Heat exchanger and air conditioner

Abstract

The present invention discloses a heat exchanger and an air conditioner. Among them, the heat exchanger includes a heat exchange tube for passing R32 refrigerant. The inner surface of the heat exchange tube is provided with tooth-shaped threads. The outer diameter of the heat exchange tube is 6.5 mm to 7.5 mm, the wall thickness t of the heat exchange tube is 0.5 mm to 1.8 mm, the tooth height h of the threads is 0.12 mm to 0.16 mm, the effective wall thickness of the heat exchange tube is 0.62 to 1.42, and the effective wall thickness is the value obtained by dividing the wall thickness of the heat exchange tube by the distance between two adjacent threads. The technical solution of the present invention has the characteristics of good safety in use and heat exchange performance of the heat exchanger.

Description

Technical Field

[0001] The present invention relates to the field of heat exchange, and particularly to a heat exchanger and an air conditioner. Background Art

[0002] A heat exchange tube is a tube body in which a heat exchange working medium needs to be arranged. By the heat exchange working medium flowing in the tube, the heat exchange process is accelerated, and it has the characteristic of high heat exchange efficiency. For example, an air conditioner heat exchanger improves the heat exchange efficiency by arranging a refrigerant in the heat exchange tube. With the improvement of users' requirements for air conditioner performance, the heat exchange performance of existing heat exchange tubes is increasingly difficult to meet users' needs. In order to improve the heat exchange performance of the heat exchange tube, structural modifications are usually made to the heat exchange tube. Structural modifications to the heat exchange tube are likely to cause changes in the safety performance of the heat exchange tube, and there is a risk of reducing the safety performance of the heat exchange tube. Summary of the Invention

[0003] The main object of the present invention is to propose a heat exchanger, aiming to improve the heat exchange performance of the heat exchanger while ensuring the safety performance of the heat exchange tube.

[0004] To achieve the above object, the heat exchanger proposed by the present invention includes a heat exchange tube for passing R32 refrigerant. The inner surface of the heat exchange tube is provided with teeth-shaped threads. The outer diameter of the heat exchange tube is 6.5 mm to 7.5 mm, the wall thickness of the heat exchange tube is 0.5 mm to 1.8 mm, the tooth height of the thread is 0.12 mm to 0.16 mm, the effective wall thickness of the heat exchange tube is 0.62 to 1.42, and the effective wall thickness is the value obtained by dividing the wall thickness of the heat exchange tube by the distance between two adjacent threads.

[0005] Optionally, the tooth height of the thread is 0.12 mm to 0.15 mm.

[0006] Optionally, the helix angle of the thread is 33° to 37°.

[0007] Optionally, the effective wall thickness is 0.78 to 1.42.

[0008] Optionally, the effective wall thickness is 0.81 to 1.42.

[0009] Optionally, the number of the threads is 56 to 70, and / or the width of the thread is 0.12 mm to 0.16 mm.

[0010] Optionally, the number of the threads is 56 to 68, and the width of the thread is 0.12 mm to 0.15 mm.

[0011] Optionally, the number of the threads is 56 to 62.

[0012] Optionally, the tooth apex angle of the thread is 10° to 16°.

[0013] Optionally, the tooth tip angle of the thread is 12° to 16°.

[0014] Optionally, the heat exchange tube is a copper heat exchange tube.

[0015] The present invention also provides an air conditioner, including the above heat exchanger.

[0016] The technical solution of the present invention sets the thread tooth height, which has a great influence on the heat exchange performance of the heat exchange tube, to 0.12 mm to 0.16 mm, having the characteristic of good heat exchange performance of the heat exchange tube. At the same time, the effective wall thickness, which has a significant influence on the internal stress of the heat exchange tube but has a weak influence on the heat exchange performance of the heat exchange tube, is set to 0.62 to 1.42, so that while the internal stress of the heat exchange tube decreases, the heat exchange performance of the heat exchange tube is not reduced. Finally, the heat exchanger with the heat exchange tube has good safety performance while improving the heat exchange performance. Description of the Drawings

[0017] In order to more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the following will briefly introduce the drawings required for use in the description of the embodiments or the prior art. Obviously, the drawings in the following description are only some embodiments of the present invention. For those of ordinary skill in the art, other drawings can be obtained based on the structures shown in these drawings without creative efforts.

[0018] Figure 1 It is a schematic structural diagram of the heat exchange tube of an embodiment of the heat exchanger of the present invention;

[0019] Figure 2 It is Figure 1 a partial structural diagram of the heat exchange tube in

[0020] Figure 3 It is a schematic diagram of the influence of the number of threads, thread width, tooth height, effective wall thickness, helix angle, and tooth tip angle on the heat exchange performance of the heat exchange tube;

[0021] Figure 4 It is a schematic diagram of the influence of the tooth height of the thread of the heat exchange tube on the heat exchange performance;

[0022] Figure 5 It is a schematic diagram of the influence of the number of threads, thread width, tooth height, effective wall thickness, helix angle, and tooth tip angle on the cost of the heat exchange tube;

[0023] Figure 6 It is a schematic diagram of the influence of the tooth height of the thread of the heat exchange tube on the cost;

[0024] Figure 7 It is a schematic diagram of the influence of the helix angle of the thread of the heat exchange tube on the heat exchange performance;

[0025] Figure 8Schematic diagram of the influence of the effective wall thickness of the heat exchange tube on the cost;

[0026] Figure 9 Schematic diagram of the influence of the number of threads, thread width, tooth height, effective wall thickness, helix angle, and tooth tip angle on the internal stress of the heat exchange tube;

[0027] Figure 10 Schematic diagram of the influence of the effective wall thickness of the heat exchange tube on the internal stress;

[0028] Figure 11 Schematic diagram of the influence of the width of the heat exchange tube thread on the internal stress;

[0029] Figure 12 Schematic diagram of the influence of the number of threads of the heat exchange tube on the internal stress;

[0030] Figure 13 Schematic diagram of the influence of the number of threads of the heat exchange tube on the cost;

[0031] Figure 14 Schematic diagram of the influence of the thread width of the heat exchange tube on the cost;

[0032] Figure 15 Schematic diagram of the influence of the tooth tip angle of the heat exchange tube thread on the heat exchange performance.

[0033] Explanation of the reference numerals in the attached drawings:

[0034] Label Name Label Name 100 Inner surface 200 Thread

[0035] The realization, functional features, and advantages of the object of the present invention will be further described in conjunction with the embodiments and with reference to the accompanying drawings. Detailed implementation manners

[0036] Next, the technical solutions in the embodiments of the present invention will be clearly and completely described in conjunction with the accompanying drawings in the embodiments of the present invention. Obviously, the described embodiments are only a part of the embodiments of the present invention, rather than all of the embodiments. All other embodiments obtained by those of ordinary skill in the art based on the embodiments of the present invention without creative efforts shall fall within the protection scope of the present invention.

[0037] It should be noted that if there are directional indications (such as up, down, left, right, front, back...) involved in the embodiments of the present invention, the directional indications are only used to explain the relative positional relationship and movement conditions between components in a specific posture (as shown in the accompanying drawings). If the specific posture changes, the directional indications will also change accordingly.

[0038] In addition, if the descriptions such as "first", "second", etc. are involved in the embodiments of the present invention, the descriptions of "first", "second", etc. are only for descriptive purposes and cannot be understood as indicating or implying their relative importance or implicitly specifying the quantity of the indicated technical features. Thus, the features defined with "first" and "second" may explicitly or implicitly include at least one such feature. In addition, the meaning of "and / or" appearing throughout the text is that it includes three parallel solutions. Taking "A and / or B" as an example, it includes solution A, or solution B, or the solution where A and B are satisfied simultaneously. In addition, the technical solutions between various embodiments can be combined with each other, but it must be based on the fact that those skilled in the art can implement it. When the combination of technical solutions is contradictory or cannot be implemented, it should be considered that such a combination of technical solutions does not exist and is not within the scope of protection required by the present invention.

[0039] The present invention provides a heat exchanger.

[0040] In the embodiments of the present invention, as Figure 1 , Figure 2 shown, the heat exchanger includes heat exchange tubes for passing R32 refrigerant. A toothed thread 200 is provided on the inner surface 100 of the heat exchange tubes. The outer diameter of the heat exchange tubes is 6.5 mm to 7.5 mm, the wall thickness t of the heat exchange tubes is 0.5 mm to 1.8 mm, and the tooth height h of the thread 200 is 0.12 mm to 0.16 mm. By providing the toothed thread 200 on the inner surface 100 of the heat exchange tubes, the surface area inside the heat exchange tubes can be effectively increased, so that the contact area between the heat exchange working medium in the heat exchange tubes and the heat exchange tubes is increased, which is beneficial to improving the heat exchange amount between the heat exchange tubes and the heat exchange working medium, thereby improving the heat exchange efficiency of the heat exchange tubes. In addition, the toothed thread 200 on the inner surface 100 of the heat exchange tubes is equivalent to providing reinforcing ribs on the inner surface 100 of the heat exchange tubes, which can enhance the mechanical strength of the heat exchange tubes. It should be noted that the width f of the thread 200 in this embodiment specifically refers to the width f of the end where the thread 200 is connected to the inner surface 100 of the heat exchange tubes, and the helix angle β refers to the angle between the plane where the thread 200 is located and the horizontal plane when the heat exchange tubes are horizontally placed.

[0041] Further, in this embodiment, the heat exchange tubes are copper heat exchange tubes. Copper heat exchange tubes have the characteristics of high heat exchange efficiency, good plasticity, and low processing difficulty. Of course, the heat exchange tubes in this embodiment are not limited to copper heat exchange tubes. In other embodiments, the heat exchange tubes can also be aluminum heat exchange tubes, which have the characteristics of light weight, high heat exchange efficiency, and easy processing.

[0042] To explore the magnitude of the influence of factors on the heat transfer performance of heat exchange tubes, six influencing factors were selected, namely the number of threads 200, the width f of the threads 200, the tooth height h of the threads 200, the effective wall thickness p of the heat exchange tube, the helix angle β of the threads 200, and the tooth apex angle α of the threads 200. Experiments were conducted through the experimental design method of finite element, and the experimental results are as Figure 3 shown. Figure 3 The influence weights of the above six influencing factors on the heat transfer performance are shown in the figure: the influence weight of the tooth apex angle α is 5.9%, the influence weight of the tooth height h of the threads 200 is 54.3%, the influence weight of the helix angle β of the threads 200 is 23.1%, the influence weight of the width f of the threads 200 is 0.2%, the influence weight of the effective wall thickness p of the heat exchange tube is 0.2%, and the influence weight of the number of threads 200 is 16.3%. The influence weights of the above six influencing factors on the internal stress from large to small are the tooth height h of the threads 200, the helix angle β, the number of threads 200, the tooth apex angle α, the width f of the threads 200, and the effective wall thickness p. Among them, the tooth height h of the threads 200 has the greatest influence on the heat transfer performance of the heat exchange tube, while the width f of the threads 200 and the effective wall thickness p basically have no influence on the heat transfer performance. It should be noted that the effective wall thickness p is the value obtained by dividing the wall thickness t by the spacing w between two adjacent threads 200.

[0043] Since the tooth height h of the threads 200 has the greatest influence on the heat transfer performance of the heat exchange tube, in order to optimize the heat transfer performance of the heat exchange tube, further, taking the tooth height h of the threads 200 as the input variable and the heat transfer performance of the heat exchange tube as the output variable, the influence of the tooth height h of the threads 200 on the heat transfer performance of the heat exchange tube was considered, and the experimental results are as Figure 4 shown. From Figure 4 it can be seen that the greater the increase in the tooth height h, the greater the improvement in the heat transfer performance of the heat exchange tube. The increase in the tooth height h of the internal threads 200 in the heat exchange tube can effectively increase the surface area of the threads 200, thereby increasing the internal surface area of the heat exchange tube. The heat transfer working medium in the heat exchange tube has a larger contact area with the heat exchange tube, thereby improving the heat transfer performance of the heat exchange tube.

[0044] Furthermore, to explore the magnitude of the influence of factors on the safety performance of heat exchange tubes, taking the internal stress of the heat exchange tube as an index and the six influencing factors of the number of threads 200, the width f of the threads 200, the tooth height h of the threads 200, the effective wall thickness p of the heat exchange tube, the helix angle β of the threads 200, and the tooth apex angle α of the threads 200 as input variables, experiments were conducted through the experimental design method of finite element, and the experimental results are as Figure 9 shown. Figure 9The influence weights of the above six influencing factors on the internal stress are shown as follows: the influence weight of the tooth tip angle α is 3.73%, the influence weight of the tooth height h of the thread 200 is 5.04%, the influence weight of the helix angle β of the thread 200 is 2.4%, the influence weight of the width f of the thread 200 is 35.64%, the influence weight of the effective wall thickness p of the heat exchange tube is 21.66%, and the influence weight of the number of the threads 200 is 31.35%. Analysis Figure 9 shows that the influence weights of the above six influencing factors on the cost from large to small are the width f of the thread 200, the number of the threads 200, the effective wall thickness p, the tooth height h, the tooth tip angle α, and the helix angle β. Among them, the width f of the thread 200, the number of the threads 200, and the effective wall thickness p are the factors that have the greatest influence on the internal stress of the heat exchange tube.

[0045] Combined with Figure 3 and Figure 9 it can be known that the change of the effective wall thickness p has basically no influence on the heat exchange performance of the heat exchange tube, but the change of the effective wall thickness p has an influence on the internal stress of the heat exchange tube. Therefore, the heat exchange performance of the heat exchange tube can be improved by changing the effective wall thickness p without affecting the heat exchange performance of the heat exchange tube.

[0046] Therefore, in this embodiment, the safety performance of the heat exchange tube is improved by changing the effective wall thickness p. In this embodiment, considering the relationship between the effective wall thickness p and the safety performance of the heat exchange tube, an experiment is carried out with the effective wall thickness p as the input quantity and the internal stress of the heat exchange tube as the output quantity. The test results are as Figure 10 shown. It can be seen from Figure 10 that as the effective wall thickness p increases, the internal stress in the heat exchange tube decreases, and the safety performance of the heat exchange tube is higher.

[0047] Therefore, in this embodiment, setting the tooth height h of the thread 200 to 0.12 mm to 0.16 mm can effectively optimize the heat exchange performance of the heat exchange tube. At the same time, in order to ensure the safety performance of the heat exchange tube, the effective wall thickness p is further limited to 0.62 to 1.42, which can effectively reduce the internal stress of the heat exchange tube to improve the safety performance of the heat exchange tube.

[0048] When the tooth height h of the thread 200 is too small, it will cause the internal surface area of the heat exchange tube to be too small, resulting in low heat exchange efficiency of the heat exchange tube. When the tooth height h is too high, it will cause the capacity of the heat exchange tube to be too small, resulting in a decrease in the flow rate of the heat exchange working medium in the heat exchange tube, and the heat or cold carried by the heat exchange working medium is reduced, affecting the heat exchange effect of the heat exchange tube. On the other hand, when the tooth height h of the thread 200 is too high, it will cause the weight of the heat exchange tube to be too large, which not only increases the consumption of materials during the manufacture of the heat exchange tube, but also increases the processing amount during the processing of the heat exchange tube, resulting in too high cost of the heat exchange tube.

[0049] This embodiment also considers the influence of the effective wall thickness p on the cost. In order to obtain the relationship between the effective wall thickness p and the cost of the heat exchange tube, an experiment is conducted with the effective wall thickness p as the input quantity and the cost of the heat exchange tube as the output quantity, and the experimental results are as follows Figure 8 shown. From Figure 8 it can be seen that the effective wall thickness p of the heat exchange tube is proportional to the cost of the heat exchange tube. When the effective wall thickness p is too large, it will lead to too high a cost of the heat exchange tube. Therefore, the effective wall thickness p is limited to be less than or equal to 1.42.

[0050] In this embodiment, the effective wall thickness p is further limited to 0.78 - 1.42, which can effectively reduce the internal stress of the heat exchange tube. Of course, the effective wall thickness p can be further limited to 0.81 - 1.42, which has the characteristic of high safety performance of the heat exchange tube.

[0051] Furthermore, while improving the heat exchange performance of the heat exchange tube, this embodiment also considers the cost of the heat exchange tube. In order to explore the magnitude of the influence of the factors on the heat exchange tube on the cost of the heat exchange tube, taking the weight of the heat exchange tube as an index, and taking the number of threads 200, the width f of the threads 200, the tooth height h of the threads 200, the effective wall thickness p of the heat exchange tube, the helix angle β of the threads 200, and the tooth tip angle α of the threads 200 as six influencing factors as input variables, an experiment is conducted through the experimental design method of finite element, and the experimental results are as follows Figure 5 shown. Figure 5 shows the influence weights of the above six influencing factors on the cost: the influence weight of the tooth tip angle α is 10.4%, the influence weight of the tooth height h of the threads 200 is 24.5%, the influence weight of the helix angle β of the threads 200 is 0.3%, the influence weight of the width f of the threads 200 is 17.22%, the influence weight of the effective wall thickness p of the heat exchange tube is 32.31%, and the influence weight of the number of threads 200 is 15.27%. Analyzing Figure 5 it can be seen that the influence weights of the above six influencing factors on the cost from large to small are the effective wall thickness p, the tooth height h, the width f of the threads 200, the number of threads 200, the tooth tip angle α, and the helix angle β. Among them, the effective wall thickness p and the tooth height h are the two factors that have the greatest influence on the cost of the heat exchange tube, and the helix angle β has basically no influence on the cost inside the heat exchange tube.

[0052] Furthermore, examine the relationship between the tooth height h of the threads 200 and the cost of the heat exchange tube. Taking the tooth height h as the input quantity and the cost of the heat exchange tube as the output quantity, the experimental results are as follows Figure 6 shown. From Figure 6It can be known that the higher the tooth height h of the thread 200 is, the greater the weight inside the heat exchange tube is. As the weight of the heat exchange tube increases, the cost of the heat exchange tube also increases. To further control the cost of the heat exchange tube, in this embodiment, the tooth height h of the thread 200 is set to 0.12 mm to 0.15 mm, which has the characteristic of low cost of the heat exchange tube.

[0053] It can be known from Figure 3 that the influence of the helix angle β of the thread 200 on the heat exchange performance of the heat exchange tube is second only to the tooth height h. To further improve the heat exchange performance of the heat exchange tube, the influence of the helix angle β on the heat exchange performance of the heat exchange tube is investigated, and the test results are as Figure 7 shown. It can be known from Figure 7 that the greater the increase in the angle of the helix angle β is, the greater the increase in the heat exchange performance inside the heat exchange tube is. The increase in the helix angle β makes the length of the thread 200 in the heat exchange tube per unit length increase, and the increase in the length of the thread 200 can increase the surface area in contact with the heat exchange working medium inside the heat exchange tube, which can effectively improve the heat exchange efficiency inside the heat exchange tube. In addition, the thread 200 has a guiding effect. When the angle of the helix angle β is too large, it will hinder the flow of the heat exchange working medium in the heat exchange tube, which is not conducive to the heat conduction of the heat exchange working medium. Moreover, if the angle of the thread 200 is too large, the processing difficulty of the heat exchange tube will be too large, resulting in a decrease in the production speed of the heat exchange tube. Therefore, in this embodiment, the helix angle β of the thread 200 is selected as 33° to 37°.

[0054] It can be known from Figure 9 that the width f of the thread 200 and the number of the thread 200 are the two factors that have the greatest influence on the stress of the heat exchange tube. In this embodiment, the width f is used as the input quantity and the stress of the heat exchange tube is used as the output quantity for testing, and the test results are as Figure 11 shown. It can be known from Figure 11 that when the width f is in the range of 0.12 mm to 0.16 mm, the stress fluctuation range of the heat exchange tube is small. When the width f is greater than 0.16 mm or when the width f is less than 0.12 mm, the stress inside the heat exchange tube decreases with the increase of the width f. When the width f is too small, the stress of the heat exchange tube is too large and the safety performance is poor. In addition, the space inside the heat exchange tube is limited, and if the width f of the heat exchange tube is too large, it will be difficult to set the thread 200. In this embodiment, the width f of the thread 200 is set to 0.12 mm to 0.16 mm, which has the characteristics of small stress inside the heat exchange tube and high safety performance of the heat exchange tube.

[0055] In this embodiment, the number of the thread 200 is used as the input quantity and the stress of the heat exchange tube is used as the output quantity for testing, and the test results are as Figure 12As shown, when the number of the threads 200 is in the range of 53 to 65, the internal stress of the heat exchange tube decreases with the increase of the number of the threads 200. When the number of the threads 200 is greater than 65, the internal stress of the heat exchange tube increases with the increase of the number of the threads 200. The internal stress of the heat exchange tube reaches the minimum value when the number of the threads 200 is 65. In this embodiment, the number of the threads 200 is set to be 56 to 70, which has the characteristic of small internal stress of the heat exchange tube.

[0056] The heat exchange tube described in this embodiment is not limited to the above technical solution. In other embodiments, it may also be that the width f of the threads 200 is set to be 0.12 mm to 0.16 mm, or the number of the threads 200 is 56 to 70. Controlling the width f of the threads 200 and the number of the threads 200 separately can also effectively control the internal stress in the heat exchange tube to improve the safety performance of the heat exchange tube.

[0057] It can be seen from Figure 5 that both the number of the threads 200 and the width f of the threads 200 have an impact on the cost of the heat exchange tube. Therefore, considering the relationship between the number of the threads 200 and the cost of the heat exchange tube, the result is as Figure 13 shown. The cost of the heat exchange tube increases with the increase of the number of the threads 200. In order to control the cost of the heat exchange tube, in this embodiment, the number of the threads 200 is further limited to 56 to 68. Of course, in order to further reduce the cost of the heat exchange tube, in this embodiment, the number of the threads 200 can be limited to 56 to 62, which has the obvious advantage of reducing the cost of the heat exchange tube.

[0058] Considering the relationship between the width f of the threads 200 and the cost of the heat exchange tube, the result is as Figure 14 shown. The cost of the heat exchange tube increases with the increase of the width f of the threads 200. In order to control the cost of the heat exchange tube, in this embodiment, the width f of the threads 200 is further limited to 0.12 mm to 0.15 mm, which has the advantage of reducing the cost of the heat exchange tube. And since the internal stress of the heat exchange tube remains basically unchanged when the width f of the threads 200 is in the range of 0.12 mm to 0.15 mm, limiting the width f of the threads 200 to 0.12 mm to 0.15 mm will not reduce the safety performance of the heat exchange tube.

[0059] It can be seen from Figure 3 that the tooth apex angle α of the threads 200 has an impact on the heat exchange performance of the heat exchange tube. In this embodiment, considering the relationship between the tooth apex angle α of the threads 200 and the heat exchange performance of the heat exchange tube, the obtained result is as Figure 15As shown, the greater the reduction in the tooth apex angle α of the heat exchange tube, the better the heat exchange performance of the heat exchange tube. When the angle of the tooth apex angle α is too large, the heat exchange performance of the heat exchange tube decreases. When the angle of the tooth apex angle α is too small, the mechanical properties of the top of the thread 200 are poor, and it is easy to be damaged during the processing, which is likely to reduce the processing speed and the yield rate of the heat exchange tube. Therefore, in this embodiment, the tooth apex angle α of the thread 200 is set to 10° to 16°.

[0060] It can be seen from Figure 9 that the tooth apex angle α of the thread 200 has an impact on the internal stress of the heat exchange tube. In this embodiment, the tooth apex angle α of the thread 200 is further set to 12° to 16°, which is beneficial to reducing the internal stress of the heat exchange tube and reducing the processing difficulty of the heat exchange tube.

[0061] Take the heat exchange tube with a tooth apex angle α of 24°, a tooth height h of the heat exchange tube of 0.145 mm, a helix angle β of the thread 200 of 30°, a width f of the thread 200 set to 0.154 mm, an effective wall thickness p of the heat exchange tube of 1.07, and 54 threads of the thread 200 as a comparison sample; take the heat exchange tube with a tooth apex angle α of 12°, a tooth height h of the heat exchange tube of 0.16 mm, a helix angle β of the thread 200 of 37°, a width f of the thread 200 set to 0.129 mm, an effective wall thickness p of the heat exchange tube of 1.38, and 62 threads of the thread 200 as the first implementation sample; take the heat exchange tube with a tooth apex angle α of 16°, a tooth height h of the heat exchange tube of 0.12 mm, a helix angle β of the thread 200 of 33°, a width f of the thread 200 set to 0.125 mm, an effective wall thickness p of the heat exchange tube of 0.823, and 56 threads of the thread 200 as the second implementation sample; detect the weight, internal stress and heat exchange performance when passing R32 refrigerant of the comparison sample, the first implementation sample and the second implementation sample. The detection results are shown in Table 1:

[0062] Table 1. Weight, internal stress and heat exchange performance of the comparison sample, the first implementation sample and the second implementation sample

[0063]

[0064] It can be seen from Table 1 that compared with the comparison sample, the heat exchange performance of the first implementation sample is 5632 W / (m 2 ·K), and the heat exchange performance of the second implementation sample is 5212 W / (m 2 ·K), which are significantly better than the heat exchange performance of the comparison sample of 4970 W / (m 2·K). In addition, the weight of the second implementation sample is less than that of the comparative sample, having a cost advantage; the stress of the first implementation sample is less than that of the comparative sample, and its safety performance is higher.

[0065] Specifically, the heat exchanger described in this embodiment further includes a plurality of fins, and the fins are connected to the heat exchange tubes. Of course, the heat exchanger may also be composed only of the heat exchange tubes.

[0066] The present invention also provides an air conditioner, which includes a heat exchanger. The specific structure of the heat exchanger refers to the above embodiment. Since this air conditioner adopts all the technical solutions of the above embodiments, it has at least all the beneficial effects brought by the technical solutions of the above embodiments, which will not be elaborated here one by one.

[0067] The above are only optional embodiments of the present invention, and do not limit the patent scope of the present invention accordingly. Any equivalent structural transformation made under the inventive concept of the present invention by using the content of the specification and drawings of the present invention, or direct / indirect application in other related technical fields is included in the patent protection scope of the present invention.

Claims

1. A heat exchanger, characterized in that, it includes heat exchange tubes for passing R32 refrigerant. The inner surface of the heat exchange tubes is provided with serrated threads. The outer diameter of the heat exchange tubes is 6.5 mm to 7.5 mm, the wall thickness of the heat exchange tubes is 0.5 mm to 1.8 mm, the tooth height of the threads is 0.12 mm to 0.16 mm, the effective wall thickness of the heat exchange tubes is 0.78 to 1.42, and the effective wall thickness is the value obtained by dividing the wall thickness of the heat exchange tubes by the distance between the roots of two adjacent threads; the helix angle of the threads is 33° to 37°; the heat exchange tubes are heat exchange copper tubes or heat exchange aluminum tubes.

2. The heat exchanger according to claim 1, characterized in that, the tooth height of the threads is 0.12 mm to 0.15 mm.

3. The heat exchanger according to claim 1, characterized in that, the effective wall thickness is 0.81 to 1.

42.

4. The heat exchanger according to claim 3, characterized in that, the number of the threads is 56 to 70, and / or the width of the threads is 0.12 mm to 0.16 mm.

5. The heat exchanger according to claim 4, characterized in that, the number of the threads is 56 to 68, and the width of the threads is 0.12 mm to 0.15 mm.

6. The heat exchanger according to claim 5, characterized in that, the number of the threads is 56 to 62.

7. The heat exchanger according to claim 5, characterized in that, the tooth apex angle of the threads is 10° to 16°.

8. The heat exchanger according to claim 7, characterized in that, the tooth apex angle of the threads is 12° to 16°.

9. An air conditioner, characterized in that, it includes the heat exchanger according to any one of claims 1 to 8.

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