangement density of the second protrusion 91 is greater, that is, the cross-sectional area of ​​the flow channel will be smaller, then according to the flow velocity calculation formula: V=G / A, under the same flow rate G, the smaller the cross-sectional area A of the flow channel, the greater the flow velocity V, and the greater the flow velocity, the greater the heat transfer coefficient, thus greatly improving the heat exchange effect.

[0084] In summary, the first working fluid inlet pipe of the compact heat exchanger of the present invention extends in the same direction as the inlet of the first working fluid channel, while the second working fluid inlet pipe is cross-connected to the inlet of the second working fluid channel. Therefore, the first and second working fluid inlets can not only be evenly distributed around the heat exchanger, improving space utilization, but also, because the second working fluid needs to make a bend when entering the second working fluid channel through the second working fluid inlet pipe, the turbulence of the second working fluid is increased, making the second working fluid more uniform and thus improving the heat exchange performance with the first working fluid.

[0085] The above embodiments are only used to illustrate the technical solutions of the present invention and are not intended to limit it. Although the present invention has been described in detail with reference to preferred embodiments, those skilled in the art should understand that modifications or equivalent substitutions can be made to the technical solutions of the present invention without departing from the spirit and scope of the technical solutions of the present invention.

Claims

1. A compact heat exchanger, characterized in that: It includes multiple heat exchange plates stacked sequentially in the vertical direction, a first working fluid channel and a second working fluid channel formed between each pair of adjacent heat exchange plates and alternately arranged in the vertical direction, a first working fluid inlet pipe connected to a plurality of first working fluid channels, and a second working fluid inlet pipe connected to a plurality of second working fluid channels. The extension direction of the first working fluid inlet pipe is the same as the extension direction at the inlet of the first working fluid channel, and the second working fluid inlet pipe is cross-connected to the inlet of the second working fluid channel. The heat exchange plate includes a first heat exchange plate and a second heat exchange plate stacked sequentially and spaced apart in the vertical direction. The first heat exchange plate includes a first gasket and a first heat exchange plate stacked on top of each other, and the second heat exchange plate includes a second gasket and a second heat exchange plate stacked on top of each other. The first heat exchange plate has a transition zone and a heat exchange zone along the direction from the inlet to the outlet of the first working fluid channel, a plurality of first protrusions formed in the transition zone, and a plurality of second protrusions formed in the heat exchange zone, with the two transition zones located on both sides of the heat exchange zone respectively. The second heat exchange plate has a transition zone and a heat exchange zone along the direction from the inlet to the outlet of the second working fluid channel, a plurality of first protrusions formed in the transition zone, and a plurality of second protrusions formed in the heat exchange zone, with the two transition zones located on both sides of the heat exchange zone respectively. The first and second protrusions are both unidirectional protrusions formed by stamping. The protrusions are hollow and form cavities. The protrusion height of the first and second protrusions is consistent with the thickness of the first gasket, the first heat exchange plate, the second gasket, and the second heat exchange plate, and is not greater than 0.1 mm. The first protrusion and the second protrusion are both arranged to protrude in the same direction. The second protrusion of the first heat exchange plate and the second protrusion of the second heat exchange plate are eccentrically arranged. A part of the second protrusion of the first heat exchange plate abuts against the bottom surface of the second heat exchange plate, and the other part faces the cavity of the second protrusion of the second heat exchange plate. A part of the second protrusion of the second heat exchange plate abuts against the bottom surface of the first heat exchange plate, and the other part faces the cavity of the second protrusion of the first heat exchange plate.

2. The compact heat exchanger as described in claim 1, characterized in that: The heat exchange plate has a first recess on each side that communicates with the first working fluid channel. The compact heat exchanger also includes a connecting plate disposed in the first recess and a distribution cavity formed between the connecting plate and the inlet of the working fluid channel. The first working fluid inlet pipe passes through the connecting plate to communicate with the distribution cavity.

3. The compact heat exchanger as described in claim 2, characterized in that: The heat exchange plate also has a second recess formed by further recessing the two inner walls opposite to the first recess, and the connecting plate is disposed in the second recess.

4. The compact heat exchanger as described in claim 1, characterized in that: The heat exchange plate also has a through hole for communicating with the second working fluid channel, and the second working fluid inlet pipe is connected to the through hole.

5. The compact heat exchanger as described in claim 4, characterized in that: The compact heat exchanger also includes a second working fluid outlet pipe connected to the through hole, and the second working fluid inlet pipe and the second working fluid outlet pipe are arranged on the same side.

6. The compact heat exchanger as described in claim 5, characterized in that: The inner diameters of the first working fluid inlet pipe and the second working fluid outlet pipe are different.

7. The compact heat exchanger as described in claim 4, characterized in that: The inlet and outlet of the first working fluid channel are of different sizes.

8. The compact heat exchanger as described in claim 4, characterized in that: The through holes are arranged diagonally on both sides of the heat exchange plate, and the inlet of the first working fluid channel and the inlet of the second working fluid channel are not located on the same side.

9. The compact heat exchanger as described in claim 2, characterized in that: The first working fluid inlet pipe does not protrude into the working fluid distribution chamber.

10. The compact heat exchanger as claimed in claim 1, characterized in that: The compact heat exchanger also includes a sequence identification structure to prevent incorrect stacking order of the first and second heat exchange plates, the sequence identification structure being a notch recessed from one side of the first or second heat exchange plate.

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