CN114729794B - Heat exchange tube, heat exchanger and air conditioning system using heat exchanger - Google Patents
Heat exchange tube, heat exchanger and air conditioning system using heat exchanger Download PDFInfo
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- CN114729794B CN114729794B CN202080079586.9A CN202080079586A CN114729794B CN 114729794 B CN114729794 B CN 114729794B CN 202080079586 A CN202080079586 A CN 202080079586A CN 114729794 B CN114729794 B CN 114729794B
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- 238000004378 air conditioning Methods 0.000 title claims abstract description 15
- 238000000034 method Methods 0.000 claims description 10
- 239000012530 fluid Substances 0.000 claims description 7
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 abstract description 179
- 230000000052 comparative effect Effects 0.000 description 66
- 239000003507 refrigerant Substances 0.000 description 30
- 238000013461 design Methods 0.000 description 15
- 230000000694 effects Effects 0.000 description 15
- 230000001965 increasing effect Effects 0.000 description 13
- 239000007788 liquid Substances 0.000 description 6
- 238000005192 partition Methods 0.000 description 5
- 238000002474 experimental method Methods 0.000 description 4
- 239000002826 coolant Substances 0.000 description 3
- 230000007423 decrease Effects 0.000 description 3
- 238000012546 transfer Methods 0.000 description 3
- 230000009286 beneficial effect Effects 0.000 description 2
- 238000004891 communication Methods 0.000 description 2
- 238000012938 design process Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000002708 enhancing effect Effects 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2500/00—Problems to be solved
- F25B2500/09—Improving heat transfers
Abstract
The application discloses a heat exchange tube, which comprises a tube body, wherein the tube body is provided with an inner wall and an axis, and two ends of the tube body are provided with an inlet and an outlet; the heat exchange tube further includes a plurality of screw threads disposed on the inner wall of the tube body at a spaced apart relationship from each other, the plurality of screw threads extending helically about an axis of the tube body from the inlet of the tube body to the outlet of the tube body. By the helix angle alpha, the number of teeth N, the tooth height h and the tooth top width W of the screw teeth of the heat exchange tube t Width of tooth bottom W b Some of these parameters are set in a certain range, and a heat exchange tube with optimized water pressure drop or heat exchange efficiency can be obtained under the condition that the weight of the heat exchange tube in unit length is kept in a certain range. The application also discloses a heat exchanger comprising the heat exchange tubes and an air conditioning system using the heat exchanger.
Description
Technical Field
The application relates to the field of air conditioning systems, in particular to a heat exchange tube, a heat exchanger and an air conditioning system using the heat exchanger.
Background
Heat exchangers are widely used as condensers and evaporators in air conditioning systems. In an air conditioning system, a heat exchanger is capable of exchanging heat between a refrigerant and water to thereby release heat from the refrigerant and condense the refrigerant, or to thereby absorb heat from the refrigerant and evaporate the refrigerant. The heat exchanger comprises a heat exchange tube, when the refrigerant flows through the heat exchanger, the refrigerant flows through the heat exchange tube, water flows through the heat exchange tube, and the refrigerant is condensed or evaporated through heat exchange between the tube wall of the heat exchange tube and the water in the heat exchange tube.
Disclosure of Invention
According to a first aspect of the present application, the present application provides a heat exchange tube comprising: the pipe body is provided with an inner wall and an axis, and two ends of the pipe body are provided with an inlet and an outlet; a plurality of thread teeth disposed on the inner wall of the pipe body in spaced apart relation to each other, the plurality of thread teeth extending helically around an axis of the pipe body from the inlet of the pipe body to the outlet of the pipe body; wherein the helix angle alpha of the thread teeth and the number N of the thread teeth satisfy the following conditions: (i) the helix angle alpha is 20-33 degrees and the number of teeth N is 39-65; or (ii) the helix angle alpha is 30-43 DEG and the number of teeth N is 45-70.
According to the first aspect described above, the helix angle α of the thread teeth and the number of teeth N of the thread teeth satisfy (i), and the pipe diameter D of the pipe body is 19.05±1mm.
According to the first aspect, the cross-sectional shape of the thread tooth is trapezoidal; wherein the tooth bottom width W of the trapezoid thread tooth b The method meets the following conditions:
and X is 1 Is any constant of 0.195-0.619; and/or the tooth height h of the trapezoidal thread teeth satisfies:
and X is 2 Is any constant of 0.176 to 0.521; and/or the tip width W of the trapezoidal thread teeth t The method meets the following conditions:
and X is 3 Is an arbitrary constant of 0.021-0.206.
According to the first aspect, the number N of the thread teeth is 53, and the helix angle α of the thread teeth is 30 °; the cross section of the thread teeth is trapezoidal, and the tooth bottom width W of the trapezoidal thread teeth b The tooth height h of the trapezoid thread tooth is 0.401mm and the tooth top width W of the trapezoid thread tooth is 0.313mm t Is 0.068mm.
According to the first aspect described above, the helix angle α of the thread teeth and the number of teeth N of the thread teeth satisfy (ii), and the pipe diameter D of the pipe body is 25.4±1mm.
According to the first aspect, the cross-sectional shape of the thread tooth is trapezoidal; wherein the tooth bottom width W of the trapezoid thread tooth b The method meets the following conditions:
and X is 1 Is any constant of 0.141 to 0.500; and/or the tooth height h of the trapezoidal thread teeth satisfies:
and X is 2 Is any constant from 0.169 to 0.570; and/or the teeth of the thread teeth being trapezoidalTop width W t The method meets the following conditions:
and X is 3 Is an arbitrary constant of 0.018 to 0.201.
According to the first aspect, the number N of the thread teeth is 68, and the helix angle α of the thread teeth is 30 °; the cross section of the thread teeth is trapezoidal, and the tooth bottom width W of the trapezoidal thread teeth b 0.454mm, a tooth height h of the trapezoidal thread teeth of 0.488mm, and a tooth top width W of the trapezoidal thread teeth t Is 0.114mm.
It is an object of the present application in a second aspect to provide another heat exchange tube comprising: the pipe body is provided with an inner wall and an axis, and two ends of the pipe body are provided with an inlet and an outlet; a plurality of thread teeth disposed on the inner wall of the pipe body in spaced apart relation to each other, the plurality of thread teeth extending helically around an axis of the pipe body from the inlet of the pipe body to the outlet of the pipe body; wherein the cross section of the thread teeth is trapezoidal, the number N of the thread teeth and the width W of the tooth bottom of the thread teeth are trapezoidal b The method meets the following conditions: (i) The number of teeth N is 46-65, and the width of the tooth bottom W b 0.321-0.521 mm; or (ii) the number of teeth N is 39 to 45, and the tooth bottom width W b 0.523-0.545 mm; or (iii) the number of teeth N is 59 to 70, and the tooth bottom width W b 0.451 to 0.627mm; or (iv) the number of teeth N is 45-58, and the tooth bottom width W b 0.628 to 0.707mm.
According to the second aspect, the thread tooth has a tooth bottom width W b And the number of teeth N of the thread teeth satisfies (i) or (ii), and the pipe diameter D of the pipe body is 19.05+ -1 mm.
According to the second aspect, the thread tooth has a tooth bottom width W b And the number of teeth N of the thread teeth satisfies (i); the tooth height h of the trapezoid thread teeth is 0.235-0.553 mm; and/or the tip width W of the trapezoidal thread teeth t 0.047-0.181 mm; and/or the helix angle alpha of the thread teeth is 30～55°。
According to the second aspect, the thread tooth has a tooth bottom width W b And the number of teeth N of the thread teeth satisfies (ii); the tooth height h of the trapezoid thread teeth is 0.355-0.523 mm; and/or the tip width W of the trapezoidal thread teeth t 0.101-0.198 mm; and/or the helix angle alpha of the thread teeth is 30-55 deg..
According to the second aspect, the thread tooth has a tooth bottom width W b And the number of teeth N of the thread teeth satisfies (iii) or (iv), and the pipe diameter D of the pipe body is 25.4+ -1 mm.
According to the second aspect, the thread tooth has a tooth bottom width W b And the number of teeth N of the thread teeth satisfies (iii); the tooth height h of the trapezoid thread teeth is 0.301-0.624 mm; and/or the tip width W of the trapezoidal thread teeth t 0.073-0.246 mm; and/or the helix angle alpha of the thread teeth is 30-55 deg..
According to the second aspect, the thread tooth has a tooth bottom width W b And the number of teeth N of the thread teeth satisfies (iv); the tooth height h of the trapezoid thread teeth is 0.447-0.634 mm; and/or the tip width W of the trapezoidal thread teeth t 0.097-0.269 mm; and/or the helix angle alpha of the thread teeth is 30-55 deg..
An object of the present application in a third aspect is to provide a heat exchanger comprising: a heat exchange tube according to any one of the first or second aspects above.
An object of the present application in a fourth aspect is to provide an air conditioning system, including: the compressor, the condenser, the throttling device and the evaporator are sequentially and fluidly connected; wherein at least one of the condenser and the evaporator employs the heat exchanger of the third aspect described above.
The application leads the helix angle alpha, the tooth number N, the tooth height h and the tooth top width W of the thread teeth of the heat exchange tube t Width of tooth bottom W b Some of these parameters are set in a certain range, and can obtain heat exchange tube with optimized water pressure drop or optimized heat exchange efficiency under the condition of maintaining the weight of heat exchange tube in a certain rangeA tube.
Drawings
FIG. 1 is a schematic block diagram of an air conditioning system of the present application;
FIG. 2A is a perspective view of the condenser of FIG. 1;
FIG. 2B is a cross-sectional view of the condenser of FIG. 2A taken along the axial direction of the cylinder;
FIG. 3A is a perspective view of a heat exchange tube according to the present application;
FIG. 3B is a radial cross-sectional view of the heat exchange tube of FIG. 3A;
FIG. 4 is an enlarged view of a portion of FIG. 3B;
FIG. 5 is a cross-sectional view of the heat exchange tube of FIG. 3A along its axial direction;
FIG. 6 is a graph showing the relationship between the flow rate of water in the heat exchange tube and the difference between the pressure drop and the water inlet and outlet temperatures of the heat exchange tube in FIG. 3A;
fig. 7A is a graph showing the effect of the number of the heat exchange tubes 1 on the water pressure drop of the heat exchanger and the small heat exchange temperature difference of the heat exchanger;
fig. 7B is a graph showing the effect of the number of low water pressure drop heat exchange tubes 1 on the water pressure drop of the heat exchanger and the small heat exchange temperature difference of the heat exchanger;
fig. 8 is a graph showing the effect of the number of heat exchange tubes 1 and the number of heat exchange tubes 1 with high heat exchange efficiency on the water pressure drop of the heat exchanger and the small heat exchange temperature difference of the heat exchanger.
Detailed Description
Various embodiments of the present application are described below with reference to the accompanying drawings, which form a part hereof. It is to be understood that, although directional terms, such as "front", "rear", "upper", "lower", "left", "right", etc., may be used in this application to describe various example structural portions and elements of the present application, these terms are used herein for convenience of description only and are determined based on the example orientations shown in the drawings. Because the embodiments disclosed herein may be arranged in a number of different orientations, the directional terminology is used for purposes of illustration and is in no way limiting.
Fig. 1 is a schematic block diagram of an air conditioning system of the present application for illustrating the location and function of a heat exchanger in the air conditioning system. As shown in fig. 1, the air conditioning system 150 includes a compressor 110, a condenser 120, a throttle device 130, and an evaporator 140, which are connected by pipes to form a closed system, and the system is filled with a refrigerant. Wherein the refrigerant sequentially flows through the compressor 110, the condenser 120, the throttling device 130, and the evaporator 140, so that the air conditioning system 150 can externally cool or heat. Specifically, the high-pressure gas refrigerant discharged from the compressor 110 flows into the condenser 120, releases heat in the condenser 120, is condensed into a high-pressure liquid refrigerant, flows into the throttle device 130, is processed into a low-pressure liquid refrigerant by the throttle device 130, flows into the evaporator 140, absorbs heat in the evaporator 140, is evaporated into a low-pressure gas refrigerant, and finally flows into the compressor 110 again, thereby completing the refrigerant cycle.
As an example, the condenser 120 and the evaporator 140 are both water-cooled heat exchangers, and the refrigerant flowing therethrough can exchange heat with external water, which absorbs heat to become hot when the refrigerant releases heat in the condenser 120; when the refrigerant absorbs heat in the evaporator 140, external water releases heat to cool. Of course, in other embodiments, the cooling medium may be other types of cooling medium, such as air, instead of water.
Fig. 2A and 2B are schematic structural views of the condenser 120 of fig. 1, for illustrating the general positions of the heat exchange tubes 200 in the condenser 120. Fig. 2A is a perspective view of the condenser 120, illustrating a refrigerant outlet and inlet and a water outlet and inlet of the case 225, and fig. 2B is a sectional view of the condenser 120 along an axial direction of the cylinder 221, illustrating an internal structure of the condenser 120.
As shown in fig. 2A, the condenser 120 includes a housing 225, and the housing 225 includes a cylindrical body 221 in the middle, left and right end portions 227 (see fig. 2B) and 228, and left and right partition plates 237 and 238. Wherein, the top of the cylinder 221 is provided with a gas refrigerant inlet 231, and the bottom of the cylinder 221 is provided with a liquid refrigerant outlet 232. A water inlet 222 and a water outlet 224 are provided on the right end 228 of the housing 225.
As shown in fig. 2B, the condenser 120 has a left chamber 236, a middle chamber 235, and a right chamber 234 inside. Wherein, a left containing cavity 236 is formed between the left end 227 of the shell and the left partition plate 237, a middle containing cavity 235 is formed between the left partition plate 237 and the right partition plate 238, and a right containing cavity 234 is formed between the right partition plate 238 and the right end 228 of the shell. Wherein the gas refrigerant inlet 231 and the liquid refrigerant outlet 232 are in communication with the intermediate chamber 235. The medium chamber 235 also comprises two heat exchange tubes 200 which are transversely arranged, and each heat exchange tube comprises a plurality of heat exchange tubes 200. Both ends of each heat exchange tube 200 are respectively communicated with the left and right receiving chambers 236 and 234. Wherein the right chamber 234 is also in communication with the water inlet 222 and the water outlet 224.
In fig. 2B, the dotted arrow shows the flow direction of the refrigerant in the condenser 120, and after the gas refrigerant flows into the medium chamber 235 from the gas refrigerant inlet 231, flows from top to bottom, is condensed into the liquid refrigerant by heat exchange with the water in the heat exchange tube 200, and finally flows out from the liquid refrigerant outlet 232.
The solid arrows show the direction of water flow in the condenser 120, and after water flows into the right chamber 234 from the water inlet 222, it enters the lower heat exchange tube 200, flows from right to left, exchanges heat with the refrigerant outside the heat exchange tube 200, then flows out of the lower heat exchange tube into the left chamber 236, the water in the left chamber 236 flows into the upper heat exchange tube 200, flows from left to right, still exchanges heat with the refrigerant outside the heat exchange tube 200, flows out of the upper heat exchange tube 200 into the right chamber 234, and finally flows out of the water outlet 224.
A specific structure of the heat exchange tube 200 is shown in fig. 3A and 3B, wherein fig. 3A shows a perspective structural view of the heat exchange tube 200 for explaining a general structure of the heat exchange tube; fig. 3B shows a radial cross-sectional view of the heat exchange tube for illustrating the tooth structure on the inner wall of the heat exchange tube 200.
As shown in fig. 3A and 3B, the heat exchange tube 200 includes a tube body 301, a first end 303, and a second end 304, wherein the tube body 301 has an axis x, and the first end 303 and the second end 304 are disposed at both ends of the tube body 301 in the direction of the axis x, respectively. As an example, water (cooling medium) flows into the tube 301 from the first end 303 and out from the second end 304 such that the first end 303 acts as an inlet for water and the second end 304 acts as an outlet for water. Of course, water may also flow in from the second end 304 and out from the first end 303.
The tube 301 has an inner wall 302 and the heat exchange tube 200 further includes a plurality of screw threads 316 disposed on the inner wall 302 in spaced relation, the screw threads 316 extending helically around the axis x of the tube 301, and in some embodiments, the screw threads 316 extending helically from the tube first end 303 to the tube second end 304 (see FIG. 5). The thread teeth 316 have a number of teeth N, which represents the number of thread teeth 316.
In some embodiments, each of the thread teeth 316 in one heat exchange tube may have the same shape, and the cross-sectional shape thereof may be a common shape, such as a triangle or trapezoid. In the embodiment shown in fig. 3A and 3B, the cross-sectional shape of the thread teeth 316 is trapezoidal.
Fig. 4 shows a partial enlarged view of the portion of the dashed box 315 of fig. 3B for further illustrating the specific structure of the screw teeth 316. As shown in fig. 4, the thread teeth 316 having a trapezoidal cross section have a tip width W t Width of tooth bottom W b Tooth height h.
In the illustrated embodiment, the tooth height h is the vertical distance between the thread teeth 316 and the inner wall 302 of the pipe body, and the tooth top width W t Sum tooth bottom width W b Representing the length of the two bases of trapezoidal thread teeth 316.
Fig. 5 is a sectional view of the heat exchange tube 200 along the direction of the axis x thereof for illustrating the specific shape of the heat exchange tube 200 and the screw teeth 316 from another angle. As shown in fig. 5, the pipe diameter D of the heat exchange pipe 200 is D, which is the cross-sectional diameter of the pipe body inner wall 302, and the larger the pipe diameter D is, the more the screw teeth 316 can be accommodated while the tooth shape and size of the screw teeth 316 remain substantially unchanged.
The thread teeth 316 also have a helix angle α, which in the illustrated embodiment represents the sharp angle formed between the thread teeth 316 and the axis x.
The applicant of the present application has found that the provision of the inwardly protruding castellated structure on the inner wall of the heat exchange tube 200 can increase the heat exchange area between the tube wall of the heat exchange tube and the fluid in the tube and can increase the turbulence disturbance of the fluid in the tube of the heat exchange tube, thereby enhancing the heat exchange performance of the heat exchange tube. On the other hand, however, turbulence in the fluid in the heat exchange tubes will cause an increase in the flow resistance of the fluid and an increase in the pressure loss (i.e., water pressure drop) of the fluid flowing through the heat exchange tubes.
In the prior art, the better the heat exchange performance of the heat exchange tube is, the larger the fluid disturbance in the tube is, but the larger the pressure drop inside the tube is. The excessive drop in water pressure inside the heat exchange tubes can cause an increase in power consumption of external driving equipment and an increase in the number of the heat exchange tubes, thereby affecting the cost of the heat exchanger.
The applicant found that the above technical problems can be solved if the heat exchange efficiency and the water pressure of each of the heat exchange tubes are reduced to a certain balance within a certain range of the number of the heat exchange tubes (i.e., the cost of the heat exchange tubes). However, the applicant has found that the two indexes of heat exchange efficiency and water pressure drop are often not optimized at the same time. The applicant has also found that, in different situations, one of these two indices may be of great interest, as long as this index is in an optimal state, while the other index remains substantially unchanged, to be able to meet different heat exchanger requirements. In particular, in the design requirements of some heat exchangers, it may be mainly concerned whether the water pressure drop is in an optimal state, but the heat exchange efficiency can be tolerated and is not in an optimal state; in the design requirements of some heat exchangers, it may be of primary concern whether the heat exchange efficiency is in an optimal state, but is tolerant of water pressure drop.
The applicant found that the two indexes of heat exchange efficiency and water pressure drop are mainly composed of the helix angle alpha, the tooth number N, the tooth height h and the tooth top width W of the screw teeth of the heat exchange tube t Width of tooth bottom W b These parameters determine. Wherein when the helix angle alpha, the number of teeth N, the tooth height h and the tooth bottom width W b When the water pressure drop is increased, the heat exchange efficiency is increased, but when the tooth top width W is wider t When the heat exchange efficiency is increased, the water pressure drop is reduced at the same time; when the helix angle alpha, the number of teeth N, the tooth height h and the tooth bottom width W b When the water pressure is reduced, the heat exchange efficiency and the water pressure are reduced at the same time, but when the tooth top width W is wider t Also decrease in time, thenThe water pressure drop can be increased but at the same time the heat exchange efficiency is reduced.
On this basis, the applicant has also paid attention to the weight of the heat exchange tubes per unit length of the heat exchange tubes, since the weight of the heat exchange tubes per unit length also affects the cost of the heat exchange tubes when the number of heat exchange tubes is fixed. Wherein the helix angle alpha of the screw thread teeth of the heat exchange tube has little influence on the weight of the heat exchange tube in unit length, and the number of teeth N, the tooth height h and the tooth top width W t Width of tooth bottom W b The weight of the heat exchange tube in unit length is positively influenced, namely, the weight of the heat exchange tube in unit length is along with the number of teeth N, the tooth height h and the tooth top width W t Width of tooth bottom W b Increases with increasing increases and decreases with decreasing them.
The applicant found that although the helix angle alpha, the number of teeth N, the tooth height h, the tooth top width W are varied t Width of tooth bottom W b All have an effect on the heat exchange efficiency of the heat exchange tube, the water pressure drop and the weight of the heat exchange tube per unit length, but these parameters are not all the same to the extent they may have an effect on them over a range of variations. Thus, within certain specified ranges, co-adjusting these parameters will have different effects on water pressure drop, heat exchange efficiency and heat exchange tube weight per unit length than when these parameters are adjusted individually.
The following are two heat exchange tubes that the applicant has found that are capable of optimizing the water pressure drop or heat exchange efficiency with the weight of the heat exchange tubes per unit length kept within a certain range.
Example 1: low water pressure drop (capable of optimizing water pressure drop) heat exchange tube
In this embodiment, the applicant found that the water pressure drop of the heat exchange tube can be greatly reduced when the helix angle α of the heat exchange tube is within a certain range. And by making the tooth height h, the tooth top width W t Width of tooth bottom W b And the number of teeth N is set in a certain range, so that the heat exchange efficiency and the weight of the heat exchange tube in unit length can be maintained to be basically unchanged. The low water pressure drop heat exchange tube of the embodiment adjusts the helix angle alpha within a certain range based on the prior heat exchange tube, and adjusts the tooth height h. Tooth top width W t Width of tooth bottom W b And the number of teeth N is set in a certain range.
Specifically, in the present embodiment, for a heat exchange tube with a constant tube diameter D, when the helix angle α of the low water pressure drop heat exchange tube is within a certain range, the low water pressure drop heat exchange tube can be greatly reduced in water pressure drop compared with the existing heat exchange tube, but the heat exchange efficiency is also reduced. After the number of teeth N is adjusted, a certain reduction of heat exchange efficiency can be made up, so that the heat exchange efficiency is maintained basically unchanged. Further, by setting the tooth height h and the tooth top width W t Sum of tooth bottom width W b The weight of the heat exchange tube in unit length can be kept basically unchanged by being arranged in a certain range. At this time, although the water pressure drop increases, the water pressure drop can be reduced as a whole as compared with the existing heat exchange tube.
More specifically, the helix angle alpha and the tooth number N of the low water pressure drop heat exchange tube are related to the tube diameter D of the low water pressure drop heat exchange tube, and the tooth height h and the tooth top width W t Width of tooth bottom W b Are related to the number of teeth N and the pipe diameter D. As an example, tooth height h, tooth top width W t Width of tooth bottom W b And pipe diameter D meet the following requirements, respectively:
as an example, the low water pressure drop heat exchange tube has a tube diameter D of 19.05mm, a helix angle alpha of 20-33 DEG, and a number of teeth N of 39-65 (N is a natural number), X 1 0.195-0.619, X 2 0.176-0.521, X 3 0.021-0.206.
As another aspectAn example is a low water pressure drop heat exchange tube having a tube diameter D of 25.4mm, a helix angle alpha of 30-43 DEG, and a number of teeth N of 45-70 (N is a natural number), X 1 0.141 to 0.500, X 2 0.169-0.570, X 3 0.018 to 0.201.
The wall thickness of the heat exchange tube with the standard tube diameter is generally 0.5mm to 0.75mm. And although the low water pressure drop heat exchange tube having the standard tube diameters of 19.05mm and 25.4mm is exemplified in the present embodiment, in practice the tube diameters of the low water pressure drop heat exchange tube have effects similar to those of the low water pressure drop heat exchange tube having the standard tube diameter within a certain range of the standard tube diameter, for example, the tube diameter is 19.05.+ -. 1mm or the tube diameter is 25.4.+ -. 1mm.
In order to more clearly show the influence of each parameter of the thread tooth of the heat exchange tube on two indexes of water pressure drop and heat exchange efficiency of the heat exchange tube and on the weight of the heat exchange tube in unit length, a single heat exchange tube is arranged as the heat exchange tube of the heat exchanger, a heat transfer experiment is carried out by using the single tube heat exchanger, and the water pressure drop through the heat exchange tube and the heat exchange efficiency of the heat exchange tube are measured to specifically explain the effects of different examples of the low water pressure drop heat exchange tube of the embodiment 1. Wherein the helix angle alpha, the number of teeth N, the tooth height h, the tooth top width W of the heat exchange tube according to various examples are shown in Table 1 t Width of tooth bottom W b And pipe diameter D. In this embodiment, a group of comparative heat exchange tubes and a series of embodiments of low water pressure drop heat exchange tubes are used as a group to perform comparative explanation, wherein the comparative heat exchange tubes 1-4 are all commercially available heat exchange tubes.
TABLE 1 different parameters of the heat exchange tubes
In this embodiment, the weight of the heat exchange tube per unit length of the low water pressure drop heat exchange tube 1 is 0.468kg/s compared to the weight of the heat exchange tube per unit length of the heat exchange tube 1 of 0.475 kg/s. From this, it can be seen that the weight of the low water pressure drop heat exchange tube 1 is similar to that of the heat exchange tube of the comparative heat exchange tube 1, and is slightly lower than that of the heat exchange tube of the comparative heat exchange tube 1.
FIG. 6 is a graph showing the relationship between the flow rate of water in the heat exchange tube and the difference between the pressure drop of water and the temperature of water entering and exiting the heat exchange tube. In heat exchange tube applications, it is desirable that the heat exchange tube be capable of accommodating a variety of different flow rates, i.e., for different flow rates, the low water pressure drop heat exchange tube exhibits consistent characteristics (i.e., low water pressure drop and at least maintaining heat exchange efficiency without a decrease in this embodiment) compared to the comparative heat exchange tube. In order to more intuitively show the difference in water pressure drop and heat exchange efficiency between the comparative heat exchange tube 1 and the low water pressure drop heat exchange tube 1, the relationship between the in-tube water flow rate (m/s) and the unit length water pressure drop (kPa/m) in the comparative heat exchange tube 1 and the low water pressure drop heat exchange tube 1 is shown in fig. 6, and the relationship between the in-tube water flow rate (m/s) and the in-and-out water temperature difference (c) in the comparative heat exchange tube 1 and the low water pressure drop heat exchange tube 1, which is an illustration of the heat exchange efficiency of the heat exchange tube, is shown. The pentagonal points in the figure represent the low water pressure drop heat exchange tubes 1 in the present embodiment, and the cross-shaped points in the figure represent the comparative heat exchange tubes 1.
As can be seen from fig. 6, at each flow rate, the water pressure drop of the low water pressure drop heat exchange tube 1 per unit length is significantly lower than that of the comparative heat exchange tube 1. At each flow rate, the heat exchange efficiency of the low water pressure drop heat exchange tube 1 is similar to that of the comparison heat exchange tube 1 or slightly lower than that of the comparison heat exchange tube 1.
Similar experiments are performed on the comparison heat exchange tube 1 and the low water pressure drop heat exchange tube 2-11, the comparison heat exchange tube 2 and the low water pressure drop heat exchange tube 12-25, the comparison heat exchange tube 3 and the low water pressure drop heat exchange tube 26-37, and the comparison heat exchange tube 4 and the low water pressure drop heat exchange tube 38-46 to detect the water pressure drop and the heat exchange efficiency of the low water pressure drop heat exchange tube in unit length under different flow rates, and the result is similar to that of the low water pressure drop heat exchange tube 1. For convenience, the ratio of each group of low water pressure drop heat exchange tubes in unit length to the corresponding comparative heat exchange tube (i.e., the index of the low water pressure drop heat exchange tube divided by the corresponding index of the corresponding comparative heat exchange tube) is shown in tables 2-5 in terms of three indices, namely water pressure drop, heat exchange efficiency, and heat exchange tube weight (abbreviated as weight). Wherein, table 2 shows the proportional relationship between the comparative heat exchange tube 1 and the low water pressure drop heat exchange tubes 1-11 in table 1 on each index, table 3 shows the proportional relationship between the comparative heat exchange tube 2 and the low water pressure drop heat exchange tubes 12-25 in table 1 on each index, table 4 shows the proportional relationship between the comparative heat exchange tube 3 and the low water pressure drop heat exchange tubes 26-37 in table 1 on each index, and table 5 shows the proportional relationship between the comparative heat exchange tube 4 and the low water pressure drop heat exchange tubes 38-46 in table 1 on each index.
Table 2 compares the proportional relationship between the heat exchange tube 1 and the low water pressure drop heat exchange tubes 1 to 11 in each index
Table 3 compares the proportional relationship between the heat exchange tube 2 and the low water pressure drop heat exchange tubes 12 to 25 in each index
Table 4 compares the proportional relationship between the heat exchange tube 3 and the low water pressure drop heat exchange tubes 26 to 37 in each index
Table 5 compares the proportional relationship between the heat exchange tube 4 and the low water pressure drop heat exchange tubes 38 to 47 at each index
As can be seen from tables 2 and 3, for the heat exchange tube having a tube diameter of 19.05mm, the low water pressure drop heat exchange tubes 1 to 11 in this embodiment can reduce the water pressure drop by at least 13% or more as compared with the comparative heat exchange tube 1, and even the water pressure drop can be reduced by approximately 20% in the low water pressure drop heat exchange tube 4. And the heat exchange efficiency and weight of the low water pressure drop heat exchange tubes 1 to 11 in the present embodiment can be maintained substantially at the level similar to the comparative heat exchange tube 1, for example, the heat exchange efficiency is not lower than 95% and the weight is not more than 101%. Even in the low water pressure drop heat exchange tube 9, in the case where the water pressure drop is reduced by approximately 18%, the heat exchange efficiency is rather higher than that of the comparative heat exchange tube 1, and the weight is almost the same as that of the comparative heat exchange tube 1. In the low water pressure drop heat exchange tubes other than the low water pressure drop heat exchange tube 9, the weight is slightly lower than that of the comparative heat exchange tube 1.
The low water pressure drop heat exchange tubes 12-25 of this embodiment can reduce the water pressure drop by at least 15% or more as compared to the comparative heat exchange tube 2, and even the water pressure drop in the low water pressure drop heat exchange tubes 12, 13 and 22 can be reduced by about 24%. And the heat exchange efficiency and weight of the low water pressure drop heat exchange tubes 12 to 25 in this embodiment can be maintained substantially at the level similar to the comparative heat exchange tube 2, for example, the heat exchange efficiency is not lower than 97%, the weight is not more than 103%, and even in the low water pressure drop heat exchange tubes 14, 17 to 19 and 25, the heat exchange efficiency is slightly higher than the comparative heat exchange tube 2 in the case where the water pressure drop is nearly 15 to 18%.
As can be seen from tables 4 and 5, for the heat exchange tube having a tube diameter of 25.4mm, the low water pressure drop heat exchange tubes 26 to 37 in this embodiment can reduce the water pressure drop by at least 13% or more as compared with the comparative heat exchange tube 3, and even the water pressure drop in the low water pressure drop heat exchange tubes 26 to 27 and 36 can be reduced by nearly 25 to 30%. And the heat exchange efficiency and weight of the low water pressure drop heat exchange tubes 26 to 37 in the present embodiment can be maintained substantially at the level similar to the comparative heat exchange tube 3, for example, the heat exchange efficiency is not lower than 98% and the weight is not more than 102%, and even in other low water pressure drop heat exchange tubes than the low water pressure drop heat exchange tube 36, the heat exchange efficiency can be slightly higher than the comparative heat exchange tube 3.
And the low water pressure drop heat exchange tubes 38-46 in this embodiment can reduce the water pressure drop by at least 15% or more, even by about 22% or so in the low water pressure drop heat exchange tubes 38 and 46, as compared to the comparative heat exchange tube 4. And the heat exchange efficiency and weight of the low water pressure drop heat exchange tubes 38 to 46 in the present embodiment can be maintained substantially at the level similar to the comparative heat exchange tube 4, for example, the heat exchange efficiency is not lower than 97%, the weight is not more than 103%, and even in the low water pressure drop heat exchange tubes 40 and 45, the heat exchange efficiency is slightly higher than the comparative heat exchange tube 4 in the case where the water pressure drop is reduced by approximately 15%.
It can be seen that these low water pressure drop heat exchange tubes 1-46 in this embodiment are capable of greatly reducing the water pressure drop without significantly reducing the heat exchange efficiency and without significantly increasing the weight, as compared to the corresponding comparative heat exchange tubes.
Application example of low water pressure drop heat exchange tube
Fig. 7A and 7B show the effect of the number of heat exchange tubes on the water pressure drop of the heat exchanger and the small heat exchange temperature difference of the heat exchanger, respectively, when different heat exchange tube designs are applied to the heat exchanger, to illustrate the design process of the heat exchanger. Fig. 7A shows a heat exchanger designed with a comparative heat exchange tube 1, and fig. 7B shows a heat exchanger designed with a low water pressure drop heat exchange tube 1. The small heat exchange temperature difference on the ordinate in the graph represents the heat exchange efficiency of the heat exchange tube.
As a specific example, the design requirements of a certain heat exchanger are:
1. heat exchange amount: 3516kW;
2. length of heat exchanger: 3.66 meters;
3. the small heat exchange temperature difference is less than or equal to 1.0 ℃;
4. the water pressure drop is less than or equal to 100kPa.
As shown in fig. 7A, under the condition of designing the heat exchanger by adopting the conventional comparative heat exchange tube 1, when the small heat exchange temperature difference is 1 ℃, the water pressure is reduced to about 160KPa, the number of heat exchange tubes is about 460, and at this time, the water pressure drop cannot meet the design requirement of the heat exchanger. And when the water pressure drop is below 100kPa, the number of the heat exchange pipes is required to reach 600.
As shown in fig. 7B, under the condition that the heat exchanger is designed by adopting the low water pressure drop heat exchange tube 1, when the water pressure drop is reduced to 100kPa, the small heat exchange temperature difference is 0.98 ℃, and the number of heat exchange tubes is 500. When the number of the heat exchange tubes reaches 600, the water pressure drop is only about 70kPa, and the small heat exchange temperature difference is only about 0.82 ℃.
It can be seen that when the low water pressure drop heat exchange tube 1 in embodiment 1 is used to design a heat exchanger, fewer heat exchange tubes are required to meet the design requirements of the heat exchanger.
In the embodiment shown in fig. 7B, the heat exchanger is designed using the low water pressure drop heat exchange tube 1, only as an exemplary illustration of the beneficial effect of using the low water pressure drop heat exchange tube to design the heat exchanger. In practice, according to different heat exchanger design requirements, other low water pressure drop heat exchange tubes can be applied to design the heat exchanger.
Example 2: first kind of high heat exchange efficiency (capable of optimizing heat exchange efficiency) heat exchange tube
In the present embodiment, the applicant found that the heat exchange efficiency of the heat exchange tube can be optimized when the number of teeth N of the heat exchange tube is within a certain range. And at this time by setting the helix angle alpha, tooth height h, tooth top width W t Sum tooth bottom width W b The water pressure drop of the heat exchange tube and the weight of the heat exchange tube in unit length can be maintained to be basically unchanged by being arranged in a certain range. The heat exchange tube with high heat exchange efficiency of the embodiment adjusts the number of teeth N within a certain range based on the existing heat exchange tube, and adjusts the helix angle alpha, the tooth height h and the tooth top width W t Sum tooth bottom width W b Is set in a certain range.
Specifically, in the present embodiment, for a heat exchange tube with a certain tube diameter D, when the number of teeth N of the heat exchange tube with high heat exchange efficiency is within a certain range, the heat exchange efficiency of the heat exchange tube with high heat exchange efficiency can be optimized (or increased) as compared with the existing heat exchange tube, but the weight of the heat exchange tube per unit length is also increased. By making the tooth bottom width W b Is arranged in a certain range and further increases the tooth height h and/or the tooth top width W t The weight of the heat exchange tube in unit length can be kept basically unchanged by being arranged in a certain range. Further to By setting the helix angle α within a certain range, the water pressure drop can be controlled within a certain range. At this time, although the tooth height h and the tooth top width W t Width of tooth bottom W b And the helix angle α will have an impact on the heat exchange efficiency, but the heat exchange efficiency as a whole can be optimized compared to existing heat exchange tubes.
As an example, the heat exchange tube with high heat exchange efficiency has a tube diameter D of 19.05mm, a number of teeth N of 46 to 65 (N is a natural number), and W b 0.321-0.521 mm, h 0.235-0.553 mm, W t The helical angle alpha is 30-55 degrees and is 0.047-0.181 mm.
As another example, the heat exchange tube with high heat exchange efficiency has a tube diameter D of 25.4mm, a number of teeth N of 59 to 70 (N is a natural number), and W b 0.451 to 0.627mm, h 0.301 to 0.624mm, W t The spiral angle alpha is 30-55 degrees and is 0.073-0.246 mm.
The wall thickness of the heat exchange tube with the standard tube diameter is generally 0.5mm to 0.75mm. Although the high heat exchange efficiency heat exchange tube having the standard tube diameters of 19.05mm and 25.4mm is exemplified in the present embodiment, the tube diameters of the high heat exchange efficiency heat exchange tube have effects similar to those of the high heat exchange efficiency heat exchange tube having the standard tube diameter within a certain range of the standard tube diameter, for example, the tube diameter is 19.05.+ -. 1mm or the tube diameter is 25.4.+ -. 1mm.
In order to more clearly show the influence of each parameter of the thread tooth of the heat exchange tube on two indexes of water pressure drop and heat exchange efficiency of the heat exchange tube and on the weight of the heat exchange tube in unit length, a single heat exchange tube is arranged as the heat exchange tube of the heat exchanger, a heat transfer experiment is performed by using the single tube heat exchanger, and the water pressure drop through the heat exchange tube and the heat exchange efficiency of the heat exchange tube are measured to specifically explain the effects of different examples of the high heat exchange efficiency heat exchange tube of embodiment 2. Wherein the helix angle α, the number of teeth N, the tooth height h, the tooth tip width W of the heat exchange tube according to various examples are shown in Table 6 t Width of tooth bottom W b And pipe diameter D. In order to more intuitively show the effect of the heat exchange tube of the present application, in the present embodiment, the heat exchange tube is grouped with a series of embodiments of the heat exchange tube with high heat exchange efficiency of the present applicationThe comparative heat exchange tubes 1-2 are all commercially available heat exchange tubes.
TABLE 6 different parameters of the heat exchange tubes
The water pressure drop and the heat exchange efficiency of the comparative heat exchange tube 1 and the high heat exchange efficiency heat exchange tube 1-11 and the water pressure drop and the heat exchange efficiency of the comparative heat exchange tube 2 and the high heat exchange efficiency heat exchange tube 12-20 in the same flow rate and the weight of the respective heat exchange tubes are detected in a unit length. For convenience, the proportional relationships between each group of high heat exchange efficiency heat exchange tubes and the corresponding comparative heat exchange tubes are shown in tables 7 to 8 in the form of tables on three indexes of water pressure drop, heat exchange efficiency and heat exchange tube weight per unit length (abbreviated as weight). Wherein, table 7 shows the proportional relationship between the comparative heat exchange tube 1 and the high heat exchange efficiency heat exchange tubes 1 to 11 in table 6 at each index, and table 8 shows the proportional relationship between the comparative heat exchange tube 2 and the high heat exchange efficiency heat exchange tubes 12 to 20 in table 6 at each index.
Table 7 compares the proportional relationship between the heat exchange tube 1 and the heat exchange tubes 1 to 11 with high heat exchange efficiency in each index
Table 8 compares the proportional relationship between the heat exchange tube 2 and the heat exchange tubes 12 to 20 with high heat exchange efficiency in each index
As can be seen from table 7, for the heat exchange tube with a tube diameter of 19.05mm, the heat exchange efficiency of the heat exchange tubes 1 to 11 with high heat exchange efficiency in this embodiment can be improved by about 5% to 12% compared with the comparative heat exchange tube 1, for example, the heat exchange tubes 5, 7, and 11 with high heat exchange efficiency are all improved by more than 10%. And the water pressure drop and weight of the heat exchange tubes 1 to 11 of high heat exchange efficiency in this embodiment can be maintained substantially at the level similar to those of the comparative heat exchange tube 1, for example, the water pressure drop is not higher than 112.2% and the weight is not higher than 105%. For example, in the heat exchange tubes 4 to 6 and 7 having high heat exchange efficiency, when the heat exchange efficiency is improved by about 10%, the water pressure drop is reduced, and the weight is improved by about 4% as compared with the comparative heat exchange tube 1. In the heat exchange tube 10 with high heat exchange efficiency, the weight and water pressure drop are reduced compared with those of the comparative heat exchange tube 1 in the case of a heat exchange efficiency improved by 5%.
As can be seen from table 8, for the heat exchange tube with a tube diameter of 25.4mm, the heat exchange efficiency of the heat exchange tube 12-20 with high heat exchange efficiency in this embodiment can be improved by about 7% -18% compared with the comparative heat exchange tube 2, for example, the heat exchange tubes 14, 16, 19 with high heat exchange efficiency are all improved by more than 10%. And the water pressure drop and weight of the heat exchange tubes 12 to 20 of the present embodiment can be maintained substantially at the same level as the comparative heat exchange tube 2, for example, the water pressure drop is not higher than 114% and the weight is not higher than 105%. For example, in the heat exchange tubes 14 and 19 with high heat exchange efficiency, in the case where the heat exchange efficiency is improved by 12% or more, the water pressure drop is reduced or kept almost unchanged, and the weight is improved by only 5% or less as compared with the comparative heat exchange tube 2. In the heat exchange tube 18 with high heat exchange efficiency, the weight is slightly reduced compared with the comparative heat exchange tube 2 and the water pressure drop is increased by only 5% or less under the condition that the heat exchange efficiency is improved by about 10%.
It can be seen that these high heat exchange efficiency heat exchange tubes 1 to 20 in the present embodiment are capable of improving heat exchange efficiency without significantly increasing the weight and maintaining the water pressure drop as compared with the corresponding comparative heat exchange tubes.
Example 3: second type heat exchange tube with high heat exchange efficiency (capable of optimizing heat exchange efficiency)
In the present embodiment, shenThe applicant found that when the tooth bottom width W of the heat exchange tube b When the heat exchange efficiency of the heat exchange tube is in a certain range, the heat exchange efficiency of the heat exchange tube can be optimized. And at this time by setting the helix angle alpha, tooth height h, tooth top width W t And the number of teeth N is set in a certain range, so that the water pressure drop of the heat exchange tube and the weight of the heat exchange tube in unit length can be maintained to be basically unchanged. The heat exchange tube with high heat exchange efficiency of the embodiment adjusts the tooth bottom width W on the basis of the existing heat exchange tube b Within a certain range by setting the helix angle alpha, tooth height h and tooth top width W t And the number of teeth N is set in a certain range.
Specifically, in the present embodiment, for a heat exchange tube with a certain tube diameter D, the tooth bottom width W of the heat exchange tube with high heat exchange efficiency b When the heat exchange efficiency is within a certain range, the heat exchange efficiency of the heat exchange tube with high heat exchange efficiency can be optimized (or increased) compared with that of the existing heat exchange tube, but the weight of the heat exchange tube in unit length can be increased. By setting the number of teeth N within a certain range and further setting the tooth height h and/or the tooth top width W t The weight of the heat exchange tube in unit length can be kept basically unchanged by being arranged in a certain range. Further, by setting the helix angle α within a certain range, the water pressure drop can be controlled within a certain range. At this time, although the tooth height h and the tooth top width W t The number of teeth N and the helix angle α will have an impact on the heat exchange efficiency, but overall the heat exchange efficiency can be optimized compared to existing heat exchange tubes.
As an example, the pipe diameter D of the high heat exchange efficiency heat exchange pipe is 19.05mm, W b 0.523-0.545, and the number of teeth N is 39-45 (N is natural number), h is 0.355-0.523mm, W t The helical angle alpha is 30-55 degrees and is 0.101-0.198 mm.
As another example, the tube diameter D of the high heat exchange efficiency heat exchange tube is 25.4mm, W b 0.628-0.707 mm, and the number of teeth N is 45-58 (N is natural number), h is 0.447-0.634 mm, W t The helix angle alpha is 30-55 degrees and is 0.097-0.269 mm.
The wall thickness of the heat exchange tube with the standard tube diameter is generally 0.5mm to 0.75mm. Although the high heat exchange efficiency heat exchange tube having the standard tube diameters of 19.05mm and 25.4mm is exemplified in the present embodiment, the tube diameters of the high heat exchange efficiency heat exchange tube have effects similar to those of the high heat exchange efficiency heat exchange tube having the standard tube diameter within a certain range of the standard tube diameter, for example, the tube diameter is 19.05.+ -. 1mm or the tube diameter is 25.4.+ -. 1mm.
In order to more clearly show the influence of each parameter of the thread tooth of the heat exchange tube on two indexes of water pressure drop and heat exchange efficiency of the heat exchange tube and on the weight of the heat exchange tube in unit length, a single heat exchange tube is arranged as the heat exchange tube of the heat exchanger, a heat transfer experiment is performed by using the single tube heat exchanger, and the water pressure drop through the heat exchange tube and the heat exchange efficiency of the heat exchange tube are measured to specifically explain the effects of different examples of the high heat exchange efficiency heat exchange tube of embodiment 3. Wherein the helix angle α, the number of teeth N, the tooth height h, the tooth tip width W of the heat exchange tube according to various examples are shown in Table 9 t Width of tooth bottom W b And pipe diameter D. In this embodiment, a group of embodiments of the comparative heat exchange tube and a series of embodiments of the heat exchange tube with high heat exchange efficiency are used as a group for comparison and explanation, wherein the comparative heat exchange tubes 1-2 are all commercially available heat exchange tubes.
TABLE 9 different parameters of the heat exchange tubes
The water pressure drop and the heat exchange efficiency of the comparative heat exchange tube 1 and the high heat exchange efficiency heat exchange tubes 21 to 26 and the water pressure drop and the heat exchange efficiency of the comparative heat exchange tube 2 and the high heat exchange efficiency heat exchange tubes 27 to 35 in the same flow rate and the weight of the respective heat exchange tubes are detected per unit length. For convenience, the proportional relationships between the heat exchange tubes of each group of high heat exchange efficiency and the corresponding comparative heat exchange tubes are shown in tables 10 to 11 in the form of tables on three indexes of water pressure drop, heat exchange efficiency and heat exchange tube weight per unit length (abbreviated as weight). Wherein, table 10 shows the proportional relationship between the comparative heat exchange tube 1 and the high heat exchange efficiency heat exchange tubes 21 to 26 in table 9 at each index, and table 11 shows the proportional relationship between the comparative heat exchange tube 2 and the high heat exchange efficiency heat exchange tubes 27 to 35 in table 9 at each index.
Table 10 compares the proportional relationship between the heat exchange tube 1 and the heat exchange tubes 21 to 26 of high heat exchange efficiency in each index
Table 11 compares the proportional relationship between the heat exchange tube 2 and the heat exchange tubes 27 to 35 with high heat exchange efficiency in each index
As can be seen from table 10, for the heat exchange tube having a tube diameter of 19.05mm, the heat exchange efficiency of the high heat exchange efficiency heat exchange tubes 21 to 26 in the present embodiment can be improved by about 5% to 7% as compared with the comparative heat exchange tube 1, for example, the heat exchange efficiency of each of the high heat exchange efficiency heat exchange tubes 21 and 23 is improved by 7% or more. And the water pressure drop and weight of the heat exchange tubes 21 to 26 of the present embodiment can be maintained substantially at the level similar to those of the comparative heat exchange tube 1, for example, the water pressure drop is not higher than 114% and the weight is not higher than 105%. For example, in the heat exchange tubes 25 and 26 having high heat exchange efficiency, in the case where the heat exchange efficiency is improved by about 5%, the water pressure drop is reduced instead, and the weight is improved by about 4% as compared with the comparative heat exchange tube 1.
As can be seen from table 11, for the heat exchange tubes having a tube diameter of 25.4mm, the heat exchange efficiency of the heat exchange tubes 27 to 35 of the embodiment can be improved by about 5% to 10% as compared with the comparative heat exchange tube 2, for example, the heat exchange tubes 27 and 29 of the high heat exchange efficiency are both improved by nearly 10%. And the water pressure drop and weight of the heat exchange tubes 27 to 35 of the present embodiment can be maintained substantially at the same level as the comparative heat exchange tube 2, for example, the water pressure drop is not higher than 110% and the weight is not higher than 104%. For example, in the heat exchange tubes 32 and 35 having high heat exchange efficiency, in the case where the heat exchange efficiency is improved by 5% or more, the water pressure drop is reduced instead, and the weight is improved by only 4% or less as compared with the comparative heat exchange tube 2.
It can be seen that these high heat exchange efficiency heat exchange tubes 21 to 35 in the present embodiment can also improve heat exchange efficiency without significantly increasing the weight and maintaining the water pressure drop as compared with the corresponding comparative heat exchange tubes.
Thus, although examples 2 and 3 provide heat exchange tubes having two different parameter ranges, it can be seen from tables 7 to 8 and tables 10 to 11 that the first high heat exchange efficiency heat exchange tubes 1 to 20 of example 2 and the second high heat exchange efficiency heat exchange tubes 21 to 35 of example 3 are each capable of optimizing the heat exchange efficiency of the heat exchange tubes while maintaining the weight of the heat exchange tubes per unit length within a certain range.
Application example of heat exchange tube with high heat exchange efficiency
Fig. 8 shows the influence of the number of heat exchange tubes on the water pressure drop of the heat exchanger and the small heat exchange temperature difference of the heat exchanger, respectively, when the heat exchanger is designed by using different heat exchange tubes, so as to explain the design process of the heat exchanger. In order to more intuitively display the effect of the heat exchange tube with high heat exchange efficiency in the present application, the number influence curve of the comparative heat exchange tube and the number influence curve of the heat exchange tube with high heat exchange efficiency are shown on the same graph, wherein curves 841 and 842 show the influence curve of the comparative heat exchange tube, and curves 851 and 852 show the influence curve of the heat exchange tube with high heat exchange efficiency 7. The small heat exchange temperature difference on the ordinate in the graph represents the heat exchange efficiency of the heat exchange tube.
As a specific example, the design requirements of a certain heat exchanger are:
1. heat exchange amount: 3516kW;
2. length of heat exchanger: 3.66 meters;
3. the small heat exchange temperature difference is less than or equal to 0.6 ℃;
4. the water pressure drop is less than or equal to 100kPa.
As shown in fig. 8, when the heat exchanger is designed by using the conventional comparative heat exchange tube 1, the number of heat exchange tubes is about 780 or more when the heat exchange temperature difference is not more than 0.6 ℃. When the heat exchanger is designed by adopting the heat exchange tubes 7 with high heat exchange efficiency, the water pressure drops to about 93kPa when the heat exchange small temperature difference is 0.6 ℃, and the number of the heat exchange tubes is about 650. And when the heat exchanger is designed by adopting 780 heat exchange tubes 7 with high heat exchange efficiency, the small heat exchange temperature difference reaches below about 0.5 ℃.
It can be seen that when the heat exchanger is designed by using the heat exchange tube 7 with high heat exchange efficiency in embodiment 2, fewer heat exchange tubes are required to meet the design requirements of the heat exchanger.
In the embodiment shown in fig. 8, the heat exchanger is designed using high heat exchange efficiency heat exchange tubes 7, only as an exemplary illustration of the beneficial effect of using high heat exchange efficiency heat exchange tube design heat exchangers. In practice, according to different design requirements of the heat exchanger, other heat exchange tubes with high heat exchange efficiency can be applied to design the heat exchanger.
Although the present application will be described with reference to the specific embodiments shown in the drawings, it should be understood that many variations of the heat exchange tube of the present application are possible without departing from the spirit and scope and the background of the teachings of the present application. Those of ordinary skill in the art will also recognize that there are different ways to alter the details of the structure of the embodiments disclosed herein, and that they fall within the spirit and scope of the present application and the claims.
Claims (12)
1. A heat exchange tube, characterized in that: the heat exchange tube (200) comprises:
a tube body (301), the tube body (301) having an inner wall (302) and an axis (x), both ends of the tube body (301) having an inlet (303) and an outlet (304);
-a plurality of screw threads (316), the plurality of screw threads (316) being arranged on the inner wall (302) of the tube body (301) at a mutual distance, the plurality of screw threads (316) extending helically around the axis (x) of the tube body (301) from the inlet (303) of the tube body (301) to the outlet (304) of the tube body (301);
wherein the wall thickness of the heat exchange tube (200) is 0.5 mm-0.75 mm, and the helix angle alpha of the thread teeth (316) and the number of teeth N of the thread teeth (316) meet the following conditions:
(i) When the pipe diameter D of the pipe body (301) is 19.05+/-1 mm, the helix angle alpha is 20-33 degrees, and the number of teeth N is 39-65; or (b)
(ii) When the pipe diameter D of the pipe body (301) is 25.4+/-1 mm, the helix angle alpha is 30-43 degrees, and the number of teeth N is 45-70.
2. A heat exchange tube according to claim 1, wherein:
the cross section of the thread teeth (316) is trapezoidal;
wherein the tooth bottom width W of the trapezoid thread tooth (316) b The method meets the following conditions:
and X is 1 Is any constant of 0.195-0.619; and/or
The tooth height h of the trapezoidal thread tooth (316) is such that:
and X is 2 Is any constant of 0.176 to 0.521; and/or
Tip width W of the trapezoidal thread teeth (316) t The method meets the following conditions:
and X is 3 Is an arbitrary constant of 0.021-0.206.
3. A heat exchange tube according to claim 2, wherein:
-the number N of thread teeth (316) is 53, -the helix angle α of the thread teeth (316) is 30 °; and
the cross section of the thread teeth (316) is trapezoidal, and the tooth bottom width W of the trapezoidal thread teeth (316) b Is 0.313mm, the tooth height h of the trapezoid thread teeth (316) is 0.401mm, and the tooth top width W of the trapezoid thread teeth (316) t Is 0.068mm.
4. A heat exchange tube according to claim 1, wherein:
the cross section of the thread teeth (316) is trapezoidal;
wherein the tooth bottom width W of the trapezoid thread tooth (316) b The method meets the following conditions:
and X is 1 Is any constant of 0.141 to 0.500; and/or
The tooth height h of the trapezoidal thread tooth (316) is such that:
and X is 2 Is any constant from 0.169 to 0.570; and/or
Tip width W of the trapezoidal thread teeth (316) t The method meets the following conditions:
and X is 3 Is an arbitrary constant of 0.018 to 0.201.
5. The heat exchange tube of claim 4, wherein:
-the number N of thread teeth (316) is 68, -the helix angle α of the thread teeth (316) is 30 °; and
the cross section of the thread teeth (316) is trapezoidal, and the tooth bottom width W of the trapezoidal thread teeth (316) b Is 0.454mm, the tooth height h of the trapezoid thread tooth (316) is 0.488mm, and the tooth top width W of the trapezoid thread tooth (316) t Is 0.114mm.
6. A heat exchange tube, characterized in that: the heat exchange tube (200) comprises:
a tube body (301), the tube body (301) having an inner wall (302) and an axis (x), both ends of the tube body (301) having an inlet (303) and an outlet (304);
-a plurality of screw threads (316), the plurality of screw threads (316) being arranged on the inner wall (302) of the tube body (301) at a mutual distance, the plurality of screw threads (316) extending helically around the axis (x) of the tube body (301) from the inlet (303) of the tube body (301) to the outlet (304) of the tube body (301);
Wherein the wall thickness of the heat exchange tube (200) is 0.5 mm-0.75 mm, the cross section of the thread teeth (316) is trapezoidal, the number N of the thread teeth (316) and the tooth bottom width W of the trapezoidal thread teeth (316) b The method meets the following conditions:
(i) When the pipe diameter D of the pipe body (301) is 19.05+/-1 mm, the tooth number N is 46-65, and the tooth bottom width W b 0.321-0.521 mm, or the number of teeth N is 39-45, and the width W of the tooth bottom b 0.523-0.545 mm; or (b)
(ii) When the pipe diameter D of the pipe body (301) is 25.4+/-1 mm, the tooth number N is 59-70, and the tooth bottom width W b 0.451 to 0.627mm, or the number of teeth N is 45 to 58, and the tooth bottom width W b 0.628 to 0.707mm.
7. The heat exchange tube of claim 6, wherein:
the tooth bottom width W of the thread tooth (316) b And the number of teeth N of the thread teeth (316) satisfies (i);
the tooth height h of the trapezoid thread teeth (316) is 0.235-0.553 mm; and/or
Tip width W of the trapezoidal thread teeth (316) t 0.047-0.181 mm; and/or
The helix angle alpha of the thread teeth (316) is 30-55 degrees.
8. The heat exchange tube of claim 6, wherein:
the tooth bottom width W of the thread tooth (316) b And the number of teeth N of the thread teeth (316) satisfies (ii);
The tooth height h of the trapezoid thread teeth (316) is 0.355-0.523 mm; and/or
Tip width W of the trapezoidal thread teeth (316) t 0.101-0.198 mm; and/or
The helix angle alpha of the thread teeth (316) is 30-55 degrees.
9. The heat exchange tube of claim 6, wherein:
when the number of teeth N is 59-70 and the width of the tooth bottom W b When the thickness is 0.451-0.627 mm:
the tooth height h of the trapezoid thread teeth (316) is 0.301-0.624 mm; and/or
Tip width W of the trapezoidal thread teeth (316) t 0.073-0.246 mm; and/or
The helix angle alpha of the thread teeth (316) is 30-55 degrees.
10. The heat exchange tube of claim 6, wherein:
when the number of teeth N is 45-58 and the width of the tooth bottom W b 0.628 to 0.707 mm:
the tooth height h of the trapezoid thread teeth (316) is 0.447-0.634 mm; and/or
Tip width W of the trapezoidal thread teeth (316) t 0.097-0.269 mm; and/or
The helix angle alpha of the thread teeth (316) is 30-55 degrees.
11. A heat exchanger, characterized in that: the heat exchanger includes:
the heat exchange tube (200) according to any one of claims 1-10.
12. An air conditioning system, characterized in that: the air conditioning system (150) includes:
A compressor (110), a condenser (120), a throttling device (130) and an evaporator (140) in fluid connection in sequence; wherein at least one of the condenser (120) and the evaporator (140) employs the heat exchanger of claim 11.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910921861.6A CN112577355A (en) | 2019-09-27 | 2019-09-27 | Heat exchange tube, heat exchanger and air conditioning system using heat exchanger |
| CN2019109218616 | 2019-09-27 | ||
| PCT/CN2020/117846 WO2021057916A1 (en) | 2019-09-27 | 2020-09-25 | Heat exchange pipe, heat exchanger and air conditioning system using heat exchanger |
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| CN202080079586.9A Active CN114729794B (en) | 2019-09-27 | 2020-09-25 | Heat exchange tube, heat exchanger and air conditioning system using heat exchanger |
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| WO (1) | WO2021057916A1 (en) |
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| CN112577355A (en) * | 2019-09-27 | 2021-03-30 | 约克（无锡）空调冷冻设备有限公司 | Heat exchange tube, heat exchanger and air conditioning system using heat exchanger |
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Also Published As
| Publication number | Publication date |
|---|---|
| CN112577355A (en) | 2021-03-30 |
| CN114729794A (en) | 2022-07-08 |
| WO2021057916A1 (en) | 2021-04-01 |
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