CN101435668A - Internal and external fin flat tube heat exchanger - Google Patents
Internal and external fin flat tube heat exchanger Download PDFInfo
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- CN101435668A CN101435668A CNA2008102323492A CN200810232349A CN101435668A CN 101435668 A CN101435668 A CN 101435668A CN A2008102323492 A CNA2008102323492 A CN A2008102323492A CN 200810232349 A CN200810232349 A CN 200810232349A CN 101435668 A CN101435668 A CN 101435668A
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Abstract
The invention discloses an inner-outer fin flat-tube heat exchanger. The heat exchanger comprises a shell body, a tube pass inlet and a tube pass outlet at both ends of the shell body, two tube plates at both ends inside the shell body, a heat exchange tube fixed between the two tube plates in parallel, a plurality of baffles and a shell pass inlet and a shell pass outlet arranged on the side wall of the shell body, wherein the heat exchange tube, the tube pass inlet and the tube pass outlet form an in-tube circulation passage; the baffles, the shell pass inlet and the shell pass outlet form a shell side circulation passage; a plurality of outer fins are arranged outside the heat exchange tube; the heat exchange tube comprises a flat tube and longitudinal corrugated inner fins arranged inside the flat tube; and a plurality of longitudinal circulation passages are formed between the flat tube and the longitudinal corrugated inner fins therein. Through adding longitudinal inner fin plates inside the prior flat tube, the inner-outer fin flat-tube heat exchanger can heat high-viscosity fluid inside the heating exchange tube well so as to obtain a heat transfer structure and heat exchange performance equivalent to those of a plate-fin heat exchanger; meanwhile, the pressure-bearing capacity of the inner-outer fin flat-tube heat exchanger is also improved effectively.
Description
Technical field
The present invention relates to a kind of heat exchanger, especially relate to a kind of internal and external fin flat tube heat exchanger.
Background technology
Heat exchanger is a kind of significant element equipment in the industry such as oil refining, chemical industry, environmental protection, the energy, electric power, usually in the construction in chemical plant, heat exchanger accounts for the 10-20% of gross investment, and at present, heat exchanger commonly used both at home and abroad can be divided into tubular type and board-like two big classes substantially.For the situation that gas converting heat is arranged, the general mode that increases fin that adopts is strengthened the heat exchange of gas side.Usually, plate-fin heat exchanger is widely used in gas-gas heat exchange, and fin-tube type heat exchanger is more is applied to the solution-air heat exchange.
For plate-fin heat exchanger, because of having the pricker jail, its part in the brazing filler metal process do not form weak link, thereby determined that plate-fin heat exchanger can not bear relative pressure higher under higher absolute pressure or the malfunction, therefore spalling takes place under limiting condition possibly, so that brings bigger economic loss and potential safety hazard.In addition, plate-fin heat exchanger is non-disconnectable, cleans difficulty, the manufacturing process complexity, and the cost height, thereby limited the use occasion of plate-fin heat exchanger.
Owing to be subjected to the influence of flat tube shell-and-tube heat exchanger structural design, developed the flat tube fin-tube type heat exchanger, promptly replace the pipe tube bank with the flat tube tube bank, thereby can make that heat exchange area is effectively improved, make its thermal efficiency near lamella heat exchanger, it can bear bigger pressure simultaneously, and process industry is simple.But for simple flat pipe heat exchanger, in petrochemical industry, the high viscosity fluid heats in the heat exchanger light pipe, fluid temperature (F.T.) is too high near tube wall often occurring, and in pipe centre fluid underheat, promptly fluid heats inhomogeneous, insufficient phenomenon, thereby influences the heat exchange efficiency of equipment.Therefore, necessaryly strengthen at the flowing heat transfer in the light pipe pipe.In addition, for fin-tube type heat exchanger, generally only increase fin in the heat exchanger tube outside, the pipe of pipe side face can bear higher absolute pressure, be applicable to occasion with high-pressure fluid running, and the range of application broad of operating pressure, as condenser, evaporimeter and air cooler etc., but the heat exchange area in its unit volume is lower with respect to plate-fin heat exchanger, and exchange capability of heat is lower than the exchange capability of heat of plate-fin heat exchanger.
Summary of the invention
Technical problem to be solved by this invention is at above-mentioned deficiency of the prior art, a kind of internal and external fin flat tube heat exchanger is provided, it is by increasing vertical inner fin plate in traditional flat tube, thereby can fully heat the high viscosity fluid in the heat exchanger tube, make its heat transfer structure and heat exchange property aspect suitable, simultaneously its bearing capacity is effectively improved with plate-fin heat exchanger.
For solving the problems of the technologies described above, the technical solution used in the present invention is: a kind of internal and external fin flat tube heat exchanger, comprise housing, be arranged on housing the tube side import and the tube side outlet at two ends up and down, lay respectively at two tube sheets at enclosure interior two ends, the a plurality of heat exchanger tubes of secured in parallel between two tube sheets, be arranged on a plurality of baffle plates that play fixedly heat exchanger tube and guide functions of enclosure interior and lay respectively at shell side import and shell side outlet on the housing sidewall, described heat exchanger tube is communicated with tube side import and tube side outlet and forms circulation passage in the pipe, described a plurality of baffle plate is communicated with shell side import and shell side outlet and forms a bow type baffle plate type shell-side circulation passage, described heat exchanger tube is outside equipped with a plurality of outer fins, it is characterized in that: described heat exchanger tube forms a plurality of longitudinal stream circulation passage by flat tube and the longitudinal ripple inner fin that is arranged on flat tube inside between described flat tube and its inner longitudinal ripple inner fin.
The quantity of described baffle plate is odd number, and described shell side import and shell side outlet are positioned at the homonymy of housing sidewall.
The bellows-shaped of described longitudinal ripple inner fin is the consecutive periods function.
The ripple of described longitudinal ripple inner fin is zigzag, rectangle or sinusoidal waveform.
Have a plurality of holes or many seams on the described longitudinal ripple inner fin continuously.
Described outer fin is flat continuous slab wing or corrugated continuous slab wing.
Have a plurality of holes or seam on described flat continuous slab wing or the corrugated continuous slab wing.
Long direction eddy generator or shutter are installed on described flat continuous slab wing or the corrugated continuous slab wing.
The present invention compared with prior art has the following advantages,, 1, rational in infrastructure, use easy to operate; 2, heat exchanger tube adopts flat tube, can increase the intraductal heat transfer area effectively, improves its heat transfer efficiency; In flat tube, add inner fin and then can increase the intraductal heat transfer area effectively, increased disturbance fluidly simultaneously, thereby make tube fluid be able to abundant heating, therefore, in flat tube, increase vertical inner fin plate and have remarkable result for heat conduction reinforced in the flat tube, thereby fully the high viscosity liquid in the heating tube makes it suitable with plate-fin heat exchanger aspect heat transfer structure and heat exchange property, and its bearing capacity also can be improved effectively simultaneously; 3, increase multi-form outer fin in the heat exchanger tube outside, make the exchange capability of heat in the heat exchanger tube outside also obtain reinforcement simultaneously, make the heat exchange area in the resultant heat exchanger unit volume be far longer than general fin-tube type heat exchanger like this, suitable with the heat exchange area in the plate-fin heat exchanger unit volume, thereby, the present invention has increased the heat exchange area of the inside and outside both sides of heat exchanger tube, thereby strengthened the heat convection of the inside and outside both sides of heat exchanger tube, the heat exchange density that makes resultant heat exchanger is much larger than general fin-tube type heat exchanger; 4, relative pressure higher under higher absolute pressure or the malfunction can be born, heat exchanger generation spalling can be effectively prevented.To sum up, the present invention can effectively increase the inside and outside heat exchange area of heat exchanger tube, the inside and outside heat convection of enhanced tube and intraductal heat transfer, makes its exchange capability of heat can reach the peer-level of plate-fin heat exchanger, has clear superiority bearing aspect the high pressure to compare with plate-fin simultaneously; It is by increasing vertical inner fin plate in traditional flat tube, thereby can fully heat the high viscosity fluid in the heat exchanger tube, make its heat transfer structure and heat exchange property aspect suitable with plate-fin heat exchanger, simultaneously its bearing capacity is effectively improved, have and make simply, keep in repair and clean advantages such as convenient.
Below by drawings and Examples, technical scheme of the present invention is described in further detail.
Description of drawings
Fig. 1 is an assembly structure schematic diagram of the present invention.
Fig. 2 is an internal structure schematic diagram of the present invention.
Fig. 3 is the structural representation of heat exchanger tube of the present invention.
Fig. 4 is the structural representation of longitudinal ripple inner fin of the present invention.
The schematic perspective view that Fig. 5 is connected with the flat continuous slab wing that has shutter for heat exchanger tube of the present invention.
Fig. 6 is the schematic perspective view that the flat continuous slab wing of heat exchanger tube of the present invention and perforate is connected.
The schematic perspective view that Fig. 7 is connected with corrugated continuous slab wing for heat exchanger tube of the present invention.
The schematic perspective view that Fig. 8 is connected with the flat continuous slab wing that cracks for heat exchanger tube of the present invention.
The schematic perspective view that Fig. 9 is connected with the flat continuous slab wing that has long direction eddy generator for heat exchanger tube of the present invention.
Description of reference numerals:
1-tube sheet; 2-heat exchanger tube; 3-baffle plate;
4-flat continuous slab wing; 5-housing; 6-flat tube;
7-longitudinal ripple inner fin; 9-corrugated continuous slab wing; 10-1-tube side import;
10-2-tube side outlet; 11-1-shell side import; 11-2-shell side outlet;
12-hole; 13-seam; 14-long direction eddy generator;
15-shutter; 17-through hole.
The specific embodiment
As shown in Figure 1 and Figure 2, the present invention includes housing 5, be arranged on the tube side import 10-1 at housing two ends about in the of 5 and tube side outlet 10-2, two tube sheets 1 that lay respectively at housing 5 inner two ends, secured in parallel are in a plurality of baffle plates 3 of a plurality of heat exchanger tubes 2 between two tube sheets 1, the fixedly heat exchanger tube 2 that is arranged on housing 5 inside and guide functions and lay respectively at shell side import 11-1 and shell side outlet 11-2 on housing 5 sidewalls, correspondence has a plurality of through holes 17 that are used to install heat exchanger tube 2 on its tube sheet 1.Wherein, described heat exchanger tube 2 is communicated with tube side import 10-1 and tube side outlet 10-2 and forms circulation passage in the pipe, described a plurality of baffle plate 3 is communicated with the shell-side circulation passage of forming a bow type baffle plate type with shell side import 11-1 and shell side outlet 11-2, and heat exchanger tube 2 is outside equipped with a plurality of outer fins.In addition, the quantity of described baffle plate 3 is odd number, and described shell side import 11-1 and shell side outlet 11-2 are positioned at the homonymy of housing 5 sidewalls.In the present embodiment, the quantity of baffle plate 3 is 7 and the staggered level board that is installed on housing 5 inwalls, and 7 baffle plates 3 are formed a baffle plate type circulation passage.In the actual use, the quantity of described baffle plate 3 also can be even number, and described shell side import 11-1 and shell side outlet 11-2 lay respectively at the both sides of housing 5 sidewalls.
In conjunction with Fig. 3, Fig. 4, described heat exchanger tube 2 forms a plurality of longitudinal stream circulation passage by flat tube 6 and the longitudinal ripple inner fin 7 that is arranged on flat tube 6 inside between described flat tube 6 and its inner longitudinal ripple inner fin 7.In addition, the bellows-shaped of described ripple is the consecutive periods function.In actual application, the dielectric viscosity that is circulated in the longitudinal ripple inner fin 7 is big more, and its ripple wavelength X sparse more and described ripple is big more, and the quantity of longitudinal stream circulation passage is few more.In the present embodiment, the bellows-shaped of longitudinal ripple inner fin 7 is a sinusoidal waveform, in the practice, can be other bellows-shaped such as zigzag or rectangle with its ripple processing and fabricating also.
In the actual use, after the heat exchanging fluid of pipe side enters from tube side import 10-1, passing a plurality of heat exchanger tubes 2 that are fixed on the tube sheet 1, specifically is to flow through from a plurality of longitudinal fin circulation passages that are distributed in heat exchanger tube 2 inside, is flowed out by tube side outlet 10-2 more at last.Owing in heat exchanger tube 2, be provided with longitudinal ripple inner fin plate 7, thereby greatly increased the heat transfer area in the heat exchanger tube 2, strengthened the fluid heat exchange of heat exchanger tube 2 inboards.
And flat continuous slab wing 4 and a plurality of baffle plate 3 are installed outside heat exchanger tube 2, flat continuous slab wing 4 is used for increasing the heat exchange area of shell-side, to strengthen the exchange capability of heat of shell-side.In the actual use, after the heat exchanging fluid of its shell-side entered from shell side import 11-1, transversal flow heat exchanger tube 2 under the guiding of baffle plate 3 was finished behind the heat transfer process and is flowed out from shell side outlet 11-2.
To sum up, because heat exchanger tube 2 inside and outside both sides all are added with fin, thereby can effectively increase heat exchange area, and the exchange capability of heat of efficient hardening both sides heat exchanging fluid; In addition,, thereby can make that heat exchange area is effectively improved, make its thermal efficiency near lamella heat exchanger because adopt the carrier of flat tube 6 as heat exchanger tube 2 inside and outside both sides fins.That is to say, the present invention is by increasing vertical inner fin plate in traditional flat tube 6, thereby can fully heat the high viscosity fluid in the heat exchanger tube 2, make its heat transfer structure and heat exchange property aspect suitable, simultaneously its bearing capacity be effectively improved with plate-fin heat exchanger.
The difference of present embodiment and embodiment 1 is, has a plurality of holes 12 on the heat exchanger tube 2 outer flat continuous slab wings of installing 4, as shown in Figure 6; Have a plurality of seams 13 on the perhaps flat continuous slab wing 4, as shown in Figure 8; A plurality of shutters 15 are installed, as shown in Figure 5 on the perhaps flat continuous slab wing 4; A plurality of long direction eddy generators 14 are installed, as shown in Figure 9 on the perhaps flat continuous slab wing 4.In actual application, flow through when the heat exchanging fluid of shell-side and to have hole 12 or to stitch 13, when the flat continuous slab wing 4 of long direction eddy generator 14 or shutter 15 perhaps is installed, the disturbance that fluid flows further increases, thereby it flows and the heat exchange boundary layer has obtained destroying effectively and attenuate, thereby improved the exchange capability of heat of shell-side, the heat exchange property of heat exchanger is further improved.During actual processing and fabricating, also can all have hole 12 in the both sides up and down of flat continuous slab wing 4 or stitch 13, perhaps descend both sides that long direction eddy generator 14 or shutter 15 all are installed thereon.
As shown in Figure 7, the difference of present embodiment and embodiment 1 is that the heat exchanger tube 2 outer outer fins of installing are corrugated continuous slab wing 9, and the 26S Proteasome Structure and Function of remainder is all identical with embodiment 1.Owing to outside the heat exchanger tube 2 corrugated continuous slab wing 9 is installed, thereby the shell-side heat exchanging fluid is mobile in the formed small space between corrugated continuous slab wing 9, thereby has further increased the disturbance that fluid flows, make the exchange capability of heat of shell-side increase.Like this, corrugated fin is installed all inside and outside heat exchanger tube 2, is improving heat exchange area and increasing disturbance, further in the reinforcing heat exchange capability, also further improve the bearing capacity of heat exchanger integral body.In addition,, also can on corrugated continuous slab wing 9, have a plurality of holes 12 or stitch 13, a plurality of long direction eddy generators 14 or shutter 15 perhaps are installed with embodiment 2.
Setting up physical model calculates and analyzes the heat-transfer character in the inner fin flat tube, specifically be to adopt finite volume method that the mobile of the flat tube light pipe of certain physical dimension and the two kinds of heat-transfer pipes of inner fin flat tube among the present invention carried out whole audience numerical simulation with heat transfer property, analyze both heat transfer properties under same boundary conditions of contrast with this.Make a concrete analysis of as follows: the flat tube light pipe and the inner fin flat tube that with the longitudinal length are 400mm are example, and in the inner fin flat tube of the present invention, the longitudinal length of flat tube 14 is that 400mm and the thickness that is arranged on the longitudinal ripple inner fin 15 of flat tube 14 inside are 0.4mm, the ripple number of cycles is 3, simultaneously, the material of longitudinal ripple inner fin 15 is that copper and its are shaped as zigzag.In addition, calculation of boundary conditions is given as follows: it is water that two kinds of heat-transfer pipe imports are all adopted pressure boundary condition, fluid working substance with outlet, and inlet temperature is T=300K; And the outer wall of inner fin flat tube and common flat tube employing constant temperature boundary condition is T=400K.
Adopt the solid coupling algorithm of stream that two kinds of heat-transfer pipes are calculated in the heat-transfer character under the high flow rate, turbulence model is selected for use and can be realized k～ε two equation models.Adopting the finite volume method to be dispersed in the zoning, is example with the inner fin flat tube, and it is 487312 that its grid is divided the node number, and trellis-type is the hexahedron structure grid.Adopt the coupled problem of SIMPLEC algorithm process speed and pressure, the discrete scheme of convective term is QUICK.By checking, adopt the analysis result relative deviation that is drawn in numerical result that above-mentioned numerical analysis method draws and " flowing in the flat tube pipe and the three-dimensional numerical value simulation of conducting heat " literary composition in 6%, thereby adopt the reliability of numerical computations model higher.Simultaneously, for the ease of problem analysis, with two kinds of heat-transfer pipes is flat tube light pipe and inner fin flat tube, under identical inlet and outlet pressure and identical inlet velocity condition, data such as its outlet temperature of comparative analysis, inlet velocity, total heat transfer, mean heat transfer coefficient are analyzed the superiority-inferiority of inner fin flat tube heat transfer property with this.Make a concrete analysis of as follows:
At first, under identical inlet and outlet pressure condition, the heat transfer property of two kinds of heat exchanger tubes of comparative analysis, its calculated data sees Table 1.
Correction data under the identical inlet and outlet pressure condition of table 1
| Reduced parameter | Outlet temperature (K) | Inlet velocity (m/s) | Total heat transfer (kW) | Mean heat transfer coefficient (W/ (m 2·K)) |
| The flat tube light pipe | 316.6 | 6.97 | 59.41 | 30688 |
| The inner fin flat tube | 325.8 | 5.0 | 67.25 | 25385 |
Table 1 illustrates under identical inlet and outlet pressure boundary condition, relative flat tube light pipe, and the outlet temperature of water conservancy project matter has improved 2.91% (promptly 9.2 ℃) in the inner fin flat tube; Under the situation of flow velocity less than the flat tube light pipe (flow velocity has reduced by 28.3%), total heat transfer has improved 13.2% on the contrary; Mean heat transfer coefficient has then reduced by 17.2%, and this is mainly caused by the reason of two aspects, and one is the reduction of inlet velocity, and certain effect that slackens has been played in the heat transfer in the inner fin flat tube; It two is that inner fin flat tube total heat transfer is greater than the flat tube light pipe, its heat transfer area is also greater than the flat tube light pipe, total heat transfer is divided, its mean heat transfer coefficient then may be less than the flat tube light pipe, but generally speaking, even under the situation of inlet velocity less than the flat tube light pipe, the whole heat transfer property of inner fin flat tube is better than the flat tube light pipe.
For the heat transfer property of multianalysis inner fin flat tube more, under identical inlet velocity condition, the further heat-transfer character of comparative analysis inner fin flat tube and flat tube light pipe.Specifically: the heat transfer property of two kinds of heat exchanger tubes of comparative analysis under identical inlet velocity condition (V=5.0m/s), its calculated data sees Table 2.
Correction data under the identical inlet velocity condition of table 2
| Reduced parameter | Outlet temperature (K) | Total heat transfer (kW) | Mean heat transfer coefficient (W/ (m 2·K)) |
| The flat tube light pipe | 317.5 | 45.90 | 23449 |
| The inner fin flat tube | 325.8 | 67.25 | 25385 |
As shown in Table 2, under identical inlet velocity condition, with respect to the flat tube light pipe, the outlet temperature of water conservancy project matter has improved 2.61% (promptly 8.3 ℃) in the inner fin flat tube; Total heat transfer has improved 46.5%; Mean heat transfer coefficient has improved 8.26%, and promptly all heat transfer indexs have all obtained improving effectively.Therefore, with respect to the flat tube light pipe, the inner fin flat tube makes that the intraductal heat transfer characteristic has obtained improving greatly, helps improving the compactedness of heat exchanger integral body.
In sum, suitably increase thickness and the number that is arranged on the longitudinal ripple inner fin 15 in the flat tube 14, selection has the inner fin material of high thermal conductivity and good material performance, has certain positive role for the whole heat transfer efficiency of further improving internal and external fin flat tube heat exchanger and compactedness.
The above; it only is preferred embodiment of the present invention; be not that the present invention is imposed any restrictions, everyly any simple modification that above embodiment did, change and equivalent structure changed, all still belong in the protection domain of technical solution of the present invention according to the technology of the present invention essence.
Claims (8)
1. internal and external fin flat tube heat exchanger, comprise housing (5), be arranged on housing (5) the tube side import (10-1) and the tube side outlet (10-2) at two ends up and down, lay respectively at two tube sheets (1) at the inner two ends of housing (5), the a plurality of heat exchanger tubes (2) of secured in parallel between two tube sheets (1), be arranged on housing (5) inner play fixedly heat exchanger tube (2) and a plurality of baffle plates (3) of guide functions and shell side import (11-1) and the shell side that lays respectively on housing (5) sidewall exports (11-2), described heat exchanger tube (2) is communicated with tube side import (10-1) and tube side outlet (10-2) and forms circulation passage in the pipe, described a plurality of baffle plate (3) is communicated with shell side import (11-1) and shell side outlet (11-2) and forms a bow type baffle plate type shell-side circulation passage, described heat exchanger tube (2) is outside equipped with a plurality of outer fins, it is characterized in that: described heat exchanger tube (2) is by flat tube (6) and be arranged on the inner longitudinal ripple inner fin (7) of flat tube (6), forms a plurality of longitudinal stream circulation passage between described flat tube (6) and its inner longitudinal ripple inner fin (7).
2. according to the described internal and external fin flat tube heat exchanger of claim 1, it is characterized in that: the quantity of described baffle plate (3) is odd number, and described shell side import (11-1) and shell side outlet (11-2) are positioned at the homonymy of housing (5) sidewall.
3. according to claim 1 or 2 described internal and external fin flat tube heat exchangers, it is characterized in that: the bellows-shaped of described longitudinal ripple inner fin (7) is the consecutive periods function.
4. according to claim 1 or 2 described internal and external fin flat tube heat exchangers, it is characterized in that: the ripple of described longitudinal ripple inner fin (7) is zigzag, rectangle or sinusoidal waveform.
5. according to claim 1 or 2 described internal and external fin flat tube heat exchangers, it is characterized in that: have a plurality of holes or many seams on the described longitudinal ripple inner fin (7) continuously.
6. according to claim 1 or 2 described internal and external fin flat tube heat exchangers, it is characterized in that: described outer fin is flat continuous slab wing (4) or corrugated continuous slab wing (9).
7. according to the described internal and external fin flat tube heat exchanger of claim 6, it is characterized in that: have a plurality of holes (12) or seam (13) on described flat continuous slab wing (4) or the corrugated continuous slab wing (9).
8. according to the described internal and external fin flat tube heat exchanger of claim 6, it is characterized in that: described flat continuous slab wing (4) or corrugated continuous slab wing (9) are gone up long direction eddy generator (14) or shutter (15) are installed.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNA2008102323492A CN101435668A (en) | 2008-11-20 | 2008-11-20 | Internal and external fin flat tube heat exchanger |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNA2008102323492A CN101435668A (en) | 2008-11-20 | 2008-11-20 | Internal and external fin flat tube heat exchanger |
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Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103307912A (en) * | 2013-06-27 | 2013-09-18 | 山东美陵化工设备股份有限公司 | Oil slurry steam generator |
| CN103712489A (en) * | 2013-12-26 | 2014-04-09 | 南通大学 | Heat exchanger for waste heat recovery of air compressor |
| CN103982329A (en) * | 2014-04-29 | 2014-08-13 | 浙江银轮机械股份有限公司 | Heat recovery unit for engine waste heat generation ORC (organic Rankine cycle) systems |
| CN105352346A (en) * | 2015-11-25 | 2016-02-24 | 张伟 | Header shell pressure bearing heat exchanger |
| CN107160975A (en) * | 2017-06-30 | 2017-09-15 | 高志男 | Vehicle |
| CN107166999A (en) * | 2017-06-30 | 2017-09-15 | 高志男 | Heat exchanger and apply its vehicle |
| CN108627035A (en) * | 2018-04-25 | 2018-10-09 | 杭州三花家电热管理系统有限公司 | Heat-exchanging component and heat-exchange system |
| US20220082336A1 (en) * | 2018-12-27 | 2022-03-17 | Eni S.P.A. | Thermal energy storage apparatus |
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- 2008-11-20 CN CNA2008102323492A patent/CN101435668A/en active Pending
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103307912A (en) * | 2013-06-27 | 2013-09-18 | 山东美陵化工设备股份有限公司 | Oil slurry steam generator |
| CN103712489A (en) * | 2013-12-26 | 2014-04-09 | 南通大学 | Heat exchanger for waste heat recovery of air compressor |
| CN103982329A (en) * | 2014-04-29 | 2014-08-13 | 浙江银轮机械股份有限公司 | Heat recovery unit for engine waste heat generation ORC (organic Rankine cycle) systems |
| CN103982329B (en) * | 2014-04-29 | 2016-03-02 | 浙江银轮机械股份有限公司 | A kind of heat recoverer for engine waste heat generating ORC system |
| CN105352346A (en) * | 2015-11-25 | 2016-02-24 | 张伟 | Header shell pressure bearing heat exchanger |
| CN107160975A (en) * | 2017-06-30 | 2017-09-15 | 高志男 | Vehicle |
| CN107166999A (en) * | 2017-06-30 | 2017-09-15 | 高志男 | Heat exchanger and apply its vehicle |
| CN107166999B (en) * | 2017-06-30 | 2024-01-12 | 高志男 | Heat exchanger and vehicle using same |
| CN107160975B (en) * | 2017-06-30 | 2024-01-12 | 高志男 | Vehicle with a vehicle body having a vehicle body support |
| CN108627035A (en) * | 2018-04-25 | 2018-10-09 | 杭州三花家电热管理系统有限公司 | Heat-exchanging component and heat-exchange system |
| US20220082336A1 (en) * | 2018-12-27 | 2022-03-17 | Eni S.P.A. | Thermal energy storage apparatus |
| US11953271B2 (en) * | 2018-12-27 | 2024-04-09 | Eni S.P.A. | Thermal energy storage apparatus |
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Open date: 20090520 |