Enhanced heat transfer and exchange assembly
By combining the flow guide shroud, honeycomb plate and spiral flow guide groove, the problems of low heat transfer efficiency and equipment vibration in traditional MVR evaporators are solved, achieving efficient and stable flow rate control and energy consumption reduction, and extending the service life of the equipment.
Patent Information
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- Filing Date
- 2025-04-10
- Publication Date
- 2026-03-03
AI Technical Summary
In the treatment of industrial wastewater with elevated boiling points, traditional MVR evaporators suffer from low heat transfer efficiency, large pressure loss due to eddy currents caused by sudden changes in flow velocity, high energy consumption, increased equipment vibration, and shortened lifespan of seals. Existing turbulence devices cannot effectively address the relationship between flow velocity and pressure drop.
The system employs a combination of a flow guide and a honeycomb plate flow stabilizer. The flow guide is a variable diameter tubular shape that buffers sudden changes in steam velocity. The three-stage cone gradually narrows the flow velocity, the honeycomb plate breaks up large eddies, the spiral guide groove enhances flow uniformity, and the guide plate guides the edge velocity to form a stable flow field and reduce turbulence losses.
It improves heat transfer efficiency, reduces system energy consumption, extends equipment life, reduces vibration, lowers maintenance costs, and is simple to modify and easy to disassemble and clean.
Smart Images
Figure CN223965934U_ABST
Abstract
Description
Technical Field
[0001] This utility model relates to the field of MVR evaporator technology, and in particular to an enhanced heat transfer component. Background Technology
[0002] In MVR evaporation systems, the heat transfer efficiency of heat exchange components directly affects system energy consumption and operational stability, but traditional heat exchangers have the following technical bottlenecks.
[0003] Conventional steam inlets employ straight pipes or simple flared structures. When steam enters the shell, abrupt changes in cross-sectional area create turbulence, resulting in a parabolic velocity distribution with high speeds at the center and low speeds at the edges. This structure leads to insufficient utilization of the effective heat transfer area and decreased evaporation efficiency. The eddies caused by sudden changes in steam velocity can cause pressure losses exceeding 3.5 kPa, corresponding to energy losses accounting for 20%-25% of the total system energy consumption. Especially when treating industrial wastewater with elevated boiling points, the conventional structure struggles to balance the relationship between flow velocity and pressure drop, requiring additional steam to maintain operation. Furthermore, the vibration acceleration caused by high-frequency eddies can reach 4.5 m / s². 2 This results in a reduction of seal life by more than 30%. Although existing technologies employ flow-disrupting devices such as baffles, they cannot eliminate the radial velocity component and instead exacerbate local flow velocity anomalies.
[0004] In view of this, there is an urgent need to develop a heat transfer component that can achieve efficient conversion of steam kinetic energy while ensuring long-term stable operation under complex working conditions. Utility Model Content
[0005] In view of this, the present invention proposes an enhanced heat transfer component.
[0006] The technical solution of this utility model is implemented as follows: This utility model provides an enhanced heat transfer component, which includes: a shell-and-tube heat exchanger and a steam inlet pipe, the steam inlet pipe being connected to the shell side of the shell-and-tube heat exchanger, and further includes: a flow guide and a honeycomb plate flow stabilizer. The flow guide is a variable diameter tubular structure, and the flow guide is disposed within the shell side of the shell-and-tube heat exchanger. One end of the flow guide with a larger opening is directly opposite the outlet of the steam inlet pipe and is spaced apart from the outlet. The honeycomb plate flow stabilizer is spaced apart at one end of the flow guide with a smaller opening.
[0007] In the above embodiments, the steam inlet and the guide shroud are kept at a distance to form a buffer space, avoiding the flow velocity impact caused by abrupt changes in cross-sectional area. The guide shroud with a variable diameter tubular structure achieves a relatively smooth transition of flow velocity. The boundary layer separation effect reduces the turbulent core area. The honeycomb plate flow stabilizer breaks the large eddies of the exhaust gas into smaller eddies, improving the uniformity of the flow field. This structure can reduce pressure drop loss, improve heat transfer efficiency, and significantly enhance vibration resistance.
[0008] In some embodiments, the flow deflector includes three-stage cones connected in series, with the cone angle of the three stages decreasing sequentially along the steam inlet pipe toward the axis of the shell-and-tube heat exchanger.
[0009] The use of a three-stage cone with progressively decreasing cone angles can reduce kinetic energy loss caused by eddies. The gradient design of the cone angles can eliminate resonant frequencies and extend the service life of the equipment.
[0010] In some embodiments, the cone angles of the three-stage cones are 45°, 35° and 25° respectively, along the direction from the steam inlet pipe toward the axis of the shell-and-tube heat exchanger.
[0011] The first-stage cone can rapidly shrink its cross-sectional area, reducing the initial peak steam velocity; the second-stage cone can further shrink to form a laminar flow transition zone; and the third-stage cone can finely adjust the flow velocity, improving the uniformity of the outlet flow velocity.
[0012] In some embodiments, a spiral guide groove is formed on the inner wall of the guide shield along the axial direction.
[0013] In the above embodiments, the steam is subjected to the shear force of the channel, forming a composite axial and circumferential flow, thereby improving the uniformity of the flow field.
[0014] In some implementations, the depth of the spiral guide groove is 1.2-1.5 mm, and the pitch is 8-10 mm.
[0015] In some embodiments, the spiral guide grooves include two spiral directions with opposite directions, and the number of spiral guide grooves in both directions is the same.
[0016] In the above embodiments, the double helix direction can counteract the centrifugal effect caused by unidirectional rotation, and the standard deviation of the radial velocity component is reduced.
[0017] In some embodiments, the honeycomb plate current stabilizer has a side-to-side distance of 2.5 mm and a wall thickness of 0.6 mm.
[0018] In some implementations, the axial distance between the honeycomb panel flow stabilizer and the flow guide is 30 mm.
[0019] In some embodiments, the axial distance between the deflector and the outlet of the steam inlet pipe is 50 mm.
[0020] In some embodiments, a flow guide plate is also included. The flow guide plate is disposed on the side of the honeycomb plate flow stabilizer away from the flow guide shroud. The flow guide plate forms a 15° angle with the axis of the flow guide shroud. Multiple flow guide plates are arranged in a circumferential array along the honeycomb plate flow stabilizer and are arranged radially.
[0021] The guide vanes are arranged in a circumferential array at a 15° angle and are located downstream of the honeycomb plate flow stabilizer. The angled design can guide the high-speed steam in the center to the edge of the shell side, thereby increasing the flow velocity at the edge. The circumferential array layout can eliminate heat transfer dead zones and improve the effective heat transfer area coverage.
[0022] The present invention has the following advantages over the prior art:
[0023] This utility model utilizes a variable-diameter guide shroud structure to eliminate abrupt changes in steam velocity, thereby increasing the uniformity index of the velocity field within the shell side and improving the utilization rate of the effective heat transfer area. The buffer space design between the guide shroud and the steam outlet, combined with the stepped contraction of the variable-diameter pipe, reduces energy loss in the turbulent core area, lowers pressure drop, and reduces the overall system energy consumption. The spaced arrangement of the honeycomb plate flow stabilizer and the guide shroud forms a pre-stabilized flow zone, disrupting the periodic shedding of eddies, reducing equipment vibration acceleration, and extending the life of seals. The non-contact layout of the guide shroud and the steam inlet pipe allows for direct replacement of traditional straight pipe inlets, resulting in a short modification period. Furthermore, the modular design of the honeycomb plate facilitates disassembly and cleaning, leading to low maintenance costs. Attached Figure Description
[0024] To more clearly illustrate the technical solutions in the embodiments of this utility model or the prior art, the drawings used in the description of the embodiments or the prior art 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.
[0025] Figure 1 This is a main sectional view of the enhanced heat transfer component of this utility model.
[0026] Figure 2 This is a main cross-sectional view of the flow guide shroud part in the enhanced heat transfer component of this utility model.
[0027] In the figure: 1-shell and tube heat exchanger, 2-steam inlet pipe, 3-flow guide shroud, 4-honeycomb plate flow stabilizer, 5-flow guide plate, 31-spiral flow guide groove. Detailed Implementation
[0028] The technical solutions of this utility model will be clearly and completely described below with reference to the embodiments of this utility model. Obviously, the described embodiments are only a part of the embodiments of this utility model, and not all of them. Based on the embodiments of this utility model, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the protection scope of this utility model.
[0029] It should be noted that when a component is referred to as being "fixed to" or "set on" another component, it can be directly on or indirectly on that other component. When a component is referred to as being "connected to" another component, it can be directly connected to or indirectly connected to that other component.
[0030] It should be understood that the terms "length", "width", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this application.
[0031] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this application, "multiple" means two or more, unless otherwise explicitly specified.
[0032] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which the embodiments of this invention pertain. If any definition stated in this section is contrary to or otherwise inconsistent with a definition stated in a patent, patent application, published patent application, or other publication incorporated herein by reference, the definitions listed here shall prevail over those incorporated herein by reference.
[0033] like Figure 1 As shown, combined with Figure 2 The enhanced heat transfer component of this utility model includes: a shell-and-tube heat exchanger 1 and a steam inlet pipe 2, the steam inlet pipe 2 being connected to the shell side of the shell-and-tube heat exchanger 1; and also includes: a flow guide 3 and a honeycomb plate flow stabilizer 4. The flow guide 3 is a variable diameter tubular structure and is disposed within the shell side of the shell-and-tube heat exchanger 1. The end of the flow guide 3 with the larger opening is directly opposite the outlet of the steam inlet pipe 2 and is spaced apart from the outlet. The honeycomb plate flow stabilizer 4 is spaced apart at the end of the flow guide 3 with the smaller opening.
[0034] In the above embodiments, the large opening end of the flow guide shroud 3 is connected to the inner wall of the shell-and-tube heat exchanger 1 via a flange, and an elastic clamp is embedded in the outer edge of the honeycomb plate, which is connected to the inner wall of the shell-and-tube heat exchanger 1. After steam is ejected from the outlet of the inlet pipe 2, it first enters the buffer space 50mm in front of the flow guide shroud 3, and then gradually contracts through three stages of cones. The compressed steam is then sprayed into the space between the honeycomb plate flow stabilizer 4 and the flow guide shroud 3, and then enters the honeycomb holes of the honeycomb plate flow stabilizer 4. The regular hexagonal honeycomb holes break the large steam eddies into micro-scale vortices, improving the turbulent kinetic energy dissipation rate. This scheme can be retrofitted into existing shell-and-tube heat exchangers. The retrofit method is simple, the structure is entirely static, and the failure rate is low.
[0035] In some embodiments, the flow guide shroud 3 includes three-stage cones connected in series, with the cone angle of the three-stage cones decreasing sequentially along the axial direction from the steam inlet pipe 2 toward the shell-and-tube heat exchanger 1.
[0036] In the above embodiments, the first-stage cone has a large cone angle, which can quickly reduce the flow velocity of the steam discharged from the steam inlet pipe 2, thereby reducing its Reynolds number. The second-stage cone has a smaller cone angle than the first-stage cone, which can help the steam form a laminar transition zone and reduce the boundary layer thickness. The third-stage cone has a smaller cone angle than the second-stage cone, which can finely adjust the flow velocity distribution and thus improve the uniformity of the outlet velocity field.
[0037] In the above embodiments, different cones can be connected by welding or by using flanges.
[0038] In some embodiments, along the axial direction of the steam inlet pipe 2 toward the shell-and-tube heat exchanger 1, the cone angles of the three-stage cones are 45°, 35° and 25°, respectively.
[0039] In the above embodiments, the circumferential length of the cone with a 45° cone angle accounts for 35% of the total length of the guide shroud, the inlet diameter is 1.2 times the diameter of the steam inlet pipe, and the contraction ratio is 1:0.8; the length of the cone with a 35° cone angle accounts for 40%, and the contraction ratio is 1:0.6; the length of the cone with a 25° cone angle accounts for 25%, and the contraction ratio is 1:0.4.
[0040] The above-mentioned dimensional design ensures a continuous transition in flow rate.
[0041] In some embodiments, the inner wall of the flow guide shroud 3 is provided with a spiral flow guide groove 31 along the axial direction.
[0042] The spiral guide channel 31 can induce steam to generate circumferential rotational flow, reduce the boundary layer thickness, and increase the wall turbulence intensity and convective heat transfer coefficient after the formation of vortices.
[0043] In some embodiments, the depth of the spiral guide groove 31 is 1.2-1.5 mm, and the pitch is 8-10 mm.
[0044] In the above embodiment, the depth from the bottom of the tank to the inner wall of the guide shroud gradually decreases from 1.5 mm at the inlet section to 1.2 mm at the outlet, forming a converging flow channel. The inlet section has a pitch of 10 mm (guide angle 18°), and the outlet section has a pitch of 8 mm (guide angle 14°), with a decreasing spiral helix angle gradient of 0.8° / 100 mm. This embodiment, through its innovative spiral guide trough design, achieves a significant breakthrough in efficient steam kinetic energy conversion, anti-fouling performance, and equipment reliability, providing a revolutionary enhanced heat transfer solution for scenarios such as high-salt wastewater treatment and food concentration.
[0045] In some embodiments, two types of spiral guide grooves 31 with opposite spiral directions are included, and the number of spiral guide grooves 31 with the two spiral directions is the same.
[0046] In the above embodiments, 12 clockwise and 12 counterclockwise spiral grooves are used, with an overlap rate of 15-20% between adjacent grooves. Inverted V-shaped grooves are machined at the ends of the grooves to utilize steam shear force to peel away deposits. The bidirectional spiral staggered layout enhances radial heat conduction and improves the temperature field uniformity index. The inverted V-shaped grooves generate localized turbulence, applying pulsating shear force to the deposits and significantly reducing the scaling rate.
[0047] In some embodiments, the honeycomb plate current stabilizer 4 has a side-to-side distance of 2.5 mm and a wall thickness of 0.6 mm.
[0048] The honeycomb pores are arranged in a tight hexagonal lattice with a center-to-center distance of 3.1 mm between adjacent pores. The pore axis is parallel to the steam flow direction. The regular hexagonal pores break the large steam eddies (diameter > 10 mm) into micro-scale vortices (diameter < 1 mm), thereby increasing the turbulent kinetic energy dissipation rate. The hydraulic diameter of the regular hexagonal pores is larger than that of circular pores of the same area.
[0049] In some embodiments, the axial distance between the honeycomb panel flow stabilizer 4 and the flow guide 3 is 30 mm.
[0050] The distance between the honeycomb panel flow stabilizer 4 and the small end outlet of the flow guide 3 is strictly set to 30±0.5mm. The 30mm distance forms a low-speed mixing zone, which improves the turbulent kinetic energy dissipation rate and reduces the wall shear stress.
[0051] In some embodiments, the axial distance between the flow guide shroud 3 and the outlet of the steam inlet pipe 2 is 50 mm.
[0052] In the above embodiments, the axial distance between the large end opening of the flow guide shroud 3 and the outlet of the steam inlet pipe 2 is strictly maintained at 50±1mm. The 50mm distance forms a low-speed premixing zone to suppress turbulence.
[0053] In some embodiments, a flow guide plate 5 is also included. The flow guide plate 5 is disposed on the side of the honeycomb plate flow stabilizer 4 away from the flow guide shroud 3. The flow guide plate 5 forms a 15° angle with the axis of the flow guide shroud 3. Multiple flow guide plates 5 are arranged in a circumferential array along the honeycomb plate flow stabilizer 4 and are arranged radially.
[0054] In the above embodiments, the root of the guide plate 5 is welded to the outer ring plate of the honeycomb plate flow stabilizer 4. The 15° tilt angle guides the high-speed steam in the center to the edge of the shell side, increasing the edge flow velocity, eliminating the heat transfer dead zone, and the radially arranged guide plates destroy the circumferential swirling flow, reducing the standard deviation of the radial velocity component.
[0055] The above description is only a preferred embodiment of the present utility model and is not intended to limit the present utility model. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present utility model should be included within the protection scope of the present utility model.
Claims
1. A heat transfer enhancement component, comprising: The shell-and-tube heat exchanger (1) and the steam inlet pipe (2) are connected to the shell side of the shell-and-tube heat exchanger (1). The steam inlet pipe (2) is connected to the shell side of the shell-and-tube heat exchanger (1). The steam inlet pipe (2) is connected to the shell side of the shell-and-tube heat exchanger (1). The steam inlet pipe (2) is connected to the shell side of the shell-and-tube heat exchanger (1). The larger opening of the steam inlet pipe (3) is directly opposite the outlet of the steam inlet pipe (2) and is spaced apart from the outlet. The steam inlet pipe (4) is spaced apart at the smaller opening of the steam inlet pipe (3).
2. The enhanced heat transfer component as described in claim 1, characterized in that... The flow guide shroud (3) includes three-stage cones connected in series. Along the axial direction of the steam inlet pipe (2) toward the shell-and-tube heat exchanger (1), the cone angle of the three-stage cones decreases sequentially.
3. The enhanced heat transfer component as described in claim 2, characterized in that, Along the axial direction of the steam inlet pipe (2) toward the shell-and-tube heat exchanger (1), the cone angles of the three-stage cones are 45°, 35° and 25° respectively.
4. The enhanced heat transfer component as described in claim 1, characterized in that, The inner wall of the flow guide (3) is provided with a spiral flow guide groove (31) along the axial direction.
5. The enhanced heat transfer component as described in claim 4, characterized in that, The depth of the spiral guide groove (31) is 1.2-1.5mm and the pitch is 8-10mm.
6. The enhanced heat transfer component as described in claim 4, characterized in that, It includes two types of spiral guide grooves (31) with opposite spiral directions, and the number of spiral guide grooves (31) with the two spiral directions is the same.
7. The enhanced heat transfer component as described in claim 1, characterized in that, The honeycomb plate current stabilizer (4) has a honeycomb hole spacing of 2.5 mm and a wall thickness of 0.6 mm.
8. The enhanced heat transfer component as described in claim 1, characterized in that, The axial distance between the honeycomb plate flow stabilizer (4) and the flow guide (3) is 30mm.
9. The enhanced heat transfer component as described in claim 1, characterized in that, The axial distance between the air guide shroud (3) and the outlet of the steam inlet pipe (2) is 50 mm.
10. The enhanced heat transfer component as described in claim 1, characterized in that, It also includes a guide plate (5), which is set on the side of the honeycomb plate flow stabilizer (4) away from the flow guide shroud (3). The guide plate (5) forms a 15° angle with the axis of the flow guide shroud (3). Multiple guide plates (5) are arranged in a circumferential array along the honeycomb plate flow stabilizer (4) and are arranged radially.