CN103968688A - Shell-and-tube heat exchanger and method for machining plate holes in shell-and-tube heat exchanger - Google Patents
Shell-and-tube heat exchanger and method for machining plate holes in shell-and-tube heat exchanger Download PDFInfo
- Publication number
- CN103968688A CN103968688A CN201410212175.9A CN201410212175A CN103968688A CN 103968688 A CN103968688 A CN 103968688A CN 201410212175 A CN201410212175 A CN 201410212175A CN 103968688 A CN103968688 A CN 103968688A
- Authority
- CN
- China
- Prior art keywords
- heat exchanger
- plate
- tube
- hole
- shell
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Abstract
The invention relates to a heat transfer technology and provides a shell-and-tube heat exchanger and a method for machining plate holes in the shell-and-tube heat exchanger. According to the technology, heat exchange tubes are distributed in a radial topological mode in cooperation with circular-ring-shaped and disk-shaped baffle plates which are arranged alternately, so that shell-pass fluid uniformly flows through all the heat exchange tubes in the radial direction, and the utilization rate of the heat exchange tubes is increased. The shell-and-tube heat exchanger mainly comprises a barrel body, tube plates, tube boxes, the heat exchange tubes and the baffle plates. The baffle plates comprise the circular-ring-shaped baffle plates and the disk-shaped baffle plates, the circular-ring-shaped baffle plates and the disk-shaped baffle plates are arranged alternately, and the total number of the baffle plates is an odd number. The heat exchange tubes are arranged on concentric circles with different diameters with the symmetrical axis of the heat exchanger as the center and are distributed evenly in the circumferential direction. The spacing between the heat exchange tubes is not a definite value, and the minimum spacing is 1.25 times larger than or equal to the outer diameter of each heat exchange tube.
Description
Technical field:
The present invention relates to a kind of heat transfer technology, be specifically related to a kind of shell-and-tube heat exchanger.Based on fractal theory, adopt radial topology exchange heat pipe to arrange, coordinate the circular plate type and the annular deflection plate that are arranged alternately, the mobile uniformity coefficient of shell-side fluid is maximized, to improve the utilization rate of heat exchanger tube.
Background technology:
Heat transmission equipment can be divided into by function: condenser, evaporimeter, reheater, superheater etc., can be divided into by the feature of heat exchanger components: shell-and-tube heat exchanger, fin-tube heat exchanger, plate type heat exchanger (comprising plate type heat exchanger and plate-fin heat exchanger).
Shell-and-tube heat exchanger is the most widely used a kind of heat exchanger of current process industrial.It is mainly made up of parts such as housing, tube sheet, heat exchanger tube, end socket, deflection plates, can adopt stainless steel, ordinary carbon steel, red copper or other non-ferrous metal as material.When operation, a kind of fluid is entered by one end fusing head connection tube, through heat exchanger tube, flows out from the adapter of other end end socket, is referred to as tube side; One other fluid is entered by an adapter of housing, and another from housing taken over and flowed out, and is referred to as shell side.The critical component that heat exchanger tube conducts heat as cold fluid and hot fluid, its structure and pattern are continued to optimize.Along with the continuous appearance of Novel efficient heat exchange tube, the range of application of shell-and-tube heat exchanger constantly expands.The measure that thermoexcell conducts heat at present has two classes, and the mobility status that (1) changes fluid is to increase flow velocity; (2) change heat-transfer surface shape and size.
The advantage of shell-and-tube heat exchanger is that the unit volume equipment heat transfer area that can provide is large, and heat-transfer effect is also better.Due to firm in structure, and the material ranges that can select is also broader, therefore strong adaptability, operating flexibility is large.Especially in high temperature, high pressure and large-scale plant, adopt more general.But contain and current conventional tubular heat exchanger in traditional design standard (as GB151-1999 shell-and-tube heat exchanger), the shortcoming of maximum is just that heat exchange area is not fully used.
For the research of the enhanced heat exchange technology of various heat exchangers, mainly concentrate on heat exchanger inner fluid change of flow state and the parameter optimization of each parts is studied to two aspects, and the main study subject of heat exchanger parameters of operating part is exactly heat exchanger tube (plate) arrangement mode (in-line arrangement or fork row), heat exchanger tube (plate) row, heat exchanger tube (plate) spacing size, fin arrangement pitch, fin shape etc.In the design of heat exchanger, the impact of the heat exchanger performances such as heat exchanger tube row and arrangement, heat exchanger tube shape, fin external form and spacing is very important.In order to improve the flow velocity of shell-and-tube heat exchanger shell-side fluid, increase heat transfer efficiency, some is often installed in housing and is restrained perpendicular deflection plate, can improve like this rate of flow of fluid, also force shell-side fluid distance according to the rules simultaneously, repeatedly form cross-flow with tube bank, be conducive to manage the increase of outer heat transfer coefficient.Baffle forms has circle to lack type (bow type), disc and annulus.Deflection plate has annular, arc, spirality etc. multiple, and these deflection plates all make top and the bottom region formation dead band and the stagnant area of shell-side fluid at hydraulic barrier, and the forced turbulent region of really playing heat exchange effect is limited.
At present conventional heat exchanger tube arrangement mode have equilateral triangle, the triangle of becoming a full member, square, become a full member square etc. several.For the ease of engineering application, the fixed dimension of having given these arrangement modes in design standard.From hydromechanical angle, the fixing size of space of heat exchanger tube is very disadvantageous to the mobile homogenising of shell-side fluid.On the other hand, owing to cannot accurately judging the flow regime of shell-side fluid in heat exchanger tube gap, as its flow velocity and pressure distribution, therefore the optimization of shell fluid flow is faced to great difficulty.
By means of the advantage of computer simulation, can carry out whole flow analysis and Strength Calculation to given heat exchanger.Aspect the numerical analysis of heat exchanger, domestic have a large amount of bibliographical informations, as adopted steady-state distribution parametric method, and the simulation of the optimum length in loop when condenser and evaporimeter are used; Adopt the simulation of the distributed constant method heat exchange property when the little heat transfer temperature difference to ripple type multichannel single process plate-type evaporator; To the simulation that under wet cooling condition, cooling-air type dry evaporator coil pipe carries out; To the simulation of marine vehicle cool house evaporimeter and room air conditioning evaporator; Simulation to fin-tube type heat exchanger diabatic process etc.
The key of heat exchanger tube heat-transfer character numerical analysis is the foundation of computation model.Conventional model comprises porous media model, physical model and periodicity unit flow passage model at present.Adopt porous media model too to simplify the internal structure of heat exchanger, analog result can not accurately reflect the details such as Real Flow Field and heat transfer conditions of regional area, and the important analog parameter of part is relevant with operation medium with structural shape, the physical dimension of heat exchanger, therefore there is certain limitation.Carry out novel shell side supporting construction flow field local detail fluidised form distribute and enhanced heat transfer mechanism study time, should not adopt porous media model.
Adopt flowing of physical model heat exchanger to carry out numerical simulation with heat-transfer character, can obtain the stream heat transfer of heat exchanger and the qualitative analysis of flow behavior, but for Large Tube shell heat exchanger, because heat exchanger tube number is huge, grid number and the amount of calculation of model increase extremely, and existing software and hardware still can not meet the demands.For this reason, researcher proposes periodically unit flow passage model simplification computational methods, has ignored near the impact on shell fluid flow and heat transfer overall performance of cloth area under control fluid flows and conducts heat cylindrical shell wall particularity.If when heat exchanger tube stringing mode is square, the fluid circulation space that desirable 4 heat exchanger tubes surround is " unit flow passage " computation model, can effectively reduce like this numerical simulation difficulty of longitudinal flow of shell-side heat exchanger.But, unit flow passage model is applicable to some longitudinal flow of shell-side heat exchanger that heat-exchanging tube bundle and tube bundle support structure are symmetric, for the shell-and-tube heat exchanger that does not possess said structure feature, as baffle heat exchanger, spiral-plate heat exchanger etc., cannot simplify like this.For the less shell-and-tube heat exchanger of diameter of the housing, even if meet the symmetric simplification requirement of unit flow passage, due near the fluid in cloth area under control cylindrical shell wall on the impact of shell fluid flow and heat transfer overall performance compared with can not ignore greatly, unit flow passage modeling result and actual condition have relatively large deviation.
Many research shows, coordinate arc, semicircle deflection plate according to the layout of traditional heat exchanger tube (equilateral triangle, the triangle of becoming a full member, square, become a full member square), be difficult to form the Uniform Flow of shell-side fluid, that is not all heat exchanger tube all uses uniform shell-side fluid to flow through around, some zone velocities are large, some zone velocities are little, and some regions or even dead band (fluid does not flow), this part heat exchanger tube reality is inoperative like this.Visible, the arrangement mode of optimization heat exchanger tube, has important engineering significance for design, the application of this type of heat exchanger.
Summary of the invention:
The present invention is directed to heat exchanger tube spatial distribution in existing shell-and-tube heat exchanger, be unfavorable for the shortcoming of shell-side fluid Uniform Flow, based on fractal theory, a kind of shell-and-tube heat exchanger is proposed, adopt the method for successively being arranged by the middle mind-set radius augment direction heat exchanger tube of arranging, heat exchanger tube is uniformly distributed at circumferencial direction, and adopts spaced annular and disc deflection plate, to realize the Uniform Flow of shell-side fluid.
Another object of the present invention is to provide the processing method of above-mentioned shell-and-tube heat exchanger plate hole.
Concrete technical scheme of the present invention is as follows:
A kind of shell-and-tube heat exchanger, mainly comprise cylindrical shell, tube sheet, bobbin carriage, heat exchanger tube and deflection plate, described cylindrical shell both sides connect left and right bobbin carriage, cylindrical shell and left pipe box junction are provided with left tube sheet, cylindrical shell and right pipe box junction are provided with right tube sheet, cylindrical shell both sides are provided with import and outlet, in cylindrical shell, be equidistantly provided with polylith deflection plate, deflection plate is parallel to left and right tube sheet setting, and deflection plate adopts annular deflection plate and disc deflection plate interphase distribution mode, the total block data of deflection plate is odd number, adjacent with the left and right tube sheet annular deflection plate that is; On each deflection plate and left and right tube sheet, be equipped with plate hole, each plate hole diameter is suitable;
In described cylindrical shell, be furnished with many heat exchanger tubes, each heat exchanger tube is along drum shaft to be arrangeding in parallel, and the plate hole that each heat exchanger tube wore on the left and right tube sheet at each deflection plate and two ends communicates with left and right bobbin carriage, is respectively equipped with tube side import and tube side outlet on left and right bobbin carriage;
Described annular deflection plate external diameter is suitable with cylindrical shell, and middle part is hollow ring; Between described disc deflection plate external diameter and cylindrical shell, leave annular vacancy.
Under the effect of described annular and disc deflection plate, shell-side fluid radially flows, and therefrom mind-set surrounding spreads or converges to center from surrounding.
The import of cylindrical shell is connected with entrance sleeve, and the outlet of cylindrical shell is connected with discharge connection.
Tube side import department is connected with entrance sleeve, and tube side exit is connected with discharge connection.
The area of the hollow ring of described annular deflection plate equates with the vacancy area of disc deflection plate.
Annular deflection plate inner circle radius r
ifor
In formula: R is cylindrical shell inside radius, the method providing according to GB151-1999 standard is determined, h=0.2～0.45R.
The radius r of disc deflection plate
ofor
In formula: R is cylindrical shell inside radius, h=0.2～0.45R.
Plate hole locations correspondence on described annular deflection plate, disc deflection plate and left and right tube sheet, the spacing >=1.25d of adjacent plate hole.
A processing method for shell-and-tube heat exchanger plate hole, wherein, on left and right tube sheet, the arrangement method of plate hole has as follows:
While arranging plate hole should first determine the closely spaced d of adjacent panels Kongzui
s, adjacent plate hole center distance d
sshould be more than or equal to 1.25d; (d
s>=1.25d); Described adjacent plate hole comprises the adjacent plate hole between adjacent plate hole and adjacent, the different adjacent layer on same layer; Plate hole is centered close to taking tube sheet center as the center of circle, on the concentric circles of different-diameter, and plate hole on each concentric circles is uniformly distributed in a circumferential direction;
(1) the 1st plate hole is set as benchmark plate hole at left and right tube sheet center; Taking the center of the 1st plate hole as initial point, d
sfor radius is justified, 6 plate holes are evenly set on this circumference, be the 1st laminate hole; Then continue successively to arrange each laminate hole according to order from inside to outside, the position of outer plate hole is taking the plate hole of internal layer as benchmark, and outer plate hole is centered close on the center line of the adjacent plate hole line of centres of internal layer two;
(2) while arranging plate hole by step 1, when the same laminate pitch of holes on certain one deck is more than or equal to 2d
swhen (minimum spacing of twice), the plate hole of its internal layer is radially moved to this layer of position, and between adjacent plate hole, increase a plate hole, making this laminate hole number is 2 times of its inner plating hole number, and this layer is a fractal layer;
The plate hole of arranging according to the method described above, since the 2nd laminate hole, determine that the method for the concentrically ringed radius in place, n laminate hole is as follows:
1. in n-1 laminate hole, choose two plate holes of arbitrary neighborhood, taking central point i, the j of these two plate holes as benchmark, determine the perpendicular bisector l of central point i, j line;
2. on perpendicular bisector l, determine a some k, this point is positioned at the outside in n-1 laminate hole, and is d with the central point i of two plate hole of n-1 layer, the distance of j
s;
3. in judging point k and n-2 laminate hole, whether the distance of nearest plate hole is more than or equal to d
s, if so, put k and be the concentrically ringed radius in place, n laminate hole to the distance at tube sheet center; If be less than d
s, a k is outwards moved to a k ' along described perpendicular bisector l, make a k ' in n-2 laminate hole recently the distance of plate hole equal d
s, put k ' and be the concentrically ringed radius in place, n laminate hole to the distance at tube sheet center.
Wherein, annular deflection plate, disc deflection plate upper plate hole forming method are identical with left and right tube sheet, and each plate hole locations is corresponding, heat exchanger tube through the plate hole on tube sheet and deflection plate after, be formed in circumferencial direction and have the shell side space of periodic feature.
Heat exchanger tube is through the feature of the flow resistances such as the space, shell side flow field forming after the plate hole of arranging according to described method has circumferentially, under the effect of described spaced annular and disc deflection plate, each root heat exchanger tube of flowing through radially (is shunted or confluxed to center by surrounding) to shell-side fluid by middle mind-set surrounding, the utilization rate that can ensure heat exchanger tube is 100%.Meanwhile, under the prerequisite of known shell-side fluid total flow, can estimate the average speed (sectional area in average speed=total flow/gap) of the heat exchanger tube of flowing through of shell-side fluid, thus the heat transfer coefficient of estimation heat exchanger tube.
According to described principle, the average headway of the heat exchanger tube of arranging is greater than 1.25d, therefore the heat exchanger tube quantity that can arrange is less than the heat exchanger tube quantity that (adjacent heat exchange tubes spacing is equal to 1.25d) obtains.Work as d
swhile getting different value, the dot matrix of the plate hole central point obtaining has the feature of geometric similarity.D
sless, plate hole is more intensive.
According to described principle, can utilize mapping software, adopt graphing method to be determined one by one the position in each laminate hole by mind-set radius augment direction in tube sheet.
The present invention compared to existing technology tool has the following advantages:
(1) heat-exchanging tube bundle of at present conventional shell-and-tube heat exchanger, the flowing law of shell-side fluid is difficult for definite, thereby also just can not ensure the utilization rate of heat exchanger tube, therefore need increase heat transfer area while design to ensure heat transfer effect.And heat-exchanging tube bundle of the present invention is evenly arranged at circumferencial direction, shell-side fluid is under the annular deflection plate of alternative arrangement and the effect of disc deflection plate, evenly geocentric vertical diverging flow Huo Xiang center aggregate flow, every heat exchanger tube all has fluid to pass through around, there is not dead band in whole flow field, the utilization rate of heat exchanger tube is 100%, can significantly reduce the design margin of heat exchange area.
(2) heat exchanger tube of the present invention is arranged the periodic feature with circumferencial direction, makes shell side flow field have periodic feature, therefore the flow direction of shell-side fluid has predictability.Can be according to the total flow of shell-side fluid and the gap size estimation average speed of shell-side fluid and the heat transfer coefficient of heat exchanger tube.In addition, can be according to the periodic feature in shell side flow field, set up the monocycle numerical analysis model of heat exchanger, compare to the block mold of setting up heat exchanger, greatly reduce modeling difficulty and reduced amount of calculation, contributing to heat transfer property and the stress distribution of Accurate Prediction heat exchanger.
(3) (shell-side fluid flows to radius augment direction when heat exchanger tube of the present invention is arranged, to adopt fractal method to make one shell-side fluid be divided into equably two strands in fractal position, vice versa), there is the effect of " rectification " in fractal locational heat exchanger tube, promoted the Uniform Flow of shell-side fluid.In addition,, because fractal topology-level time can reach infinitely great, therefore, the present invention is not subject to the restriction of heat exchanger external diameter, is specially adapted to Large Tube shell-type pressure vessel, as the design of large-scale EO reactor (diameter 8m, heat exchanger tube radical nearly 20,000).
Brief description of the drawings:
Fig. 1 is the structural representation of shell-and-tube heat exchanger.
Fig. 2 is the schematic diagram of successively arranging of plate hole.
Fig. 3 is the structural representation of annular deflection plate.
Fig. 4 is the structural representation of disc deflection plate.
Fig. 5 is the structural representation of left and right tube sheet.
In figure, 1-tube side discharge connection; 2-left pipe box; The left tube sheet of 3-; 4-shell side entrance sleeve; 5-cylindrical shell; 6-shell side discharge connection; The right tube sheet of 7-; 8-right pipe box; 9-tube side entrance sleeve; 10-right support abutment; 11-disc and donut 1; 12-disk deflection plate 1; 13-disc and donut 2; 14-disk deflection plate 2; 15-disc and donut 3; 16-left support abutment; 17-heat exchanger tube.
Detailed description of the invention:
Embodiment mono-:
Design a heat exchanger, be mainly made up of parts such as housing, tube sheet, heat exchanger tube, bobbin carriage, deflection plates, material is not limit, as shown in Figure 1.Tube side fluid is entered by the tube side entrance sleeve 9 on right pipe box 8, collects from left to right, and discharged by tube side discharge connection 1 after stream heat-exchanging tube bundle 17 at left pipe box 2; Shell-side fluid enters from the shell side entrance sleeve 4 of columniform cylindrical shell 5, under the effect of deflection plate, makes Radial Flow at shell side, forms cross-flow with tube side fluid, discharges finally by the shell side entrance sleeve 7 by cylindrical shell 5.
The left tube sheet 3 that heat-exchanging tube bundle is welded to connect with cylindrical shell 5 and right tube sheet 7 are fixing, and through each deflection plate.Tube sheet all has the plate hole consistent with heat exchanger tube external diameter with on deflection plate (annular and circular plate type).Respectively as shown in Figure 3,4, the structure of left and right tube sheet as shown in Figure 5, has corresponding plate hole above to the structure of annular and circular plate type deflection plate.The vacancy part of the hollow ring of annular deflection plate and disc deflection plate needn't be established plate hole.
The major parameter of heat exchanger, as diameter of the housing, length, heat exchanger tube diameter and deflection plate quantity are determined by technological design.Wherein heat exchanger tube radical and deflection plate quantity may need to revise according to method for designing of the present invention.
The number of deflection plate is necessary for odd number, and is necessary for annular deflection plate near the deflection plate of two tube sheets, so could form uniform shell-side fluid and flow.In the time that the scheme adopting is as shown in Figure 1 taken in the import and export of shell side, the region at shell side import and outlet place can not form Uniform Flow, and the method that can adopt circumferencial direction to be evenly arranged multiple adapters improves this two uniformitys that region is mobile.
The thickness of tube sheet designs by the requirement of GB151-1999 standard, and the size of all plate holes and tolerance are all determined by standard-required.
According to heat exchanger tube arrangement mode of the present invention, the mean gap of heat exchanger tube should be greater than the heat exchanger tube external diameter of 1.25 times, therefore sequencable heat exchanger tube sum should be less than the heat exchanger tube radical by GB151-1999 standard design; Improved again the utilization rate of heat exchanger tube due to radial topology arrangement mode, the efficiency of heat-exchanging tube bundle improves, and can make up the deficiency that pipe number reduces.If Calculation of Heat Transfer result shows to need to increase heat exchange area, can increase diameter of the housing, to increase heat exchanger tube radical.
Embodiment bis-:
According to plate hole arrangement principle of the present invention, adopt following steps to determine the position of plate hole.
1. as shown in Figure 2, set up polar coordinate system, coordinate origin is placed in the center of tube sheet, and radial coordinate is r, and circumferencial direction coordinate is
.The 1st plate hole is set at tube sheet center.
2. determine the minimum spacing d of plate hole
s.Taking (r=0) as the center of circle, d
smake the 1st concentric circles for radius, (3) evenly arrange 6 plate holes on this concentric circles on principle, and wherein 1 plate hole is centered close to
on.The spacing of these 6 plate holes meets d
sthe requirement of>=1.25d.
3. according to definite method of described concentric circles radius, calculating the 2nd concentrically ringed radius is 2d
s, 6 plate holes are evenly set on this circle.The spacing of these 6 plate holes is 2d
s, according to the requirement of step (2), the number in this laminate hole is doubled to (the 2nd laminate hole count is 12), be the 1st point of shaped position herein.The spacing of investigating the 2nd laminate hole and the 1st laminate hole, meets d
sthe requirement of>=1.25d.
4. according to definite method of described concentric circles radius, calculate the 3rd concentrically ringed radius and be
12 plate holes are evenly set on this circle.These plate holes meet d with respect to the position in the 2nd laminate hole
sthe requirement of>=1.25d.
5. according to definite method of described concentric circles radius, adopt graphing method to determine the 4th concentrically ringed radius in place, laminate hole, with point
for the center of circle (this point is that on accompanying drawing 2, in the 4th laminate hole the center of the plate hole of overstriking mark), d
sfor radius is justified, this circle with
have two intersection points, wherein away from the radius vector of that intersection point at tube sheet center as the 4th concentrically ringed radius in place, laminate hole.(2) 12 plate holes of evenly arranging on this concentric circles on principle.
With reference to above step, can determine one by one the position in each laminate hole.The 23 laminate holes of having arranged altogether on tube sheet shown in Fig. 2, experienced 4 times fractal, point shaped position is successively at the the 2nd, 5,10,23 laminate hole places.
Application example one:
The mist of certain reactor through with feed stream heat exchange after, need it be cooled to after 60 DEG C from 110 DEG C with recirculated cooling water, enter absorption tower and inhale.The flow of known mist is 2.4 × 10
5kg/h, pressure is 6.9MPa, and the pressure of recirculated cooling water is 0.4MPa, and the inlet temperature of recirculated water is 29 DEG C, and the temperature of outlet is 39 DEG C, adopts a shell-and-tube heat exchanger of design of heat exchanger method design of the present invention, meets working condition requirement.
Consider water easily fouling under low flow velocity, and the speed of water in tube side is larger, therefore tube side medium is recirculated water, shell side medium is mist.The physical parameter of recirculated water when 85 DEG C ((110+60)/2=85) is: density is 994.3kg/m
3, specific heat at constant pressure is 4.174kJ/ (kgK), and thermal conductivity factor is for being 0.624W/ (mK), and viscosity is 0.742 × 10
-3pas; The physical parameter of mist when 34 DEG C ((29+39)/2=34) is: density is 90kg/m
3, specific heat at constant pressure is 3.297kJ/ (kgK), and thermal conductivity factor is for being 0.0279W/ (mK), and viscosity is 1.5 × 10
-5pas.
Carried out designing and calculating according to " GB151-1999 shell-and-tube heat exchanger " and related design handbook, the basic parameter of the heat exchanger obtaining comprises:
Housing internal diameter: 1450mm heat exchanger tube size: Φ 25 × 2.5mm
Heat exchanger tube spacing: 44mm heat exchanger tube length: 7000mm
Heat exchanger tube radical: 980 number of baffles: 14
Baffle(s) spacing: 450mm deflection plate circle lacks height: 360mm
Shell side is taken over internal diameter: 310mm tube side is taken over internal diameter: 370mm
Adopt heat exchanger tube arrangement method of the present invention, on annular deflection plate, disc deflection plate and tube sheet that design obtains, plate hole is arranged respectively as shown in Fig. 3,4,5.The inner circle radius r of annular deflection plate
ifor 330mm; The exradius r of disc deflection plate
ofor 650mm.
Fractal through 3 times altogether, 787 heat exchanger tubes of having arranged.Heat exchanger tube radical is 80% of equilateral triangle arrangement, taking the inlet temperature of shell side and tube side medium and mass flow as boundary condition, adopt computational fluid dynamics software FLUENT to set up the monocycle numerical model of shell side, tube side and heat exchanger tube, the outlet temperature that calculates tube side (cooling water) is 38.3 DEG C, the outlet temperature of shell side (mist) is 57.2 DEG C, meets design requirement.
Visible, adopt shell-and-tube heat exchanger of the present invention under the prerequisite meeting design requirement, the more traditional design of heat exchange efficiency significantly improves, thereby has reduced the quantity of heat exchanger tube.
Claims (9)
1. a shell-and-tube heat exchanger, it is characterized in that: mainly comprise cylindrical shell, tube sheet, bobbin carriage, heat exchanger tube and deflection plate, described cylindrical shell both sides connect left, right pipe box, cylindrical shell and left pipe box junction are provided with left tube sheet, cylindrical shell and right pipe box junction are provided with right tube sheet, cylindrical shell both sides are provided with import and outlet, in cylindrical shell, be equidistantly provided with polylith deflection plate, deflection plate is parallel to a left side, right tube sheet setting, and deflection plate adopts annular deflection plate and disc deflection plate interphase distribution mode, the total block data of deflection plate is odd number, with a left side, what right tube sheet was adjacent is annular deflection plate, on each deflection plate and left and right tube sheet, be equipped with plate hole, each plate hole diameter is suitable,
In described cylindrical shell, be furnished with many heat exchanger tubes, each heat exchanger tube is along drum shaft to be arrangeding in parallel, and the plate hole that each heat exchanger tube wore on the left and right tube sheet at each deflection plate and two ends communicates with left and right bobbin carriage, is respectively equipped with tube side import and tube side outlet on left and right bobbin carriage;
Described annular deflection plate external diameter is suitable with cylindrical shell, and middle part is hollow ring; Between described disc deflection plate external diameter and cylindrical shell, leave annular vacancy.
Under the effect of described annular and disc deflection plate, shell-side fluid radially flows, and therefrom mind-set surrounding spreads or converges to center from surrounding.
2. shell-and-tube heat exchanger according to claim 1, is characterized in that: the import of cylindrical shell is connected with entrance sleeve, and the outlet of cylindrical shell is connected with discharge connection.
3. shell-and-tube heat exchanger according to claim 1, is characterized in that: tube side import department is connected with entrance sleeve, and tube side exit is connected with discharge connection.
4. shell-and-tube heat exchanger according to claim 1, is characterized in that: the area of the hollow ring of described annular deflection plate equates with the vacancy area of disc deflection plate.
5. shell-and-tube heat exchanger according to claim 4, is characterized in that: annular deflection plate inner circle radius r
ifor
In formula: R is cylindrical shell inside radius, h=0.2～0.45R.
6. shell-and-tube heat exchanger according to claim 4, is characterized in that: the radius r of disc deflection plate
ofor
In formula: R is cylindrical shell inside radius, h=0.2～0.45R.
7. shell-and-tube heat exchanger according to claim 1, is characterized in that: plate hole locations correspondence on described annular deflection plate, disc deflection plate and left and right tube sheet, the spacing >=1.25d of adjacent plate hole.
8. the processing method of the arbitrary described shell-and-tube heat exchanger plate hole of claim 1-7, wherein, on left and right tube sheet, the arrangement method of plate hole has following feature:
While arranging plate hole should first determine the closely spaced d of adjacent panels Kongzui
s, adjacent plate hole center distance d
sshould be more than or equal to 1.25d; (d
s>=1.25d); Described adjacent plate hole comprises the adjacent plate hole between adjacent plate hole and adjacent, the different adjacent layer on same layer; Plate hole is centered close to taking tube sheet center as the center of circle, on the concentric circles of different-diameter, and plate hole on each concentric circles is uniformly distributed in a circumferential direction;
(1) the 1st plate hole is set as benchmark plate hole at left and right tube sheet center; Taking the center of the 1st plate hole as initial point, d
sfor radius is justified, 6 plate holes are evenly set on this circumference, be the 1st laminate hole; Then continue successively to arrange each laminate hole according to order from inside to outside, the position of outer plate hole is taking the plate hole of internal layer as benchmark, and outer plate hole is centered close on the center line of the adjacent plate hole line of centres of internal layer two;
(2) while arranging plate hole by step 1, when the same laminate pitch of holes on certain one deck is more than or equal to 2d
swhen (minimum spacing of twice), the plate hole of its internal layer is radially moved to this layer of position, and between adjacent plate hole, increase a plate hole, making this laminate hole number is 2 times of its inner plating hole number, and this layer is a fractal layer;
The plate hole of arranging according to the method described above, since the 2nd laminate hole, determine that the method for the concentrically ringed radius in place, n laminate hole is as follows:
1. in n-1 laminate hole, choose two plate holes of arbitrary neighborhood, taking central point i, the j of these two plate holes as benchmark, determine the perpendicular bisector l of central point i, j line;
2. on perpendicular bisector l, determine a some k, this point is positioned at the outside in n-1 laminate hole, and is d with the central point i of two plate hole of n-1 layer, the distance of j
s;
3. in judging point k and n-2 laminate hole, whether the distance of nearest plate hole is more than or equal to d
s, if so, put k and be the concentrically ringed radius in place, n laminate hole to the distance at tube sheet center; If be less than d
s, a k is outwards moved to a k ' along described perpendicular bisector l, make a k ' in n-2 laminate hole recently the distance of plate hole equal d
s, put k ' and be the concentrically ringed radius in place, n laminate hole to the distance at tube sheet center.
9. the processing method of shell-and-tube heat exchanger plate hole according to claim 8, wherein, annular deflection plate, disc deflection plate upper plate hole forming method are identical with left and right tube sheet, and each plate hole locations is corresponding, heat exchanger tube through the plate hole on tube sheet and deflection plate after, be formed in circumferencial direction and have the shell side space of periodic feature.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410212175.9A CN103968688B (en) | 2014-05-19 | 2014-05-19 | The processing method of a kind of shell-and-tube heat exchanger and plate hole thereof |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410212175.9A CN103968688B (en) | 2014-05-19 | 2014-05-19 | The processing method of a kind of shell-and-tube heat exchanger and plate hole thereof |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103968688A true CN103968688A (en) | 2014-08-06 |
| CN103968688B CN103968688B (en) | 2016-01-13 |
Family
ID=51238496
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410212175.9A Active CN103968688B (en) | 2014-05-19 | 2014-05-19 | The processing method of a kind of shell-and-tube heat exchanger and plate hole thereof |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN103968688B (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106770432A (en) * | 2016-11-16 | 2017-05-31 | 南京工业大学 | A kind of removable pipe array heat transfer performance test device |
| CN108506957A (en) * | 2018-07-05 | 2018-09-07 | 北京蓝爱迪电力技术有限公司 | A kind of boiler coal dust burning heating equipment |
| CN109974510A (en) * | 2019-05-08 | 2019-07-05 | 张化机（苏州）重装有限公司 | A kind of baffle plate |
| CN110285692A (en) * | 2019-07-03 | 2019-09-27 | 昆山市三维换热器有限公司 | Desulfurization slurry cooler |
| CN110455096A (en) * | 2019-08-27 | 2019-11-15 | 东方电气集团东方锅炉股份有限公司 | Baffle plate support structure and its shell-and-tube heat exchanger with shunt effect |
| CN112539668A (en) * | 2020-11-30 | 2021-03-23 | 杭州科百特过滤器材有限公司 | Heat exchanger and manufacturing method thereof |
| CN112629292A (en) * | 2020-12-17 | 2021-04-09 | 上海铠韧气体工程股份有限公司 | High-efficiency heat exchanger |
| CN113928574A (en) * | 2021-11-19 | 2022-01-14 | 中国直升机设计研究所 | Heat exchanger of helicopter cooling system |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2005042957A (en) * | 2003-07-24 | 2005-02-17 | Toshiba Corp | Heat exchanger and manufacturing method thereof |
| CN1724957A (en) * | 2005-06-16 | 2006-01-25 | 西安交通大学 | Circular disk type chemical heat pump reactor |
| CN102252540A (en) * | 2011-08-23 | 2011-11-23 | 东南大学 | Heat exchanger of Cantor set fractal structure type |
| CN202361873U (en) * | 2011-12-16 | 2012-08-01 | 中国石油化工股份有限公司 | Structure capable of improving shell side fluid energy exchange effect of tubular equipment |
| CN103471431A (en) * | 2013-09-26 | 2013-12-25 | 上海锅炉厂有限公司 | Fixed tube-sheet heat exchanger with temperature control function |
| CN203824384U (en) * | 2014-05-19 | 2014-09-10 | 南京工业大学 | Tube and shell type heat exchanger |
-
2014
- 2014-05-19 CN CN201410212175.9A patent/CN103968688B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2005042957A (en) * | 2003-07-24 | 2005-02-17 | Toshiba Corp | Heat exchanger and manufacturing method thereof |
| CN1724957A (en) * | 2005-06-16 | 2006-01-25 | 西安交通大学 | Circular disk type chemical heat pump reactor |
| CN102252540A (en) * | 2011-08-23 | 2011-11-23 | 东南大学 | Heat exchanger of Cantor set fractal structure type |
| CN202361873U (en) * | 2011-12-16 | 2012-08-01 | 中国石油化工股份有限公司 | Structure capable of improving shell side fluid energy exchange effect of tubular equipment |
| CN103471431A (en) * | 2013-09-26 | 2013-12-25 | 上海锅炉厂有限公司 | Fixed tube-sheet heat exchanger with temperature control function |
| CN203824384U (en) * | 2014-05-19 | 2014-09-10 | 南京工业大学 | Tube and shell type heat exchanger |
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106770432A (en) * | 2016-11-16 | 2017-05-31 | 南京工业大学 | A kind of removable pipe array heat transfer performance test device |
| CN108506957A (en) * | 2018-07-05 | 2018-09-07 | 北京蓝爱迪电力技术有限公司 | A kind of boiler coal dust burning heating equipment |
| CN109974510A (en) * | 2019-05-08 | 2019-07-05 | 张化机（苏州）重装有限公司 | A kind of baffle plate |
| CN109974510B (en) * | 2019-05-08 | 2024-02-23 | 张化机（苏州）重装有限公司 | Baffle plate |
| CN110285692A (en) * | 2019-07-03 | 2019-09-27 | 昆山市三维换热器有限公司 | Desulfurization slurry cooler |
| CN110455096A (en) * | 2019-08-27 | 2019-11-15 | 东方电气集团东方锅炉股份有限公司 | Baffle plate support structure and its shell-and-tube heat exchanger with shunt effect |
| CN112539668A (en) * | 2020-11-30 | 2021-03-23 | 杭州科百特过滤器材有限公司 | Heat exchanger and manufacturing method thereof |
| CN112629292A (en) * | 2020-12-17 | 2021-04-09 | 上海铠韧气体工程股份有限公司 | High-efficiency heat exchanger |
| CN113928574A (en) * | 2021-11-19 | 2022-01-14 | 中国直升机设计研究所 | Heat exchanger of helicopter cooling system |
Also Published As
| Publication number | Publication date |
|---|---|
| CN103968688B (en) | 2016-01-13 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN203824384U (en) | Tube and shell type heat exchanger | |
| CN103968688B (en) | The processing method of a kind of shell-and-tube heat exchanger and plate hole thereof | |
| CN201517899U (en) | Pipe shell type heat exchanger | |
| CN102261968A (en) | Method and device for predicting node temperature of shell and tube heat exchanger | |
| Yang et al. | Numerical investigation on shell-side performances of combined parallel and serial two shell-pass shell-and-tube heat exchangers with continuous helical baffles | |
| CN101480595B (en) | Slurry bubble column reactor with needle type fin column tube bundle | |
| CN106123651A (en) | Heat exchanger with saddle | |
| CN112361854A (en) | Micro-channel heat exchanger | |
| Wen et al. | Flow resistance and convective heat transfer performances of airflow through helical-tube bundles | |
| CN201748839U (en) | Micro disturbed flow rod-baffle heat exchanger | |
| CN201187959Y (en) | External diversion deflector rod type closed circulation water heat exchanger | |
| CN203432382U (en) | Horizontal shell type condenser | |
| CN103411451B (en) | Rectification type tube-shell type heat exchanger | |
| CN203810987U (en) | Liquid cooler | |
| CN103148717A (en) | Novel horizontal type crude oil heat exchanger | |
| CN113028863B (en) | J-shaped baffle plate heat exchanger | |
| Habib et al. | Correlations of flow maldistribution parameters in an air cooled heat exchanger | |
| CN204806943U (en) | Heat exchanger | |
| CN203810986U (en) | Straight-tube exchanger | |
| CN207147286U (en) | A kind of removable lamella heat exchanger with impingement baffle | |
| CN205156699U (en) | Double -helical -baffle heat exchanger | |
| CN210892838U (en) | Cooling device | |
| Liu et al. | CFD study on the radial distribution of coolants in the inlet section of rod-baffle-multi-tubular reactor | |
| CN201764855U (en) | Heat exchanger | |
| Singh et al. | Design the Shell and Tube Heat Exchanger with the help of Programming using MATLAB software |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant |