CN213067200U - Axial blade reverse rotational flow heat exchange sleeve - Google Patents
Axial blade reverse rotational flow heat exchange sleeve Download PDFInfo
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- CN213067200U CN213067200U CN202021065319.XU CN202021065319U CN213067200U CN 213067200 U CN213067200 U CN 213067200U CN 202021065319 U CN202021065319 U CN 202021065319U CN 213067200 U CN213067200 U CN 213067200U
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Abstract
The utility model relates to the technical field of fluid heat transfer, more specifically, relate to a reverse whirl heat transfer sleeve pipe of axial blade, including first pipe and second pipe, the second pipe is worn to locate in the first pipe, and the first pipe is equipped with the first water inlet that flows in the hot-fluid, and the second pipe is equipped with the second water inlet that flows in the cold fluid, and the hot-fluid is opposite with the flow direction of cold fluid; a first rotational flow component is arranged at the first water inlet and rotatably sleeved on the outer wall of the second pipe, and the first rotational flow component is positioned between the first pipe and the second pipe; and a second rotational flow component is arranged at the second water inlet and is rotatably arranged in the second pipe. The first rotational flow component and the second rotational flow component of the utility model can rotate automatically, thereby promoting the flow of fluid and improving the heat convection efficiency; part of the pressure loss is reasonably converted, and the effective utilization rate of energy is improved; just the utility model discloses the cold fluid is opposite with the flow direction of hot-fluid, and heat transfer sheathed tube local area obtains temperature resistant protection, extension heat transfer sheathed tube life.
Description
Technical Field
The utility model relates to a technical field of fluid heat transfer, more specifically relates to a reverse whirl heat transfer sleeve pipe of axial blade.
Background
In the industrial fields of energy, chemical industry, food and the like, heat exchange equipment is one of the most important devices in industrial application, and the heat exchange performance of the heat exchange equipment usually determines the effective utilization rate of energy and the investment of equipment cost. Therefore, the research on the technology of enhancing heat transfer has been receiving much attention. The heat exchange tube is used as a core element of the heat exchange equipment, the actual heat exchange efficiency of the heat exchange equipment is always influenced by the physical property and the shape structure of the material of the heat exchange tube, and the enhanced heat transfer technology is an important support technology for improving the heat exchange performance of the heat exchange tube.
The enhanced heat transfer technology has various forms, and the disturbance enhanced heat exchange is formed by utilizing a built-in insert more commonly. In a plurality of built-in forms, the heat exchange performance is comprehensively improved in view of the advantages of small occupied size, convenience in installation and maintenance, compact and reliable structure and the like of a heat exchange form of placing the axial blade cyclone at the inlet section, and the fluid forms strong vortex flow after flowing through the cyclone, so that a strong scouring effect is also exerted on the pipe wall, and the formation of scale on the inner wall of the pipeline is reduced. However, in the heat exchange process, the axial vane swirler installed in the pipeline occupies a part of the flow channel, so that the volume of the flow channel is reduced, and the additional energy loss caused by flow resistance is inevitably accompanied while the heat transfer is enhanced. In order to solve the problem of extra energy loss, pumping power is required to be increased, but the heat exchange performance of the heat exchange tube is improved, but the improvement range is limited, and the consumption of the pumping power is difficult to compensate.
SUMMERY OF THE UTILITY MODEL
An object of the utility model is to overcome not enough among the prior art, provide a reverse whirl heat transfer sleeve pipe of axial blade, the pressure loss is low, heat transfer intensity is big, and heat transfer sheathed tube local region obtains temperature resistant protection, has longer life.
In order to solve the technical problem, the utility model discloses a technical scheme is:
the axial blade reverse rotational flow heat exchange sleeve comprises a first pipe and a second pipe, wherein the second pipe coaxially penetrates through the first pipe, the first pipe is provided with a first water inlet for flowing hot fluid, the second pipe is provided with a second water inlet for flowing cold fluid, and the flowing directions of the hot fluid and the cold fluid are opposite; a first rotational flow component is arranged at the first water inlet and rotatably sleeved on the outer wall of the second pipe, and the first rotational flow component is positioned between the first pipe and the second pipe; and a second rotational flow component is arranged at the second water inlet and is rotatably arranged in the second pipe.
In the reverse rotational flow heat exchange sleeve with the axial blades, the hot fluid is conveyed into the first pipe from the first water inlet, flows through the first rotational flow component to form strong vortex flow, and generates unstable flow and secondary flow at local positions in the flow process; cold fluid is conveyed into the second pipe from the second water inlet, flows through the second rotational flow assembly to form strong vortex flow, and unsteady flow and secondary flow are generated at local positions in the flow process; the unstable flow and the secondary flow can impact and thin a boundary layer and a flow boundary layer through strong disturbance, and heat transfer and mass transfer and convective heat exchange between cold fluid and hot fluid are promoted; in the heat exchange process, fluids with different temperatures are in a reverse convection heat exchange mode, so that the local area of the heat exchange sleeve is protected against temperature, the service life of the heat exchange sleeve can be prolonged, and the effective utilization rate and the service time of the heat exchange sleeve are improved; the forced flow of the hot fluid and the cold fluid promotes the first rotational flow component and the second rotational flow component to rotate automatically, and the flow channels occupied by the first rotational flow component and the second rotational flow component change along with the flow of the fluid, so that part of pressure loss is converted reasonably, and the convection heat exchange efficiency and the effective utilization rate of energy can be effectively improved. In addition, strong rotational flow impact can flush scales on the inner walls of the first pipe and the second pipe, and the scales are discharged out of the heat exchange sleeve along with the flowing of hot fluid and cold fluid, so that the obstruction of the scales on heat exchange and the obstruction of the flowing of the fluid are reduced, the cleaning and maintenance workload of the heat exchange sleeve is reduced, and the maintenance cost is reduced.
Furthermore, the first pipe is a symmetrical tubular structure with a cylindrical middle part and hemispherical two ends, the second pipe is a cylindrical tubular structure, the second pipe coaxially penetrates through the first pipe, and the joint of the first pipe and the second pipe is in sealing connection.
Further, the first pipe is provided with a first water outlet, the second pipe is provided with a second water outlet, the first water inlet and the first water outlet are located at two ends of the first pipe, the first water inlet is arranged upwards, the first water outlet is arranged downwards, the second water inlet and the second water outlet are located at two ends of the second pipe, the second water inlet is arranged close to the first water outlet, and the second water outlet is arranged close to the first water inlet.
Further, the first cyclone assembly comprises a first bearing, a first retainer ring and a first cyclone provided with a first through hole, the first cyclone is sleeved outside the second pipe, the first bearing is installed at two ends of the first cyclone, and the first retainer ring is installed on the outer wall of the second pipe and is respectively located at two ends of the first cyclone.
Furthermore, a first spiral structure is arranged on the periphery of the first cyclone, and a first spiral flow passage is formed between the first spiral structure and the inner wall of the first pipe.
Furthermore, two ends of the first spiral flow channel are provided with first speed regulating sliding covers for regulating the flow rate of the hot fluid.
Furthermore, the second cyclone assembly comprises a support rod, a second bearing, a second retainer ring and a second cyclone provided with a second through hole, the end of the support rod is mounted at the end of the second pipe, the second cyclone is sleeved outside the support rod, the second bearing is mounted at two ends of the second cyclone, and the second retainer ring is mounted at two ends of the support rod and located at two ends of the second cyclone.
Furthermore, a second spiral structure is arranged on the periphery of the second cyclone, and a second spiral flow passage is formed between the second spiral structure and the inner wall of the second pipe.
Furthermore, a second speed regulation sliding cover used for regulating the flow speed of cold fluid is arranged at two ends of the second spiral flow channel.
Furthermore, a rotation safety gap is reserved between the first cyclone and the inner wall of the first pipe and between the second cyclone and the inner wall of the second pipe.
Compared with the prior art, the beneficial effects of the utility model are that:
the utility model is provided with a first rotational flow component at a first water inlet of hot fluid and a second rotational flow component at a second water inlet of cold fluid, and unstable flow and secondary flow are generated at local positions in the flowing process; the unstable flow and the secondary flow can impact and thin a boundary layer and a flowing boundary layer through strong disturbance, the heat exchange contact time of the working fluid and a heat exchange surface is prolonged, the heat transfer and mass transfer and the convective heat exchange between a cold fluid and a hot fluid are promoted, and the heat exchange efficiency of the heat exchange sleeve can be effectively improved;
the hot fluid flows through the first rotational flow component and the cold fluid flows through the vortex formed by the second rotational flow component, so that the inner wall scales of the first pipe and the second pipe are washed, the cleaning and maintenance workload of the heat exchange sleeve can be reduced, and the maintenance cost is reduced;
the flow direction of the cold fluid and the flow direction of the hot fluid are opposite, the fluids with different temperatures are in a reverse convection heat exchange mode, the local area of the heat exchange sleeve is protected against temperature, the service life of the heat exchange sleeve can be prolonged, and the effective utilization rate of the heat exchange sleeve is improved;
the utility model discloses but first whirl subassembly and second whirl subassembly self-rotation, self-rotation's speed changes along with the change of velocity of flow, and the runner that occupies changes along with fluidic flow, and the hindrance of runner is corresponding to be reduced: the flow of fluid is promoted, and the convection heat exchange efficiency is effectively improved; part of the pressure loss is reasonably converted, and the effective utilization rate of energy is effectively improved;
the utility model discloses compact structure, the equipment and the maintenance of being convenient for, and the part source is convenient, low cost can change at any time, effectively saves time, manpower and material resources.
Drawings
FIG. 1 is a schematic structural view of the axial blade reverse rotational flow heat exchange sleeve of the present invention;
FIG. 2 is an exploded view of the axial blade reverse rotational flow heat exchange sleeve of the present invention;
FIG. 3 is a schematic view of the assembly of the first swirler and the first speed-regulating sliding cover and the assembly of the second swirler and the second speed-regulating sliding cover in a half-open state;
FIG. 4 is an exploded view of the first swirler and the first speed regulation slide and the second swirler and the second speed regulation slide;
FIG. 5 is a line graph of heat flux of three axial vane reverse cyclone heat exchange sleeves;
FIG. 6 is a temperature cloud of a heat exchange sleeve without a swirler in a simulation test;
FIG. 7 is a temperature cloud of a non-rotatable axial vane swirl heat exchange sleeve in a simulation test;
FIG. 8 is a temperature cloud chart of the axial vane cyclone heat exchange sleeve in the simulation test of the present invention;
FIG. 9 is a pressure cloud of a heat exchange jacket without a cyclone in a simulation test;
FIG. 10 is a pressure cloud of a non-rotatable axial vane swirl heat exchange sleeve in a simulation test;
FIG. 11 is a pressure cloud chart of the axial vane cyclone heat exchange sleeve in the simulation test;
in the drawings: 1-a first tube; 11-a first water inlet; 12-a first water outlet; 2-a second tube; 21-a second water inlet; 22-a second water outlet; 3-a first swirl component; 31-a first bearing; 32-a first collar; 33-a first cyclone; 34-a first helix; 4-a second swirl component; 41-a support bar; 42-a second bearing; 43-a second collar; 44-a second cyclone; 45-a second helix; 46-a connecting plate; 47-bar shaped holes; 5-a first speed-regulating sliding cover; 51-a first connection; 52-first slide; 6-a second speed regulating sliding cover; 61-second connecting portion 61; 62-second sliding part.
Detailed Description
The present invention will be further described with reference to the following embodiments. Wherein the showings are for the purpose of illustration only and are shown by way of illustration only and not in actual form, and are not to be construed as limiting the present patent; for a better understanding of the embodiments of the present invention, some parts of the drawings may be omitted, enlarged or reduced, and do not represent the size of an actual product; it will be understood by those skilled in the art that certain well-known structures in the drawings and descriptions thereof may be omitted.
The same or similar reference numerals in the drawings of the embodiments of the present invention correspond to the same or similar parts; in the description of the present invention, it should be understood that if there are the terms "upper", "lower", "left", "right", etc. indicating the orientation or positional relationship based on the orientation or positional relationship shown in the drawings, it is only for convenience of description and simplification of the description, but it is not intended to indicate or imply that the device or element referred to must have a specific orientation, be constructed in a specific orientation, and be operated, and therefore the terms describing the positional relationship in the drawings are only for illustrative purposes and are not to be construed as limitations of the present patent, and those skilled in the art can understand the specific meanings of the terms according to specific situations.
Examples
Fig. 1 to 4 show an embodiment of the reverse rotational flow heat exchange sleeve with axial blades of the present invention, which includes a first pipe 1 and a second pipe 2, wherein the second pipe 2 coaxially penetrates through the first pipe 1, the first pipe 1 is provided with a first water inlet 11 for flowing hot fluid, the second pipe 2 is provided with a second water inlet 21 for flowing cold fluid, and the flow directions of the hot fluid and the cold fluid are opposite; a first rotational flow component 3 is arranged at the first water inlet 11, the first rotational flow component 3 is rotatably sleeved on the outer wall of the second pipe 2, and the first rotational flow component 3 is positioned between the first pipe 1 and the second pipe 2; the second water inlet 21 is provided with a second cyclone assembly 4, and the second cyclone assembly 4 is rotatably arranged inside the second pipe 2. In this embodiment, the horizontal distance between the first cyclone assembly 3 and the second cyclone assembly 4 can be set to 1m to ensure axial flow of water flow which is fully developed, and by using the disturbance effect of the cyclone, heat is fully exchanged, and certainly, the distance between the first cyclone assembly 3 and the second cyclone assembly 4 can be adjusted according to the application scene requirement; the mounting mode of the first cyclone assembly 3 and the second cyclone assembly 4 can adopt a detachable connection mode so as to be convenient for replacing the cyclone assemblies of different models and cleaning and maintaining the cyclone assemblies.
In the implementation of this embodiment: hot fluid is conveyed into the first pipe 1 through the first water inlet 11, the hot fluid flows through the first cyclone assembly 3 to form strong vortex flow, and unstable flow and secondary flow are generated at local positions in the flowing process; similarly, cold fluid is conveyed into the second pipe 2 from the second water inlet 21, and the cold fluid flows through the second cyclone assembly 4 to form strong vortex flow, so that unstable flow and secondary flow are generated at local positions in the flowing process; unstable flow and secondary flow can impact and thin a boundary layer and a flowing boundary layer through strong disturbance, the heat exchange contact time of working fluid and a heat exchange surface is prolonged, heat transfer and mass transfer and convective heat exchange between cold fluid and hot fluid are promoted, water scale on the inner walls of the first pipe 1 and the second pipe 2 is scoured, the heat exchange efficiency of a heat exchange sleeve is effectively improved, the cleaning and maintenance workload of the heat exchange sleeve is reduced, and the maintenance cost is reduced;
the flow directions of the cold fluid and the hot fluid are opposite, and the fluids with different temperatures are in a reverse convection heat exchange mode, so that the local area of the heat exchange sleeve is protected against temperature, the service life of the heat exchange sleeve can be prolonged, and the effective utilization rate of the heat exchange sleeve and the service time of the heat exchange sleeve are improved;
the forced flow of hot fluid and cold fluid impels first whirl subassembly 3 and second whirl subassembly 4 self-rotation, and the rate of self-rotation changes along with the change of velocity of flow, and the runner that first whirl subassembly 3, second whirl subassembly 4 occupy changes along with the flow of fluid, and the hindrance effect of runner is corresponding to be reduced, can promote the flow of fluid, and partial pressure loss obtains reasonable conversion, can effectively promote the effective utilization ratio of convection heat transfer efficiency and energy.
Specifically, first pipe 1 is that the middle part is the cylinder, both ends are hemispherical symmetrical tubular structure, and second pipe 2 is cylindrical tubular structure, and second pipe 2 is coaxial cross-under in first pipe 1 inside and the handing-over department sealing connection of first pipe 1, second pipe 2, prevents that the rivers from permeating. The first tube 1 is arranged into a symmetrical tubular structure, so that the heat exchange sleeve can be endowed with an attractive appearance; the joint of the first pipe 1 and the second pipe 2 can adopt a connecting structure which is easy to operate and has good sealing performance like welding. In order to reduce the mass of the heat exchange sleeve of the present invention, the first tube 1 and the second tube 2 of the present embodiment can be made of aluminum material, but the selection of the material is preferred for obtaining light mass and good thermal conductivity, and is not taken as the restrictive regulation of the present invention.
Wherein, first pipe 1 is equipped with first delivery port 12, and second pipe 2 is equipped with second delivery port 22, and first water inlet 11, first delivery port 12 are located the both ends of first pipe 1 and first water inlet 11 sets up, and first delivery port 12 sets up down, and second water inlet 21, second delivery port 22 are located the both ends of second pipe 2 and second water inlet 21 are close to first delivery port 12 setting, second delivery port 22 is close to first water inlet 11 setting. In this embodiment, the first water inlet 11 and the first water outlet 12 are tubular structures, and are welded to the outer wall of the first pipe 1 in a seamless manner, so as to ensure that water flow is impermeable and sealed; the second water inlet 21 and the second water outlet 22 are tubular structures and are respectively connected with each other in a flange mode through pipelines; the first water inlet 11 is arranged upwards, is connected with an external hot water pipe and is used for introducing hot fluid; the first water outlet 12 is arranged downwards, is connected with the inlet of the other group of heat exchange lantern rings or the inlet of the circulation loop and is used for flowing out hot fluid; the first water inlet 11 and the second water outlet 22 are located at the same end, and the second water inlet 21 and the first water outlet 12 are located at the same end, so that the local area of the heat exchange sleeve is protected against temperature, the service life of the heat exchange sleeve can be prolonged, and the effective utilization rate of the heat exchange sleeve is improved. The diameter of the tubular structure in the embodiment can be adjusted according to the application scene requirement, and the length of the tubular structure can be set according to the heat on-way loss requirement; a certain distance is reserved between the first water inlet 11 and the end part of the first cyclone 33, and the distance can be set to be 10cm, so that the phenomenon that the pressure is unstable and changes to influence the flow speed change due to the fact that water flows from the first water inlet 11 into a large space to meet the resistance of the first cyclone 33 is avoided, and stable flow is ensured; a certain distance is left between the first water outlet 12 and the second cyclone 44, which can be set to 20cm, to ensure the sufficient heat exchange of the flow, and the inflow part of the second pipe 2 can be sufficiently preheated, to ensure the improvement of the heat exchange performance of the flow.
The first cyclone assembly 3 includes a first bearing 31, a first retainer ring 32 and a first cyclone 33 having a first through hole, the first cyclone 33 is sleeved outside the second pipe 2, the first bearing 31 is installed at two ends of the first cyclone 33, the first retainer ring 32 is installed on the outer wall of the second pipe 2, and the first retainer ring 32 is respectively located at two ends of the first cyclone 33. Wherein, first helical structure 34 is equipped with in first swirler 33 periphery, and first spiral runner is formed between first helical structure 34 and the first pipe 1 inner wall. In this embodiment, the first bearing 31 is installed at the left end and the right end of the first cyclone 33 in an embedded sealing manner, the outer diameter of the first bearing 31 matches and corresponds to the inner diameter of the first through hole, and the inner diameter of the first bearing 31 matches and corresponds to the outer wall of the second pipe 2, so that the first cyclone 33 is installed on the second pipe 2 through the first bearing 31 and has a self-rotation function; the sides of the two groups of first bearings 31 are provided with first retainer rings 32, the first retainer rings 32 are fastened on the outer wall of the second pipe 2, and the first swirler 33 is prevented from moving in the axial direction; the first retainer ring 32 is not exposed and is positioned in the end face of the first bearing 31, so that the fluid flow is prevented from being influenced; the first helical structure 34 may be left-handed or right-handed, and may be selected and replaced as desired. It should be noted that, in the present embodiment, the arrangement of the first spiral structure 34 and the first spiral flow channel is preferable for obtaining a better turbulent flow effect, and is not taken as a limiting provision of the present invention; in the present embodiment, the first cyclone 33 is preferably made of aluminum to reduce the mass of the heat exchange casing, but it is not intended as a limitation of the present invention.
In order to adjust the flow rate of the hot fluid and widen the application range of the heat exchange sleeve, in this embodiment, the first speed-adjusting sliding covers 5 for adjusting the flow rate of the hot fluid are disposed at two ends of the first spiral flow channel, and the first speed-adjusting sliding covers 5 are detachably mounted between the first bearing 31 and the first retainer ring 32. Specifically, the method comprises the following steps: the first spiral flow channels are provided with a plurality of first inlets located on one end surface of the first cyclone 33 and a plurality of first outlets located on the other end surface of the first cyclone 33, the first speed regulation sliding cover 5 is provided with a first connecting portion 51 and a first sliding portion 52 connected to the first connecting portion 51, the first sliding portion 52 corresponds to the first inlets and the first sliding portion 52 to the first outlets one by one, and the opening degrees of the first inlets and the first outlets can be adjusted by rotating the first speed regulation sliding cover 5, as shown in fig. 3 and 4. When the device is applied, the size of the opening of the inlet and the outlet of the first spiral flow channel is adjusted through the first speed-adjusting sliding cover 5 according to the requirements of application occasions so as to adjust the flow rate of hot fluid.
In addition, the first speed slide cover 5 of the present embodiment is further rotatably installed between the first bearing 31 and the first retainer ring 32, and the first sliding portion 52 is provided as a fan-shaped inclined hole. With the arrangement, when the hot fluid flows through the fan-shaped inclined hole, the first speed regulation sliding cover 5 can be pushed to rotate, and the rotation speed of the first cyclone 33 is stabilized and balanced, so that the function of automatic speed regulation is realized.
The second cyclone assembly 4 includes a support rod 41, a second bearing 42, a second retainer ring 43 and a second cyclone 44 having a second through hole, wherein the end of the support rod 41 is mounted at the end of the second pipe 2, the second cyclone 44 is sleeved outside the support rod 41, the second bearing 42 is mounted at two ends of the second cyclone 44, the second retainer ring 43 is mounted at the support rod 41, and the second retainer ring 43 is located at two ends of the second cyclone 44. Wherein, the periphery of the second swirler 44 is provided with a second spiral structure 45, and a second spiral flow channel is formed between the second spiral structure 45 and the inner wall of the second pipe 2. In this embodiment: a flange interface is arranged at the second water inlet 21, a plurality of connecting plates 46 are arranged at one end of the supporting rod 41 in a circumferential extending manner, the connecting plates 46 are fixedly connected with the flange interface, the supporting rod 41 is fixed in the second pipe 2, and the supporting rod 41 and the second pipe 2 are coaxially arranged; a strip-shaped hole 47 is formed in the connecting plate 46 so as to facilitate fluid flow and reduce fluid flow resistance; the strip-shaped holes 47 are all positioned in the center of the connecting plate 46, so that the flow resistance is reduced, and the strip-shaped holes are used as a flow stabilizer, so that the flow is in a fully developed state, and the change of pressure and flow rate is stabilized; the shape of the strip-shaped hole 47 is prolate and elliptical, so that fluid smoothly flows through the strip-shaped hole 47, and the pressure loss is greatly reduced; the left end and the right end of the second cyclone 44 are respectively provided with the second bearing 42 in an embedded sealing mode, the outer diameter of the second bearing 42 is matched and corresponding to the inner diameter of the second through hole, the inner diameter of the second bearing 42 is matched and corresponding to the outer wall of the supporting rod 41, and therefore the second cyclone 44 is arranged on the supporting rod 41 through the second bearing 42 and has a self-rotating function; the side parts of the two groups of second bearings 42 are provided with second retainer rings 43, and the second retainer rings 43 are fastened on the periphery of the support rod 41 and prevent the second swirler 44 from moving in the axial direction; the connecting piece for fixing the second retainer ring 43 is not exposed and is positioned in the end face of the second bearing 42, so that the fluid flow is prevented from being influenced; the second helical structure 45 may be left-handed or right-handed, and may be selected and replaced as desired. It should be noted that the arrangement of the second spiral structure 45 and the second spiral flow channel in this embodiment is preferable for obtaining a better turbulent flow effect, and is not taken as a limiting rule of the present invention; in the present embodiment, the second cyclone 44 is preferably made of aluminum to reduce the mass of the heat exchange casing, but not as a limitation of the present invention.
In order to adjust the flow rate of the hot fluid and widen the application range of the heat exchange sleeve, in this embodiment, the second speed-adjusting sliding covers 6 for adjusting the flow rate of the cold fluid are disposed at two ends of the second spiral flow channel, and the second speed-adjusting sliding covers 6 are installed between the second bearing 42 and the second retainer 43. Specifically, the method comprises the following steps: the second spiral flow channels are provided with a plurality of second inlets located on one end surface of the second cyclone 44 and a plurality of second outlets located on the other end surface of the second cyclone 44, the second speed regulation sliding cover 6 is provided with a second connecting portion 61 and a second sliding portion 62 connected to the second connecting portion 61, the second sliding portion 62 corresponds to the second inlets and the second sliding portion 62 corresponds to the second outlets one by one, and the opening degrees of the second inlets and the second outlets can be adjusted by rotating the second speed regulation sliding cover 6, as shown in fig. 3 and 4. When the device is applied, the size of the opening of the inlet and the outlet of the second spiral flow channel is adjusted through the second speed-adjusting sliding cover 6 according to the requirements of application occasions so as to adjust the flow rate of hot fluid.
In addition, the second speed slide cover 6 of the present embodiment is further rotatably installed between the second bearing 42 and the second retainer 43, and the second slide portion 62 is provided as a fan-shaped inclined hole. With the arrangement, when the hot fluid flows through the fan-shaped inclined hole, the second speed regulation sliding cover 6 can be pushed to rotate, and the rotation speed of the second cyclone 44 is stabilized and balanced, so that the function of automatic speed regulation is realized.
A rotation safety clearance is left between the first cyclone 33 and the inner wall of the first pipe 1 and between the second cyclone 44 and the inner wall of the second pipe 2. The rotation safety clearance is provided for the first cyclone 33 to safely rotate in the first pipe 1 and the second cyclone 44 to safely rotate in the second pipe 2, so as to ensure the working stability of the first cyclone 33 and the second cyclone 44, and the rotation safety clearance in this embodiment may be set to 1cm, or may be set to other clearances according to the application requirements.
In the present embodiment, the helix angles of the first helical structure 34 and the second helical structure 45 are calculated by the formula α ═ arctan (H/n pi d), where: h is a lead, namely the height of the moving point which rises along the axial direction after rotating for a circle; n is the ratio of the circumference corresponding to the actual lead to the full circumference corresponding to the total lead; d is the diameter of an imaginary cylinder with the generatrix passing through the equal width of the upper protrusion and the groove of the tooth form. d is represented by the formula: D-0.6495P, wherein: p is the axial distance between two corresponding points on the radius line of adjacent teeth, D is the diameter of an imaginary cylinder coincident with the crest of the external thread or the root of the internal thread, and 0.6495 is an empirical correction coefficient.
For verifying the utility model discloses an actively the effect, this embodiment and the heat transfer sleeve pipe of no swirler type and the axial blade whirl heat transfer sleeve pipe of non-rotatable type (hereinafter referred to as no swirler type and non-rotatable type for short) as the contrast, carry out analogue simulation test to the heat transfer sleeve pipe of this embodiment:
in consideration of designability of the first and second screw structures 34 and 45, and also in order to obtain a high swirl strength remarkably, the blade angles of the first and second swirlers 33 and 44 are set to 30 °. Considering that the flow velocity in the pipe is preferable to be smooth and fully developed, assuming that the flow types are all smooth and fully developed, the tests were performed under conditions of flow reynolds numbers (hereinafter, Re is used) of 4000, 5000, 6000, 7000 and 8000, respectively. The water temperatures at the first water inlet 11 of the first pipe 1 and the second water inlet 21 of the second pipe 2 are set to 323K and 298K, respectively. A pressure-based solver is adopted, a non-swirler type and a non-rotatable type are calculated by steady-state solution, and a rotatable type is calculated by non-steady-state solution. Neglecting the influence of gravity, set the wall to have no slip, the impervious condition. Setting the density ρ of waterWater (W)Is 998.2Kg/m3Specific heat capacity of water cp water4182J/Kg.K, heat conductivity coefficient of water lambdaWater (W)0.6 w/m.K, kinematic viscosity of water muWater (W)0.001003 Kg/m.s; setting the density rho of aluminum materialAluminiumIs 2179Kg/m3Specific heat capacity of aluminum cP aluminium871J/Kg.K, and the thermal conductivity coefficient lambda of aluminumAluminiumIs 202.4 w/m.K. The non-swirler type and the non-rotatable type use a SIMPLE solution algorithm, and the rotatable type uses a PISO solution algorithm. The gradient term adopts a node-based scheme, the pressure term adopts a PISO scheme, the momentum term adopts a QUICK scheme, and the other parameter terms adopt a second-order scheme. ANSYS fluent16.0 is adopted to carry out numerical solution on the flow and heat exchange conditions in the sleeve, equations (1) - (3) are established by a Reynolds time-average method to solve the three-dimensional flow of the turbulent flow, RNG control equations (4) and (5) are adopted, and the lower limit value of the limiting wall surface of the scaled wall surface function is 11.06.
Mass equation:
the momentum equation:
energy equation:
k equation:
wherein:
the equation of ε:
wherein:
in the above-mentioned formula, the first and second groups,
representing the reynolds average velocity component; ρ represents a density; p represents pressure; u'iRepresents the pulsation velocity;
represents the mass force; t represents time; alpha is alphakAnd alphaεRespectively representing the reciprocal of the pluronic number of the turbulent kinetic energy and the dissipation ratio effective turbulent flow; mu.stIndicates turbulent viscosity; β represents a thermal expansion coefficient; giIndicating accelerationDegree; pr (Pr) oftRepresenting the prandtl number; t represents a temperature; c1ε、C2ε、C3εAre all model constants; sijThe average strain rate is indicated. Known through Fluent help files: alpha is alphak＝αε≈1.393，Cμ＝0.0845，Prt＝0.7179，C1ε＝1.42，C2ε＝1.68，C3ε＝1.3，β＝0.012，η0＝4.3；
The results of the total pressure drop Δ P (unit: Pa) are shown in the following table:
non-rotatable type meshing to remove first cyclone 33, second cyclone 44 solids, leaving the flow path as the fluid domain, second tube 2 heat exchange solids portion as the solids domain solution, dividing the mixing mesh. The rotatable type of meshing then retains the solid portion and divides into solid domains, with the flow path acting as a fluid domain scheme, dividing the mixing mesh. The rotatable moving grid is set by adopting the scheme of smoothening and Remeshing and a 6DOF model, the gravity center position, the mass and the moment of inertia of a moving area and a wall surface are defined in a programming mode, only the axial rotation freedom degree is opened, and the rest five moving freedom degrees are restrained.
Based on the above total pressure drop test results, the temperature cloud charts of FIGS. 6 to 8, the pressure cloud charts of FIGS. 9 to 11, and the heat flux q (unit: W/m) of FIG. 52) The test results show that:
compared with the non-rotatable type, the rotatable type has the advantage that the pressure drop is obviously reduced along with Re, and the main reason is that the swirler has the self-rotating function, so that the originally occupied flow channel is changed along with the flowing of fluid, the change of the volume of the flow channel presents flexibility, and partial pressure loss can be reasonably converted. At the same time, the heat flux of the heat exchange surface of the rotatable type is along withThe increase of Re is obviously increased, the maximum change is 8000 at Re, and the maximum change is increased by 600W/m compared with the non-rotatable type2Increased by 852W/m compared with the type without a swirler2. Compared with the non-swirl type, the non-rotation type has the same increment rule, and the heat flux change is increased by 200W/m only compared with the non-swirl type2Left and right. Therefore, the heat exchange effect caused by the non-rotatable type is weak (due to the fact that the flow speed is high, the contact time of the working fluid and the heat exchange surface is short, and the heat exchange change between the convection heat exchange areas is small). In the range of Re less than 6000 and with increasing Re the rotational speed of the rotatable type increases, but is not sufficient to achieve good turbulent heat transfer, mainly because part of the power is consumed to provide the lowest starting rotational condition of the swirler. In the range of Re greater than 6000, the rotational swirl strength is slightly reduced, but the heat exchange effect is obvious, mainly because of sufficient disturbance and the increase of the heat exchange contact time of the working fluid and the heat exchange surface, thereby greatly improving the convection heat exchange effect in the pipe, reasonably converting the pressure loss and improving the maximum effective utilization rate of energy. In view of the pressure drop conversion and the heat exchange effect of the heat exchange tube, the rotatable type is superior to the non-rotatable type in comprehensive heat exchange performance.
As can be seen from the temperature cloud chart analysis of fig. 6 to 8, the rotatable type temperature distribution is more uniform than the other two types, the rotational flow heat exchange with appropriate rotational flow strength is helpful for promoting the heat and mass transfer of the flow in the pipe, and for the part of the inlet of the first pipe 1 relative to the outer wall of the second pipe 2, the local area is protected against temperature, which is beneficial for prolonging the service life of the heat exchange sleeve. As can be seen from the analysis of the pressure cloud charts in fig. 9 to 11, compared with the non-rotational flow type, although the pressure drop distribution of the other two types is larger, the pressure loss paid by the rotatable type is reasonably converted in terms of the comprehensive heat exchange effect, the flow in the pipe is fully disturbed, the heat exchange contact time of the working fluid and the heat exchange surface is increased, and finally, the higher comprehensive heat exchange performance is obtained.
It is obvious that the above embodiments of the present invention are only examples for clearly illustrating the present invention, and are not limitations to the embodiments of the present invention. Other variations and modifications will be apparent to persons skilled in the art in light of the above description. And are neither required nor exhaustive of all embodiments. Any modification, equivalent replacement, and improvement made within the spirit and principle of the present invention should be included in the protection scope of the claims of the present invention.
Claims (10)
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| CN202021065319.XU CN213067200U (en) | 2020-06-10 | 2020-06-10 | Axial blade reverse rotational flow heat exchange sleeve |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN111707113A (en) * | 2020-06-10 | 2020-09-25 | 东莞理工学院 | A kind of axial blade reverse swirling heat exchange sleeve |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN111707113A (en) * | 2020-06-10 | 2020-09-25 | 东莞理工学院 | A kind of axial blade reverse swirling heat exchange sleeve |
| CN111707113B (en) * | 2020-06-10 | 2024-10-01 | 东莞理工学院 | Axial blade reverse rotational flow heat exchange sleeve |
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