CN115962589A - Heat exchanger and refrigerating system - Google Patents
Heat exchanger and refrigerating system Download PDFInfo
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- CN115962589A CN115962589A CN202310130775.XA CN202310130775A CN115962589A CN 115962589 A CN115962589 A CN 115962589A CN 202310130775 A CN202310130775 A CN 202310130775A CN 115962589 A CN115962589 A CN 115962589A
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- 238000005192 partition Methods 0.000 claims abstract description 50
- 238000013021 overheating Methods 0.000 claims abstract description 28
- 239000007788 liquid Substances 0.000 claims abstract description 21
- 230000005494 condensation Effects 0.000 claims abstract description 18
- 238000009833 condensation Methods 0.000 claims abstract description 18
- 238000005057 refrigeration Methods 0.000 claims abstract description 12
- 238000009434 installation Methods 0.000 claims description 13
- 238000000926 separation method Methods 0.000 claims description 2
- 238000001816 cooling Methods 0.000 abstract description 4
- 239000003507 refrigerant Substances 0.000 description 26
- 230000008901 benefit Effects 0.000 description 6
- 230000000694 effects Effects 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- 238000009423 ventilation Methods 0.000 description 3
- 239000002131 composite material Substances 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 2
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 description 1
- 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
- 238000010276 construction Methods 0.000 description 1
- 239000010949 copper Substances 0.000 description 1
- 229910052802 copper Inorganic materials 0.000 description 1
- 238000009792 diffusion process Methods 0.000 description 1
- 230000002349 favourable effect Effects 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
- 230000000149 penetrating effect Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 239000007787 solid Substances 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
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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 overheating removing component is positioned in the shell and comprises a partition wall, a baffle plate and a first heat exchange tube, the partition wall is configured to divide the inner space of the shell into an overheating removing cavity and a condensation cavity communicated with the overheating removing cavity through a vent hole in the partition wall, a gaseous working medium inlet is communicated with the overheating removing cavity, a liquid working medium outlet is communicated with the condensation cavity, the baffle plate is arranged in the overheating removing cavity and configured to form a baffling flow channel in the overheating removing cavity, the inlet end of the baffling flow channel is communicated with the gaseous working medium inlet, the condensation cavity is communicated with the outlet end of the baffling flow channel, the first heat exchange tube comprises an overheating removing tube section which is positioned in the overheating removing cavity and used for cooling the gaseous working medium in the overheating removing cavity, and at least part of the overheating removing tube section is positioned in the baffling 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 overheating cavity into a liquid working medium.
Description
Technical Field
The disclosure relates to the technical field of heat exchange equipment, in particular to a heat exchanger and a refrigerating system.
Background
At present, the heat exchangers most used in a refrigeration system 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.
In some refrigeration systems, for example, in the refrigeration system of a commercial water chiller, the high-temperature and high-pressure refrigerant gas discharged from the compressor is in a superheated state, and therefore the refrigerant at the inlet of the condenser of the refrigeration system is generally in a superheated state. Refrigerant gas in an overheated state firstly generates single-phase sensible heat exchange (desuperheating heat exchange) in a shell of the condenser, and refrigerant steam only releases heat but 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 to be converted into a liquid refrigerant in the saturation state. The heat exchange intensity of latent heat exchange is 10-20 times that of single-phase sensible heat exchange.
The heat exchange amount of the heat exchange of the superheat area under partial working conditions can reach up to 10% of the total heat exchange amount of the condenser, but the heat exchange strength of the single-phase sensible heat exchange is low, so that the superheat degree of a 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 energy efficiency and cost optimization of condensers, such as horizontal condensers used in commercial chiller units.
Disclosure of Invention
The purpose of the present disclosure is 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 desuperheating component is positioned in the shell and comprises a partition wall, a baffle plate and a first heat exchange tube, the partition wall is configured to divide the inner space of the shell into a desuperheating cavity and a condensing cavity communicated with the desuperheating cavity through a vent hole in the partition wall, the gaseous working medium inlet is communicated with the desuperheating cavity, the liquid working medium outlet is communicated with the condensing cavity, the baffle plate is arranged in the desuperheating cavity and is configured to form a baffling flow channel in the desuperheating cavity, the inlet end of the baffling flow channel is communicated with the gaseous working medium inlet, the condensing cavity is communicated with the outlet end of the baffling flow channel, the first heat exchange tube comprises a desuperheating tube section positioned in the desuperheating cavity and used for cooling the gaseous working medium in the desuperheating cavity, and at least part of the desuperheating tube section is positioned in the baffling 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) is such that:
delta P is the pressure drop generated by the gaseous working medium flowing 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 constant and takes 0.02-0.25.
l b Is the spacing between adjacent baffles (42) in m;
D k is the inner diameter of the shell (1) and has the unit of m;
rho is the density of the gaseous working medium at the gaseous working medium inlet (1A), kg/m 3 ；
u is the flow velocity calculated according to the flow cross section of the overheating area, and m/s;
epsilon is a constant, and the value is 0.1-0.5.
In some embodiments, the heat exchanger further comprises a heat removal chamber inlet, and the partition wall comprises a box body having the heat removal chamber and having a heat removal chamber inlet, and the heat exchanger comprises an air inlet pipe which passes through the gaseous working medium inlet and is connected with the heat removal chamber inlet.
In some embodiments, the desuperheating chamber extends in the axial direction of the first heat exchange tube, and the baffles are arranged at intervals in the desuperheating chamber in the axial direction of the first heat exchange tube.
In some embodiments, the inlet end of the baffling flow channel is located at the axial middle of the desuperheating chamber along the first heat exchange tube, and the outlet end of the baffling flow channel is located at the axial end of the desuperheating chamber along the first heat exchange tube.
In some embodiments, the heat exchanger includes two of the baffle flow passages arranged in an axial direction of the first heat exchange tube.
In some embodiments, the heat exchanger further comprises a baffle plate disposed at an angle to the axis of the desuperheating pipe section, the baffle plate having a through hole for the desuperheating pipe section to pass through.
In some embodiments, the partition wall includes two cover plates having pipe holes and arranged at intervals, and the first heat exchange pipe has both axial ends penetrating through the pipe holes of the two cover plates.
In some embodiments, the partition wall is configured to divide the desuperheating chamber into an installation chamber and a gas collecting chamber communicated with the installation chamber, the gaseous working medium inlet is communicated with the installation chamber, the baffle plate and the desuperheating pipe section are arranged in the installation chamber, an inlet end of the baffle channel is communicated with the gaseous working medium inlet, the gas collecting chamber is communicated with an outlet end of the baffle channel, and the vent hole in the partition wall is communicated with the gas collecting chamber and the condensation chamber.
In the heat exchanger of some embodiments of the present invention,
the mounting cavity is defined by the partition wall; or
The installation cavity is formed by the separation wall and the shell together; or
The gas collection cavity is surrounded by the partition wall; or
The gas collecting cavity is defined by the separating wall and the shell together.
In some embodiments, at least a portion of the wall portion of the partition wall is a double wall, the double wall includes an inner wall and an outer wall disposed outside the inner wall, the inner wall forms at least a portion of the wall of the installation cavity, the gas collecting cavity is surrounded by the inner wall and the outer wall or by the inner wall, the outer wall and the housing, and the plurality of vent holes are disposed on the outer wall.
In the heat exchanger of some embodiments, the plurality of vent holes are uniformly distributed on the partition wall.
In the heat exchanger of some embodiments, the plurality of ventilation holes are divided into a plurality of ventilation hole groups in which the diameters of the ventilation holes are sequentially reduced from a side away from the second heat exchange pipe to a side close to the second heat exchange pipe.
In some embodiments, the heat exchanger further comprises a support plate assembly through which the partition wall of the desuperheating assembly is connected to the inner wall of the housing.
In some embodiments, the heat exchanger further comprises a second heat exchange tube having a diameter smaller than or equal to a diameter of the first heat exchange tube.
In some embodiments of the heat exchanger, the first heat exchange tubes are finned tubes or bare tubes.
In some embodiments, the housing is cylindrical, the partition wall is a box body having the de-superheating chamber and extends in the axial direction of the housing, and the first heat exchange pipe and the second heat exchange pipe extend in the axial direction of the housing, wherein the ratio of the length of the box body to the length of the housing is 0.4-1.
In some embodiments, the heat exchanger further comprises a second heat exchange tube, wherein the ratio of the number of the first heat exchange tubes to the sum of the number of the first heat exchange tubes and the number of the second heat exchange tubes is 10 to 25%.
In the heat exchanger of some embodiments, the desuperheating component satisfies:
ε＝0.1-0.5；
wherein, T in The temperature of the gaseous working medium at the gaseous working medium inlet is K;
T out the unit is K, and the temperature of the gaseous working medium of the vent hole is K;
T wall the average temperature of the outer surface of the desuperheated pipe section is expressed in K;
d is the inner diameter of the 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 gaseous working medium inlet, and the unit is m/s;
l is the length of the overheating removing pipe section and is in the unit of m;
d is the outer diameter of the first heat exchange tube and has the unit of m;
d k the equivalent diameter of the tube distribution of the first heat exchange tube is m;
lambda is the heat conductivity coefficient of the gaseous working medium in the desuperheating cavity at the average temperature, W/(m × K);
C p the specific heat capacity of the gaseous working medium in the desuperheating cavity at the average temperature is kJ/(kg K);
mu is the viscosity of the gaseous working medium in the desuperheating cavity at the average temperature, pa s;
μ w the viscosity of the gaseous working medium in the de-superheating cavity is at the average temperature of the tube wall of the first heat exchange tube, and the unit is P a *s；
P t The tube spacing of the first heat exchange tube is m;
pr is the prandtl number.
A second aspect of the present disclosure provides a refrigeration system comprising a condenser, the condenser being the heat exchanger according to the first aspect of the present disclosure.
Based on this heat exchanger that the disclosure provided, through setting up to go the overheat chamber and set up the baffling board and form the baffling runner going to overheat intracavity, can be to the gaseous state working medium of overheated state, like gaseous state refrigerant, carry out continuous baffling and vortex, make full use of goes the heat transfer area who goes the overheat pipe section of overheat intracavity, strengthen gaseous state working medium and go the heat exchange efficiency who goes the overheat pipe section of the first heat exchange tube of overheat intracavity, thereby reach the effect that reduces the temperature of the gaseous state working medium of overheated state with less first heat exchange tube. The total number of baffles can be reasonably set according to the pressure drop delta P required to be controlled when the gaseous refrigerant flows through the de-superheating assembly.
Other features of the present disclosure and advantages thereof will become apparent from the following detailed description of exemplary embodiments thereof, which proceeds with reference to the accompanying drawings.
Drawings
The accompanying drawings, which are included to provide a further understanding of the disclosure and are incorporated in and constitute a part of this application, illustrate embodiment(s) of the disclosure and together with the description serve to explain the disclosure and not to limit the disclosure. In the drawings:
fig. 1 is a schematic structural diagram of a heat exchange assembly of a heat exchanger according to an embodiment of the present disclosure.
Fig. 2 is a schematic sectional structural view of a heat exchange assembly of the heat exchanger of the embodiment shown in fig. 1.
Fig. 3 is a structural schematic diagram of a combined structure of a desuperheating assembly and an air inlet pipe of the heat exchanger of the embodiment shown in fig. 1, which does not include the first heat exchange pipe.
Fig. 4 is an exploded view of the composite 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 structure of fig. 5.
Fig. 7 is a side view of the structure of fig. 5.
FIG. 8 is a schematic view of the baffles of the desuperheating assembly of the heat exchanger of FIG. 1.
FIG. 9 is a schematic view of the construction of the double-walled outer wall of the dividing wall of the desuperheating assembly of the heat exchanger of FIG. 1.
FIG. 10 is a schematic view of a portion of the outer wall shown in FIG. 9.
Detailed Description
The technical solutions in the embodiments of the present disclosure will be clearly and completely described below with reference to the drawings in the embodiments of the present disclosure, and it is obvious that the described embodiments are only a part of the embodiments of the present disclosure, and not all of the 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 derived by a person skilled in the art from the embodiments disclosed herein without making any creative effort, shall fall within the protection scope of the present disclosure.
The relative arrangement of the components and steps, the numerical expressions, and numerical values set forth in these embodiments do not limit the scope of the present disclosure unless specifically stated otherwise. Meanwhile, it should be understood that the sizes of the respective portions shown in the drawings are not drawn in an actual proportional relationship for the convenience of description. Techniques, methods, and apparatus known to those of ordinary skill in the relevant art may not be discussed in detail but are intended to be part of the specification where appropriate. In all examples shown and discussed herein, any particular value should be construed as merely illustrative, and not limiting. Thus, other examples of the exemplary embodiments may have different values. It should be noted that: like reference numbers and letters refer to like items in the following figures, and thus, once an item is defined in one figure, it need not be discussed further in subsequent figures.
In the description of the present disclosure, it should be understood that the terms "first", "second", etc. are used to define the components, and are used only for convenience of distinguishing the corresponding components, and if not otherwise stated, the terms have no special meaning, and thus, should not be construed as limiting the scope of the present disclosure.
In the description of the present disclosure, it is to be understood that the orientation or positional relationship indicated by the directional terms such as "front, rear, upper, lower, left, right", "lateral, vertical, horizontal" and "top, bottom", etc., are generally based on the orientation or positional relationship shown in the drawings, and are presented only for the convenience of describing and simplifying the disclosure, and in the absence of a contrary indication, these directional terms are not intended to indicate and imply that the device or element being referred to must have a particular orientation or be constructed and operated in a particular orientation, and therefore, should not be taken as limiting the scope of the disclosure; the terms "inner and outer" refer to the inner and outer relative to the profile 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 shell 1, a desuperheating member 4 and a second heat exchanging pipe 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, a baffle 42 and a first heat exchange tube 43. The partition wall 41 is configured to partition the internal space of the casing 1 into the desuperheating chamber 41C and the condensation chamber 1C communicating with the desuperheating chamber 41C through the vent hole 41B on the partition wall 41. The gaseous working medium inlet 1A is communicated with the de-superheating cavity 41C. The liquid working medium outlet 1B is communicated with the condensation cavity 1C. A baffle plate 42 is provided in the desuperheating chamber 41C, and is configured to form a baffled flow passage P in the desuperheating chamber 41C. The inlet end PA of the baffling flow passage 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 de-superheating section 431 located in the de-superheating chamber 41C for cooling the gaseous working medium in the de-superheating chamber 41C, and at least part of the de-superheating section 431 is located in the baffled flow passage P.
The second heat exchange tube 3 is located in the condensation chamber 1C and configured to condense the gaseous working medium entering the condensation chamber 1C from the overheating chamber 41C into a liquid working medium.
Wherein the number of baffles (42) is such that:
delta P is the pressure drop generated by the gaseous working medium flowing 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 constant and takes 0.02-0.25.
l b Is the spacing between adjacent baffles (42) in m;
D k is the inner diameter of the shell (1) and has the unit of m;
rho is the density of the gaseous working medium at the gaseous working medium inlet (1A), kg/m 3 ；
u is the flow velocity calculated according to the flow cross section of the overheating area, and m/s;
epsilon is a constant and takes a value of 0.1-0.5.
Through setting up to go hot chamber 41C and set up baffling board 42 in going hot chamber 41C and form baffling runner P, can be to the gaseous state working medium of overheated state, like the gaseous state refrigerant, carry out continuous baffling and vortex, make full use of goes the heat transfer area of going the super heat pipe section 431 in hot chamber 41C, strengthen the gaseous state working medium and go the heat exchange efficiency of the super heat pipe section 431 that goes of the first heat exchange tube 43 in the hot chamber 41C, thereby reach the effect that reduces the temperature of the gaseous state working medium of overheated state with less first heat exchange tube 43. The total number of baffles can be reasonably set according to the pressure drop delta P required to be controlled when the gaseous refrigerant flows through the de-superheating assembly. As the value of c increases, the pressure drop Δ P also increases.
The heat exchanger according to the embodiment 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, where the heat exchange assembly mainly includes a shell 1, an air inlet pipe 2, a second heat exchange pipe 3, an overheating removing assembly 4, a pipe plate 5, a support device 6, and a liquid outlet pipe 7. In addition, the heat exchanger further comprises a seal head (not shown) for forming a heat exchange medium chamber with the tube plate 5, an inlet and an outlet for the heat exchange medium chamber to enter and exit the heat exchange medium, 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, for example, water.
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 of the horizontal condenser is as shown in fig. 1, the overheating removing assembly 4 is located above the inside of the shell 1, and the second heat exchange tube 3 is located below the overheating removing 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 exchanging pipe 43 and the second heat exchanging pipe 3 are respectively protruded into the tube plates 5 located at both axial ends of the shell 1 so as to be located in the shell 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 having a desuperheating chamber inlet 41A, and the heat exchanger includes the intake pipe 2, and the intake pipe 2 is connected to the desuperheating chamber inlet 41A through the gaseous working medium inlet 1A. The gaseous working medium inlet 1A can be communicated with the overheating removing cavity 41C through the air inlet pipe 2 and the overheating removing cavity inlet 41A.
In some embodiments of the heat exchanger, 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 at intervals in the desuperheating chamber 41C in the axial direction of the first heat exchange tube 43. This setting does benefit to gaseous refrigerant's flow path longer to with remove abundant heat transfer between the superheater tube section 431, do benefit to the heat exchange efficiency who improves single-phase sensible heat transfer.
In the heat exchangers of some embodiments, as shown in fig. 1, 3 to 6, the inlet end PA of the baffled flow path 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 baffled flow path 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 channels P arranged in the axial direction of the first heat exchange tube 43.
In some embodiments, as shown in fig. 1, 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 for the desuperheating pipe section 431 to pass through. This setting does benefit to gaseous refrigerant and transversely flows through to remove superheated pipe section 431, improves gaseous refrigerant and removes the heat transfer intensity between superheated pipe section 431 to do benefit to and improve the holistic heat exchange efficiency of heat exchanger. In the embodiment shown in fig. 1-10, the baffle 42 is perpendicular to the axis of the desuperheated section 431.
In the heat exchanger of some embodiments, as shown in fig. 1 to 7, the partition wall 41 includes two cover plates 414 having pipe holes 414A arranged at intervals, and both axial ends of the first heat exchange pipe 503 pass through the pipe holes 414A of the two cover 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 the installation chamber C1 and the gas collecting chamber C2 communicating with the installation chamber C1. The gaseous working medium inlet 1A is communicated with the installation cavity C1. The baffle plate 42 and the de-superheating section 431 are arranged in the installation chamber C1. The inlet end PA of the baffling flow passage P is communicated with the gaseous working medium inlet 1A. The gas collecting cavity C2 is communicated with the outlet end PB of the baffling flow channel P. The vent hole 41B on the partition wall 41 communicates the gas collecting chamber C2 and the condensing chamber 3C.
In the heat exchanger of some embodiments, as shown in fig. 1 to 7, the installation chamber C1 is surrounded by the partition wall 41, and the gas collecting chamber C2 is surrounded by the partition wall 41. Also in the illustrated embodiment, the mounting chamber C1 may be defined by the partition wall 41 and the housing 1 together, and the gas collecting chamber C2 may be defined by the partition wall 41 and the housing 1 together.
In the heat exchanger of some embodiments, 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 outwardly of the inner wall 412. Inner wall 412 forms at least a portion of the wall of mounting cavity C1. The gas collecting chamber C2 is defined by an inner wall 412 and an outer wall 416, and the plurality of vent holes 41B are provided in the outer wall 416.
In the illustrated embodiment, the gas collecting chamber C2 may be enclosed by the inner wall 412, the outer wall 416 and the housing 1, with a plurality of vent holes 41B provided 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 vent 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 vent holes 41B are divided into a plurality of vent hole groups in which the diameters of the vent holes 41B are sequentially reduced from the side away from the second heat exchange tube 3 to the side close 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 connecting wall 415, and a closing plate 414. As previously described, the double wall includes an inner wall 412 and an outer wall 416 positioned outside of the inner wall 412.
The inner wall 412 includes a second wall 4121 spaced apart from the first wall 411 and third walls 4122 disposed at both sides of the second wall 4121. The first wall 411 is connected to the 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 that is arched toward the 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 that is large in top and small in bottom. Each baffle plate 42 is connected with the cylindrical main body, and a circulation hole is formed between the baffle plates and the cylindrical main body for gaseous working media to pass through.
The outer wall 416 includes a fourth wall 4161 attached to the second wall 4121 at a side away from the first wall 411 and two porous plates 4162 respectively disposed at two sides of the fourth wall 4161, wherein each porous plate 4162 is further provided with an edge plate 4163 at a side away from the fourth wall 4161, and the edge plate 4163 is connected to the first wall 411.
The end connecting wall 415 is a flat tube, both end connecting walls 415 are connected to both ends of the tubular main body in the axial direction of the casing 1 and connected to the first wall 411 and the outer layer wall 416, respectively, a cross-sectional shape of a wall surface of the flat tube connected to the first wall 411 perpendicular to the axis of the casing 1 is the same as a cross-sectional shape of the first wall 411 perpendicular to the axis of the casing 1, and a cross-sectional shape of a wall surface of the flat tube connected to the outer layer wall 416 perpendicular to the axis of the casing 1 is the same as a cross-sectional shape of the outer layer wall 416 perpendicular to the axis of the casing 1. The two sealing plates 414 are respectively connected to the sides of the flat cylinders far away from the cylindrical main body.
Thus, a mounting chamber C1 is formed in the cylindrical body, a gas collecting chamber C2 is formed by the third wall 4122 of the inner wall 412, the porous plate 4162 of the outer wall 4162 and the edge plate 4163 on each side of the cylindrical body, and the mounting chamber C1 and the gas collecting chamber C2 are communicated through the end connecting wall 415.
As shown in fig. 10, a plurality of vent holes 41B are uniformly distributed on each perforated plate 4162. In this embodiment, from the bottom to the top, every two rows of the vent holes 41B form a vent hole group, and the diameters of the vent holes 41B of the plurality of vent hole groups increase from the bottom to the top in sequence. The air holes 41B are sized to distribute the superheated vapor-liquid mixed refrigerant, and the refrigerant may flow into the condensation chamber 3C through the air holes 41B having different diameters, and the refrigerant in liquid form may flow out through the air holes 41B having smaller diameters at the bottom, and the refrigerant in gaseous form may gradually flow out through the air holes 41B that are sequentially enlarged at the top. The diameter of the vent hole 41B in which the aperture is the smallest is, for example, 2mm. The increment of the diameters of the two adjacent groups of the vent 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 through the support plate assembly 6.
In the heat exchangers 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 of the heat exchanger, the first heat exchange tubes 43 are finned tubes or bare tubes.
As shown in fig. 1 to 2, the casing 1 has a cylindrical shape, the partition wall 41 is a box having the superheat chamber 41C and extends in the axial direction of the casing 1, and the first heat exchanging pipe 43 and the second heat exchanging pipe 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 heat exchange space is reasonably divided between overheating heat exchange and condensation heat exchange, the first heat exchange tube 43 is favorably utilized to fully realize overheating of the gaseous working medium, and the gaseous refrigerant is favorably prevented from being excessively cooled in the overheating chamber 41C to form the liquid working medium.
In the heat exchangers of some embodiments, the ratio of the number of the first heat exchanging pipes 43 to the sum of the number of the first heat exchanging pipes 43 and the second heat exchanging pipes 3 is 10 to 25%. The proportion is reasonably set, so that the first heat exchange tube 43 is favorable for fully realizing the overheating of the gaseous working medium and preventing the gaseous refrigerant from being excessively cooled in the overheating cavity 41C to form the liquid working medium.
In the heat exchanger of some embodiments, the desuperheating component 4 satisfies:
ε＝0.1-0.5；
wherein, T in The temperature of the gaseous working medium at the gaseous working medium inlet 1A is K;
T out the temperature of the gaseous working medium of the vent hole 41B is K;
T wall is the average temperature of the outer surface of the desuperheated section 431 in units of K;
rho is the density of the gaseous working medium at the gaseous working medium inlet 1A, kg/m 3 ；
D is the inner diameter of the 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 desuperheating pipe section 431 of the first heat exchange pipe 43 in m;
n is the number of the first heat exchange tubes 43;
d is the outer diameter of the first heat exchange tube 43 in m;
d k is a first heat exchange tube43 equivalent diameter in m;
λ is the heat conductivity coefficient of the gaseous working medium in the desuperheating chamber 41C at the average temperature, W/(m × K);
C p the specific heat capacity of the gaseous working medium in the desuperheating cavity 41C at the average temperature is expressed in kJ/(kg K);
mu is the viscosity of the gaseous working medium in the desuperheating chamber 41C at the average temperature, P a *s；
μ w The viscosity of the gaseous working medium in the superheat removing cavity 41C at the average temperature of the tube wall of the first heat exchange tube 43 is expressed by P a *s；
P t The tube pitch of the first heat exchange tubes 43 (the pitch between the central axes of two adjacent first heat exchange tubes 43) in m;
D k is the inner diameter of the housing 1 in m;
l b is the spacing of adjacent baffles 42 in m;
u is the flow velocity, m/S, calculated as the flow cross section of the superheat zone (see shaded portion S in fig. 5);
pr is the Plantt number;
epsilon is a constant and takes a value of 0.1-0.5.
In the embodiment disclosed, reference is made to the mean temperature of the gaseous working medium in the desuperheating chamber 41C, generally denoted T in And T out Average value of (a).
The factors such as the outer diameter of a heat exchange pipe, the pipe spacing and the like which affect the heat exchange capacity of the heat exchanger are comprehensively controlled by adjusting the parameter epsilon, so that the inlet flow speed of the gaseous refrigerant is kept within a reasonable range, and the pressure drop generated by the gaseous refrigerant is the minimum when the heat exchanger obtains the heat exchange performance as high as possible. Wherein, as the parameter epsilon increases, the total heat exchange coefficient of the de-superheating area is smaller.
The embodiment of the disclosure also provides a refrigeration system, which includes 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 of the embodiments of the present disclosure have at least one of the following technical effects:
the heat exchanger is including going the overheated subassembly, goes the overheated subassembly and include partition wall, baffling board and first heat exchange tube, can be under the condition that does not increase auxiliary assembly and heat transfer area, through setting up baffling board in going the overheated intracavity to the gaseous state working medium of overheated state carry out continuous baffling and vortex, strengthen its and first heat exchange tube be located go the heat exchange efficiency who goes the overheated intracavity to the gaseous state working medium section to reach the effect that reduces overheated gaseous state working medium temperature. The desuperheating assembly can replace a conventional impingement plate in a heat exchanger.
In the heat exchanger of the embodiment of the disclosure, the gaseous working medium entering the shell of the heat exchanger from the gaseous working medium inlet is distributed to the two axial ends of the shell of the heat exchanger in a diffusion manner, so that the baffling heat exchange between the gaseous working medium and the heat removal pipe section is increased, the heat exchange area of the heat removal pipe section is fully utilized, and the gaseous working medium which is subjected to heat removal reaches the phase change transition temperature and then enters the condensation cavity through the vent hole in the partition wall to be further cooled into liquid by the second heat exchange pipe.
Finally, it should be noted that: the above examples are intended only to illustrate the technical solutions of the present disclosure and not to limit them; although the present disclosure has been described in detail with reference to preferred embodiments, those of ordinary skill in the art will understand that: modifications to the embodiments of the disclosure or equivalent replacements of parts of the technical features may be made, which are all covered by the technical solution claimed by the disclosure.
Claims (19)
1. A heat exchanger, comprising:
the device comprises a shell (1) and a gas working medium outlet (1A), wherein the shell is provided with a gas working medium inlet (1A) and a liquid working medium outlet (1B);
a desuperheating assembly (4) located within the housing (1) and including a partition wall (41), a baffle plate (42) and a first heat exchange tube (43), the partition wall (41) being configured to divide the interior space of the housing (1) into a desuperheating chamber (41C) and a condensing chamber (1C) communicating with the desuperheating chamber (41C) through a vent (41B) in the partition wall (41), the gaseous working medium inlet (1A) communicating with the desuperheating chamber (41C), the liquid working medium outlet (1B) communicating with the condensing chamber (1C), the baffle plate (42) being disposed within the desuperheating chamber (41C) and configured to form a baffle flow passage (P) within the desuperheating chamber (41C), an inlet end (PA) of the baffle flow passage (P) communicating with the gaseous working medium inlet (1A), the condensing chamber (1C) communicating with an outlet end (PB) of the baffle flow passage (P), the first heat exchange tube (43) including a section 431 located within the desuperheating chamber (41C) to cool the desuperheating chamber (41C), the section (431) being located within at least the desuperheating chamber (41C); and
the second heat exchange tube (3) is positioned in the condensation cavity (1C) and is configured to condense the gaseous working medium entering the condensation cavity (1C) from the desuperheating cavity (41C) into a liquid working medium; wherein the number of baffles (42) is such that:
delta P is the pressure drop generated by the gaseous working medium flowing 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 constant and takes 0.02-0.25.
l b Is the spacing between adjacent baffles (42) in m;
D k is the inner diameter of the shell (1) and has the unit of m;
rho is the density of the gaseous working medium at the gaseous working medium inlet (1A), kg/m 3 ；
u is the flow velocity calculated according to the flow cross section of the overheating area, and m/s;
epsilon is a constant, and the value is 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 with a desuperheating chamber inlet (41A), the heat exchanger comprising an inlet pipe (2), the inlet pipe (2) being connected with the desuperheating chamber inlet (41A) through the gaseous working medium inlet (1A).
3. A heat exchanger according to claim 1 wherein the de-superheating chamber (41C) extends in the axial direction of the first heat exchange tube (43), and a plurality of said baffles (42) are arranged in the de-superheating 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 baffled flow path (P) is located in the axial middle of the desuperheating chamber (41C) along the first heat exchange tube (43) and the outlet end (PB) of the baffled flow path (P) is located at the axial end of the desuperheating chamber (41C) along the first heat exchange tube (43).
5. The heat exchanger according to claim 4, characterized in that it comprises two of said baffled flow channels (P) arranged in the axial direction of the first heat exchange tube (43).
6. The heat exchanger according to claim 1, characterized in that the baffle (42) is arranged at an angle to the axis of the desuperheating pipe section (431), the baffle (42) having a through hole (42A) for the desuperheating pipe section (431) to pass through.
7. The heat exchanger according to claim 1, wherein the partition wall (41) includes two cover plates (414) having tube holes (414A) arranged at intervals, and the first heat exchange tube (43) has its axial both ends respectively passed through the tube holes (414A) of the two cover plates (414).
8. The heat exchanger according to claim 1, characterized in that the partition wall (41) is configured to divide the desuperheating chamber (41C) into a mounting chamber (C1) and a gas collecting chamber (C2) communicating with the mounting chamber (C1), the gaseous working medium inlet (1A) communicating with the mounting chamber (C1), the baffle plate (42) and the desuperheating section (431) being disposed in the mounting chamber (C1), the inlet end (PA) of the baffle flow channel (P) communicating with the gaseous working medium inlet (1A), the gas collecting chamber (C2) communicating with the outlet end (PB) of the baffle flow channel (P), the vent hole (41B) on the partition wall (41) communicating the gas collecting chamber (C2) with the condensing chamber (3C).
9. The heat exchanger of claim 8,
the mounting cavity (C1) is surrounded by the partition wall (41); or
The installation cavity (C1) is enclosed by the partition wall (41) and the shell (1) together; or
The gas collection chamber (C2) is surrounded by the separation wall (41); or
The gas collection chamber (C2) is enclosed by the partition wall (41) and the housing (1).
10. The heat exchanger according to claim 8, characterized in that at least part of the wall portion of the partition wall (41) is a double wall, the double wall comprising an inner wall (412) and an outer wall (416) arranged outside the inner wall (412), the inner wall (412) constituting at least part of the chamber wall of the installation chamber (C1), the gas collection chamber (C2) being enclosed by the inner wall (412) and the outer wall (416) or by the inner wall (412), the outer wall (416) and the housing (1), the plurality of vent holes (41B) being arranged in the outer wall (416).
11. The heat exchanger according to claim 8, wherein the plurality of vent holes (41B) are evenly distributed on the partition wall (41).
12. The heat exchanger according to claim 11, wherein the plurality of vent holes (41B) are divided into a plurality of vent hole groups in which diameters of the vent holes (41B) are sequentially reduced from a side away from the second heat exchange tube (3) to a side close 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), the partition wall (41) of the desuperheating assembly (4) being connected to an inner wall of the housing (1) by the support plate assembly (6).
14. Heat exchanger according to any 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 tubes (43) are finned tubes or bare tubes.
16. The heat exchanger according to any one of claims 1 to 12, wherein the shell (1) is cylindrical, the partition wall (41) is a box having the de-superheating chamber (41C) and extends in the axial direction of the shell (1), and the first heat exchange pipe (43) and the second heat exchange pipe (3) extend in the axial direction of the shell (1), wherein the ratio of the length of the box to the length of the shell (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 the first heat exchange tubes (43) to the sum of the number of the first heat exchange tubes (43) and the second heat exchange tubes (3) is 10-25%.
18. The heat exchanger, as set forth in any of claims 8 to 12, characterized in that the desuperheating assembly (4) satisfies:
ε＝0.1-0.5；
wherein, T in The temperature of the gaseous working medium at the gaseous working medium inlet (1A) is K;
T out the gaseous working medium temperature of the vent hole (41B) is K;
T wall is the average temperature of the outer surface of the de-superheating pipe section (431) in K;
d is the inner diameter of the air inlet pipe (2) connected with the gaseous working medium inlet (1A), and the unit is m;
v is the flow speed 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) in m;
d is the outer diameter of the first heat exchange tube (43) and has the unit of m;
d k the equivalent diameter of the first heat exchange tube (43) is m;
lambda is the heat conductivity coefficient of the gaseous working medium in the de-superheating cavity (41C) at the average temperature, W/(m & ltK);
cp is the specific heat capacity of the gaseous working medium in the overheating removing cavity (41C) at the average temperature, and the unit is kJ/(kg K);
mu is the viscosity of the gaseous working medium in the de-superheating cavity (41C) at the average temperature, pa s;
μ w the viscosity of the gaseous working medium in the overheating removing cavity (41C) at the average temperature of the tube wall of the first heat exchange tube (43) is expressed by P a *s；
P t Is the tube pitch of the first heat exchange tube (43) and has the unit of m;
pr is the prandtl 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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| CN202310130775.XA CN115962589B (en) | 2023-02-17 | 2023-02-17 | Heat exchanger and refrigeration system |
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| CN202310130775.XA CN115962589B (en) | 2023-02-17 | 2023-02-17 | Heat exchanger and refrigeration system |
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Citations (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102022870A (en) * | 2010-12-09 | 2011-04-20 | 海尔集团公司 | Method for improving supercooling degree of screw machine set and screw machine set adopting same |
| CN202041026U (en) * | 2010-11-29 | 2011-11-16 | 海尔集团公司 | Condenser and structure design device thereof |
| US20130219932A1 (en) * | 2010-08-19 | 2013-08-29 | Behr Gmbh & Co. Kg | Coolant condenser assembly |
| 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 |
| 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 |
| US20210396474A1 (en) * | 2018-10-15 | 2021-12-23 | Provides Metalmeccanica S.R.L. | Vertical heat exchanger |
| 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 |
| 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 |
-
2023
- 2023-02-17 CN CN202310130775.XA patent/CN115962589B/en active Active
Patent Citations (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20130219932A1 (en) * | 2010-08-19 | 2013-08-29 | Behr Gmbh & Co. Kg | Coolant condenser assembly |
| CN202041026U (en) * | 2010-11-29 | 2011-11-16 | 海尔集团公司 | Condenser and structure design device thereof |
| CN102022870A (en) * | 2010-12-09 | 2011-04-20 | 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 |
| US20210396474A1 (en) * | 2018-10-15 | 2021-12-23 | Provides Metalmeccanica 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 |
| 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 |
Non-Patent Citations (1)
| Title |
|---|
| 李德涛等: "[1]李德涛, 虞斌, 田文文, 等.基于正交试验的管壳式换热器折流板结构参数优化", 《化工机械》, no. 48, 30 June 2021 (2021-06-30) * |
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