CN211824013U - 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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- CN211824013U CN211824013U CN201921623734.XU CN201921623734U CN211824013U CN 211824013 U CN211824013 U CN 211824013U CN 201921623734 U CN201921623734 U CN 201921623734U CN 211824013 U CN211824013 U CN 211824013U
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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 an inlet and an outlet are arranged at two ends of the tube body; the heat exchange tube further comprises a plurality of screw threads provided on the inner wall of the tube body in a spaced relationship with each other, the plurality of screw threads spirally extending from the inlet of the tube body to the outlet of the tube body about an axis of the tube body. By changing the helix angle alpha and the number of teeth of the thread teeth of the heat exchange tubeN, tooth height h, tooth tip width WtWidth of tooth bottom WbAnd a part of the parameters are set in a certain range, so that the heat exchange tube with optimized water pressure drop or the heat exchange tube with optimized 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 can exchange heat between refrigerant and water to cause the refrigerant to radiate heat and to be condensed, or cause the refrigerant to absorb heat and to be evaporated. When a refrigerant flows through the heat exchanger, the refrigerant flows through the heat exchange tube, water flows through the heat exchange tube, and the refrigerant exchanges heat with the water in the heat exchange tube through the tube wall of the heat exchange tube to be condensed or evaporated.
SUMMERY OF THE UTILITY MODEL
The inner wall of the heat exchange tube is provided with the tooth-shaped structure protruding inwards, on one hand, the tooth-shaped structure can increase the heat exchange area between the tube wall of the heat exchange tube and fluid in the tube, and can increase turbulence disturbance of the fluid in the heat exchange tube, so that the heat exchange performance of the heat exchange tube is enhanced. On the other hand, turbulent disturbance of the fluid inside the heat exchange tube will increase the flow resistance of the fluid, and increase the pressure loss (i.e., water pressure drop) of the fluid flowing through the heat exchange tube.
At present, the better the heat exchange performance of the heat exchange tube, the larger the fluid disturbance in the tube, and thus the larger the pressure drop inside the tube. The excessive pressure drop inside the heat exchange tubes causes the increase of the power consumption of external driving equipment, and the number of the heat exchange tubes needs to be increased, so that the cost of the heat exchanger is influenced. Therefore, how to balance the water pressure drop and the heat exchange performance is very important in the design of the heat exchange tube.
In order to solve the above problems, an object of the present application in a first aspect is to provide a heat exchange tube comprising: a tube having an inner wall and an axis, the tube having an inlet and an outlet at two ends; a plurality of thread teeth disposed on the inner wall of the tubular body in spaced relation to one another, the plurality of thread teeth extending helically around an axis of the tubular body from the inlet of the tubular body to the outlet of the tubular body; wherein the helix angle alpha of the thread teeth and the number of teeth N of the thread teeth satisfy: (i) the helix angle alpha is 20-33 degrees, and the tooth number N is 39-65; or (ii) the helix angle alpha is 30 to 43 DEG, and the number of teeth N is 45 to 70.
According to the first aspect described above, the helix angle α of the thread teeth and the number N of the thread teeth satisfy (i), and the pipe diameter D of the pipe body is 19.05 ± 1 mm.
According to the first aspect described above, the cross-sectional shape of the thread tooth is trapezoidal; wherein the width W of the bottom of the trapezoidal thread toothbSatisfies the following conditions:
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 °; and the cross section of the thread tooth is trapezoidal, and the tooth bottom width W of the trapezoidal thread toothbIs 0.313mm, the height h of the trapezoidal thread teeth is 0.401mm, and the crest width W of the trapezoidal thread teethtIs 0.068 mm.
According to the first aspect described above, the helix angle α of the thread teeth and the number N of the thread teeth satisfy (ii), and the pipe diameter D of the pipe body is 25.4 ± 1 mm.
According to the first aspect described above, the cross-sectional shape of the thread tooth is trapezoidal; wherein the width W of the bottom of the trapezoidal thread toothbSatisfies the following conditions:
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 °; and the cross section of the thread tooth is trapezoidal, and the tooth bottom width W of the trapezoidal thread toothbIs 0.454mm, the height h of the trapezoidal thread teeth is 0.488mm, and the crest width W of the trapezoidal thread teethtIs 0.114 mm.
It is an object of the present application in a second aspect to provide another heat exchange tube comprising: a tube having an inner wall and an axis, the tube having an inlet and an outlet at two ends; a plurality of thread teeth disposed on the inner wall of the tubular body in spaced relation to one another, the plurality of thread teeth extending helically around an axis of the tubular body from the inlet of the tubular body to the outlet of the tubular body; wherein the cross-sectional shape of the thread teeth is trapezoidal, the number of teeth N of the thread teeth and the width W of the bottom of the trapezoidal thread teethbSatisfies the following conditions: (i) what is needed isThe number of teeth N is 46 to 65, and the width of the tooth bottom Wb0.321-0.521 mm; or (ii) the number N of teeth is 39 to 45, and the width W of the tooth bottomb0.523-0.545 mm; or (iii) the number N of teeth is 59 to 70, and the width W of the tooth bottomb0.451-0.627 mm; or (iv) the number N of teeth is 45 to 58, and the width W of the tooth bottombIs 0.628-0.707 mm.
According to the second aspect, the width W of the bottom of the thread toothbAnd 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 width W of the bottom of the thread toothbAnd the number of teeth N of the thread teeth satisfies (i); the tooth height h of the trapezoidal thread tooth is 0.235-0.553 mm; and/or the crest width W of the trapezoidal thread tootht0.047-0.181 mm; and/or the helix angle alpha of the thread teeth is 30-55 degrees.
According to the second aspect, the width W of the bottom of the thread toothbAnd the number of teeth N of the thread teeth satisfies (ii); the tooth height h of the trapezoidal thread tooth is 0.355-0.523 mm; and/or the crest width W of the trapezoidal thread tootht0.101-0.198 mm; and/or the helix angle alpha of the thread teeth is 30-55 degrees.
According to the second aspect, the width W of the bottom of the thread toothbAnd 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 width W of the bottom of the thread toothbAnd the number of teeth N of the thread teeth satisfies (iii); the tooth height h of the trapezoidal thread tooth is 0.301-0.624 mm; and/or the crest width W of the trapezoidal thread tootht0.073-0.246 mm; and/or the helix angle alpha of the thread teeth is 30-55 degrees.
According to the second aspect, the width W of the bottom of the thread toothbAnd the number of teeth N of the thread teeth satisfies (iv); the tooth height h of the trapezoidal thread tooth is 0.447-0.634 mm; and/or the crest width W of the trapezoidal thread tootht0.097-0.269 mm; and/or the helix angle alpha of the thread teeth is 30-55 degrees.
It is an object of the present application in a third aspect to provide a heat exchanger comprising: a heat exchange tube according to any one of the first or second aspects described above.
It is an object of the present application in a fourth aspect to provide an air conditioning system comprising: the compressor, the condenser, the throttling device and the evaporator are sequentially in fluid connection; wherein at least one of the condenser and the evaporator employs the heat exchanger of the third aspect.
The heat exchange tube is provided with a helical angle alpha of thread teeth, a tooth number N, a tooth height h and a tooth top width WtWidth of tooth bottom WbAnd a part of the parameters are set in a certain range, so that the heat exchange tube with optimized water pressure drop or the heat exchange tube with optimized 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.
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 drum;
fig. 3A is a perspective view of the heat exchange tube of the present application;
FIG. 3B is a radial cross-sectional view of the heat exchange tube of FIG. 3A;
FIG. 4 is a partial enlarged view of FIG. 3B;
FIG. 5 is a cross-sectional view of the heat exchange tube of FIG. 3A taken along the axial direction thereof;
FIG. 6 is a graph showing the relationship between the flow velocity of water in the tube and the pressure drop of water, and the temperature difference between inlet and outlet water;
FIG. 7A is a graph showing the effect of comparing the number of heat exchange tubes 1 on the water pressure drop of a heat exchanger and the small temperature difference of the heat exchange of the heat exchanger;
FIG. 7B is a graph showing the influence of the number of the heat exchange tubes 1 with low water pressure drop on the water pressure drop of the heat exchanger and the small temperature difference of the heat exchange of the heat exchanger;
fig. 8 is a graph showing the effect of comparing the respective numbers of the heat exchange tubes 1 and the heat exchange tubes 1 with high heat exchange efficiency on the water pressure drop of the heat exchanger and the small temperature difference of the heat exchange of the heat exchanger.
Detailed Description
Various embodiments of the present application will now be described with reference to the accompanying drawings, which form a part hereof. It should be understood that although directional terms such as "front," "rear," "upper," "lower," "left," "right," and the like may be used herein to describe various example structural portions and elements of the application, these terms are used herein for convenience of description only and are to be determined based on the example orientations shown in the drawings. Because the embodiments disclosed herein can be arranged in a variety of orientations, these directional terms are used for purposes of illustration only and are not to be construed as limiting. Wherever possible, the same or similar reference numbers used in this application refer to the same or like parts.
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 throttling device 130, and an evaporator 140, which are connected by piping to form a closed system, and a refrigerant is charged in the system. Wherein, the refrigerant flows through the compressor 110, the condenser 120, the throttling device 130 and the evaporator 140 in sequence, so that the air conditioning system 150 can cool or heat the outside. Specifically, the high-pressure gas refrigerant discharged from the compressor 110 flows into the condenser 120, is condensed into a high-pressure liquid refrigerant by releasing heat from the condenser 120, then flows into the expansion device 130, is expanded into a low-pressure liquid refrigerant, then flows into the evaporator 140, absorbs heat from 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 through them can exchange heat with the external water, and when the refrigerant releases heat in the condenser 120, the external water absorbs the heat to become hot; as the refrigerant absorbs heat in the evaporator 140, the outside water releases heat and becomes cold. Of course, in other embodiments, the cooling medium may not be water, but may be other types of cooling media, such as air, etc.
Fig. 2A and 2B are schematic structural views of the condenser 120 of fig. 1, illustrating the general position of the heat exchange pipe 200 in the condenser 120. Fig. 2A is a perspective view of the condenser 120 for illustrating a refrigerant inlet and a refrigerant outlet and a water inlet on the casing 225, and fig. 2B is a cross-sectional view of the condenser 120 along the axial direction of the drum 221 for illustrating an internal structure of the condenser 120.
As shown in fig. 2A, the condenser 120 includes a casing 225, and the casing 225 includes a cylinder 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, condenser 120 has left chamber 236, middle chamber 235 and right chamber 234 therein. Wherein, a left cavity 236 is formed between the left end 227 of the housing and the left divider plate 237, a middle cavity 235 is formed between the left divider plate 237 and the right divider plate 238, and a right cavity 234 is formed between the right divider plate 238 and the right end 228 of the housing. Wherein the gas refrigerant inlet 231 and the liquid refrigerant outlet 232 are in communication with the middle volume chamber 235. The middle cavity 235 further comprises two rows of heat exchange tubes 200 which are transversely arranged, and each row comprises a plurality of heat exchange tubes 200. Both ends of each heat exchange tube 200 are respectively communicated with the left and right chambers 236 and 234. Wherein the right volume 234 is also in communication with the water inlet 222 and the water outlet 224.
Wherein, the dotted arrows show the flowing direction of the refrigerant in the condenser 120, and after the gas refrigerant flows into the middle receiving chamber 235 from the gas refrigerant inlet 231, it flows from top to bottom, and 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 flow direction of water in the condenser 120, and when the water flows into the right chamber 234 from the water inlet 222, enters the heat exchange tubes 200 in the lower row, flows from right to left and exchanges heat with the refrigerant outside the heat exchange tubes 200, and then flows out of the heat exchange tubes in the lower row into the left chamber 236, the water in the left chamber 236 flows into the heat exchange tubes 200 in the upper row, flows from left to right and still exchanges heat with the refrigerant outside the heat exchange tubes 200, flows out of the heat exchange tubes 200 in the upper row into the right chamber 234, and finally flows out of the water outlet 224.
A specific structure of the heat exchange pipe 200 is shown in fig. 3A and 3B, wherein fig. 3A shows a perspective view of the heat exchange pipe 200 for explaining a general structure thereof; fig. 3B shows a radial cross-sectional view of the heat exchange tube for explaining a tooth-shaped structure on the inner wall of the heat exchange tube 200.
As shown in fig. 3A and 3B, the heat exchange tube 200 comprises a tube body 301 having an axis x, a first end 303 and a second end 304, wherein the first end 303 and the second end 304 are respectively provided at both ends of the tube body 301 in the direction of the axis x. As an example, water (cooling medium) flows into the pipe body 301 from the first end 303 and flows out from the second end 304 such that the first end 303 serves as an inlet for water and the second end 304 serves 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 body 301 has an inner wall 302 and the heat exchange tube 200 further comprises a plurality of helical teeth 316 spaced apart on the inner wall 302, the helical teeth 316 extending helically about the axis x of the tube body 301, as one example, the helical teeth 306 extending helically from the tube body first end 303 to the tube body second end 304 (see fig. 5). The thread teeth 316 have a number of teeth N, which represents the number of thread teeth 316.
As an example, each of the thread teeth 316 may have the same shape, and the cross-sectional shape thereof may be a general shape, such as a triangle or a trapezoid, and in the embodiment of the present application, the cross-sectional shape of the thread tooth 316 may be a trapezoid.
Fig. 4 shows a close-up view of the dashed box 315 portion of fig. 3B to further illustrate the specific structure of the thread tooth 316. As shown in FIG. 4, the trapezoidal cross-sectional thread tooth 316 has a crest width WtWidth of tooth bottom WbAnd a tooth height h.
In the embodiment shown, the tooth height h is the perpendicular distance between the thread tooth 316 and the inner wall 302 of the tubular bodyTooth tip width WtAnd width W of tooth bottombShowing the length of the two bases of the trapezoidal thread tooth 316.
Fig. 5 is a sectional view of the heat exchange tube 200 in the direction of the axis x thereof, for illustrating the specific shape of the heat exchange tube 200 and the screw tooth 316 from another angle. As shown in fig. 5, the heat exchange tube 200 has a tube diameter D, which is the cross-sectional diameter of the inner wall 302 of the tube body, and the larger the tube diameter D is, the more thread teeth 316 can be accommodated, while the tooth shape of the thread teeth 316 remains substantially the same.
The thread teeth 316 also have a helix angle α, which in the embodiment shown represents the acute angle subtended between the thread teeth 316 and the axis x.
The arrangement of the tooth-shaped structure protruding inwards on the inner wall of the heat exchange tube 200 can increase the heat exchange area between water and the inner wall of the heat exchange tube 200, and turbulence disturbance is brought to further increase the heat exchange performance. However, the turbulent disturbance of water in the heat exchange pipe 200 increases the resistance to the flow of water, the pressure loss (i.e., water pressure drop) of water flowing through the heat exchange pipe 200 increases, and the number of heat exchange pipes 200 needs to be increased in order to reduce the water pressure drop, resulting in an increase in cost.
In the application of the heat exchange tubes in the heat exchanger, people mainly care about two indexes, namely heat exchange efficiency and water pressure drop, of a single heat exchange tube within a certain range of the number of the heat exchange tubes (namely the cost of the heat exchange tubes). However, the applicant has found that often these two criteria cannot be optimized simultaneously. The applicant also found that in different situations, one of the two indexes can be focused on, and as long as the one index is in an optimized state, and the other index is maintained basically unchanged, different heat exchanger requirements can be met. Particularly, in the design requirements of some heat exchangers, the water pressure drop is mainly concerned whether the water pressure drop is in an optimized state, and the heat exchange efficiency can be tolerated not to be in an optimized state; in some heat exchanger design requirements, it is a major concern that heat exchange efficiency is not optimized, but that water pressure drop can be tolerated.
The two indexes of heat exchange efficiency and water pressure drop are mainly composed of the helical angle alpha of the thread teeth of the heat exchange tube, the tooth number N and the tooth heighth. Tooth tip width WtWidth of tooth bottom WbThese parameters are determined. Wherein when the helix angle alpha, the number of teeth N, the tooth height h and the tooth bottom width W are equalbWhen increased, the water pressure drop can be increased while the heat exchange efficiency is increased, and when the tooth crest width W is increasedtWhen the heat exchange efficiency is increased, the water pressure drop can be reduced while the heat exchange efficiency is increased; when the helix angle alpha, the number of teeth N, the tooth height h and the tooth bottom width WbWhen reduced, the heat exchange efficiency can be reduced while reducing the water pressure drop, and when the tooth crest width W is reducedtWhen the pressure is reduced, the heat exchange efficiency is reduced while the water pressure drop is increased.
On this basis, the applicant has also paid attention to the weight of the heat exchange tube per unit length thereof, because the weight of the heat exchange tube per unit length also affects the cost of the heat exchange tube when the number of the heat exchange tubes is fixed. Wherein, the helical angle alpha of the thread tooth of the heat exchange tube hardly influences the weight of the heat exchange tube in unit length, and the tooth number N, the tooth height h and the tooth top width WtWidth of tooth bottom WbAll can have positive influence on the weight of the heat exchange tube in unit length, namely the weight of the heat exchange tube in unit length can be along with the tooth number N, the tooth height h and the tooth top width WtWidth of tooth bottom WbIncreases and decreases as they decrease.
The applicant has found that, although the helix angle α, the number of teeth N, the tooth height h, and the tooth tip width W are variedtWidth of tooth bottom WbAll have an influence 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 different from each other in the extent to which they may be affected within a certain variation range thereof. So that the parameters are adjusted cooperatively in certain specific ranges, which has different effects on the water pressure drop, the heat exchange efficiency and the weight of the heat exchange tube per unit length than those of the parameters adjusted independently.
The following are two heat exchange tubes discovered by the applicant, which can respectively optimize two indexes of water pressure drop or heat exchange efficiency under the condition that the weight of the heat exchange tube in unit length is kept in a certain range.
Example 1: low water pressure drop (optimized) heat exchange tube
In this embodiment, the applicant found that the water pressure drop of the low water pressure drop heat exchange pipe can be greatly reduced when the helix angle α of the low water pressure drop heat exchange pipe is within a certain range. And by setting the tooth height h and the tooth crest width WtWidth of tooth bottom WbAnd the number N of the teeth is set within 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.
Specifically, in this embodiment, for a heat exchange tube with a certain tube diameter D, when the helix angle α of the low water pressure drop heat exchange tube is within a certain range, the water pressure drop of the low water pressure drop heat exchange tube can be greatly reduced compared with the existing heat exchange tube, but the heat exchange efficiency will also be reduced accordingly. After the number of teeth N is adjusted, a certain reduction amount of the heat exchange efficiency can be compensated, so that the heat exchange efficiency is kept basically unchanged. Further, the tooth height h and the tooth crest width W are adjustedtAnd a tooth bottom width WbThe weight of the heat exchange tube in unit length can be kept basically constant within a certain range. At this time, although the water pressure drop is increased, the water pressure drop can be reduced as a whole as compared with the conventional heat exchange pipe.
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 WtWidth of tooth bottom WbBoth in relation to the number of teeth N and the pipe diameter D. As an example, the tooth height h and the tooth tip width WtWidth of tooth bottom WbAnd the pipe diameter D respectively meet the following requirements:
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 to 33 DEG, and a number of teeth N of 39 to 65(N is a natural number), X10.195 to 0.619, X20.176 to 0.521, X3Is 0.021-0.206.
As another example, the low water pressure drop heat exchange tube has a tube diameter D of 25.4mm, a helix angle alpha of 30 to 43 DEG, and the number of teeth N of 45 to 70(N is a natural number), X10.141 to 0.500, X20.169 to 0.570, X3Is 0.018-0.201.
It should be noted that although the low water pressure drop heat exchange pipes with standard pipe diameters of 19.05mm and 25.4mm are exemplified in the present embodiment, in practice, the pipe diameters of the low water pressure drop heat exchange pipes have similar effects to those of the low water pressure drop heat exchange pipes with the standard pipe diameters within a certain range, for example, the pipe diameter is 19.05 ± 1mm or the pipe diameter is 25.4 ± 1 mm.
In order to more clearly show the influence of each parameter of the thread teeth of the heat exchange tube on two indexes of the water pressure drop and the heat exchange efficiency of the heat exchange tube and 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 a single-tube heat exchanger, and the water pressure drop of the heat exchange tube and the heat exchange efficiency of the heat exchange tube are measured, so as to specifically explain the effects of different examples of the low water pressure drop heat exchange tube in embodiment 1. The helical angle α, the number of teeth N, the tooth height h, and the tooth crest width W of each exemplary heat exchange tube are shown in table 1tWidth of tooth bottom WbAnd tube diameter D. In order to more intuitively express the effect of the heat exchange tubes of the present application, in the present embodiment, a group of examples of a comparative heat exchange tube and a series of low water pressure drop heat exchange tubes of the present application is used as a group for comparative explanation, wherein the comparative heat exchange tubes 1 to 4 are all commercially available heat exchange tubes.
TABLE 1 different parameters of the individual heat exchange tubes
In this example, the heat exchange tube weight per unit length of the low water pressure drop heat exchange tube 1 was 0.468kg/s compared to 0.475kg/s for the heat exchange tube weight per unit length of the heat exchange tube 1. Therefore, the weight of the low-water-pressure-drop heat exchange tube 1 is similar to that of the comparative heat exchange tube 1 and is slightly lower than that of the comparative heat exchange tube 1.
FIG. 6 is a graph showing the relationship between the flow velocity of water in the tube and the pressure drop of water and the temperature difference of inlet and outlet water in 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, that is, for different flow rates, the low water pressure drop heat exchange tube exhibits consistent characteristics (i.e., in this embodiment, low water pressure drop and at least no reduction in heat exchange efficiency maintained) over a comparable heat exchange tube. In order to more intuitively show the difference between the water pressure drop and the heat exchange efficiency of the comparative heat exchange tube 1 and the low water pressure drop heat exchange tube 1, fig. 6 shows the relationship between the flow rate (m/s) of water in the tube and the water pressure drop (kPa/m) per unit length in the comparative heat exchange tube 1 and the low water pressure drop heat exchange tube 1, and the relationship between the flow rate (m/s) of water in the tube and the temperature difference (deg.c) of water in and out of the comparative heat exchange tube 1 and the low water pressure drop heat exchange tube 1, wherein the temperature difference of water in and out is an indication of the heat exchange efficiency. The five-pointed star 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, 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. Under each flow velocity, the heat exchange efficiency of the low-water-pressure-drop heat exchange tube 1 is similar to that of the comparative heat exchange tube 1 or slightly lower than that of the comparative heat exchange tube 1.
Similar experiments are carried out on a comparison heat exchange tube 1 and low water pressure drop heat exchange tubes 1-11, a comparison heat exchange tube 2 and low water pressure drop heat exchange tubes 12-25, a comparison heat exchange tube 3 and low water pressure drop heat exchange tubes 26-37 and a comparison heat exchange tube 4 and low water pressure drop heat exchange tubes 38-46, so that the water pressure drop and the heat exchange efficiency of the low water pressure drop heat exchange tubes in unit length under different flow rates can be detected, and the result is similar to that of the low water pressure drop heat exchange tube 1. For convenience, in the form of tables, the proportional relationship between each group of low water pressure drop heat exchange tubes within a unit length and the corresponding comparison heat exchange tubes in terms of three indexes of water pressure drop, heat exchange efficiency and weight (weight for short) of the heat exchange tubes is shown in tables 2 to 5. Wherein, table 2 shows the proportional relationship of the comparison heat exchange tube 1 and the low water pressure drop heat exchange tubes 1 to 11 in table 1 in each index, table 3 shows the proportional relationship of the comparison heat exchange tube 2 and the low water pressure drop heat exchange tubes 12 to 25 in table 1 in each index, table 4 shows the proportional relationship of the comparison heat exchange tube 3 and the low water pressure drop heat exchange tubes 26 to 37 in table 1 in each index, and table 5 shows the proportional relationship of the comparison heat exchange tube 4 and the low water pressure drop heat exchange tubes 38 to 46 in table 1 in each index.
Table 2 shows 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 shows 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 comparison of the proportional relationship between the heat exchange tubes 3 and the low water pressure drop heat exchange tubes 26-37 in each index
TABLE 5 comparison of the relationship of the heat exchange tubes 4 to the low water pressure drop heat exchange tubes 38-47 in each index
As can be seen from tables 2 and 3, for the heat exchange tubes with a tube diameter of 19.05mm, the water pressure drop of the heat exchange tubes 1 to 11 with low water pressure drop in the present embodiment can be reduced by at least 13% compared with the comparative heat exchange tube 1, and even the water pressure drop in the heat exchange tube with low water pressure drop 4 can be reduced by nearly 20%. And the heat exchange efficiency and the weight of the low water pressure drop heat exchange tubes 1-11 in the embodiment can be basically maintained at the similar level as the comparison 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. And in the other low water pressure drop heat exchange tubes except the low water pressure drop heat exchange tube 9, the weight is also slightly lower than that of the comparative heat exchange tube 1.
Compared with the comparative heat exchange tube 2, the low water pressure drop heat exchange tubes 12 to 25 in the present embodiment can reduce the water pressure drop by at least 15%, and even reduce the water pressure drop by about 24% in the low water pressure drop heat exchange tubes 12, 13 and 22. In addition, the heat exchange efficiency and the weight of the low-water-pressure-drop heat exchange tubes 12 to 25 in the embodiment can be basically maintained at a level similar to that of the comparative heat exchange tube 2, for example, the heat exchange efficiency is not lower than 97% and 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 that of the comparative heat exchange tube 2 on the contrary under the condition that the water pressure drop is reduced to approximately 15 to.
As can be seen from tables 4 and 5, for the heat exchange tubes with the tube diameter of 25.4mm, compared with the comparative heat exchange tube 3, the water pressure drop of the low water pressure drop heat exchange tubes 26 to 37 in the present embodiment can be reduced by at least more than 13%, and even the water pressure drop of the low water pressure drop heat exchange tubes 26 to 27 and 36 can be reduced by approximately 25 to 30%. And the heat exchange efficiency and weight of the low water pressure drop heat exchange pipes 26 to 37 in the embodiment can be substantially maintained at a level similar to that of the comparative heat exchange pipe 3, for example, the heat exchange efficiency is not lower than 98% and the weight is not more than 102%, and even in the low water pressure drop heat exchange pipes other than the low water pressure drop heat exchange pipe 36, the heat exchange efficiency can be slightly higher than that of the comparative heat exchange pipe 3.
And compared with the comparative heat exchange tube 4, the low water pressure drop heat exchange tubes 38 to 46 in the embodiment can reduce the water pressure drop by at least more than 15%, and even reduce the water pressure drop by about 22% in the low water pressure drop heat exchange tubes 38 and 46. And the heat exchange efficiency and weight of the low water pressure drop heat exchange tubes 38 to 46 in this embodiment can be substantially maintained at a level similar to that of the comparative heat exchange tube 4, for example, the heat exchange efficiency is not lower than 97% and 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 that of the comparative heat exchange tube 4 in the case where the water pressure drop is reduced by approximately 15%.
It can be seen that the low water pressure drop heat exchange tubes 1-46 of the present embodiment can significantly reduce 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 pipe
Fig. 7A and 7B show the influence of the number of heat exchange tubes on the water pressure drop of the heat exchanger and the small temperature difference of the heat exchange of the heat exchanger, respectively, when the heat exchanger is designed using different heat exchange tubes, to explain the design process of the heat exchanger. Of these, 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. Wherein, the small temperature difference of the heat exchange of the ordinate in the figure represents the heat exchange efficiency of the heat exchange tube.
As a specific example, the design requirements for a heat exchanger are:
1. the heat exchange amount is as follows: 3516 kW;
2. length of the heat exchanger: 3.66 m;
3. the small temperature difference of heat exchange is less than or equal to 1.0 ℃;
4. the water pressure drop is less than or equal to 100 kPa.
As shown in fig. 7A, under the condition that the heat exchanger is designed by using the prior comparative heat exchange tube 1, when the heat exchange small temperature difference is 1 ℃, the water pressure drop is about 160KPa, and the number of the heat exchange tubes is about 460, at this time, the water pressure drop cannot meet the design requirement of the heat exchanger. When the water pressure drop is below 100kPa, the number of the heat exchange tubes needs to be 600.
As shown in FIG. 7B, under the condition that the heat exchanger is designed by using the low water pressure drop heat exchange tubes 1, when the water pressure is reduced to 100kPa, the small heat exchange temperature difference is 0.98 ℃, and the number of the 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 heat exchange small temperature difference is only about 0.82 ℃.
Therefore, when the heat exchanger is designed by adopting the low-water-pressure-drop heat exchange tube 1 in the embodiment 1, the design requirement of the heat exchanger can be met only by needing fewer heat exchange tubes.
In the embodiment shown in fig. 7B, the heat exchanger is designed by using the low water pressure drop heat exchange pipe 1, which is only used as an exemplary illustration to show the beneficial effect of designing the heat exchanger by using the low water pressure drop heat exchange pipe. In fact, according to different design requirements of the heat exchanger, other low-water-pressure-drop heat exchange pipes can be applied to design the heat exchanger.
Example 2: first heat exchange tube with high heat exchange efficiency (capable of optimizing heat exchange efficiency)
In this embodiment, the applicant found that the heat exchange efficiency of the heat exchange tube with high heat exchange efficiency can be optimized when the number N of the teeth of the heat exchange tube with high heat exchange efficiency is within a certain range. And at the same time, the helix angle alpha, the tooth height h and the tooth crest width W are adjustedtAnd width W of tooth bottombThe water pressure drop of the heat exchange tube with high heat exchange efficiency and the weight of the heat exchange tube in unit length can be kept basically unchanged within a certain range.
Particularly, in this embodiment, for the certain heat exchange tube of pipe diameter D, when the number of teeth N of the heat exchange tube of high heat exchange efficiency was in certain extent, the heat exchange tube of high heat exchange efficiency was compared with current heat exchange tube, and heat exchange efficiency can obtain optimizing (or increasing), but the heat exchange tube weight in the unit length also can increase thereupon. By making the tooth bottom width WbSet within a certain range, and further set the tooth height h and/or the tooth crest width WtThe weight of the heat exchange tube in unit length can be kept basically unchanged within 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, the tooth height h and the tooth tip width W are measuredtWidth of tooth bottom WbAnd the helix angle alpha, will have an effect on the heat exchange efficiency, but the heat exchange efficiency can be optimized overall compared to the prior heat exchange tubes.
As oneIn an example, the pipe diameter D of the heat exchange pipe with high heat exchange efficiency is 19.05mm, the number of teeth N is 46-65 (N is a natural number), and W isb0.321-0.521 mm, h 0.235-0.553 mm, Wt0.047-0.181 mm, and a helix angle alpha of 30-55 deg.
As another example, the heat exchange tube with high heat exchange efficiency has a tube diameter D of 25.4mm, the number of teeth N of 59-70 (N is a natural number), and Wb0.451-0.627 mm, h 0.301-0.624 mm, Wt0.073-0.246 mm and a helix angle alpha of 30-55 degrees.
It should be noted that although the heat exchange tubes with high heat exchange efficiency having standard tube diameters of 19.05mm and 25.4mm are exemplified in the present embodiment, the tube diameter of the heat exchange tube with high heat exchange efficiency actually has similar effect to that of the heat exchange tube with high heat exchange efficiency having 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 ± 1 mm.
In order to more clearly show the influence of each parameter of the thread teeth of the heat exchange tube on two indexes of the water pressure drop and the heat exchange efficiency of the heat exchange tube and 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 a single heat exchanger, the water pressure drop of the heat exchange tube and the heat exchange efficiency of the heat exchange tube are measured, and the effects of different examples of the heat exchange tube with high heat exchange efficiency in embodiment 2 are specifically explained. The helical angle α, the number of teeth N, the tooth height h, and the tooth crest width W of each exemplary heat exchange tube are shown in table 6tWidth of tooth bottom WbAnd tube diameter D. In order to more intuitively show the effect of the heat exchange tube of the present application, in this embodiment, a group of embodiments comparing the heat exchange tube with a series of heat exchange tubes with high heat exchange efficiency of the present application is used as a group for performing a grouping comparison description, wherein the comparison heat exchange tubes 1-2 are all commercially available heat exchange tubes.
TABLE 6 different parameters of the individual heat exchange tubes
And detecting the water pressure drop and the heat exchange efficiency of the comparison heat exchange tube 1 and the heat exchange tubes with high heat exchange efficiency 1-11 and the comparison heat exchange tube 2 and the heat exchange tubes with high heat exchange efficiency 12-20 in unit length at the same flow velocity, and the weight of the respective heat exchange tubes. For convenience, in the form of tables, tables 7 to 8 show the proportional relationship between each group of heat exchange tubes with high heat exchange efficiency and the corresponding comparison heat exchange tubes in terms of three indexes, namely, the water pressure drop, the heat exchange efficiency and the weight (weight for short) of the heat exchange tube per unit length. Wherein, table 7 shows the proportional relationship between the comparison heat exchange tube 1 and the heat exchange tubes with high heat exchange efficiency 1-11 in table 6 at each index, and table 8 shows the proportional relationship between the comparison heat exchange tube 2 and the heat exchange tubes with high heat exchange efficiency 12-20 in table 6 at each index.
Table 7 shows 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 shows 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 the tube diameter of 19.05mm, compared with the comparative heat exchange tube 1, the heat exchange efficiency of the heat exchange tubes 1-11 with high heat exchange efficiency in the embodiment can be improved by about 5% -12%, 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 the weight of the heat exchange tubes 1-11 with high heat exchange efficiency in the embodiment can be basically maintained at the similar level as the comparison 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 pipes 4-6 and 7 with high heat exchange efficiency, the water pressure drop is reduced on the contrary under the condition that the heat exchange efficiency is improved by about 10%, and the weight is also improved by about 4% compared with that of the heat exchange pipe 1. In the heat exchange tube 10 with high heat exchange efficiency, the weight and water pressure drop are both reduced in comparison with the comparative heat exchange tube 1 under the condition that the heat exchange efficiency is 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 tubes 12 to 20 with high heat exchange efficiency in this embodiment can be improved by about 7% to 18% compared with the comparative heat exchange tube 2, for example, the heat exchange tubes 14, 16, and 19 with high heat exchange efficiency are all improved by more than 10%. And the water pressure drop and the weight of the heat exchange tubes 12-20 with high heat exchange efficiency in the embodiment can be basically maintained at the same level as those of 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 rather reduced or almost maintained, and the weight is improved by only within 5% 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 under the condition that the heat exchange efficiency is improved by about 10%, and the water pressure drop is only improved by within 5%.
It can be seen that, compared with the corresponding comparative heat exchange tubes, the heat exchange tubes 1 to 20 with high heat exchange efficiency in the present embodiment can improve the heat exchange efficiency while maintaining the water pressure drop and without significantly increasing the weight.
Example 3: second heat exchange tube with high heat exchange efficiency (capable of optimizing heat exchange efficiency)
In this embodiment, the applicant found that the width W of the tooth bottom of the heat exchange tube with high heat exchange efficiencybWhen in a certain range, the heat exchange efficiency of the heat exchange tube with high heat exchange efficiency can be optimized. And at the same time, the helix angle alpha, the tooth height h and the tooth crest width W are adjustedtAnd the number N of the teeth is set within a certain range, so that the water pressure drop of the heat exchange tube with high heat exchange efficiency and the weight of the heat exchange tube in unit length can be kept basically unchanged.
Particularly, in the embodiment, for the heat exchange tube with a certain tube diameter D, the tooth bottom width W of the heat exchange tube with high heat exchange efficiencybWithin a certain rangeWhen enclosing the interior, high heat exchange efficiency heat exchange tube compares with current heat exchange tube, and heat exchange efficiency can obtain optimizing (or increasing), but the heat exchange tube weight in the unit length also can increase thereupon. By setting the number of teeth N within a certain range and further setting the tooth height h and/or the tooth tip width WtThe weight of the heat exchange tube in unit length can be kept basically unchanged within 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, the tooth height h and the tooth tip width W are measuredtThe number of teeth N and the helix angle α have an influence on the heat exchange efficiency, but the heat exchange efficiency as a whole can be optimized compared with the conventional heat exchange tube.
As an example, the pipe diameter D of the heat exchange pipe with high heat exchange efficiency is 19.05mm, and the pipe diameter W of the heat exchange pipe with high heat exchange efficiency is Wb0.523 to 0.545, a number N of teeth of 39 to 45(N is a natural number), h of 0.355 to 0.523mm, and Wt0.101 to 0.198mm and a helix angle alpha of 30 to 55 degrees.
As another example, the heat exchange tube with high heat exchange efficiency has a tube diameter D of 25.4mm and a tube diameter W ofb0.628-0.707 mm, N45-58 (N is natural number), h 0.447-0.634 mm, Wt0.097-0.269 mm, and a helix angle alpha of 30-55 deg.
It should be noted that although the heat exchange tubes with high heat exchange efficiency having standard tube diameters of 19.05mm and 25.4mm are exemplified in the present embodiment, the tube diameter of the heat exchange tube with high heat exchange efficiency actually has similar effect to that of the heat exchange tube with high heat exchange efficiency having 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 ± 1 mm.
In order to more clearly show the influence of each parameter of the thread teeth of the heat exchange tube on two indexes of the water pressure drop and the heat exchange efficiency of the heat exchange tube and 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 a single-tube heat exchanger, and the water pressure drop of the heat exchange tube and the heat exchange efficiency of the heat exchange tube are measured, so as to specifically explain the effects of different examples of the heat exchange tube with high heat exchange efficiency in embodiment 3. The helix angle α and the number of teeth of each exemplary heat exchange tube are shown in table 9N, tooth height h, tooth tip width WtWidth of tooth bottom WbAnd tube diameter D. In order to more intuitively show the effect of the heat exchange tube of the present application, in this embodiment, a group of embodiments comparing the heat exchange tube with a series of heat exchange tubes with high heat exchange efficiency of the present application is used as a group for performing a grouping comparison description, wherein the comparison heat exchange tubes 1-2 are all commercially available heat exchange tubes.
TABLE 9 different parameters of the individual heat exchange tubes
The water pressure drop and the heat exchange efficiency of the comparison heat exchange tube 1 and the heat exchange tubes 21-26 with high heat exchange efficiency and the comparison heat exchange tube 2 and the heat exchange tubes 27-35 with high heat exchange efficiency in unit length at the same flow velocity are detected, and the weight of the respective heat exchange tubes is detected. For convenience, in the form of tables, tables 10 to 11 show the proportional relationship between each group of heat exchange tubes with high heat exchange efficiency and the corresponding comparison heat exchange tubes in terms of three indexes, i.e., the water pressure drop, the heat exchange efficiency and the weight (weight for short) of the heat exchange tube per unit length. Wherein, table 10 shows the proportional relationship between the comparative heat exchange tube 1 and the heat exchange tubes 21 to 26 with high heat exchange efficiency in table 9 at each index, and table 11 shows the proportional relationship between the comparative heat exchange tube 2 and the heat exchange tubes 27 to 35 with high heat exchange efficiency 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 with 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 the table 10, for the heat exchange tubes with the tube diameter of 19.05mm, the heat exchange efficiency of the heat exchange tubes 21-26 with high heat exchange efficiency in this embodiment can be improved by about 5% -7% compared with the comparative heat exchange tube 1, for example, the heat exchange tubes 21 and 23 with high heat exchange efficiency are both improved by more than 7%. And the water pressure drop and the weight of the heat exchange tubes 21-26 with high heat exchange efficiency in the embodiment can be basically maintained at a level similar to that 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 of high heat exchange efficiency, in the case where the heat exchange efficiency is improved by about 5%, the water pressure drop is rather reduced, and the weight is also improved by only about 4% as compared with the comparative heat exchange tube 1.
As can be seen from table 11, for the heat exchange tubes with a tube diameter of 25.4mm, the heat exchange efficiency of the heat exchange tubes 27-35 with high heat exchange efficiency in this embodiment can be improved by about 5% -10% compared with the comparative heat exchange tube 2, for example, the heat exchange tubes 27 and 29 with high heat exchange efficiency are both improved by nearly 10%. And the water pressure drop and the weight of the heat exchange tubes 27-35 with high heat exchange efficiency in the embodiment can be basically maintained at the similar level as the comparison heat exchange tubes 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 of high heat exchange efficiency, in the case where the heat exchange efficiency is improved by 5% or more, the water pressure drop is rather reduced, and the weight is also improved by only within 4% as compared with the comparative heat exchange tube 2.
It can be seen that, compared with the corresponding comparative heat exchange tubes, the heat exchange tubes 21 to 35 with high heat exchange efficiency in the present embodiment can also improve the heat exchange efficiency while maintaining the water pressure drop and without significantly increasing the weight.
Therefore, although the heat exchange tubes of two different parameter ranges are provided in examples 2 and 3, it can be seen from tables 7 to 8 and tables 10 to 11 that the first heat exchange efficiency heat exchange tubes 1 to 20 of example 2 and the second heat exchange efficiency heat exchange tubes 21 to 35 of example 3 are each capable of optimizing the index of heat exchange efficiency of the heat exchange tubes with the weight of the heat exchange tubes per unit length kept within a certain range.
Application example of heat exchange pipe 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 temperature difference of the heat exchange of the heat exchanger, respectively, when the heat exchanger is designed by using different heat exchange tubes, which is used 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 of the present application, the number influence curve of the comparison 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 the curves 841 and 842 show the influence curves of the comparison heat exchange tube, and the curves 851 and 852 show the influence curves of the heat exchange tube 7 with high heat exchange efficiency. Wherein, the small temperature difference of the heat exchange of the ordinate in the figure represents the heat exchange efficiency of the heat exchange tube.
As a specific example, the design requirements for a heat exchanger are:
1. the heat exchange amount is as follows: 3516 kW;
2. length of the heat exchanger: 3.66 m;
3. the small temperature difference of heat exchange is less than or equal to 0.6 ℃;
4. the water pressure drop is less than or equal to 100 kPa.
As shown in fig. 8, when the heat exchanger is designed by using the conventional comparative heat exchange tube 1, the number of the heat exchange tubes is about 780 or more when the small 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, when the heat exchange small temperature difference is 0.6 ℃, the water pressure drop is about 93kPa, 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 temperature difference of heat exchange reaches below about 0.5 ℃.
Therefore, when the heat exchanger is designed by adopting the heat exchange tube 7 with high heat exchange efficiency in the embodiment 2, the design requirement of the heat exchanger can be met only by needing fewer heat exchange tubes.
In the embodiment shown in fig. 8, the heat exchanger is designed by using the heat exchange tubes 7 with high heat exchange efficiency, which is only used as an exemplary illustration to show the beneficial effect of designing the heat exchanger by using the heat exchange tubes with high heat exchange efficiency. In fact, 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 particular embodiments shown in the drawings, it should be understood that the heat exchange tubes of the present application may take many forms without departing from the spirit and scope of the teachings of the present application. Those of ordinary skill in the art will also realize that there are different ways of varying the details of the structures in the embodiments disclosed in this application that fall within the spirit and scope of the application and the claims.
Claims (16)
1. A heat exchange tube, its characterized in that: the heat exchange pipe (200) includes:
a tube (301), the tube (301) having an inner wall (302) and an axis (x), the tube (301) having an inlet (303) and an outlet (304) at both ends;
a plurality of thread teeth (316), the plurality of thread teeth (316) being arranged on the inner wall (302) of the tube body (301) in a spaced apart relationship, the plurality of thread teeth (316) extending helically around an 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 helix angle α of the thread teeth (316) and the number of teeth N of the thread teeth (316) satisfy:
(i) the helix angle alpha is 20-33 degrees, and the tooth number N is 39-65; or
(ii) The helix angle alpha is 30-43 DEG, and the number of teeth N is 45-70.
2. The heat exchange tube of claim 1, wherein:
the helix angle alpha of the thread teeth (316) and the number N of the thread teeth (316) satisfy (i), and the pipe diameter D of the pipe body (301) is 19.05 +/-1 mm.
3. The heat exchange tube of claim 2, wherein:
the cross section of the thread tooth (316) is trapezoidal;
wherein the width W of the bottom of the trapezoidal thread tooth (316)bSatisfies the following conditions:
The tooth height h of the trapezoidal thread tooth (316) satisfies:
The crest width W of the trapezoidal thread tooth (316)tSatisfies the following conditions:
4. A heat exchange tube according to claim 3, wherein:
the number N of the thread teeth (316) is 53, and the helix angle alpha of the thread teeth (316) is 30 degrees; and
the cross section of the thread tooth (316) is trapezoidal, and the tooth bottom width W of the trapezoidal thread tooth (316)bIs 0.313mm, the height h of the trapezoidal thread teeth (316) is 0.401mm, and the crest width W of the trapezoidal thread teeth (316) istIs 0.068 mm.
5. The heat exchange tube of claim 1, wherein:
the helix angle alpha of the thread teeth (316) and the number N of the thread teeth (316) satisfy (ii), and the pipe diameter D of the pipe body (301) is 25.4 +/-1 mm.
6. The heat exchange tube of claim 5, wherein:
the cross section of the thread tooth (316) is trapezoidal;
wherein the width W of the bottom of the trapezoidal thread tooth (316)bSatisfies the following conditions:
The tooth height h of the trapezoidal thread tooth (316) satisfies:
The crest width W of the trapezoidal thread tooth (316)tSatisfies the following conditions:
7. The heat exchange tube of claim 6, wherein:
the number N of the thread teeth (316) is 68, and the helix angle alpha of the thread teeth (316) is 30 degrees; and
the cross section of the thread tooth (316) is trapezoidal, and the tooth bottom width W of the trapezoidal thread tooth (316)bIs 0.454mm, the height h of the trapezoidal thread teeth (316) is 0.488mm, and the crest width W of the trapezoidal thread teeth (316)tIs 0.114 mm.
8. A heat exchange tube, its characterized in that: the heat exchange pipe (200) includes:
a tube (301), the tube (301) having an inner wall (302) and an axis (x), the tube (301) having an inlet (303) and an outlet (304) at both ends;
a plurality of thread teeth (316), the plurality of thread teeth (316) being arranged on the inner wall (302) of the tube body (301) in a spaced apart relationship, the plurality of thread teeth (316) extending helically around an 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 cross-sectional shape of the thread tooth (316) is trapezoidal, the number of teeth N of the thread tooth (316) and the width W of the bottom of the trapezoidal thread tooth (316) arebSatisfies the following conditions:
(i) the number of teeth N is 46-65, and the width of the tooth bottom Wb0.321-0.521 mm; or
(ii) The number of teeth N is 39-45, and the width W of the tooth bottomb0.523-0.545 mm; or
(iii) The number of teeth N is 59-70, and the width W of the tooth bottomb0.451-0.627 mm; or
(iv) The number of teeth N is 45-58, and the width W of the tooth bottombIs 0.628-0.707 mm.
9. The heat exchange tube of claim 8, wherein:
the width W of the bottom of the thread tooth (316)bAnd the number N of the thread teeth (316) satisfies (i) or (ii), and the pipe diameter D of the pipe body (301) is 19.05 + -1 mm.
10. The heat exchange tube of claim 9, wherein:
the width W of the bottom of the thread tooth (316)bAnd the number N of the thread teeth (316) satisfies (i);
the tooth height h of the trapezoidal thread tooth (316) is 0.235-0.553 mm; and/or
The crest width W of the trapezoidal thread tooth (316)t0.047-0.181 mm; and/or
The helix angle alpha of the thread teeth (316) is 30-55 degrees.
11. The heat exchange tube of claim 9, wherein:
the width W of the bottom of the thread tooth (316)bAnd the number N of the thread teeth (316) satisfies (ii);
the tooth height h of the trapezoidal thread tooth (316) is 0.355-0.523 mm; and/or
The crest width W of the trapezoidal thread tooth (316)t0.101-0.198 mm; and/or
The helix angle alpha of the thread teeth (316) is 30-55 degrees.
12. The heat exchange tube of claim 8, wherein:
the width W of the bottom of the thread tooth (316)bAnd the number of teeth N of the thread teeth (316) satisfies (iii) or (iv), and the pipe diameter D of the pipe body (301) is 25.4 + -1 mm.
13. The heat exchange tube of claim 12, wherein:
the width W of the bottom of the thread tooth (316)bAnd the number N of the thread teeth (316) satisfies (iii);
the tooth height h of the trapezoidal thread tooth (316) is 0.301-0.624 mm; and/or
The crest width W of the trapezoidal thread tooth (316)t0.073-0.246 mm; and/or
The helix angle alpha of the thread teeth (316) is 30-55 degrees.
14. The heat exchange tube of claim 12, wherein:
the width W of the bottom of the thread tooth (316)bAnd the number N of the thread teeth (316) satisfies (iv);
the tooth height h of the trapezoidal thread teeth (316) is 0.447-0.634 mm; and/or
The crest width W of the trapezoidal thread tooth (316)t0.097-0.269 mm; and/or
The helix angle alpha of the thread teeth (316) is 30-55 degrees.
15. A heat exchanger, characterized by: the heat exchanger includes:
a heat exchange tube (200) according to any one of claims 1-14.
16. An air conditioning system characterized by: the air conditioning system (150) comprises:
a compressor (110), a condenser (120), a throttling device (130) and an evaporator (140) which are in fluid connection in sequence; wherein at least one of the condenser (120) and the evaporator (140) employs the heat exchanger of claim 15.
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2021057916A1 (en) * | 2019-09-27 | 2021-04-01 | 约克（无锡）空调冷冻设备有限公司 | Heat exchange pipe, heat exchanger and air conditioning system using heat exchanger |
| CN113702783A (en) * | 2021-08-27 | 2021-11-26 | 陕西省地方电力（集团）有限公司 | Cable partial discharge detection method, system, equipment and medium |
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2019
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2021057916A1 (en) * | 2019-09-27 | 2021-04-01 | 约克（无锡）空调冷冻设备有限公司 | Heat exchange pipe, heat exchanger and air conditioning system using heat exchanger |
| CN114729794A (en) * | 2019-09-27 | 2022-07-08 | 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 |
| CN114729794B (en) * | 2019-09-27 | 2024-02-27 | 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 |
| CN113702783A (en) * | 2021-08-27 | 2021-11-26 | 陕西省地方电力（集团）有限公司 | Cable partial discharge detection method, system, equipment and medium |
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