CN201688731U - Efficient modular return displacement type heat-exchange unit - Google Patents
Efficient modular return displacement type heat-exchange unit Download PDFInfo
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- CN201688731U CN201688731U CN2010202200870U CN201020220087U CN201688731U CN 201688731 U CN201688731 U CN 201688731U CN 2010202200870 U CN2010202200870 U CN 2010202200870U CN 201020220087 U CN201020220087 U CN 201020220087U CN 201688731 U CN201688731 U CN 201688731U
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Abstract
The utility model relates to a heat exchanger, in particular to an efficient modular return displacement type heat-exchange unit which comprises a primary fluid with a primary fluid inlet flange and a primary fluid outlet flange which are connected by an external pipeline, and a pipe sheet connected the primary fluid inlet flange and the primary fluid outlet flange; the pipe sheet fixes a heat-exchange pipe and horizontally extending into a cylinder with a chamber; the heat-exchange unit is characterized by also comprising a cylinder, one side of the cylinder is provided with an opening, the chamber of the cylinder is horizontally distributed with return clapboards up and down at intervals above the cylinder with the chamber, and the horizontal cylinder with the chamber is communicated with the vertical cylinder by a porous radiant pipe. The efficient modular return displacement type heat-exchange unit improves heat efficiency and energy utilization rate, increase water yield, reduces cost, shrinks the construction space, and is convenient for maintenance and cleaning, and simple in manufacture process.
Description
Technical field
The utility model relates to heat exchanger, is a kind of high-efficiency module back-stroke displacement heat-exchanger rig specifically.
Background technology
In the prior art, volumetric heat exchanger mainly contains: RV series volumetric heat exchanger, be divided into vertical, horizontal two kinds, existing vertical, horizontal volumetric heat exchanger is that heat exchanger tube is connected with tube sheet, and the mode with welding is inserted in the housing of volumetric heat exchanger again; Its primary fluid and secondary heating agent stroke are too short, the secondary heating agent is in static heating substantially in the volume tank body, can't realize the heat convection in the thermal conduction study, therefore the heating agent utilization rate is extremely low, be about 50% only, wasted a large amount of available energys, increased expense, capacity utilization is not high, and the slough is arranged, and water yield is less, and steel quantity consumption is higher, floor space is big, extract the heat exchanger tube requisite space out and require greatly, spatial altitude requires harsh, and the coefficient of heat transfer (K value) is very low, vapour-water heat exchange heat transfer coefficient (K value) is 1800-2500W/(m2.k), water-water heat exchange heat transfer coefficient (K value) is 800-1600W/(m2.k); Once, the heat exchange of secondary heating agent is insufficient, the supply water temperature instability, when primary fluid was high temperature and high pressure steam, condensing water temperature height, pressure were low, must install steam trap additional and the hydroecium that condenses, its ability operate as normal, and be not easy to recycle, need special condensate pump and condensate tank, but its ability operate as normal, the corollary equipment investment is big, installs extremely inconvenient; Cause the heat exchanger tube fouling after working long hours easily, resistance strengthens, and causes pump power to strengthen, waste electric power, and the coefficient of heat transfer reduces greatly, wasted the energy, strengthened coal consumption and power consumption, do not reach the purpose of energy-saving and emission-reduction.When fouling is serious, even make device damage, the pressure that causes pipeline raises, cause danger such as booster, blast, and the manufacture craft of existing volumetric heat exchanger is extremely complicated, maintenance cost is high, equipment is not quick detachable, the easy crystallization of mineral ion, easily obstruction, perishable, be not durable, be subjected to its structural limitations, heat exchanger tube service life is generally in 3-5 years.
Sum up that the said equipment exists problem be:
A, manufacturing process are extremely complicated, the cost height;
B, calcium, magnesium ion easily precipitate, crystallization;
C, equipment thermal efficiency are low, waste energy the operating cost height;
D, maintenance inconvenience, the maintenance cost height, service life is short;
E, when primary fluid is steam, condensing water temperature is too high, by being pressed droop loss big, can only add drain valve and condensate pump and condensate tank ability operate as normal.The primary fluid outlet temperature is too high, and the primary fluid outlet temperature is higher than 50 ℃ of secondary heating agent imports more than-70 ℃, has promptly wasted the energy, has strengthened other corollary equipments investments again, has strengthened floor space and spatial altitude requirement simultaneously;
F, to be heated stroke short, and the slough is arranged, and mechanical loss is big, easy to leak;
G, mounting process complexity, high to civil engineering and load capacity requirement, the equipment operating weight is big, is not easy to install.
Summary of the invention
The purpose of this utility model provide a kind of module back-stroke formula structure, volume big and can improve the thermal efficiency and energy utilization rate, increase water yield, reduce cost and dwindle space, no slough, the utmost point be not easy fouling, maintenance clean make things convenient for, high-efficiency module back-stroke displacement heat-exchanger rig that manufacture craft is easy.
The purpose of this utility model is to realize like this, design a kind of high-efficiency module back-stroke displacement heat-exchanger rig, comprise the primary fluid that primary fluid suction flange and primary fluid outlet(discharge) flange are connected by Outer Tube, comprise the tube sheet that connects primary fluid suction flange and primary fluid outlet(discharge) flange import department, tube sheet fixedly heat exchanger tube level stretches to the chamber cylindrical shell, it is characterized in that: also comprise a cylindrical shell, cylindrical shell one STH, perforate is stretched in the cavity of cylindrical shell chamber cylindrical shell level, in the cavity of cylindrical shell, from more than the chamber cylindrical shell up and down the horizontal interval arrange the backhaul dividing plate, form a plurality of backhaul mixing chamber, the chamber cylindrical shell of level is communicated with by the porous radiant tube with vertical cylindrical shell, during work, primary fluid enters in the end socket through the primary fluid suction flange, flow through put in horizontal heat exchange tube in the end socket after, the repetition backhaul that process U type heat exchanger tube and end socket dividing plate are divided into is flowed out through the primary fluid outlet(discharge) flange by the heat exchanger tube outlet that puts in the end socket; The secondary heating agent is through the chamber cylindrical shell lower end secondary heating agent suction flange in the cylindrical shell outside, in the chamber cylindrical shell, carry out heat exchange, flow in the cylindrical shell by the porous radiant tube, horizontally disposed backhaul dividing plate about in the cylindrical shell, formed backhaul mixing chamber, after the abundant mixing of process backhaul mixing chamber, stirring, the backhaul, discharge through the secondary heating agent outlet(discharge) flange of cylindrical shell upper end.
Described chamber cylindrical shell section is a vertical little ellipsoid of placing, and the cylindrical shell section is a vertical big ellipsoid of placing, and the height of chamber cylindrical shell is 1/2 to 2/3 of a cylindrical shell height, and the chamber cylindrical shell is welded in the perforate in cylindrical shell left side.
The described primary fluid suction flange position of keeping right in chamber cylindrical shell upper end, the secondary heating agent outlet(discharge) flange position of keeping right in chamber cylindrical shell lower end, primary fluid suction flange and secondary heating agent outlet(discharge) flange are welded on the end socket, end socket is connected by flange with the chamber cylindrical shell again, connect tube sheet between end socket, flange and the chamber shell flange, tube sheet fixedly heat exchanger tube level stretches to the chamber cylindrical shell.
On the cylindrical shell cavity of described chamber cylindrical shell upper end thermometer boss and pressure gauge connection II are arranged respectively, thermometer that is connected with the pressure gauge connection II by thermometer boss and Pressure gauge are measured secondary heat medium temperature and the pressure in the cylindrical shell cavity respectively.
Described cylindrical shell top is a secondary heating agent outlet(discharge) flange, and secondary heating agent outlet(discharge) flange is drawn the secondary heating agent by pipeline.
Be fixed with hanger about on the described cylindrical shell.
Heat exchanger tube in the described chamber cylindrical shell is divided into a plurality of backhauls district by the end socket dividing plate, successively decreases gradually from primary fluid suction flange to the heat exchanger tube quantity in primary fluid outlet(discharge) flange backhaul district.
Described chamber cylindrical shell is a stretched head of cylindrical shell, and the chamber cylindrical shell leaves 1/3 to 1/4 outside cylindrical shell, and described tube side is that primary fluid is high-temperature steam, high-temperature water passage.
Horizontally disposed backhaul dividing plate up and down in the described cylindrical shell has formed 4 backhaul mixing chamber.
Described bearing adopts the saddle-shape bearing.
Described shell side is that the secondary heating agent is a water stream channel.
Described heat exchanger tube adopts dual damascene spiral shell fiber crops copper tube, nickel alloy or Nitinol pipe.
The beneficial effects of the utility model: housing adopts low alloy steel plate to make, and heat-exchanging tube bundle is dual damascene spiral shell fiber crops copper tube, nickel alloy or the Nitinol pipe of φ 16,19,25,32 * (2.0) 1.5mm.This heat exchanger general advantage is as the bearing capacity height, droop loss is little by pressing, zone efficiency of heating surface height, heat resistance is good, and manufacturing process is simple, dischargeable capacity big (be 1.5 of other heat exchangers under the equal conditions---2.5 times), cost is lower, and the utmost point is not easy fouling, and maintenance management is easy, outside the performances such as long service life, also have following important feature:
(1) the utility model has been used modular, chamber, return-stroke type structure, under the equivalent technology condition, appearance and size is than other volumetric heat exchanger little 80-90%, floor space has reduced 85-90%, other volumetric heat exchanger of weight ratio few 60-70%, raw materials consumption has reduced 40-50%, has reduced the requirement of service clearance simultaneously, and easier dismounting, replacing, maintenance;
(2) bearing capacity height of the present utility model, droop loss is little by pressing, zone efficiency of heating surface height, heat resistance is good, manufacturing process is simple, under the equivalent technology condition, can reach the high-speed and continuous water outlet, and water yield is big, be other volumetric heat exchangers 1.5-2.5 doubly, manufacturing cost is lower, equal conditions has reduced 55% than other volumetric heat exchangers down, repair and maintenance is easy, the repair and maintenance expense is cheap, only is 45-55% expense of other volumetric heat exchangers, long service life, heat exchanger tube service life is more than 15-20 years, and body service life is more than 20-25 years;
(3) the utility model heat transfer coefficient height, save heat exchange area, the heat transfer coefficient (K value) of general volumetric heat exchanger, vapour-water heat exchange heat transfer coefficient (K value) is 1800-2500W/ (㎡ .K), water-water heat exchange heat transfer coefficient (K value) is 800-1600W/ (㎡ .K), under the equivalent technology condition, vapour of the present utility model-water heat exchange heat transfer coefficient (K value) is 5500-8500W/ (㎡ .K), bigger 2.5-3 times than other volumetric heat exchanger, heat exchange area can reduce 40-60%, and the heat exchanger tube radical reduces 45-55%; Under the equivalent technology condition, water-water heat exchange heat transfer coefficient (K value) is 2300-3700W/ (㎡ .K) bigger 2-2.5 times than other volumetric heat exchanger, heat exchange area can reduce 40-50%, and the heat exchanger tube radical reduces 45-50%;
(4) the heat-exchanging tube bundle subdivision of high-efficiency module back-stroke displacement heat exchanger, science are arranged the heat-exchanging tube bundle utilization rate height of each unit, no heat exchanging corner;
(5) good sealing effect, the housing of high-efficiency module back-stroke displacement heat exchanger connect the employing welding, and heat-exchanging tube bundle and tube sheet adopt welding, Hydraulic expansion-jointing, and be solid and reliable;
(6) new high-efficiency, zone heating, heat utilization efficiency height.The condensing water temperature that high-efficiency module back-stroke displacement heat exchanger vapour-water heat exchange is discharged is low, generally below 15-25 ℃, both there be not leakage losses, do not need to install steam trap yet, under the equivalent technology condition, the utility model is saved the energy (steam or high-temperature water) 45-55% than other volumetric heat exchangers.Runner is many, and the zone heating divides: high-temperature region, middle warm area, low-temperature space, ultra-low temperature region.The heat exchange zone is not in same tube side, and subregion heats, and heat exchange is abundant, and it is fast to go out water speed, and leaving water temperature is stable;
(7) during high-efficiency module back-stroke displacement heat exchanger vapour-water heat exchange, the condensate water pressure of discharge is more than 65-70% of steam pressure, can utilize the overbottom pressure of self to be back to the boiler room.Saved condensate pump, condensate tank and station investment, it is all greatly convenient to design simultaneously and manage;
(8) the hydrodynamics hydraulic characteristic(s) is good, the flow resistance of primary fluid and secondary heating agent is little, flow speed stability, design is from the angle of the best of breed relation of the pressure drop and the coefficient of heat transfer, droop loss with minimum exchanges the highest heat exchange effect for, and the energy of consumes least obtains maximum benefit when allowing use, reduce the waste of the energy, realize the purpose of energy-saving and emission-reduction;
(9) unique porous radiant tube designs, make that the leaving water temperature of equipment is more stable, add abundant mixing, backhaul, the stirring of backhaul mixing chamber, make that leaving water temperature of the present utility model is more stable, there is not the slough, lighter, less impurity and crystalline solid can flow out equipment along the direction of current fully, and the equipment utmost point is not easy fouling;
(10) special heat exchanger tube arrangement has increased flow velocity, has improved film coefficient of heat transfer, thereby improves overall heat-transfer coefficient, makes the compact conformation of heat exchanger, and cross-flow, adverse current, turbulence state are stronger.The high-efficiency module back-stroke displacement heat exchanger unique design utilizes minimum energy consumption to reach best heat exchange effect;
(11) craft science of the present utility model, easy access, floor space is little, and process pipe is convenient to install, and long service life, and heat exchanger tube service life is more than 15-20 years, and body service life is more than 20-25 years.
Description of drawings
The utility model is described in further detail below in conjunction with the embodiment accompanying drawing:
Fig. 1 is a structural representation of the present utility model;
Fig. 2 is a schematic side view of the present utility model;
Fig. 3 is a schematic top plan view of the present utility model;
Fig. 4 is a tube sheet stringing generalized section of the present utility model.
Among the figure: 1, primary fluid outlet(discharge) flange; 2, primary fluid suction flange; 3, end socket; 4, flange; 5, tube sheet; 6, pressure gauge connection I; 7, thermometer boss; 8, pressure gauge connection II; 9, secondary heating agent outlet(discharge) flange; 10, safety valve; 11, cylindrical shell; 12, backhaul dividing plate; 13, hanger; 14, deflection plate; 15, heat exchanger tube; 16, chamber dividing plate; 17, chamber cylindrical shell; 18, maintenance population; 19, porous radiant tube; 20, sewage draining exit; 21, water return outlet; 22, bearing; 23, secondary heating agent suction flange; 24, end socket dividing plate.
The specific embodiment
As shown in Figure 1, the high-efficiency module back-stroke displacement heat-exchanger rig, comprise the primary fluid that primary fluid suction flange 2 and primary fluid outlet(discharge) flange 1 are connected by Outer Tube, comprise the tube sheet 5 that connects primary fluid suction flange 2 and primary fluid outlet(discharge) flange 1 import department, tube sheet 5 fixedly heat exchanger tube 15 levels stretches to chamber cylindrical shell 17, it is characterized in that: also comprise a cylindrical shell 11, cylindrical shell 11 1 STHs, perforate is stretched in the cavity of cylindrical shell 11 chamber cylindrical shell 17 levels, in the cavity of cylindrical shell 11, from the chamber cylindrical shell more than 17 up and down the horizontal interval arrange backhaul dividing plate 12, form a plurality of backhaul mixing chamber, the chamber cylindrical shell 17 of level is communicated with by porous radiant tube 19 with vertical cylindrical shell 11, during work, primary fluid in primary fluid suction flange 2 enters end socket 3, flow through put in horizontal heat exchange tube 15 in the end socket after, the repetition backhaul that process U type heat exchanger tube 15 and end socket dividing plate 24 are divided into is flowed out through primary fluid outlet(discharge) flange 1 by heat exchanger tubes 15 outlets that put in the end socket 3; The secondary heating agent is through the chamber cylindrical shell 17 lower end secondary heating agent suction flanges 23 in cylindrical shell 11 outsides, in chamber cylindrical shell 17, carry out heat exchange, flow in the cylindrical shell 11 by porous radiant tube 19, horizontally disposed backhaul dividing plate 12 about in the cylindrical shell 11, formed backhaul mixing chamber, after the abundant mixing of process backhaul mixing chamber, stirring, the backhaul, discharge through the secondary heating agent outlet(discharge) flange 9 of cylindrical shell 11 upper ends.
In fact, by secondary heating agent suction flange 23, secondary heating agent outlet(discharge) flange 9, porous radiant tube 19, chamber cylindrical shell 17, water return outlet 21, sewage draining exit 20 is connected to form shell side with cylindrical shell 11, secondary heating agent suction flange 23 is at the lower-left of chamber cylindrical shell 17 end, secondary heating agent outlet(discharge) flange 9 is at the left upper end of cylindrical shell 11, porous radiant tube 19 is fixed on the bottom righthand side of chamber cylindrical shell 17, water return outlet 21 is the lower end in the left side of cylindrical shell 11, sewage draining exit 20 is the lower end in the right side of cylindrical shell 11, sewage draining exit 20 is connected with chamber cylindrical shell 17 and cylindrical shell 11, is separated by horizontally disposed backhaul dividing plate 12 up and down in the cylindrical shell 11 to form multilayer backhaul mixing chamber.
As shown in Figure 2, provide the left view of Fig. 1, from left view, chamber cylindrical shell 17 sections are vertical little ellipsoids of placing, cylindrical shell 11 sections are vertical big ellipsoids of placing, the height of chamber cylindrical shell 17 is 1/2 of cylindrical shell 11 height---2/3, and chamber cylindrical shell 17 is welded in the perforate in cylindrical shell 11 left sides.Primary fluid suction flange 2 position of keeping right in chamber cylindrical shell 17 upper ends, secondary heating agent suction flange 1 position of keeping right in chamber cylindrical shell 17 lower ends.Primary fluid suction flange 2 and secondary heating agent outlet(discharge) flange 1 are welded on the end socket 3, end socket 3 is connected by flange 4 with chamber cylindrical shell 17 again, connect tube sheet 5 between end socket 3, flange 4 and chamber cylindrical shell 17 flanges, tube sheet 5 fixedly heat exchanger tube 15 levels stretches to chamber cylindrical shell 17.On cylindrical shell 11 cavitys of chamber cylindrical shell 17 upper ends thermometer boss 7 and pressure gauge connection II 8 are arranged respectively, thermometer that is connected with pressure gauge connection II 8 by thermometer boss 7 and Pressure gauge are measured secondary heat medium temperature and the pressure in cylindrical shell 11 cavitys respectively.Cylindrical shell 11 tops are secondary heating agent outlet(discharge) flange 9, and secondary heating agent outlet(discharge) flange 9 is drawn the secondary heating agent by pipeline.Be fixed with hanger 13 about on the cylindrical shell 11.
As shown in Figure 3, Fig. 3 provides the vertical view of Fig. 1, from vertical view, chamber cylindrical shell 17 is stretched heads of cylindrical shell 11, chamber cylindrical shell 17 leaves 1/3 to 1/4 outside cylindrical shell 11, primary fluid suction flange 2 and secondary heating agent outlet(discharge) flange 1 are welded in end socket 3 left ends, and end socket 3 is connected by flange 4 with chamber cylindrical shell 17 again, and chamber cylindrical shell 17 lower ends connect secondary heating agent suction flange 23.Pressure gauge connection I 6 is on chamber cylindrical shell 17, and thermometer boss 7, pressure gauge connection II 8, secondary heating agent outlet(discharge) flange 9, safety valve 10 are on cylindrical shell 11; Pressure gauge connection I 6, thermometer boss 7, pressure gauge connection II 8, secondary heating agent outlet(discharge) flange 9, safety valve 10 distribute on the horizontal center line of chamber cylindrical shell 17 and cylindrical shell 11.Diagonal angle, two hanger 13 left and right sides distributes on the cylindrical shell 11.Cylindrical shell 11 right-hand members welding maintenance population 18 is to make things convenient for Equipment Inspection and maintenance.
As shown in Figure 4, Fig. 4 is a tube sheet stringing generalized section, and the heat exchanger tube 15 in the chamber cylindrical shell 17 is divided into a plurality of backhauls district by end socket dividing plate 24, as A, B, C, D, E, F, A1, B1, C1, D1, E1, the F1 of Fig. 4.The design of backhaul district is 8 in general, all be fine for 10 or 12, as can be seen from Figure 4, the heat exchanger tube quantity in 1 backhaul district is successively decreased gradually from primary fluid suction flange 2 to the primary fluid outlet(discharge) flange, because being gradually, the arranged of heat exchanger tube 15 successively decreases, therefore, when primary fluid is high-temperature steam or high-temperature water, in exothermic process, gradate and be low-temperature condensate or water at low temperature, heat exchanger tube 15 in each backhaul all is full shapes, when therefore primary fluid flows in heat exchanger tube 15, can keep higher flow velocity, form strong cross-flow, adverse current and turbulent flow.In like manner, the secondary heating agent enters in the chamber cylindrical shell 17 by secondary heating agent suction flange 23, the a plurality of up and down big capacitor of secondary heating agent through being divided into by chamber dividing plate 16, and the baffling effect of being played by deflection plate 14, primary fluid and secondary heating agent are adverse current fully, cross-flow, add that heat exchanger tube 15 is the arrangement mode that successively decreases gradually, different variation (being that actual internal area is in different size) has also taken place in the actual internal area in each chamber (be current the area by housing), the secondary heating agent in housing in the shape of a spiral, piston shape is irregular flows, thereby, secondary heating agent and primary fluid have formed strong cross-flow, adverse current and turbulent flow, strong cross-flow, adverse current and turbulent flow have strengthened the heat exchange effect, have improved the coefficient of heat transfer greatly.
In the utility model, the horizontally disposed backhaul dividing plate 12 up and down in the cylindrical shell 11 has formed 4 backhaul mixing chamber, after the abundant mixing of process I, II, III, IV backhaul mixing chamber, stirring, the backhaul, flows out through secondary heating agent outlet(discharge) flange 9.The secondary heating agent enters in the chamber cylindrical shell 17 by chamber cylindrical shell 17 bottom secondary heating agent suction flanges 23, then by chamber dividing plate 16 water conservancy diversion and deflection plate 14 bafflings, through up and down 2,3 or a plurality of chamber that varies in size (because successively decreasing gradually of heat exchanger tube 15 formed the chamber that varies in size; The water of equal in quality, temperature raises, density reduces, volume increases accordingly), because the secondary heating agent is a process that heat absorption is expanded always, the size variation of chamber, primary fluid and secondary heating agent form strong adverse current and cross-flow, thereby the perfect heat exchange type of flow in the formation thermal conduction study, strong adverse current and cross-flow have improved the Reynolds coefficient, have strengthened film coefficient of heat transfer, impel the abundant heat release of primary fluid in the heat exchanger tube 15, the secondary heating agents absorb heat fully in the chamber cylindrical shell 17, and the porous radiant tube 19 from the upper right side of chamber cylindrical shell 17 flows in the cylindrical shells 11 then.
In the utility model, as Fig. 2, shown in Figure 4, bearing 22 adopts the saddle-shape bearing, and is rational in infrastructure, stressed even, is convenient to install.
In order better to improve the coefficient of heat transfer of the present utility model (K value), heat exchanger tube adopts dual damascene spiral shell fiber crops copper tube, nickel alloy or Nitinol pipe, has both strengthened the coefficient of heat transfer (K value), has improved service life again.
In order to reduce maintenance cost, adopted Long Circle modular tube sheet, whole heat exchange tube core can be extracted out, has reduced maintenance cost greatly, has reduced maintenance difficulty and intensity.
For the better equipment thermal efficiency that improves, effective use of energy sources, we have adopted multiple-pass, multithread road, many bafflings, the cross-flow of multi-cavity chamber.The high-efficiency module back-stroke displacement heat exchanger compact conformation, small, save land area and building height, save construction investment, be convenient to design arrangement, operation is convenient simultaneously.High-efficiency module back-stroke displacement heat exchanger adopts low alloy steel plate and non-ferrous alloy to make and has effectively prevented corrosion.The bearing capacity height is pressed droop loss little, thermal efficiency height (more than 99.7%), heat resistance is good, and manufacturing process is simple, and cost is lower, performances such as maintenance management is easy, long service life (reaching more than 20 years) has effectively prevented some disadvantages of other volumetric heat exchangers.Be the upgrading products of four-stroke volumetric heat exchanger, vertical volumetric heat exchanger, horizontal volumetric heat exchanger and some other volumetric heat exchanger.
Dual damascene spiral shell fiber crops copper tube, nickel alloy or Nitinol pipe are as heat exchanger tube 15, high-efficiency module back-stroke displacement heat exchanger is when operation work, special shape, special comb mode, make trembling and dither that heat exchanger tube 15 do not stop in chamber cylindrical shell 17, branch, ion that calcium magnesium in the secondary heating agent etc. adheres to fouling easily can't adhere to, so the utmost point is not easy fouling on heat exchanger tube 15 outer walls.
After operation a period of time, branch, ion and solid impurity etc. that the calcium magnesium that can't adhere to etc. adheres to fouling easily flow out chamber cylindrical shell 17 through 19 following currents of porous radiant tube, flow in the cylindrical shell 11, because impact and stirring that porous radiant tube 19 is powerful, branch, ion that less, lighter calcium magnesium etc. adheres to fouling easily are mingled in the current through secondary heating agent outlet(discharge) flange 9 these equipment of outflow, the solid impurity that can't flow out is deposited on the bottom in chamber cylindrical shell 17 and the cylindrical shell 11, discharges by the sewage draining exit 20 that is arranged on chamber cylindrical shell 17 and cylindrical shell 11 bottoms.
Claims (10)
1. high-efficiency module back-stroke displacement heat-exchanger rig, comprise the primary fluid that primary fluid suction flange (2) and primary fluid outlet(discharge) flange (1) are connected by Outer Tube, comprise the tube sheet (5) that connects primary fluid suction flange (2) and primary fluid outlet(discharge) flange (1) import department, tube sheet (5) fixedly heat exchanger tube (15) level stretches to chamber cylindrical shell (17), it is characterized in that: also comprise a cylindrical shell (11), cylindrical shell (11) one STHs, from horizontal interval layout backhaul dividing plate (12) up and down chamber cylindrical shell (17) more than, the chamber cylindrical shell (17) of level is communicated with by porous radiant tube (19) with vertical cylindrical shell (11) in the cavity of cylindrical shell (11).
2. high-efficiency module back-stroke displacement heat-exchanger rig according to claim 1, it is characterized in that: described chamber cylindrical shell (17) section is a vertical little ellipsoid of placing, cylindrical shell (11) section is a vertical big ellipsoid of placing, the height of chamber cylindrical shell (17) is 1/2 of cylindrical shell (a 11) height---2/3, and chamber cylindrical shell (17) is welded in the perforate in cylindrical shell (11) left side.
3. high-efficiency module back-stroke displacement heat-exchanger rig according to claim 1, it is characterized in that: described primary fluid suction flange (2) position of keeping right in chamber cylindrical shell (17) upper end, secondary heating agent outlet(discharge) flange (1) position of keeping right in chamber cylindrical shell (17) lower end, primary fluid suction flange (2) and secondary heating agent outlet(discharge) flange (1) are welded on the end socket (3), end socket (3) is connected by flange (4) with chamber cylindrical shell (17) again, end socket (3), connect tube sheet (5) between flange (4) and chamber cylindrical shell (17) flange, tube sheet (5) fixedly heat exchanger tube (15) level stretches to chamber cylindrical shell (17).
4. high-efficiency module back-stroke displacement heat-exchanger rig according to claim 1, it is characterized in that: on cylindrical shell (11) cavity of described chamber cylindrical shell (17) upper end thermometer boss (7) and pressure gauge connection II (8) are arranged respectively, measure cylindrical shell (11) cavity interior secondary heat medium temperature and pressure respectively by thermometer and Pressure gauge that thermometer boss (7) is connected with pressure gauge connection II (8).
5. high-efficiency module back-stroke displacement heat-exchanger rig according to claim 1 is characterized in that: described cylindrical shell (11) top is a secondary heating agent outlet(discharge) flange (9), and secondary heating agent outlet(discharge) flange (9) is drawn the secondary heating agent by pipeline.
6. high-efficiency module back-stroke displacement heat-exchanger rig according to claim 1 is characterized in that: described cylindrical shell (11) is fixed with hanger (13) about going up.
7. high-efficiency module back-stroke displacement heat-exchanger rig according to claim 1, it is characterized in that: the heat exchanger tube (15) in the described chamber cylindrical shell (17) is divided into a plurality of backhauls district by end socket dividing plate (24), successively decreases gradually from primary fluid suction flange (2) to the heat exchanger tube quantity in primary fluid outlet(discharge) flange (1) backhaul district.
8. high-efficiency module back-stroke displacement heat-exchanger rig according to claim 1 is characterized in that: described chamber cylindrical shell (17) is a stretched head of cylindrical shell (11), and chamber cylindrical shell (17) leaves 1/3 to 1/4 outside cylindrical shell (11).
9. high-efficiency module back-stroke displacement heat-exchanger rig according to claim 1 is characterized in that: the horizontally disposed backhaul dividing plate (12) up and down in the described cylindrical shell (11) has formed 4 backhaul mixing chamber.
10. high-efficiency module back-stroke displacement heat-exchanger rig according to claim 1 is characterized in that: described heat exchanger tube (15) adopts dual damascene spiral shell fiber crops copper tube, nickel alloy or Nitinol pipe.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010202200870U CN201688731U (en) | 2010-06-09 | 2010-06-09 | Efficient modular return displacement type heat-exchange unit |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010202200870U CN201688731U (en) | 2010-06-09 | 2010-06-09 | Efficient modular return displacement type heat-exchange unit |
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| Publication Number | Publication Date |
|---|---|
| CN201688731U true CN201688731U (en) | 2010-12-29 |
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| CN2010202200870U Expired - Fee Related CN201688731U (en) | 2010-06-09 | 2010-06-09 | Efficient modular return displacement type heat-exchange unit |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114234583A (en) * | 2022-02-28 | 2022-03-25 | 山东宝阳干燥设备科技有限公司 | High-efficient drying-machine of graphite |
-
2010
- 2010-06-09 CN CN2010202200870U patent/CN201688731U/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114234583A (en) * | 2022-02-28 | 2022-03-25 | 山东宝阳干燥设备科技有限公司 | High-efficient drying-machine of graphite |
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