CN115962589B - Heat exchanger and refrigeration system - Google Patents
Heat exchanger and refrigeration system Download PDFInfo
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- CN115962589B CN115962589B CN202310130775.XA CN202310130775A CN115962589B CN 115962589 B CN115962589 B CN 115962589B CN 202310130775 A CN202310130775 A CN 202310130775A CN 115962589 B CN115962589 B CN 115962589B
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- 238000000926 separation method Methods 0.000 claims abstract description 9
- 238000001816 cooling Methods 0.000 claims abstract description 7
- 238000005192 partition Methods 0.000 claims description 46
- 238000009423 ventilation Methods 0.000 claims description 16
- 238000004891 communication Methods 0.000 claims description 15
- 238000009434 installation Methods 0.000 claims description 9
- 238000007789 sealing Methods 0.000 claims description 8
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- 239000003507 refrigerant Substances 0.000 description 26
- 230000009286 beneficial effect Effects 0.000 description 4
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- 230000008859 change Effects 0.000 description 3
- 238000000034 method Methods 0.000 description 3
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- RTAQQCXQSZGOHL-UHFFFAOYSA-N Titanium Chemical compound [Ti] RTAQQCXQSZGOHL-UHFFFAOYSA-N 0.000 description 1
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 1
- 229910052782 aluminium Inorganic materials 0.000 description 1
- 239000002131 composite material Substances 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 239000010949 copper Substances 0.000 description 1
- 229910052802 copper Inorganic materials 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000014509 gene expression Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
- 238000000638 solvent extraction Methods 0.000 description 1
- 239000010936 titanium Substances 0.000 description 1
- 229910052719 titanium Inorganic materials 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
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Abstract
The present disclosure provides a heat exchanger and a refrigeration system. The heat exchanger includes: the shell is provided with a gaseous working medium inlet and a liquid working medium outlet; the device comprises a shell, a desuperheating component, a baffle plate and a first heat exchange tube, wherein the shell is internally provided with a separation wall, the separation wall is used for separating the internal space of the shell into a desuperheating cavity and a condensation cavity communicated with the desuperheating cavity through a vent hole on the separation wall, a gaseous working medium inlet is communicated with the desuperheating cavity, a liquid working medium outlet is communicated with the condensation cavity, the baffle plate is arranged in the desuperheating cavity and is used for forming a baffle flow channel in the desuperheating cavity, an inlet end of the baffle flow channel is communicated with the gaseous working medium inlet, the condensation cavity is communicated with an outlet end of the baffle flow channel, the first heat exchange tube comprises a desuperheating tube section positioned in the desuperheating cavity for cooling the gaseous working medium in the desuperheating cavity, and at least part of the desuperheating tube section is positioned in the baffle flow channel; and a second heat exchange tube positioned in the condensing cavity and configured to condense the gaseous working medium entering the condensing cavity from the desuperheating cavity into a liquid working medium.
Description
Technical Field
The present disclosure relates to the field of heat exchange devices, and in particular, to a heat exchanger and a refrigeration system.
Background
At present, the most used heat exchangers in refrigeration systems are shell-and-tube heat exchangers or plate heat exchangers manufactured by using materials such as copper, aluminum, titanium and the like and utilizing a solid heat conduction principle, and the main working principle is that refrigerant working media and secondary refrigerant working media are respectively positioned in different processes and exchange heat through convection and heat conduction modes of heat exchange tubes.
In some refrigeration systems, for example, in a refrigeration system of a commercial water-cooling unit, a high-temperature and high-pressure refrigerant gas discharged through a compressor is in an overheated state, and therefore, a refrigerant at a condenser inlet of the refrigeration system is also generally in an overheated state. The refrigerant gas in the overheat state firstly generates single-phase sensible heat exchange (desuperheating heat exchange) in the shell of the condenser, and the refrigerant steam only releases heat and does not generate phase change; the refrigerant gas is cooled from the overheat state to the saturation state, and then the refrigerant gas in the saturation state generates latent heat exchange and is converted into a liquid refrigerant in the saturation state. The heat exchange strength of the latent heat exchange is 10-20 times of that of the single-phase sensible heat exchange.
The heat exchange amount of the superheating heat exchange generally accounts for about 6% of the total heat exchange amount of the condenser, and the heat exchange amount of the superheating area heat exchange under partial working conditions can reach up to 10% of the total heat exchange amount of the condenser, but because the heat exchange intensity of single-phase sensible heat exchange is lower, the superheat degree of the refrigerant can be reduced by sacrificing a large amount of top heat exchange area of the condenser or using additional auxiliary cooling equipment in the heat exchanger. This prevents further increases in energy efficiency and cost optimization of condensers, such as the horizontal condensers used in commercial chiller units.
Disclosure of Invention
The invention aims to provide a heat exchanger and a refrigeration system, which aim to solve the problem that the heat exchange strength of single-phase sensible heat exchange of the heat exchanger is low.
A first aspect of the present disclosure provides a heat exchanger comprising:
The shell is provided with a gaseous working medium inlet and a liquid working medium outlet;
The device comprises a shell, a desuperheating component, a liquid working medium outlet and a first heat exchange tube, wherein the shell is internally provided with a partition wall, a baffle plate and a first heat exchange tube, the partition wall is used for partitioning the internal space of the shell into a desuperheating cavity and a condensation cavity communicated with the desuperheating cavity through a vent hole on the partition wall, a gaseous working medium inlet is communicated with the desuperheating cavity, the liquid working medium outlet is communicated with the condensation cavity, the baffle plate is arranged in the desuperheating cavity and is used for forming a baffle flow channel in the desuperheating cavity, the inlet end of the baffle flow channel is communicated with the gaseous working medium inlet, the condensation cavity is communicated with the outlet end of the baffle flow channel, the first heat exchange tube comprises a desuperheating tube section positioned in the desuperheating cavity for cooling the gaseous working medium in the desuperheating cavity, and at least part of the desuperheating tube section is positioned in the baffle flow channel; and
The second heat exchange tube is positioned in the condensation cavity and is configured to condense the gaseous working medium entering the condensation cavity from the desuperheating cavity into liquid working medium;
Wherein the number of baffles (42) satisfies:
Δp is the pressure drop generated by the flow of gaseous working fluid through the desuperheating assembly (4);
n is the number of the first heat exchange tubes (43);
n b is the total number of baffles (42);
c is a constant and takes a value of 0.02-0.25.
L b is the distance between adjacent baffles (42) in m;
d k is the inner diameter of the shell (1), and the unit is m;
ρ is the density of the gaseous working medium inlet (1A), kg/m 3;
u is the flow velocity calculated according to the flow section of the superheating area, m/s;
epsilon is a constant and takes a value of 0.1-0.5.
In some embodiments, the heat exchanger comprises an air inlet pipe, and the air inlet pipe penetrates through the gaseous working medium inlet and is connected with the desuperheating cavity inlet.
In some embodiments, the desuperheating chamber extends axially of the first heat exchange tube, and the plurality of baffles are spaced axially of the first heat exchange tube within the desuperheating chamber.
In some embodiments, the inlet end of the baffling flow channel is positioned at the axial middle part of the desuperheating cavity along the first heat exchange tube, and the outlet end of the baffling flow channel is positioned at the axial end part of the desuperheating cavity along the first heat exchange tube.
In some embodiments, the heat exchanger includes two of the baffling flow passages arranged along an axial direction of the first heat exchange tube.
In some embodiments, the baffle plate is disposed at an angle to the axis of the desuperheating pipe section, and the baffle plate is provided with a through hole for the desuperheating pipe section to pass through.
In some embodiments, the partition wall comprises two sealing plates with pipe holes arranged at intervals, and two axial ends of the first heat exchange pipe respectively pass through the pipe holes on the two sealing plates.
In some embodiments, the separation wall is configured to separate the desuperheating chamber into a mounting chamber and an air collection chamber in communication with the mounting chamber, the gaseous working medium inlet is in communication with the mounting chamber, the baffle and the desuperheating pipe section are disposed in the mounting chamber, the inlet end of the baffle flow channel is in communication with the gaseous working medium inlet, the air collection chamber is in communication with the outlet end of the baffle flow channel, and the vent hole on the separation wall is in communication with the air collection chamber and the condensing chamber.
In the heat exchanger of some embodiments,
The installation cavity is surrounded by the separation wall; or alternatively
The mounting cavity is defined by the partition wall and the shell; or alternatively
The gas collection cavity is surrounded by the separation wall; or alternatively
The gas collection cavity is jointly enclosed by the partition wall and the shell.
In some embodiments, at least part of the wall portion of the partition wall is a double-layer wall, the double-layer wall comprises an inner layer wall and an outer layer wall arranged outside the inner layer wall, the inner layer wall forms at least part of the cavity wall of the installation cavity, the gas collection cavity is surrounded by the inner layer wall and the outer layer wall or surrounded by the inner layer wall, the outer layer wall and the shell, and the plurality of vent holes are arranged on the outer layer wall.
In some embodiments, the plurality of ventilation holes are uniformly distributed on the partition wall.
In some embodiments, the plurality of ventilation holes are divided into a plurality of ventilation hole groups in which the diameters of the ventilation holes sequentially decrease from a side away from the second heat exchange tube to a side close to the second heat exchange tube.
In some embodiments, the heat exchanger further comprises a support plate assembly, the partition wall of the desuperheating assembly being connected to an inner wall of the housing by the support plate assembly.
In some embodiments, the diameter of the first heat exchange tube is less than or equal to the diameter of the second heat exchange tube.
In some embodiments, the first heat exchange tube is a fin tube or a light tube.
In some embodiments, the shell is cylindrical, the partition wall is a box body with the desuperheating cavity and extends along the axial direction of the shell, and the first heat exchange tube and the second heat exchange tube extend along the axial direction of the shell, wherein the ratio of the length of the box body to the length of the shell is 0.4-1.
In some embodiments, the ratio of the number of first heat exchange tubes to the sum of the number of first heat exchange tubes and the number of second heat exchange tubes is 10-25%.
In some embodiments of the heat exchanger, the desuperheating assembly satisfies:
ε＝0.1-0.5；
Wherein T in is the temperature of the gaseous working medium at the gaseous working medium inlet, and the unit is K;
T out is the temperature of the gaseous working medium of the vent hole, and the unit is K;
T wall is the average temperature of the outer surface of the desuperheated pipe section, and the unit is K;
D is the inner diameter of an air inlet pipe connected with the gaseous working medium inlet, and the unit is m;
v is the flow velocity of the gaseous working medium at the inlet of the gaseous working medium, and the unit is m/s;
l is the length of the desuperheated pipe section, and the unit is m;
d is the outer diameter of the first heat exchange tube, and the unit is m;
d k is the equivalent diameter of the first heat exchange tube, and the unit is m;
λ is the coefficient of thermal conductivity of the gaseous working medium in the desuperheating cavity at the average temperature, W/(m×k);
c p is the specific heat capacity of the gaseous working medium in the desuperheating cavity at the average temperature, and the unit is kJ/(kg. Times.K);
mu is the viscosity of the gaseous working medium in the desuperheating cavity at the average temperature, pa;
Mu w is the viscosity of the gaseous working medium in the desuperheating cavity at the average temperature of the pipe wall of the first heat exchange pipe, and the unit is P a s;
p t is the pipe spacing of the first heat exchange pipe, and the unit is m;
Pr is the Planet number.
A second aspect of the present disclosure provides a refrigeration system comprising a condenser, the condenser being a heat exchanger according to the first aspect of the present disclosure.
Based on the heat exchanger that this disclosure provided, through setting up to remove overheated chamber and set up the baffling board and form the baffling runner in removing overheated intracavity, can carry out continuous baffling and vortex to overheated state's gaseous working medium, like gaseous refrigerant, make full use of removes overheated pipe section's heat transfer area in the overheated intracavity, strengthen gaseous working medium and remove overheated pipe section's of overheated intracavity first heat exchange tube heat exchange efficiency to reach the effect of reducing overheated state's gaseous working medium's temperature with less first heat exchange tube. The total number of baffles can be reasonably set according to the pressure drop deltap required to be controlled by the gaseous refrigerant flowing through the desuperheating component.
Other features of the present disclosure and its advantages will become apparent from the following detailed description of exemplary embodiments of the disclosure, which proceeds with reference to the accompanying drawings.
Drawings
The accompanying drawings, which are included to provide a further understanding of the disclosure, illustrate and explain the present disclosure, and together with the description serve to explain the present disclosure. In the drawings:
Fig. 1 is a schematic structural view of a heat exchange assembly of a heat exchanger according to an embodiment of the present disclosure.
Fig. 2 is a schematic cross-sectional view of a heat exchange assembly of the heat exchanger of the embodiment of fig. 1.
Fig. 3 is a schematic structural view of a combined structure of a desuperheating assembly and an intake pipe of the heat exchanger of the embodiment of fig. 1 excluding a first heat exchange tube.
Fig. 4 is an exploded view of the combined structure shown in fig. 3.
FIG. 5 is a schematic view of the composite structure of FIG. 3 with the outer wall removed.
Fig. 6 is a schematic cross-sectional view of fig. 5.
Fig. 7 is a schematic side view of fig. 5.
Fig. 8 is a schematic view of the structure of baffles of the desuperheating assembly of the heat exchanger shown in fig. 1.
Fig. 9 is a schematic view of the outer wall construction of the double wall of the partition wall of the desuperheating assembly of the heat exchanger shown in fig. 1.
Fig. 10 is a schematic view of a partial structure of the outer wall shown in fig. 9.
Detailed Description
The following description of the technical solutions in the embodiments of the present disclosure will be made clearly and completely with reference to the accompanying drawings in the embodiments of the present disclosure, and it is apparent that the described embodiments are only some embodiments of the present disclosure, not all embodiments. The following description of at least one exemplary embodiment is merely illustrative in nature and is in no way intended to limit the disclosure, its application, or uses. All other embodiments, which can be made by one of ordinary skill in the art without inventive effort, based on the embodiments in this disclosure are intended to be within the scope of this disclosure.
The relative arrangement of the components and steps, numerical expressions and numerical values set forth in these embodiments do not limit the scope of the present disclosure unless it is specifically stated otherwise. Meanwhile, it should be understood that the sizes of the respective parts shown in the drawings are not drawn in actual scale for convenience of description. Techniques, methods, and apparatus known to one of ordinary skill in the relevant art may not be discussed in detail, but should be considered part of the specification where appropriate. In all examples shown and discussed herein, any specific values should be construed as merely illustrative, and not a limitation. Thus, other examples of the exemplary embodiments may have different values. It should be noted that: like reference numerals and letters denote like items in the following figures, and thus once an item is defined in one figure, no further discussion thereof is necessary in subsequent figures.
In the description of the present disclosure, it should be understood that the use of terms such as "first," "second," etc. for defining components is merely for convenience in distinguishing corresponding components, and the terms are not meant to be construed as limiting the scope of the present disclosure unless otherwise indicated.
In the description of the present disclosure, it should be understood that the azimuth or positional relationships indicated by the azimuth terms such as "front, rear, upper, lower, left, right", "lateral, vertical, horizontal", and "top, bottom", etc., are generally based on the azimuth or positional relationships shown in the drawings, merely to facilitate description of the present disclosure and to simplify the description, and these azimuth terms do not indicate and imply that the apparatus or elements referred to must have a specific azimuth or be configured and operated in a specific azimuth, and thus should not be construed as limiting the scope of protection of the present disclosure; the orientation word "inner and outer" refers to inner and outer relative to the contour of the respective component itself.
In order to solve the technical problem that the heat exchange strength of single-phase sensible heat exchange of a heat exchanger in the related art is low, the embodiment of the disclosure provides a heat exchanger and a refrigeration system with the heat exchanger. As shown in fig. 1 to 10, the heat exchanger includes a housing 1, a desuperheating assembly 4, and a second heat exchange tube 3.
The housing 1 has a gaseous working medium inlet 1A and a liquid working medium outlet 1B.
The desuperheating assembly 4 is located within the housing 1 and includes a partition wall 41, baffles 42 and a first heat exchange tube 43. The partition wall 41 is configured to partition the internal space of the casing 1 into a desuperheating chamber 41C and a condensing chamber 1C communicating with the desuperheating chamber 41C through a vent hole 41B on the partition wall 41. The gaseous working medium inlet 1A communicates with the desuperheating chamber 41C. The liquid working medium outlet 1B is communicated with the condensation cavity 1C. The baffle 42 is disposed in the desuperheating chamber 41C and is configured to form a baffle flow path P in the desuperheating chamber 41C. The inlet end PA of the baffling flow channel P is communicated with the gaseous working medium inlet 1A. The condensation chamber 1C communicates with the outlet end PB of the baffle flow path P. The first heat exchange tube 43 includes a desuperheating tube section 431 located within the desuperheating chamber 41C for cooling the gaseous working fluid within the desuperheating chamber 41C, at least a portion of the desuperheating tube section 431 being located within the baffle flow path P.
The second heat exchange tube 3 is located in the condensation chamber 1C and is configured to condense the gaseous working medium entering the condensation chamber 1C from the desuperheating chamber 41C into a liquid working medium.
Wherein the number of baffles (42) satisfies:
Δp is the pressure drop generated by the flow of gaseous working fluid through the desuperheating assembly (4);
n is the number of the first heat exchange tubes (43);
n b is the total number of baffles (42);
c is a constant and takes a value of 0.02-0.25.
L b is the distance between adjacent baffles (42) in m;
d k is the inner diameter of the shell (1), and the unit is m;
ρ is the density of the gaseous working medium inlet (1A), kg/m 3;
u is the flow velocity calculated according to the flow section of the superheating area, m/s;
epsilon is a constant and takes a value of 0.1-0.5.
By arranging the desuperheating cavity 41C and arranging the baffle plate 42 in the desuperheating cavity 41C to form the baffle flow channel P, the gaseous working medium in an overheated state, such as a gaseous refrigerant, can be continuously baffled and disturbed, the heat exchange area of the desuperheating pipe section 431 in the desuperheating cavity 41C is fully utilized, the heat exchange efficiency of the gaseous working medium and the desuperheating pipe section 431 of the first heat exchange pipe 43 in the desuperheating cavity 41C is enhanced, and the effect of reducing the temperature of the gaseous working medium in an overheated state by using fewer first heat exchange pipes 43 is achieved. The total number of baffles can be reasonably set according to the pressure drop deltap required to be controlled by the gaseous refrigerant flowing through the desuperheating component. As the value of c increases, the pressure drop Δp increases.
The heat exchanger of the embodiments of the present disclosure is further described below with reference to fig. 1 to 10. Fig. 1 shows a schematic structural diagram of a heat exchange assembly of a heat exchanger according to an embodiment of the present disclosure, the heat exchange assembly mainly including a housing 1, an air inlet pipe 2, a second heat exchange pipe 3, a desuperheating assembly 4, a tube sheet 5, a support device 6 and a liquid outlet pipe 7. In addition, the heat exchanger further includes a header (not shown) for forming a heat exchange medium chamber with the tube sheet 5, an inlet and an outlet for the heat exchange medium to enter and exit from the heat exchange medium chamber, and the like. In this embodiment, the gaseous working medium is a gaseous refrigerant (refrigerant), the liquid working medium is a liquid refrigerant, and the heat exchange medium is water, for example.
In the embodiment of the disclosure, the heat exchanger is a horizontal condenser, the shell 1 is cylindrical, after the horizontal condenser is installed in place, the heat exchange assembly is shown in fig. 1, the desuperheating assembly 4 is located above the inside of the shell 1, and the second heat exchange tube 3 is located below the desuperheating assembly 4. The first heat exchange tube 43 and the second heat exchange tube 3 each extend in the axial direction of the casing 1, so that the axial directions of the first heat exchange tube 43 and the second heat exchange tube 3 are in the same direction as the axial direction of the casing 1. Both ends of the first heat exchange tube 43 and the second heat exchange tube 3 extend into the tube sheets 5 at both axial ends of the casing 1, respectively, so as to be positioned in the casing 1.
In the heat exchanger of some embodiments, as shown in fig. 1 to 4 and 7, the partition wall 41 includes a box body having a desuperheating chamber 41C and has a desuperheating chamber inlet 41A, and the heat exchanger includes an intake pipe 2, and the intake pipe 2 is connected to the desuperheating chamber inlet 41A through the gaseous working medium inlet 1A. Communication between the gaseous working medium inlet 1A and the desuperheating chamber 41C can be achieved through the air inlet pipe 2 and the desuperheating chamber inlet 41A.
In the heat exchanger of some embodiments, as shown in fig. 1, 4 to 6, the desuperheating chamber 41C extends in the axial direction of the first heat exchange tube 43, and a plurality of baffles 42 are arranged in the desuperheating chamber 41C at intervals in the axial direction of the first heat exchange tube 43. The arrangement is beneficial to the longer flow path of the gaseous refrigerant, so that the heat exchange with the superheating pipe section 431 is sufficient, and the heat exchange efficiency of single-phase sensible heat exchange is improved.
In the heat exchanger of some embodiments, as shown in fig. 1,3 to 6, the inlet end PA of the baffle flow passage P is located at the axial middle of the desuperheating chamber 41C along the first heat exchange tube 43, and the outlet end PB of the baffle flow passage P is located at the axial end of the desuperheating chamber 41C along the first heat exchange tube 43.
In the heat exchanger of some embodiments, as shown in fig. 1, 3 to 6, the heat exchanger includes two baffle flow passages P arranged in the axial direction of the first heat exchange tube 43.
In some embodiments of the heat exchanger, as shown in fig. 1, the baffle 42 is disposed at an angle to the axis of the desuperheater pipe section 431, and the baffle 42 has a through hole 42A through which the desuperheater pipe section 431 passes. The arrangement is beneficial to the gaseous refrigerant to transversely flow through the desuperheating pipe section 431, and improves the heat exchange strength between the gaseous refrigerant and the desuperheating pipe section 431, thereby being beneficial to improving the overall heat exchange efficiency of the heat exchanger. In the embodiment shown in fig. 1-10, the baffles 42 are perpendicular to the axis of the desuperheated pipe section 431.
In some embodiments of the heat exchanger, as shown in fig. 1 to 7, the partition wall 41 includes two sealing plates 414 having tube holes 414A spaced apart, and the axial ends of the first heat exchange tubes 503 pass through the tube holes 414A in the two sealing plates 414.
In the heat exchanger of some embodiments, as shown in fig. 1, 2 and 4, the partition wall 41 is configured to partition the desuperheating chamber 41C into a mounting chamber C1 and a gas collection chamber C2 communicating with the mounting chamber C1. The gaseous working medium inlet 1A is communicated with the installation cavity C1. A baffle 42 and a desuperheated pipe section 431 are disposed within the mounting cavity C1. The inlet end PA of the baffling flow channel P is communicated with the gaseous working medium inlet 1A. The gas collection chamber C2 is communicated with the outlet end PB of the baffling flow channel P. The vent hole 41B in the partition wall 41 communicates the gas collection chamber C2 with the condensation chamber 3C.
In the heat exchanger of some embodiments, as shown in fig. 1 to 7, the installation cavity C1 is surrounded by the partition wall 41, and the gas collection cavity C2 is surrounded by the partition wall 41. Also in the illustrated embodiment, the installation cavity C1 may be defined by the partition wall 41 and the housing 1 together, and the gas collection cavity C2 may be defined by the partition wall 41 and the housing 1 together.
In some embodiments of the heat exchanger, as shown in fig. 2 and 4, at least part of the wall portion of the partition wall 41 is a double wall. The double wall includes an inner wall 412 and an outer wall 416 disposed outside the inner wall 412. The inner layer wall 412 constitutes at least part of the cavity wall of the installation cavity C1. The gas collection chamber C2 is surrounded by an inner wall 412 and an outer wall 416, and a plurality of ventilation holes 41B are provided in the outer wall 416.
In the illustrated embodiment, the gas collection chamber C2 may be defined by an inner wall 412, an outer wall 416, and the housing 1, with a plurality of vent holes 41B disposed in the outer wall.
In the heat exchanger of some embodiments, as shown in fig. 3 to 4 and 9 to 10, the plurality of ventilation holes 41B are uniformly distributed on the partition wall 41.
In the heat exchanger of some embodiments, as shown in fig. 10, the plurality of ventilation holes 41B are divided into a plurality of ventilation hole groups in which the diameters of the ventilation holes 41B sequentially decrease from the side away from the second heat exchange tube 3 to the side closer to the second heat exchange tube 3.
As shown in fig. 1 to 10, the partition wall 41 of the embodiment of the present disclosure includes a first wall 411, a double wall, an end connection wall 415, and a sealing plate 414. As previously described, the double wall includes an inner wall 412 and an outer wall 416 that is external to the inner wall 412.
The inner wall 412 includes a second wall 4121 spaced apart from the first wall 411 and third walls 4122 spaced apart from both sides of the second wall 4121. The first wall 411 is connected to two third walls 4122, respectively, and the first wall 411 and the second wall 412 are connected to form a cylindrical body. The cross section of the first wall 411 perpendicular to the axis of the housing 1 is an arc-shaped curve arched toward a side away from the second wall 412, and the cross section of the second wall 412 perpendicular to the axis of the housing 1 is a trapezoid with a large upper side and a small lower side. Each baffle 42 is connected to the cylindrical body and forms a flow aperture with the cylindrical body for the passage of gaseous working medium.
The outer layer wall 416 includes a fourth wall 4161 attached to a side of the second wall 4121 remote from the first wall 411 and two perforated plates 4162 provided separately on both sides of the fourth wall 4161, and an edge plate 4163 is further provided on a side of each perforated plate 4162 remote from the fourth wall 4161, the edge plate 4163 being connected to the first wall 411.
The end connection walls 415 are flat tubes, and the two end connection walls 415 are respectively connected to both ends of the tubular body in the axial direction of the housing 1 and connected to the first wall 411 and the outer layer wall 416, and the cross-sectional shape of the wall surface of the flat tube connected to the first wall 411, which is perpendicular to the axis of the housing 1, is the same as the cross-sectional shape of the first wall 411, which is perpendicular to the axis of the housing 1, and the cross-sectional shape of the wall surface of the flat tube connected to the outer layer wall 416, which is perpendicular to the axis of the housing 1, is the same as the cross-sectional shape of the outer layer wall 416, which is perpendicular to the axis of the housing 1. The two sealing plates 414 are respectively connected to one side of the flat cylinder far away from the cylindrical main body.
Thus, the cylindrical body forms a mounting cavity C1 therein, and the third wall 4122 of the inner layer wall 412, the perforated plate 4162 of the outer plate 4162, and the edge plate 4163 on each side of the cylindrical body form a gas collecting cavity C2, the mounting cavity C1 and the gas collecting cavity C2 communicating through the end connecting wall 415.
As shown in fig. 10, a plurality of ventilation holes 41B are uniformly distributed on each perforated plate 4162. In the present embodiment, from low to high, one vent group is formed for every two rows of the vent holes 41B, and the diameters of the vent holes 41B of the plurality of vent groups increase in order from bottom to top. The size of the vent hole 41B is set so as to distribute the superheated vapor-liquid mixed refrigerant, the refrigerant can flow into the condensation chamber 3C through the vent holes 41B with different apertures, the liquid refrigerant flows out through the vent holes 41B with smaller apertures at the bottom, and the gaseous refrigerant gradually flows out through the vent holes 41B which are sequentially enlarged. The diameter of the vent hole 41B in which the aperture is smallest is, for example, phi 2mm. The incremental change in the diameters of the adjacent two sets of ventilation holes 41B may be, for example, 2mm to 3mm.
In some embodiments of the heat exchanger, as shown in fig. 1, the heat exchanger further comprises a support plate assembly 6, and the partition wall 41 of the desuperheating assembly 4 is connected to the inner wall of the housing 1 by the support plate assembly 6.
In the heat exchanger of some embodiments, the diameter of the first heat exchange tube 43 is smaller than or equal to the diameter of the second heat exchange tube 3. For example, the first heat exchange tube 43 may be a heat exchange tube smaller than the second heat exchange tube 3 by one size, and the inner diameter of the first heat exchange tube 43 is, for example, 19.05mm to 22.23mm.
In some embodiments, the first heat exchange tube 43 is a fin tube or a light pipe.
As shown in fig. 1 to 2, the casing 1 is cylindrical, the partition wall 41 is a box body having a desuperheating chamber 41C and extends in the axial direction of the casing 1, and the first heat exchange tube 43 and the second heat exchange tube 3 extend in the axial direction of the casing 1. Wherein the ratio of the length of the box body to the length of the shell 1 is 0.4-1. The relative size of the box body and the shell 1 is reasonably set, so that the reasonable division of the heat exchange space between the overheat removing heat exchange and the condensation heat exchange is facilitated, the overheat removing of the gaseous working medium is fully realized by utilizing the first heat exchange tube 43, and the excessive cooling of the gaseous working medium in the overheat removing cavity 41C is prevented from forming a liquid working medium.
In the heat exchanger of some embodiments, the ratio of the number of the first heat exchange tubes 43 to the sum of the numbers of the first heat exchange tubes 43 and the second heat exchange tubes 3 is 10 to 25%. The reasonable setting of the ratio is beneficial to fully realizing the desuperheating of the gaseous working medium by using the first heat exchange tube 43 and preventing the gaseous working medium from being excessively cooled in the desuperheating cavity 41C to form a liquid working medium.
In some embodiments of the heat exchanger, the desuperheating assembly 4 satisfies:
ε＝0.1-0.5；
Wherein T in is the temperature of the gaseous working medium at the gaseous working medium inlet 1A, and the unit is K;
T out is the temperature of the gaseous working medium of the vent 41B, and the unit is K;
T wall is the average temperature of the outer surface of the desuperheated pipe section 431 in K;
ρ is the density of the gaseous working medium inlet 1A, kg/m 3;
d is the inner diameter of an air inlet pipe 2 connected with a gaseous working medium inlet 1A, and the unit is m;
v is the flow velocity of the gaseous working medium at the gaseous working medium inlet 1A, and the unit is m/s;
L is the length of the desuperheating pipe section 431 of the first heat exchange pipe 43, and the unit is m;
n is the number of first heat exchange tubes 43;
d is the outer diameter of the first heat exchange tube 43 in m;
d k is the equivalent diameter of the first heat exchange tube 43, and the unit is m;
λ is the thermal conductivity coefficient of the gaseous working medium in the desuperheating cavity 41C at the average temperature, W/(m×k);
C p is the specific heat capacity of the gaseous working medium in the desuperheating cavity 41C at the average temperature, and the unit is kJ/(kg. Times.K);
μ is the viscosity of the gaseous working medium in the desuperheating chamber 41C at average temperature, P a s;
Mu w is the viscosity of the gaseous working medium in the desuperheating chamber 41C at the average temperature of the tube wall of the first heat exchange tube 43, and the unit is P a s;
P t is the tube pitch of the first heat exchange tubes 43 (the pitch between the central axes of adjacent two first heat exchange tubes 43), in m;
D k is the inner diameter of the shell 1, and the unit is m;
l b is the spacing of adjacent baffles 42 in m;
u is the flow velocity calculated according to the flow section of the superheated zone (see the hatched portion S in fig. 5 for the flow section of the superheated zone), m/S;
Pr is the Plandter number;
epsilon is a constant and takes a value of 0.1-0.5.
In the disclosed embodiment, the average temperature of the gaseous working fluid in the desuperheating chamber 41C is referred to generally as the average of T in and T out.
The parameters epsilon are adjusted to comprehensively control factors such as the outer diameter of a heat exchange tube, the tube spacing and the like which influence the heat exchange capacity of the heat exchanger, so that the flow velocity of the inlet of the gaseous refrigerant is kept within a reasonable range, and the pressure drop generated by the gaseous refrigerant under the condition that the heat exchange capacity is as high as possible is obtained by the heat exchanger is minimum. Wherein, as the parameter epsilon increases, the total heat exchange coefficient of the superheating area is smaller.
The embodiment of the disclosure also provides a refrigeration system, which comprises a condenser, and is characterized in that the condenser is the heat exchanger of the embodiment of the disclosure. The refrigeration system of the embodiment of the disclosure has the advantages of the heat exchanger of the embodiment of the disclosure. As can be seen from the above description, the heat exchanger and the refrigeration system according to the embodiments of the present disclosure have at least one of the following technical effects:
the heat exchanger comprises a desuperheating component, the desuperheating component comprises a partition wall, a baffle plate and a first heat exchange tube, and the gaseous working medium in an overheated state can be continuously baffled and disturbed through the baffle plate arranged in the desuperheating cavity, so that the heat exchange efficiency of the desuperheating component and the desuperheating tube section of the first heat exchange tube in the desuperheating cavity is enhanced, and the effect of reducing the temperature of the overheated gaseous working medium is achieved. The desuperheating assembly can replace conventional impingement plates within a heat exchanger.
In the heat exchanger of the embodiment of the disclosure, gaseous working media entering the shell of the heat exchanger from the gaseous working media inlet are distributed in a diffusing way to the two axial ends of the shell of the heat exchanger, so that the baffling heat exchange of the gaseous working media and the heat removing pipe section is increased, the heat exchange area of the heat removing pipe section is fully utilized, and the gaseous working media after the heat removing reaches the phase change transition temperature enters the condensation cavity through the vent hole on the partition wall and is further cooled into liquid by the second heat exchange pipe.
Finally, it should be noted that: the above embodiments are merely for illustrating the technical solution of the present disclosure and are not limiting thereof; although the present disclosure has been described in detail with reference to preferred embodiments, those of ordinary skill in the art will appreciate that: modifications may be made to the specific embodiments of the disclosure or equivalents may be substituted for part of the technical features that are intended to be included within the scope of the claims of the disclosure.
Claims (19)
1. A heat exchanger, comprising:
the shell (1) is provided with a gaseous working medium inlet (1A) and a liquid working medium outlet (1B);
-a desuperheating assembly (4) located within the housing (1) and comprising a partition wall (41), a baffle (42) and a first heat exchange tube (43), the partition wall (41) being configured to partition an interior space of the housing (1) into a desuperheating chamber (41C) and a condensation chamber (1C) in communication with the desuperheating chamber (41C) through a vent hole (41B) in the partition wall (41), the gaseous medium inlet (1A) being in communication with the desuperheating chamber (41C), the liquid medium outlet (1B) being in communication with the condensation chamber (1C), the baffle (42) being arranged within the desuperheating chamber (41C) and being configured to form a baffle flow path (P) within the desuperheating chamber (41C), an inlet end (PA) of the flow path (P) being in communication with an outlet end (PB) of the baffle flow path (P), the first heat exchange tube (431) comprising at least one of the gaseous medium sections (431) located within the desuperheating chamber (41C) passing through the cooling section (41C); and
A second heat exchange tube (3) located in the condensation chamber (1C) and configured to condense the gaseous working medium entering the condensation chamber (1C) from the desuperheating chamber (41C) into a liquid working medium; wherein the number of baffles (42) satisfies:
Δp is the pressure drop generated by the flow of gaseous working fluid through the desuperheating assembly (4);
n is the number of the first heat exchange tubes (43);
n b is the total number of baffles (42);
c is a constant, and the value is 0.02-0.25;
l b is the distance between adjacent baffles (42) in m;
d k is the inner diameter of the shell (1), and the unit is m;
ρ is the density of the gaseous working medium inlet (1A), kg/m 3;
u is the flow velocity calculated according to the flow section of the superheating area, m/s;
epsilon is a constant and takes a value of 0.1-0.5.
2. The heat exchanger according to claim 1, characterized in that the partition wall (41) comprises a box with the desuperheating chamber (41C) and has a desuperheating chamber inlet (41A), the heat exchanger comprising an air inlet pipe (2), the air inlet pipe (2) being connected to the desuperheating chamber inlet (41A) through the gaseous medium inlet (1A).
3. The heat exchanger according to claim 1, wherein the desuperheating chamber (41C) extends in an axial direction of the first heat exchange tube (43), and a plurality of the baffles (42) are arranged in the desuperheating chamber (41C) at intervals in the axial direction of the first heat exchange tube (43).
4. A heat exchanger according to claim 3, wherein the inlet end (PA) of the baffle flow channel (P) is located in an axial middle of the desuperheating chamber (41C) along the first heat exchange tube (43), and the outlet end (PB) of the baffle flow channel (P) is located in an axial end of the desuperheating chamber (41C) along the first heat exchange tube (43).
5. A heat exchanger according to claim 4, characterized in that it comprises two said baffle channels (P) arranged in the axial direction of the first heat exchange tube (43).
6. The heat exchanger according to claim 1, wherein the baffle (42) is disposed at an angle to the axis of the desuperheating pipe section (431), and the baffle (42) has a through hole (42A) through which the desuperheating pipe section (431) passes.
7. A heat exchanger according to claim 1, wherein the partition wall (41) comprises two sealing plates (414) having tube holes (414A) arranged at intervals, and the axial ends of the first heat exchange tubes (43) respectively pass through the tube holes (414A) in the two sealing plates (414).
8. The heat exchanger according to claim 1, wherein the partition wall (41) is configured to partition the desuperheating chamber (41C) into a mounting chamber (C1) and a gas collecting chamber (C2) in communication with the mounting chamber (C1), the gaseous working medium inlet (1A) is in communication with the mounting chamber (C1), the baffle plate (42) and the desuperheating pipe section (431) are provided in the mounting chamber (C1), an inlet end (PA) of the baffle flow channel (P) is in communication with the gaseous working medium inlet (1A), the gas collecting chamber (C2) is in communication with an outlet end (PB) of the baffle flow channel (P), and the vent hole (41B) on the partition wall (41) is in communication with the gas collecting chamber (C2) and the condensing chamber (1C).
9. The heat exchanger of claim 8, wherein the heat exchanger is configured to heat the heat exchanger,
The installation cavity (C1) is surrounded by the partition wall (41); or alternatively
The installation cavity (C1) is jointly enclosed by the separation wall (41) and the shell (1); or alternatively
The gas collection cavity (C2) is surrounded by the separation wall (41); or alternatively
The gas collection chamber (C2) is defined by the partition wall (41) and the housing (1).
10. The heat exchanger according to claim 8, wherein at least part of the partition wall (41) is a double wall, the double wall includes an inner wall (412) and an outer wall (416) disposed outside the inner wall (412), the inner wall (412) constitutes at least part of the chamber wall of the installation chamber (C1), the gas collection chamber (C2) is surrounded by the inner wall (412) and the outer wall (416) or by the inner wall (412), the outer wall (416) and the housing (1), and the plurality of ventilation holes (41B) are disposed on the outer wall (416).
11. The heat exchanger according to claim 8, wherein a plurality of the ventilation holes (41B) are uniformly distributed on the partition wall (41).
12. A heat exchanger according to claim 11, wherein the plurality of ventilation holes (41B) are divided into a plurality of ventilation hole groups in which the diameters of the ventilation holes (41B) decrease in order from a side away from the second heat exchange tube (3) to a side closer to the second heat exchange tube (3).
13. The heat exchanger according to any one of claims 1 to 12, further comprising a support plate assembly (6), wherein the partition wall (41) of the desuperheating assembly (4) is connected to an inner wall of the housing (1) by means of the support plate assembly (6).
14. The heat exchanger according to any one of claims 1 to 12, wherein the diameter of the first heat exchange tube (43) is smaller than or equal to the diameter of the second heat exchange tube (3).
15. The heat exchanger according to any one of claims 1 to 12, wherein the first heat exchange tube (43) is a fin tube or a light tube.
16. The heat exchanger according to any one of claims 1 to 12, wherein the housing (1) is cylindrical, the partition wall (41) is a box having the desuperheating chamber (41C) and extends in an axial direction of the housing (1), and the first heat exchange tube (43) and the second heat exchange tube (3) extend in the axial direction of the housing (1), wherein a ratio of a length of the box to a length of the housing (1) is 0.4 to 1.
17. The heat exchanger according to any one of claims 1 to 12, wherein the ratio of the number of first heat exchange tubes (43) to the sum of the number of first heat exchange tubes (43) and the number of second heat exchange tubes (3) is 10-25%.
18. The heat exchanger according to any one of claims 8 to 12, wherein the desuperheating assembly (4) satisfies:
ε＝0.1-0.5；
wherein T in is the temperature of the gaseous working medium at the gaseous working medium inlet (1A) and the unit is K;
T out is the temperature of the gaseous working medium of the vent hole (41B), and the unit is K;
t wall is the average temperature of the outer surface of the desuperheated pipe section (431) and is expressed as K;
D is the inner diameter of an air inlet pipe (2) connected with the gaseous working medium inlet (1A), and the unit is m;
v is the flow velocity of the gaseous working medium at the gaseous working medium inlet (1A) and the unit is m/s;
l is the length of the desuperheated pipe section (431) and the unit is m;
d is the outer diameter of the first heat exchange tube (43) and the unit is m;
d k is the equivalent diameter of the first heat exchange tube (43) and the unit is m;
λ is the thermal conductivity coefficient of the gaseous working medium in the desuperheating cavity (41C) at the average temperature, W/(m×k);
cp is the specific heat capacity of the gaseous working medium in the desuperheating cavity (41C) at the average temperature, and the unit is kJ/(kg. Times.K);
mu is the viscosity of the gaseous working medium in the desuperheating cavity (41C) at the average temperature, pa;
Mu w is the viscosity of the gaseous working medium in the desuperheating cavity (41C) at the average temperature of the pipe wall of the first heat exchange pipe (43), and the unit is P a s;
P t is the pipe spacing of the first heat exchange pipe (43), and the unit is m;
Pr is the Planet number.
19. A refrigeration system comprising a condenser, wherein the condenser is a heat exchanger according to any one of claims 1 to 18.
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| DE102010039511A1 (en) * | 2010-08-19 | 2012-02-23 | Behr Gmbh & Co. Kg | Refrigerant condenser assembly |
| CN202041026U (en) * | 2010-11-29 | 2011-11-16 | 海尔集团公司 | Condenser and structure design device thereof |
| CN102022870B (en) * | 2010-12-09 | 2014-02-19 | 海尔集团公司 | Method for improving supercooling degree of screw machine set and screw machine set adopting same |
| CN103644686A (en) * | 2013-12-24 | 2014-03-19 | 上海环球制冷设备有限公司 | Efficient tube-fin-type condenser device and using method thereof |
| CN106440865A (en) * | 2016-09-28 | 2017-02-22 | 华中科技大学 | Shell-and-tube heat exchanger with rotating baffle plates |
| CN107062709A (en) * | 2017-05-22 | 2017-08-18 | 珠海格力电器股份有限公司 | Condenser and refrigerating system |
| EP3640575B1 (en) * | 2018-10-15 | 2022-12-07 | Wieland Provides S.r.l. | Vertical heat exchanger |
| CN210107818U (en) * | 2019-05-28 | 2020-02-21 | 苏州必信空调有限公司 | Shell and tube condenser and refrigerating system thereof |
| CN114459264A (en) * | 2020-11-10 | 2022-05-10 | 中国石油化工股份有限公司 | Shell-and-tube heat exchanger with grid supporting plate |
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| CN219301057U (en) * | 2023-02-17 | 2023-07-04 | 珠海格力电器股份有限公司 | Heat exchanger and refrigeration system |
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