Variable cross-section composite corrugated plate flow guide bulge reinforced heat exchanger

Abstract

The utility model discloses a variable cross-section composite corrugated plate flow guide bulge reinforced heat exchanger, which relates to the technical field of heat exchangers and comprises a brazed plate heat exchanger body. The brazed plate heat exchanger body is provided with a hot fluid inlet, a hot fluid outlet, a cold fluid inlet and a cold fluid outlet; the brazed plate heat exchanger body is provided with a plurality of plates which are stacked in sequence; a medium total channel is formed between every two adjacent plate sheets; the medium main channel is provided with a plurality of V-shaped flow channels, and a plurality of flow guide protrusions are fixedly arranged on the inner side walls of the V-shaped flow channels. The medium main channel for the hot fluid to flow through is correspondingly communicated with the hot fluid inlet and the hot fluid outlet; a medium main channel through which cold fluid flows is correspondingly communicated with the cold fluid inlet and the cold fluid outlet; and the medium main channels for the hot fluid to flow through and the medium main channels for the cold fluid to flow through are sequentially arranged in a staggered manner. The liquid film continuity can be destroyed, oil film updating is promoted, local turbulence can be induced, and the heat exchange effect is improved.

Description

Technical Field

[0001] This utility model relates to the field of heat exchanger technology, and in particular to a variable cross-section composite corrugated plate heat exchanger with flow-guiding protrusions. Background Technology

[0002] A brazed plate heat exchanger is a high-efficiency heat exchanger made by brazing a series of metal plates with a certain corrugated shape.

[0003] As the temperature of the machine tool processing oil decreases, the viscosity of the oil increases, which increases the flow resistance. The continuous liquid film covering the flow channel wall will hinder heat exchange. Therefore, the use of traditional brazed plate heat exchangers will result in poor heat exchange effect and is not suitable for oil cooling. Utility Model Content

[0004] The purpose of this invention is to provide a variable cross-section composite corrugated plate heat exchanger with enhanced flow guidance protrusions to solve the problems existing in the prior art. It can disrupt the continuity of the liquid film, promote oil film renewal, and induce local turbulence to improve the heat exchange effect.

[0005] To achieve the above objectives, this utility model provides the following solution:

[0006] This utility model provides a variable cross-section composite corrugated plate heat exchanger with enhanced flow guidance protrusions, including a brazed plate heat exchanger body; the brazed plate heat exchanger body has a hot fluid inlet, a hot fluid outlet, a cold fluid inlet, and a cold fluid outlet; and the brazed plate heat exchanger body has multiple plates stacked sequentially; a general medium channel is formed between two adjacent plates; the general medium channel has multiple V-shaped flow channels, and multiple flow guidance protrusions are fixedly arranged on the inner sidewall of the V-shaped flow channels; the direction of the plate towards or away from another plate is a first direction, and the height direction of the flow guidance protrusions is parallel to the first direction. The height direction of the guide protrusion, the width direction of the guide protrusion, and the fluid flow direction are all perpendicular to each other; the width of the guide protrusion is less than the width of the flow channel at the corresponding position of the V-shaped flow channel, and the height of the guide protrusion is less than the height of the flow channel at the corresponding position of the V-shaped flow channel; the total medium channel for hot fluid flow is connected to the hot fluid inlet and the hot fluid outlet respectively; the total medium channel for cold fluid flow is connected to the cold fluid inlet and the cold fluid outlet respectively; and the total medium channel for hot fluid flow and the total medium channel for cold fluid flow are arranged alternately.

[0007] Preferably, the width of the guide protrusion is less than 1 / 2 of the width of the flow channel at the corresponding position of the V-shaped flow channel; and the height of the guide protrusion is 1 / 3 to 1 / 2 of the height of the flow channel at the corresponding position of the V-shaped flow channel.

[0008] Preferably, the V-shaped flow channel includes a first straight channel and a second straight channel, the first straight channel and the second straight channel are arranged in a V-shape and connected at their ends; a flow guide protrusion is provided at the middle of the first straight channel, the middle of the second straight channel and the connection between the first straight channel and the second straight channel.

[0009] Preferably, at least a portion of the flow channel between the inlet and outlet of the main medium channel has a gradually increasing cross-sectional area.

[0010] Preferably, the main medium channel includes a main inlet, a main outlet, and multiple flow units; each flow unit includes multiple V-shaped channels that are sequentially connected end-to-end; the inlet end of the V-shaped channel near the main inlet is connected to the main inlet, and the outlet end of the V-shaped channel near the main outlet is connected to the main outlet; the cross-sectional area of ​​the flow channel from the inlet end to the outlet end of the V-shaped channel gradually increases; and the cross-sectional area of ​​the flow channel of each V-shaped channel from the main inlet to the main outlet also gradually increases.

[0011] Preferably, the angle between the first straight channel and the second straight channel is 60° to 100°.

[0012] Preferably, on the cross-sectional plane formed by the height direction and the width direction of the guide protrusion, the cross-sectional shape of the guide protrusion is triangular or trapezoidal.

[0013] Preferably, the height of the V-shaped flow channel is 2mm to 4mm.

[0014] Preferably, the flow direction of the hot fluid in the main medium channel is opposite to the flow direction of the cold fluid in the two adjacent main medium channels.

[0015] Preferably, the flow unit further includes multiple connecting channels; the V-shaped flow channels of each flow unit are arranged in parallel; in the fluid flow direction, the corresponding outlet end of the V-shaped flow channel of each flow unit is connected to a connecting channel, and the connecting channel is connected to the corresponding inlet end of the V-shaped flow channel of each flow unit in the next level.

[0016] The present invention achieves the following technical advantages over the prior art:

[0017] The variable cross-section composite corrugated plate heat exchanger with guided protrusions provided by this utility model features guided protrusions that extend from the inner wall of a V-shaped flow channel. The width and height of these protrusions are smaller than the dimensions of the corresponding positions within the flow channel. When fluid flows through these protrusions, they disrupt the continuity of the liquid film, promoting oil film renewal and preventing the formation of a continuous and stable laminar film flow. In laminar flow, the fluid adheres tightly to the wall, forming a thick, stagnant liquid film with high thermal resistance. The presence of the guided protrusions forces the liquid film to break and separate at the protrusions, forming discrete fluid clusters or vortices, thus disrupting the continuity of the liquid film. The fluid flows through the guided... When a flow protrusion occurs, the sudden change in the flow channel cross-section (the flow channel narrows at the protrusion) creates a local low-pressure zone behind the protrusion, leading to boundary layer separation. The separated fluid forms vortices downstream of the protrusion, drawing in the stagnant liquid film near the wall to the mainstream region, while simultaneously pushing fresh fluid from the mainstream region towards the wall, thus renewing the liquid film. The guide protrusions generate multi-directional disturbances to the fluid. The distributed arrangement of the guide protrusions creates continuous turbulence induction points throughout the flow channel, causing local turbulent regions to overlap and ultimately forming a strong disturbance flow field throughout the entire medium channel, significantly improving the heat transfer coefficient. Attached Figure Description

[0018] To more clearly illustrate the technical solutions in the embodiments of this utility model or the prior art, the drawings used in the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this utility model. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0019] Figure 1 A schematic diagram of the overall structure of a single plate in the variable cross-section composite corrugated plate heat exchanger with flow guiding protrusions provided by this utility model;

[0020] Figure 2 A schematic diagram of a flow channel formed by two plates with their A-sides facing each other;

[0021] Figure 3 This is a schematic diagram of a flow channel formed by two plates with their A and B sides facing each other.

[0022] In the picture:

[0023] 10 - V-shaped flow channel; 11 - First straight channel; 12 - Second straight channel;

[0024] 20-plate; 21-A side; 22-B side; 23-through hole; 24-ridge; 25-slot. Detailed Implementation

[0025] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only some embodiments of the present utility model, and not all embodiments. Based on the embodiments of the present utility model, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the protection scope of the present utility model.

[0026] The purpose of this invention is to provide a variable cross-section composite corrugated plate heat exchanger with enhanced flow guidance protrusions to solve the problems existing in the prior art. It can disrupt the continuity of the liquid film, promote oil film renewal, and induce local turbulence to improve the heat exchange effect.

[0027] To make the above-mentioned objectives, features and advantages of this utility model more apparent and understandable, the utility model will be further described in detail below with reference to the accompanying drawings and specific embodiments.

[0028] Example 1

[0029] This embodiment provides a variable cross-section composite corrugated plate heat exchanger with enhanced flow guidance protrusions, such as... Figures 1-3 As shown, it includes a brazed plate heat exchanger body; the brazed plate heat exchanger body has a hot fluid inlet, a hot fluid outlet, a cold fluid inlet, and a cold fluid outlet; and the brazed plate heat exchanger body has multiple plates 20 stacked sequentially; a medium general channel is formed between two adjacent plates 20; the medium general channel has multiple V-shaped flow channels 10, and multiple flow guiding protrusions are fixedly provided on the inner sidewall of the V-shaped flow channels 10; the direction of the plate 20 towards or away from another plate 20 is a first direction, the height direction of the flow guiding protrusion is parallel to the first direction, and the height direction of the flow guiding protrusion, the width direction of the flow guiding protrusion, and the fluid flow direction are all perpendicular to each other; the flow guiding protrusions The width of the channel is less than the channel width at the corresponding position of the V-shaped channel 10 (the channel width, channel height, and channel extension direction are perpendicular to each other, and the channel height refers to the dimension from one plate to another), and the height of the guide protrusion is less than the channel height at the corresponding position of the V-shaped channel 10; the total medium channel for hot fluid flow is connected to the hot fluid inlet and hot fluid outlet respectively; the total medium channel for cold fluid flow is connected to the cold fluid inlet and cold fluid outlet respectively; and the total medium channel for hot fluid flow and the total medium channel for cold fluid flow are arranged alternately in sequence (that is, each plate 20 is arranged alternately in sequence along the first direction).

[0030] The guide protrusions extend from the inner wall of the V-shaped flow channel 10. Their width and height are both smaller than the dimensions of the corresponding positions within the flow channel. When fluid flows through them, the guide protrusions disrupt the continuity of the liquid film, promoting film renewal and preventing the formation of a continuous and stable laminar film flow. In laminar flow, the fluid adheres tightly to the wall, forming a thick, stagnant liquid film with high thermal resistance. The presence of the guide protrusions forces the liquid film to break and separate at the protrusions, forming discrete fluid clusters or vortices, thus disrupting the continuity of the liquid film. When fluid flows through the guide protrusions, the sudden change in the flow channel cross-section... The change (narrowing of the flow channel at the protrusion) will create a local low-pressure area behind the protrusion, leading to boundary layer separation. The separated fluid forms a vortex downstream of the protrusion, which entrains the stagnant liquid film near the wall to the mainstream area, while pushing the fresh fluid in the mainstream area to the wall, thus achieving liquid film renewal. The guide protrusion will generate multi-directional disturbances to the fluid. The distributed arrangement of the guide protrusion will form continuous turbulence induction points in the entire flow channel, causing local turbulent regions to overlap, and finally forming a strong disturbance flow field in the entire medium channel, which greatly improves the heat transfer coefficient.

[0031] The following are the specifications regarding the brazed plate heat exchanger body:

[0032] Among the optional solutions in this embodiment, the more preferred one is as follows: Figure 1 As shown, the V-shaped flow channel 10 includes a first straight channel 11 and a second straight channel 12. The first straight channel 11 and the second straight channel 12 are arranged in a V-shape and their ends are connected. A flow guide protrusion is provided in the middle of the first straight channel 11, the middle of the second straight channel 12, and at the connection between the first straight channel 11 and the second straight channel 12.

[0033] Among the optional solutions in this embodiment, the more preferred one is as follows: Figure 1 As shown, the angle between the first straight channel 11 and the second straight channel 12 is 60° to 100°.

[0034] Among the optional solutions in this embodiment, the more preferred one is as follows: Figure 1 As shown, the flow unit also includes multiple connecting channels; the V-shaped flow channels 10 of each flow unit are arranged in parallel; in the direction of fluid flow, the corresponding outlet end of the V-shaped flow channel 10 of each flow unit is connected to a connecting channel, and the connecting channel is connected to the corresponding inlet end of the V-shaped flow channel 10 of each flow unit in the next level.

[0035] Specifically, the variable cross-section composite corrugated plate flow guide protrusion enhanced heat exchanger of this embodiment is a modified design based on the existing brazed plate heat exchanger: namely, flow guide protrusion, variable cross-section flow channel and deep channel design.

[0036] Specifically, through the above three modifications, it can be made suitable for use in oil coolers to cool the oil used in processing equipment such as machine tools, thereby increasing the efficiency of oil-cooled heat exchangers, reducing the operating resistance of the unit, reducing the power consumption of the unit, and increasing the overall cooling capacity.

[0037] The following are the settings instructions regarding the guide protrusions:

[0038] In the optional solutions of this embodiment, it is more preferred that the width of the guide protrusion is less than 1 / 2 of the width of the flow channel at the corresponding position of the V-shaped flow channel 10; and the height of the guide protrusion is 1 / 3 to 1 / 2 of the height of the flow channel at the corresponding position of the V-shaped flow channel 10.

[0039] Among the optional solutions in this embodiment, the more preferred one is as follows: Figure 1 As shown, on the cross-sectional plane formed by the height direction and the width direction of the guide protrusion, the cross-sectional shape of the guide protrusion is triangular or trapezoidal.

[0040] The following are the relevant settings instructions for variable cross-section flow channels:

[0041] Specifically, the cross-sectional area of ​​the flow channel gradually increases along the flow direction. For hot fluids, in the high-temperature zone at the inlet, the cross-section accelerates the flow, breaks the liquid film, and enhances turbulent heat transfer; in the low-temperature zone at the outlet, the large cross-section reduces the flow velocity and reduces pressure loss.

[0042] Among the optional solutions in this embodiment, the more preferred one is as follows: Figure 1 As shown, at least a portion of the flow channel between the inlet and outlet of the main medium channel has a gradually increasing cross-sectional area.

[0043] Among the optional solutions in this embodiment, the more preferred one is as follows: Figure 1 As shown, the main medium channel includes a main inlet, a main outlet, and multiple flow units (there are four through holes 23 at the four corners of a single plate 20, two of which are selected as the main inlet and main outlet respectively, and multiple diversion channels are set at the positions corresponding to the through holes 23. The through holes 23 are connected to multiple V-shaped flow channels 10 through the multiple diversion channels. That is, the fluid enters through a through hole 23, and is diverted through multiple diversion channels to each connected V-shaped flow channel 10, and then sequentially flows through subsequent connecting channels and the next level of V-shaped flow channels 10 to another one). The flow proceeds through the through-hole 23 in the same direction as the existing one (the arrangement of this part is the same and will not be described in detail here); the flow unit includes multiple V-shaped flow channels 10 that can be connected end to end in sequence; the inlet end of the V-shaped flow channel 10 near the main inlet can be connected to the main inlet, and the outlet end of the V-shaped flow channel 10 near the main outlet can be connected to the main outlet; the cross-sectional area of ​​the flow channel from the inlet end of the V-shaped flow channel 10 to the outlet end of the V-shaped flow channel 10 gradually increases; and the cross-sectional area of ​​the flow channel of each V-shaped flow channel 10 from the main inlet to the main outlet also gradually increases.

[0044] Specifically, a single plate 20 has multiple ridges 24 and grooves 25 arranged in a staggered pattern; there are two ways in which two plates 20 form a medium flow channel relative to each other: the first is, as shown in... Figure 2 As shown, the ridges 24 and grooves 25 on the A-side 21 and B-side 22 (A-side 21 and B-side 22 are opposite each other) of a single plate 20 are identical. The A-side 21 of one plate 20 is opposite to the A-side 21 of another plate 20. The ridges 24 on the A-side 21 of the two plates 20 are opposite to each other to form corresponding flow channels, and the grooves 25 are opposite to each other to form corresponding flow channels (similarly, the B-side 22 of the two plates 20 is opposite to the B-side 22 of other adjacent plates 20. Similarly, the ridges 24 on the surface are opposite to each other to form corresponding flow channels, and the grooves 25 are opposite to each other to form corresponding flow channels); the second type, as Figure 3 As shown, the structures of surface A 21 and surface B 22 on a single plate 20 are different. Surface A 21 on one plate 20 is opposite to surface B 22 on another plate 20. The ridge 24 of surface A 21 is opposite to the groove 25 of surface B 22. Based on the difference in curvature between the two, corresponding flow channels are formed. Similarly, the groove 25 of surface A 21 is opposite to the ridge 24 of surface B 22. Based on the difference in curvature between the two, corresponding flow channels are formed.

[0045] Specifically, Figure 2 and Figure 3 The single plate 20 corresponds to Figure 1 A side view diagram.

[0046] Specifically, the resulting flow channels have a gradually changing width, while their height remains consistent, resulting in a gradually changing cross-sectional area.

[0047] The following are the settings instructions for deep channels:

[0048] Among the optional solutions in this embodiment, the more preferred one is as follows: Figure 1 As shown, the height of the V-shaped flow channel 10 is 2mm to 4mm (that is, the height of the V-shaped flow channel 10 formed on a single plate 20 is 1mm to 2mm, which is deeper than the traditional height of 0.5mm to 1mm).

[0049] Regarding other related settings:

[0050] Among the optional solutions in this embodiment, the more preferred one is as follows: Figure 1 As shown, the flow direction of the hot fluid in the main medium channel is opposite to the flow direction of the cold fluid in the two adjacent main medium channels.

[0051] Specifically, the material of plate 20 can be oil-resistant titanium alloy / stainless steel with nickel plating.

[0052] Specifically, other related settings of the brazed plate heat exchanger body can be the same as the existing settings, including but not limited to the hot fluid inlet and hot fluid outlet being on the same side or on opposite sides; the same applies to the cold fluid inlet and cold fluid outlet.

[0053] Specifically, the processing of plate 20 involves laser cutting of a variable cross-section corrugated plate with precision controlled within ±0.1mm; the brazing process uses silver-based brazing filler metal (Sn-Ag-Cu alloy) in a vacuum furnace at a temperature of 600℃-650℃.

[0054] Assembly process: 20-layer plate stack → fixing with locating pins → vacuum brazing → pressure test (1.5 times working pressure).

[0055] This utility model uses specific examples to illustrate its principles and implementation methods. The above description of the embodiments is only for the purpose of helping to understand the method and core idea of ​​this utility model. At the same time, for those skilled in the art, there will be changes in the specific implementation methods and application scope based on the idea of ​​this utility model. In summary, the content of this specification should not be construed as a limitation of this utility model.

Claims

1. A variable cross-section composite corrugated plate heat exchanger with enhanced flow guidance protrusions, characterized in that: Including the body of the brazed plate heat exchanger; The brazed plate heat exchanger body has a hot fluid inlet, a hot fluid outlet, a cold fluid inlet, and a cold fluid outlet; and the brazed plate heat exchanger body has multiple plates stacked sequentially; a general medium channel is formed between two adjacent plates; The main medium channel has multiple V-shaped flow channels, and multiple flow-guiding protrusions are fixedly provided on the inner sidewalls of the V-shaped flow channels; the direction of the plate towards or away from another plate is a first direction, the height direction of the flow-guiding protrusions is parallel to the first direction, and the height direction, width direction, and fluid flow direction of the flow-guiding protrusions are all perpendicular to each other; the width of the flow-guiding protrusions is less than the width of the flow channel at the corresponding position of the V-shaped flow channel, and the height of the flow-guiding protrusions is less than the height of the flow channel at the corresponding position of the V-shaped flow channel; The main medium channels through which hot fluid flows are connected to the hot fluid inlet and the hot fluid outlet respectively; the main medium channels through which cold fluid flows are connected to the cold fluid inlet and the cold fluid outlet respectively; and the main medium channels through which hot fluid flows and the main medium channels through which cold fluid flows are arranged alternately in sequence.

2. The variable cross-section composite corrugated plate heat exchanger with flow-guiding protrusions as described in claim 1, characterized in that: The width of the guide protrusion is less than 1 / 2 of the width of the flow channel at the corresponding position of the V-shaped flow channel; and the height of the guide protrusion is 1 / 3 to 1 / 2 of the height of the flow channel at the corresponding position of the V-shaped flow channel.

3. The variable cross-section composite corrugated plate heat exchanger with enhanced flow guide protrusions according to claim 1, characterized in that: The V-shaped flow channel includes a first straight channel and a second straight channel, which are arranged in a V-shape and connected at their ends. A flow-guiding protrusion is provided at the middle of the first straight channel, the middle of the second straight channel, and at the connection between the first straight channel and the second straight channel.

4. The variable cross-section composite corrugated plate heat exchanger with enhanced flow guide protrusions according to claim 1, characterized in that: At least a portion of the flow channel between the inlet and outlet of the main medium channel has a gradually increasing cross-sectional area.

5. The variable cross-section composite corrugated plate heat exchanger with flow-guiding protrusions as described in claim 4, characterized in that: The media channel includes a main inlet, a main outlet, and multiple flow units; The flow unit includes a plurality of V-shaped channels that are connected end to end in sequence; the inlet end of the V-shaped channel near the main inlet is connected to the main inlet, and the outlet end of the V-shaped channel near the main outlet is connected to the main outlet. The cross-sectional area of ​​the flow channel from the inlet end to the outlet end of the V-shaped flow channel gradually increases; and the cross-sectional area of ​​the flow channel of each of the V-shaped flow channels from the total inlet to the total outlet also gradually increases.

6. The variable cross-section composite corrugated plate heat exchanger with enhanced flow guide protrusions according to claim 3, characterized in that: The angle between the first straight channel and the second straight channel is 60° to 100°.

7. The variable cross-section composite corrugated plate heat exchanger with enhanced flow guide protrusions according to claim 2, characterized in that: On the cross-sectional plane formed by the height direction and the width direction of the guide protrusion, the cross-sectional shape of the guide protrusion is triangular or trapezoidal.

8. The variable cross-section composite corrugated plate heat exchanger with flow-guiding protrusions according to claim 2, characterized in that: The height of the V-shaped flow channel is 2mm to 4mm.

9. The variable cross-section composite corrugated plate heat exchanger with flow-guiding protrusions as described in claim 1, characterized in that: The flow direction of the hot fluid in the main medium channel is opposite to the flow direction of the cold fluid in the two adjacent main medium channels.

10. The variable cross-section composite corrugated plate heat exchanger with flow-guiding protrusions according to claim 5, characterized in that: The circulation unit also includes multiple connecting channels; the V-shaped flow channels of each circulation unit are arranged in parallel. In the direction of fluid flow, the corresponding outlet end of the V-shaped flow channel of each of the flow units is connected to a connecting channel, and the connecting channel is connected to the corresponding inlet end of the V-shaped flow channel of each of the next flow units.

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