CN209763847U - Dry-type shell-and-tube heat exchanger for improving liquid supply distribution of refrigerant - Google Patents
Dry-type shell-and-tube heat exchanger for improving liquid supply distribution of refrigerant Download PDFInfo
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- CN209763847U CN209763847U CN201920208162.2U CN201920208162U CN209763847U CN 209763847 U CN209763847 U CN 209763847U CN 201920208162 U CN201920208162 U CN 201920208162U CN 209763847 U CN209763847 U CN 209763847U
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- refrigerant
- distribution
- heat exchange
- heat exchanger
- shell
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- 239000003507 refrigerant Substances 0.000 title claims abstract description 71
- 239000007788 liquid Substances 0.000 title claims abstract description 66
- 238000005192 partition Methods 0.000 claims description 19
- 238000005452 bending Methods 0.000 claims description 14
- 230000003068 static effect Effects 0.000 claims description 14
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 abstract description 2
- 229910052802 copper Inorganic materials 0.000 abstract description 2
- 239000010949 copper Substances 0.000 abstract description 2
- 239000000463 material Substances 0.000 abstract description 2
- 239000008240 homogeneous mixture Substances 0.000 abstract 1
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 239000000203 mixture Substances 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 1
- 230000007812 deficiency Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 230000008676 import Effects 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
- 239000011148 porous material Substances 0.000 description 1
- 102220007331 rs111033633 Human genes 0.000 description 1
- 102220029346 rs34541442 Human genes 0.000 description 1
- 102220012898 rs397516346 Human genes 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
- 238000013517 stratification Methods 0.000 description 1
- 239000002699 waste material Substances 0.000 description 1
Landscapes
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
The utility model discloses a dry shell-and-tube heat exchanger for improving the distribution of refrigerant liquid supply.A refrigerant distribution box is arranged at one end of a refrigerant inlet of a shell, and a uniform gas-liquid homogeneous mixture is formed as the refrigerant liquid supply by separating and remixing a gas-liquid two-phase refrigerant, so that the gas-liquid two-phase refrigerant is uniformly distributed and enters each heat exchange tube; by designing the heat exchange tube structure, the total length of the flow path of each heat exchange tube and the on-way resistance are basically equal to form an equal-resistance heat exchange tube bundle, and the internal resistance loss of each heat exchange tube is equal to ensure that the liquid supply of the refrigerant is uniformly distributed; the liquid supply of the refrigerant in the heat exchanger is uniformly distributed, so that the side heat transfer efficiency of the refrigerant is improved, the copper material consumption of the heat exchanger is reduced, the weight of the heat exchanger is lightened, and the measured temperature at the outlet of the heat exchanger can more effectively reflect the real superheat degree of the heat exchanger.
Description
Technical Field
The utility model relates to a dry-type shell and tube heat exchanger.
Background
In the dry evaporator, a capillary tube, a pore plate, a thermostatic expansion valve or an electronic expansion valve directly controls a gas-liquid two-phase refrigerant to enter a tube side of the evaporator, the refrigerant liquid is completely converted into gas in the tube, and a cooled (heated) medium flows in a shell side outside the tube. The shell side is provided with spoilers for changing the flow direction of fluid, and the spoilers are often used for designing a shell side medium flow channel in a dry evaporator, so that the heat transfer effect can be improved, the spoilers also play a role in supporting a tube bundle, and the number of the spoilers is determined according to the property and the flow of the medium and the size of a heat exchanger.
The conventional dry evaporator generally adopts a circular shell (seamless steel tube, straight welded tube or spiral welded tube, etc.), so the tube box, the tube plate, the sealing gasket and the spoiler are all circular. With reference to the attached drawings 1-3, the tube pass is as follows:
1. The supply cavity is a circular tube box, the height difference delta h between the highest point and the lowest point of the liquid supply distribution cavity is larger, so the static pressure difference delta p of a liquid column in the cavity is larger, and a gas-liquid two-phase refrigerant (a gaseous refrigerant is low in density and is separated upwards; a liquid refrigerant is high in density and is separated downwards) entering the cavity has larger static pressure difference delta p of the liquid column in the cavity, so the gas-liquid stratification phenomenon is aggravated, the liquid supply distribution is uneven, the gaseous refrigerant is mostly distributed in the upper heat exchange tube, the proportion of the distributed refrigerant is small, the heat exchange area is large, and the waste of the heat exchange area is caused; most of the lower heat exchange tubes are liquid refrigerants, the proportion of the distributed refrigerants is large, the heat exchange area is small, the shortage of the heat exchange area is caused, the refrigerants are not completely evaporated, and finally the compressor is caused to absorb air and take liquid.
2. as shown in a part E in the attached drawing 1, the U-shaped bent part of the bend or the elbow is arranged in parallel, and the bend or the elbow has gradually increased bending radius and gradually increased semi-circumference in the direction from the center of the shell to the inner diameter of the shell, and the circumference increase proportion is pi times of the increased bending radius, so that the flow lengths of the heat exchange tubes with different bending radii are inconsistent, and the generated local resistance loss is inconsistent. Because the local resistance loss is five times of the on-way resistance loss, the phenomenon of uneven liquid supply distribution is aggravated by the inconsistency of the resistance loss in the heat exchange tube.
The above are inherent structural deficiencies that conventional dry shell and tube heat exchangers cannot overcome.
SUMMERY OF THE UTILITY MODEL
Utility model purpose: to the above problem, the utility model aims at providing a dry-type shell and tube heat exchanger improves the refrigerant and supplies liquid distribution, makes the refrigerant side supply liquid distribution more even.
The technical scheme is as follows: the utility model provides an improve dry-type shell and tube heat exchanger that refrigerant supplied liquid and distribute, which comprises a housin, a plurality of heat exchange tubes, the casing is provided with the refrigerant distributor box in refrigerant import one end, be provided with baffle A in the box of refrigerant distributor box, baffle B transversely separates in proper order inside and establishes to the static pressure chamber, the distribution chamber, the mixing chamber, install the gaseous state distributing pipe that all communicates static pressure chamber and distribution chamber on the baffle A, liquid distributing pipe, gaseous state distributing pipe is located the top of liquid distributing pipe, gaseous state distributing pipe, liquid distributing pipe has seted up a plurality of through-holes A respectively on being in the pipeline section in the distribution chamber, through-hole A, through-hole B forms the region with the height on vertical height, a plurality of through-holes C have been seted up on the baffle B, the refrigerant.
Furthermore, the box body of the refrigerant distribution box is composed of an outer end plate, a shell, a heat exchange tube connecting plate and a shell side partition plate, wherein the heat exchange tube connecting plate and the shell side partition plate are arranged in the shell, a refrigerant inlet is connected into the static pressure chamber from the outer end plate, and a heat exchange tube inlet is connected into the mixing chamber from the heat exchange tube connecting plate. Namely, the box body of the refrigerant distribution box can be manufactured independently, and can also be formed by utilizing part of the existing structure of the heat exchanger.
furthermore, the gaseous distribution pipe and the liquid distribution pipe are L-shaped pipes, the transverse pipes of the gaseous distribution pipe and the liquid distribution pipe are installed by penetrating through the partition plate A, the vertical pipes of the gaseous distribution pipe and the liquid distribution pipe are pipe sections in the distribution chamber, and the vertical pipes are correspondingly provided with a plurality of through holes A or through holes B.
furthermore, at least one gas distribution pipe and at least one liquid distribution pipe are arranged and distributed at intervals in the radial direction of the shell to form more uniform multiple transverse air flows and multiple transverse liquid flows.
Furthermore, a plurality of through holes A are formed in the gas distribution pipe, a plurality of through holes B are formed in the liquid distribution pipe, and a plurality of through holes C are formed in the partition board B at regular triangular intervals.
Furthermore, the hole shapes of the through hole A, the through hole B and the through hole C are respectively one of circular, triangular and square.
furthermore, the heat exchange tubes have at least three passes, the bending radius of the U-shaped elbow of the same heat exchange tube at each pass of the turn is matched, and the total length of the flow path of each heat exchange tube is equal to the resistance along the flow path.
Furthermore, the bending radius of the U-shaped elbow at the one-way turning part is the same as that of the U-shaped elbow at the two-way turning part of the same heat exchange tube.
Has the advantages that: compared with the prior art, the utility model has the advantages that: 1. the gas-liquid two-phase refrigerant is separated and remixed to form a uniform gas-liquid mixture as the refrigerant liquid supply, so that the gas-liquid two-phase refrigerant is uniformly distributed to enter each heat exchange tube; 2. by designing the heat exchange tube structure, the total length of the flow path of each heat exchange tube and the on-way resistance are basically equal to form an equal-resistance heat exchange tube bundle, and the internal resistance loss of each heat exchange tube is equal to ensure that the liquid supply of the refrigerant is uniformly distributed; 3. the liquid supply of the refrigerant in the heat exchanger is uniformly distributed, so that the side heat transfer efficiency of the refrigerant is improved, the copper material consumption of the heat exchanger is reduced, the weight of the heat exchanger is lightened, and the measured temperature at the outlet of the heat exchanger can more effectively reflect the real superheat degree of the heat exchanger.
Drawings
FIG. 1 is a schematic structural view of a conventional U-shaped dry shell-and-tube heat exchanger;
FIG. 2 is a right side view of FIG. 1;
FIG. 3 is a schematic view of the feed chamber of FIG. 1;
FIG. 4 is a schematic structural view of the heat exchanger of the present invention;
FIG. 5 is a schematic view of a refrigerant distribution box;
FIG. 6 is a cross-sectional view taken along line D-D of FIG. 5;
FIG. 7 is a schematic structural view of a separator B;
Fig. 8(a) is a heat exchange tube turn coupling layout view as viewed from the left side of fig. 4, and fig. 8(b) is a heat exchange tube turn coupling layout view as viewed from the right side of fig. 4.
Detailed Description
The invention will be further elucidated with reference to the drawings and specific embodiments, which are intended to illustrate the invention and are not intended to limit the scope of the invention.
A dry shell-and-tube heat exchanger for improving liquid supply distribution of a refrigerant is shown in figure 4 and comprises a shell 1, a plurality of heat exchange tubes 2, a refrigerant distribution box 3, a refrigerant inlet 4, a heat exchange tube connecting plate 5 and a shell side partition plate 6.
Referring to fig. 5, the refrigerant distribution box 3 is disposed at one end of the shell 1 connected to the refrigerant inlet 4, the box 31 of the refrigerant distribution box 3 can be made separately, or can be formed by using part of the existing structure of the heat exchanger, for example, the outer end plate 3101 is disposed to form with the shell 1, the heat exchange tube connecting plate 5 and the shell side partition plate 6 of the heat exchanger, and the refrigerant distribution box 3 further includes a partition plate a32, a partition plate B33, a gas distribution pipe 37 and a liquid distribution pipe 38.
The partition plate a32 and the partition plate B33 are provided in the case 31, and the interior of the case 31 is partitioned into the static pressure chamber 34, the distribution chamber 35, and the mixing chamber 36 in this order. The refrigerant inlet 4 is connected from the outer end plate 3101 to the static pressure chamber 34 and the heat exchange tube inlet is connected from the heat exchange tube connecting plate 5 to the mixing chamber 36.
gaseous state distributing pipe 37, liquid distributing pipe 38 are the L venturi tube, gaseous state distributing pipe 37 inverts and is located liquid distributing pipe 38's top, gaseous state distributing pipe 37, liquid distributing pipe 38 all wears to locate baffle A32 through the horizontal pipeline section of L venturi tube and installs, vertical pipeline section is in the distribution chamber 35, gaseous state distributing pipe 37's vertical pipeline section is downward, seted up a plurality of through-hole A39 on it, liquid distributing pipe 38's vertical pipeline section is upwards, seted up a plurality of through-hole B310 on it, then gaseous state distributing pipe 37, liquid distributing pipe 38 equally divide and have communicated static pressure chamber 34 and distribution chamber 35 respectively, through-hole A39, through-hole B310 that set up on the vertical pipeline section are in same section region on vertical height. As shown in fig. 6, at least one of the gaseous distribution pipe 37 and the liquid distribution pipe 38 is disposed and radially spaced in the housing 1, a plurality of through holes a39 on the gaseous distribution pipe 37 and a plurality of through holes B310 on the liquid distribution pipe 38 are disposed at regular triangle intervals, and the through holes a and B are respectively in one of a circular shape, a triangular shape and a square shape.
As shown in fig. 7, the partition B33 is provided with a plurality of through holes C311, which are arranged in regular triangle intervals, and the through holes C are in one of circular, triangular and square shapes.
The gas-liquid two-phase refrigerant enters the refrigerant distribution box from the refrigerant inlet, the gas and the liquid are completely separated in the static pressure chamber, the gaseous refrigerant is distributed at the upper part of the static pressure chamber, the liquid refrigerant is distributed at the lower part of the static pressure chamber, the gaseous refrigerant flows into the gaseous distribution pipe, a plurality of uniform transverse air flows distributed from the through holes A enter the distribution chamber, the liquid refrigerant flows into the liquid distribution pipe and is distributed into a plurality of uniform transverse liquid flows from the through holes B enter the distribution chamber, because the through holes A and B are in the same section of area in the vertical height, a plurality of transverse air flows and a plurality of transverse liquid flows are in a parallel mixed flow state in the same section of area in the height, then a more uniform gas-liquid uniform mixture is formed through the through holes C on the partition board B and enters the mixing chamber, then the refrigerant enters the inlet of the heat exchange tube, so that the gaseous refrigerant and the liquid refrigerant are uniformly distributed and enter each heat exchange tube.
The heat exchange tubes 2 have at least three passes, the U-shaped elbows of the same heat exchange tube 2 at the turning positions of each pass have different bending radiuses and are matched for use, so that the total length of the passes of each heat exchange tube 2 is equal or basically equal, the on-pass resistance of each heat exchange tube 2 is equal or basically equal, the internal resistance loss of each heat exchange tube is equal, and an equal-resistance heat exchange tube bundle is formed, so that the uniform liquid supply distribution of the refrigerant is ensured, and the side heat transfer efficiency of the refrigerant is improved.
The heat exchange tube comprises a straight tube section and a U-shaped elbow, and the specific design of the heat exchange tube is described by combining the attached drawings 4, 8(a) and 8(b), how to form an equal-resistance heat exchange tube bundle with the total flow length and the equal resistance along the flow path:
The total flow length L1 of the first heat exchange tube is equal to the length D11 of the first straight tube segment, the length pi × R11 of the first straight tube segment, the length D12 of the second straight tube segment, the length pi × R12 of the second U-shaped elbow segment, the length D13 of the third straight tube segment, the length pi × R13 of the third U-shaped elbow segment and the length D14 of the fourth straight tube segment, that is, L1 is equal to D11, pi × R11, D12, pi × R12, D13, pi × R13 and D14;
The total flow length L2 of the second heat exchange tube is equal to the length D21 of the first straight tube segment, the length pi × R21 of the first pass U-shaped elbow, the length D22 of the second straight tube segment, the length pi × R22 of the second pass U-shaped elbow, the length D23 of the third straight tube segment, the length pi × R23 of the third pass U-shaped elbow and the length D24 of the fourth straight tube segment, that is, L2 is equal to D21, pi × R21, D22, pi × R22, D23, pi × R23 and D24;
The third heat exchange tube, the fourth heat exchange tube and the like are analogized in sequence;
The total flow length L1 of the first heat exchange tube and the total flow length L2 of the second heat exchange tube are described, because D11 is D12-D13-D14-D21-D22-D23-D24, the U-shaped bend is designed to adopt cross rows for the connection of the straight tube sections, such as:
R11＝R23、R12＝R22、R13＝R21，
Or R11 ═ R23, R12 ═ R21, R13 ═ R22,
Or R11 ═ R21, R12 ═ R22, R13 ═ R23,
Or R11 ═ R21, R12 ═ R23, R13 ═ R22,
or R11 ═ R22, R12 ═ R21, R13 ═ R23,
Or R11 ═ R22, R12 ═ R23, R13 ═ R21, i.e. R11+ R12+ R13 ═ R21+ R22+ R23, so L1 ═ L2.
for the same heat exchange tube, the bending radius of the U-shaped elbow at the single-pass turning position is the same, and the bending radius of the U-shaped elbow at the double-pass turning position is the same.
Through the matching use of the U-shaped elbows with different bending radiuses, the straight pipe sections are connected in a cross arrangement mode, all the heat exchange pipes have the basically same U-shaped elbow bending radius, the basically same bending radius brings similar semi-circumference, and also brings similar local resistance loss, the similar local resistance loss brings similar internal resistance loss of the heat exchange pipes, and the phenomenon of aggravating uneven liquid supply distribution is avoided due to the similarity of the internal resistance loss of the heat exchange pipes.
Claims (8)
1. A dry shell and tube heat exchanger for improving liquid supply distribution of a refrigerant comprises a shell (1) and a plurality of heat exchange tubes (2), and is characterized in that: the shell (1) is provided with a refrigerant distribution box (3) at one end of a refrigerant inlet (4), a partition plate A (32) is arranged in a box body (31) of the refrigerant distribution box (3), the partition plate B (33) divides the interior into a static pressure chamber (34), a distribution chamber (35) and a mixing chamber (36) in sequence, a gaseous distribution pipe (37) and a liquid distribution pipe (38) which are communicated with the static pressure chamber (34) and the distribution chamber (35) are installed on the partition plate A (32), the gaseous distribution pipe (37) is positioned above the liquid distribution pipe (38), a plurality of through holes A (39) and a plurality of through holes B (310) are respectively arranged on pipe sections of the gaseous distribution pipe (37) and the liquid distribution pipe (38) in the distribution chamber (35), the through holes A (39) and the through holes B (310) form a same-height area on the vertical height, a plurality of through holes C (311) are arranged on the partition plate B (33), the, the inlet of the heat exchange tube is connected to a mixing chamber (36).
2. A dry shell and tube heat exchanger for improved refrigerant feed distribution as set forth in claim 1, wherein: a box body (31) of the refrigerant distribution box (3) is composed of an outer end plate (3101), a shell (1), a heat exchange tube connecting plate (5) in the shell (1) and a shell side partition plate (6), a refrigerant inlet (4) is connected into the static pressure chamber (34) from the outer end plate (3101), and a heat exchange tube inlet is connected into the mixing chamber (36) from the heat exchange tube connecting plate (5).
3. a dry shell and tube heat exchanger for improved refrigerant feed distribution as set forth in claim 1, wherein: the gas distribution pipe (37) and the liquid distribution pipe (38) are L-shaped pipes, the transverse pipes of the L-shaped pipes are installed through the partition plate A (32), the vertical pipes of the L-shaped pipes are pipe sections in the distribution chamber (35), and a plurality of through holes A (39) or through holes B (310) are correspondingly formed in the vertical pipes.
4. A dry shell and tube heat exchanger for improved refrigerant feed distribution as set forth in claim 1, wherein: at least one gas distribution pipe (37) and at least one liquid distribution pipe (38) are arranged and radially distributed at intervals in the shell (1).
5. A dry shell and tube heat exchanger for improved refrigerant feed distribution as set forth in claim 1, wherein: a plurality of through holes A (39) are arranged on the gas distribution pipe (37), a plurality of through holes B (310) are arranged on the liquid distribution pipe (38), and a plurality of through holes C (311) are arranged on the partition board B (33) at regular triangle intervals.
6. A dry shell and tube heat exchanger for improved refrigerant feed distribution as set forth in claim 1, wherein: the hole shapes of the through hole A (39), the through hole B (310) and the through hole C (311) are respectively one of circular, triangular and square.
7. A dry shell and tube heat exchanger for improved refrigerant feed distribution as set forth in claim 1, wherein: the heat exchange tubes (2) have at least three passes, the bending radius of the U-shaped elbow of the same heat exchange tube (2) at each pass of turning is matched, and the total length of the flow path of each heat exchange tube (2) is equal to the resistance along the flow path.
8. A dry shell and tube heat exchanger for improved refrigerant feed distribution according to claim 7 wherein: the same heat exchange tube (2) has the same bending radius of the U-shaped elbow at the single-pass turning position and the same bending radius of the U-shaped elbow at the double-pass turning position.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201920208162.2U CN209763847U (en) | 2019-02-18 | 2019-02-18 | Dry-type shell-and-tube heat exchanger for improving liquid supply distribution of refrigerant |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201920208162.2U CN209763847U (en) | 2019-02-18 | 2019-02-18 | Dry-type shell-and-tube heat exchanger for improving liquid supply distribution of refrigerant |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109813153A (en) * | 2019-02-18 | 2019-05-28 | 江苏科技大学 | A kind of dry pipe shell type heat exchanger improving refrigerant feed liquid distribution |
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2019
- 2019-02-18 CN CN201920208162.2U patent/CN209763847U/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109813153A (en) * | 2019-02-18 | 2019-05-28 | 江苏科技大学 | A kind of dry pipe shell type heat exchanger improving refrigerant feed liquid distribution |
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| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20191210 |
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| CF01 | Termination of patent right due to non-payment of annual fee |