Heat exchange tube, heat exchanger and air conditioner

Abstract

The present disclosure provides a heat exchange tube, a heat exchanger and an air conditioner. The heat exchange tube includes: the outer wall surface of a tube base body is provided with a first fin and a second fin; the first fin includes a fin root perpendicular to the outer wall surface of the tube base body and a fin portion parallel to the outer wall surface of the tube base body; the second fin is arranged on the tube base body covered by the fin portion, and the end of the second fin penetrates out of the outside of the fin portion, and the fin portion is provided with a first cut portion for the second fin to pass through. The heat exchange tube of the present disclosure significantly increases the external heat exchange area of the heat exchange tube. The design of the first cut portion extending upward from the tube base body through the first fin makes full use of the processable space on the surface of the heat exchange tube. Under the refrigeration condition, the semi-closed structure formed by the first fin is conducive to the evaporation of the liquid refrigerant, and the second fin increases the surface unevenness to strengthen heat exchange. When in the heating condition, the second fin can quickly pierce the condensate film, and the condensate can be quickly discharged to the outer wall surface of the tube base body.

Description

Technical Field

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

[0002] In a central air-conditioning water-cooled heat pump heat exchanger, the heat transfer coefficient inside the tube is enhanced by the internal thread structure of the tube. Due to the limitations of the existing tube internal extrusion forming process that can be economically processed on a large scale, the improvement of the internal efficiency of the heat exchange tube is limited. Outside the heat exchange tube, due to the particularity that the refrigeration and heating conditions of the heat pump working conditions can be switched, it is required that the external fin type of the heat exchange tube has a structure that can meet both enhanced evaporation and enhanced condensation. According to the existing evaporation and condensation theories, the fin type for enhanced evaporation tends to form a semi-closed cavity structure feature, and the fin type for enhanced condensation tends to form a structure feature of a tall, thin, and sharp point. The former is beneficial to the nucleation and growth of bubbles, and the latter is beneficial to the rapid discharge of condensate.

[0003] The known heat exchange tubes cannot meet the requirements of both enhanced evaporation and enhanced condensation, and the structure needs to be optimized. Summary of the Invention

[0004] Therefore, the technical problem to be solved by the present disclosure is that the known heat exchange tubes cannot meet the requirements of both enhanced evaporation and enhanced condensation, and the structure needs to be optimized, so as to provide a heat exchange tube, a heat exchanger, and an air conditioner.

[0005] To solve the above problems, the present disclosure provides a heat exchange tube, including:

[0006] A tube base;

[0007] The outer wall surface of the tube base is provided with a first fin and a second fin;

[0008] The first fin includes a fin root perpendicular to the outer wall surface of the tube base, and a fin portion parallel to the outer wall surface of the tube base, and the fin portion is arranged at the end of the fin root;

[0009] The second fin is arranged on the tube base covered by the fin portion, and the end of the second fin extends out of the fin portion, and the fin portion is provided with a first cut portion for the second fin to pass through.

[0010] The object of the present disclosure and the technical measures to solve its technical problems can be further realized by the following technical measures.

[0011] Optionally, a fin tip is provided on the side of the fin portion facing away from the tube base, and the fin tip is perpendicular to the outer wall surface of the tube base.

[0012] Optionally, the dimension of the root portion of the fin along the axial direction of the tube base is the thickness L1 of the root portion of the fin, satisfying L1 = 0.05 mm - 0.2 mm; the dimension of the second fin along the axial direction of the tube base is the thickness L2 of the second fin, satisfying L2 = 0.05 mm - 0.2 mm; the dimension of the tip portion of the fin along the axial direction of the tube base is the thickness L6 of the tip portion of the fin, satisfying L6 = 0.05 mm - 0.2 mm.

[0013] Optionally, the dimension of the tip portion of the fin along the direction perpendicular to the outer wall surface of the tube base is the thickness H4 of the tip portion of the fin, satisfying H4 = 0.05 mm - 0.2 mm.

[0014] Optionally, the dimension of the first fin along the axial direction of the tube base is the thickness L3 of the first fin, satisfying L3 = 0.1 mm - 0.4 mm.

[0015] Optionally, the distance from the end of the second fin to the outer wall surface of the tube base is the height H2 of the second fin, and the distance from the end of the tip portion of the fin to the outer wall surface of the tube base is the height H1 of the first fin, satisfying H1 = H2 = 0.5 mm - 1.2 mm.

[0016] Optionally, the distance from the end of the tip portion of the fin to the side of the fin portion facing away from the tube base is the height H3 of the tip portion of the fin, satisfying H3 = 0.1 mm - 0.5 mm.

[0017] Optionally, the distance L4 along the axial direction of the projection of the tip portion of the fin and the root portion of the fin on the outer wall surface of the tube base satisfies L4 = 0.055 mm - 0.2 mm.

[0018] Optionally, the distance L5 along the axial direction of the projection of the second fin and the root portion of the fin on the outer wall surface of the tube base satisfies L5 = 0.125 mm - 0.25 mm.

[0019] Optionally, the dimension of the first cut portion along the axial direction of the tube base is the depth L7 of the first cut portion, satisfying L7 = 0.05 mm - 0.35 mm.

[0020] Optionally, a second cut portion is provided on the tip portion of the fin.

[0021] Optionally, the dimension of the second cut portion along the direction perpendicular to the outer wall surface of the tube base is the depth H5 of the second cut portion, satisfying H5 = 0.05 mm - 0.5 mm; the dimension along the circumferential direction of the tube base of the bottom of the second cut portion is the bottom width L11 of the second cut portion, satisfying L11 = 0.02 mm - 0.2 mm; the included angle θ1 between the two side walls of the second cut portion satisfies θ1 = 0 - 90°.

[0022] Optionally, a pit structure is further provided on the outer wall surface of the tube base covered by the fin portion.

[0023] Optionally, there are multiple first fins, and the multiple first fins are arranged circumferentially along the outer wall surface of the tube base body and respectively extend spirally along the axis of the tube base body on the outer wall surface of the tube base body; there are multiple second fins, and the multiple second fins are arranged circumferentially along the outer wall surface of the tube base body and respectively extend spirally along the axis of the tube base body on the outer wall surface of the tube base body;

[0024] The number of the first fins is equal to the number of the second fins.

[0025] Optionally, a third cut portion is provided between adjacent two fin tips. The dimension of the third cut portion in the direction perpendicular to the outer wall surface of the tube base body is the depth H6 of the third cut portion, and H6 = 0.05 mm - 0.5 mm is satisfied; the dimension of the bottom of the third cut portion in the circumferential direction of the tube base body is the bottom width L12 of the third cut portion, and L12 = 0.02 mm - 0.2 mm is satisfied; the included angle θ2 between the two side walls of the third cut portion satisfies θ2 = 0 - 90°.

[0026] Optionally, the center distance L10 between adjacent two second cut portions satisfies L10 = 0.3 mm - 1.2 mm.

[0027] Optionally, the spacing L8 between adjacent two second fins satisfies L8 = 0.3 mm - 1.2 mm.

[0028] Optionally, the first cut portion is at least one of a trapezoid, an arc, and a V shape.

[0029] Optionally, a flow guiding groove is provided on the side surface of the fin portion facing away from the tube base body, and the flow guiding groove is at least one of a straight shape, a V shape, and an X shape.

[0030] Optionally, an inner rib structure is provided on the inner wall surface of the tube base body. There are multiple inner rib structures, and the multiple inner rib structures are arranged circumferentially along the inner wall surface of the tube base body and respectively extend spirally along the axis of the tube base body on the inner wall surface of the tube base body.

[0031] A heat exchanger uses the above heat exchange tube.

[0032] An air conditioner uses the above heat exchange tube.

[0033] The heat exchange tube, the heat exchanger, and the air conditioner provided by the present disclosure at least have the following beneficial effects:

[0034] For the heat exchange tube of the present disclosure, the combined structure of the Γ-shaped first fins and the needle-shaped second fins is adopted, which significantly increases the heat exchange area outside the heat exchange tube. The design of the first cut portion extending upward from the tube base body through the first fins makes full use of the processable space on the surface of the heat exchange tube.

[0035] Under the refrigeration condition, the liquid refrigerant evaporates, and the semi-closed structure formed by the first fin is conducive to the evaporation process of nucleation, growth, and detachment of the liquid refrigerant. The intermittent and slender second fins increase the surface unevenness at that place, becoming efficient refrigerant vaporization core points and further strengthening the heat transfer.

[0036] When in the heating condition, the gaseous refrigerant outside the heat exchange tube condenses. The intermittent and slender second fins can quickly pierce the condensate film, and the condensate generated by the latter can be quickly discharged to the outer wall surface of the tube base body. The efficient condensation of the gaseous refrigerant and the timely discharge of the condensate reduce the stacking thickness of the refrigerant on the surface of the heat exchange tube, reduce the condensation thermal resistance, and improve the condensation heat transfer efficiency. Brief Description of the Drawings

[0037] Figure 1 It is a schematic structural view of the heat exchange tube of the present disclosure;

[0038] Figure 2 is Figure 1 the enlarged view at A in

[0039] Figure 3 It is the circumferential view of the heat exchange tube of the present disclosure along the tube base body;

[0040] Figure 4 It is the axial view of the heat exchange tube of the present disclosure along the tube base body;

[0041] Figure 5 It is the radial view of the heat exchange tube of the present disclosure along the tube base body;

[0042] Figure 6 It is a schematic structural view of the diversion groove of the heat exchange tube of the present disclosure.

[0043] The reference numerals are shown as:

[0044] 1. Tube base body; 2. First fin; 3. Second fin; 4. Fin root; 5. Fin part; 6. First cut part; 7. Fin tip; 8. Second cut part; 9. Pit structure; 10. Third cut part; 11. Diversion groove; 12. Inner rib structure. Detailed Embodiments

[0045] To make the purpose, technical solutions, and advantages of the present disclosure clearer, the technical solutions of the present disclosure will be clearly and completely described below in conjunction with specific embodiments of the present disclosure and the corresponding drawings. Obviously, the described embodiments are only a part of the embodiments of the present disclosure, rather than all the embodiments. Based on the embodiments in the present disclosure, all other embodiments obtained by those of ordinary skill in the art without creative efforts belong to the scope of protection of the present disclosure.

[0046] Combined with Figures 1 to 6As shown in the figure, this embodiment discloses a heat exchange tube, including: a tube base body 1; a first fin 2 and a second fin 3 are provided on the outer wall surface of the tube base body 1; the first fin 2 includes a fin root 4 perpendicular to the outer wall surface of the tube base body 1, and a fin portion 5 parallel to the outer wall surface of the tube base body 1. The fin portion 5 is arranged at the end of the fin root 4, and the two form a Γ-shaped structure; the second fin 3 is arranged on the tube base body 1 covered by the fin portion 5, and the end of the second fin 3 penetrates to the outside of the fin portion 5, and a first cut portion 6 for the second fin 3 to pass through is provided on the fin portion 5.

[0047] For the heat exchange tube of this embodiment, the combined structure of the Γ-shaped first fin 2 and the needle-shaped second fin 3 significantly increases the external heat exchange area of the heat exchange tube. The design of the first cut portion 6 extending upward from the tube base body 1 through the first fin 2 makes full use of the processable space on the surface of the heat exchange tube.

[0048] Under the refrigeration condition, the liquid refrigerant evaporates. The semi-closed structure formed by the first fin 2 is conducive to the evaporation process of the liquid refrigerant for nucleation, growth, and detachment. The upward-extending intermittent and slender second fin 3 increases the surface unevenness at this place, becoming an efficient refrigerant vaporization core point and further strengthening the heat exchange.

[0049] Under the heating condition, the gaseous refrigerant outside the heat exchange tube condenses. The intermittent and slender second fin 3 can quickly pierce the condensate film, and the condensate generated by the latter can be quickly discharged to the outer wall surface of the tube base body 1. The efficient condensation of the gaseous refrigerant and the timely discharge of the condensate reduce the accumulation thickness of the refrigerant on the surface of the heat exchange tube, reduce the condensation thermal resistance, and improve the condensation heat exchange efficiency.

[0050] In some embodiments, a fin tip 7 is provided on the side of the fin portion 5 facing away from the tube base body 1, and the fin tip 7 is arranged perpendicular to the outer wall surface of the tube base body 1. Under the heating condition, the fin tip 7 can quickly pierce the condensate film, and the condensate generated can also be quickly discharged to the outer wall surface of the tube base body 1.

[0051] In some embodiments, the dimension of the fin root 4 along the axial direction of the tube base body 1 is the thickness L1 of the fin root 4, satisfying L1 = 0.05 mm - 0.2 mm; the dimension of the second fin 3 along the axial direction of the tube base body 1 is the thickness L2 of the second fin 3, satisfying L2 = 0.05 mm - 0.2 mm; the dimension of the fin tip 7 along the axial direction of the tube base body 1 is the thickness L6 of the fin tip 7, satisfying L6 = 0.05 mm - 0.2 mm. In some embodiments, the dimension of the fin tip 7 along the direction perpendicular to the outer wall surface of the tube base body 1 is the thickness H4 of the fin tip 7, satisfying H4 = 0.05 mm - 0.2 mm. When the shape and size of the first fin 2 and the second fin 3 are within the above range, the heat exchange tube is convenient to process and can realize large-scale processing. At the same time, the heat exchange tube with this shape has high evaporation and condensation performance.

[0052] In some embodiments, L1 = L2 = L6 = H4 = 0.12 mm, and at this time, the heat exchange tube has the best effect.

[0053] In some embodiments, the dimension of the first fin 2 along the axial direction of the tube base 1 is the thickness L3 of the first fin 2, and L3 = 0.1 mm - 0.4 mm is satisfied. When the shape and dimension of the fin are within the above range, the heat exchange tube is convenient to process and large-scale processing can be realized. At the same time, the heat exchange tube with this shape has high evaporation and condensation performance.

[0054] In some embodiments, L3 = 0.25 mm, and at this time, the heat exchange tube has the best effect.

[0055] In some embodiments, the distance from the end of the second fin 3 to the outer wall surface of the tube base 1 is the height H2 of the second fin 3, and the distance from the end of the fin tip 7 to the outer wall surface of the tube base 1 is the height H1 of the first fin 2, and H1 = H2 = 0.5 mm - 1.2 mm is satisfied. When the shape and dimension of the fin are within the above range, the heat exchange tube is convenient to process and large-scale processing can be realized. At the same time, the heat exchange tube with this shape has high evaporation and condensation performance.

[0056] In some embodiments, H1 = H2 = 1.0 mm, and at this time, the heat exchange tube has the best effect.

[0057] In some embodiments, the distance from the end of the fin tip 7 to the side surface of the fin part 5 facing away from the tube base 1 is the height H3 of the fin tip 7, and H3 = 0.1 mm - 0.5 mm is satisfied. When the shape and dimension of the fin are within the above range, the heat exchange tube is convenient to process and large-scale processing can be realized. At the same time, the heat exchange tube with this shape has high evaporation and condensation performance.

[0058] In some embodiments, H3 = 0.4 mm, and at this time, the heat exchange tube has the best effect.

[0059] In some embodiments, the distance L4 along the axial direction of the tube base 1 between the projections of the fin tip 7 and the fin root 4 on the outer wall surface of the tube base 1 satisfies L4 = 0.055 mm - 0.2 mm. When the shape and dimension of the fin are within the above range, the heat exchange tube is convenient to process and large-scale processing can be realized. At the same time, the heat exchange tube with this shape has high evaporation and condensation performance.

[0060] In some embodiments, L4 = 0.06 mm, and at this time, the heat exchange tube has the best effect.

[0061] In some embodiments, the distance L5 along the axial direction of the tube base 1 between the projection of the second fin 3 and the fin root 4 on the outer wall surface of the tube base 1 satisfies L5 = 0.125 mm - 0.25 mm. When the shape and size of the fin are within the above range, the heat exchange tube is convenient to process and can be mass-produced. At the same time, the heat exchange tube with this shape has high evaporation and condensation performance.

[0062] In some embodiments, L5 = 0.24 mm, and at this time, the heat exchange tube has the best effect.

[0063] In some embodiments, the dimension along the axial direction of the tube base 1 of the first cut portion 6 is the depth L7 of the first cut portion 6, and it satisfies L7 = 0.05 mm - 0.35 mm. When the shape and size of the fin are within the above range, the heat exchange tube is convenient to process and can be mass-produced. At the same time, the condensate on the second fin 3 can quickly reach the outer wall surface of the tube base 1, and the heat exchange tube with this shape has high evaporation and condensation performance.

[0064] In some embodiments, L7 = 0.18 mm, and at this time, the heat exchange tube has the best effect.

[0065] In some embodiments, a second cut portion 8 is provided on the fin tip 7, so that the fin tip 7 forms an intermittent spiked structure, which can quickly pierce the condensate film and make it flow down quickly. Similarly, it increases the degree of surface unevenness at the fin portion 5 and provides efficient refrigerant vaporization core points.

[0066] In some embodiments, the dimension along the direction perpendicular to the outer wall surface of the tube base 1 of the second cut portion 8 is the depth H5 of the second cut portion 8, and it satisfies H5 = 0.05 mm - 0.5 mm; the dimension along the circumferential direction of the tube base 1 of the bottom of the second cut portion 8 is the bottom width L11 of the second cut portion 8, and it satisfies L11 = 0.02 mm - 0.2 mm; the included angle θ1 between the two side walls of the second cut portion 8 satisfies θ1 = 0 - 90°. When the shape of the second cut portion 8 is within the above range, the heat exchange tube is convenient to process and can be mass-produced. At the same time, the piercing effect on the condensate film is the best, and the heat exchange tube with this shape has high evaporation and condensation performance.

[0067] In some embodiments, L11 = 0.1 mm and θ1 = 45°, and at this time, the heat exchange tube has the best effect.

[0068] In some embodiments, a pit structure 9 is further provided on the outer wall surface of the tube base 1 covered by the fin portion 5. The pit structure 9 can be a rectangular pit and is evenly distributed along the outer peripheral wall of the tube base 1. Setting the pit structure 9 in the semi-closed structure formed by the first fin 2 can increase the density of the vaporization core and enhance the heat exchange efficiency.

[0069] In some embodiments, there are multiple first fins 2, and the multiple first fins 2 are arranged circumferentially along the outer wall surface of the tube base 1 and helically extend along the axis of the tube base 1 on the outer wall surface of the tube base 1; there are multiple second fins 3, and the multiple second fins 3 are arranged circumferentially along the outer wall surface of the tube base 1 and helically extend along the axis of the tube base 1 on the outer wall surface of the tube base 1; the number of the first fins 2 is equal to the number of the second fins 3. Thus, the fin portions 5 of adjacent first fins 2 form a spiral flow channel structure on the outer wall surface of the tube base 1, and the tall and thin second fins 3 are arranged at intervals and penetrate through the flow channel structure. The combined fins of this structure have both the effects of enhancing evaporation and enhancing condensation.

[0070] In some embodiments, the fin per inch (FPI) of the first fins 2 and the second fins 3 in the axial direction of the tube base 1 is 30 - 100, that is, the number of fins per inch is 30 - 100.

[0071] In some embodiments, the number of fins per inch is 56, and at this time, the heat exchange tube has the best effect.

[0072] In some embodiments, a third cut portion 10 is provided between adjacent two fin tip portions 7. The dimension of the third cut portion 10 in the direction perpendicular to the outer wall surface of the tube base 1 is the depth H6 of the third cut portion 10, and H6 satisfies H6 = 0.05 mm - 0.5 mm; the dimension of the bottom of the third cut portion 10 along the circumferential direction of the tube base 1 is the bottom width L12 of the third cut portion 10, and L12 satisfies L12 = 0.02 mm - 0.2 mm; the included angle θ2 between the two side walls of the third cut portion 10 satisfies θ2 = 0 - 90°. On the basis that the second cut portion 8 cuts the fin tip portions 7 of each first fin 2 into a discontinuous spike structure, in order to make the fin tip portions 7 of adjacent first fins 2 also discontinuous, the third cut portion 10 is designed, and the shape of the third cut portion 10 is preferably the same as the shape of the second cut portion 7.

[0073] In some embodiments, L12 = 0.1 mm and θ2 = 45°, and at this time, the heat exchange tube has the best effect.

[0074] In some embodiments, the center distance L10 between adjacent two second cut portions 8 satisfies L10 = 0.3 mm - 1.2 mm.

[0075] In some embodiments, L10 = 0.9 mm, and at this time, the heat exchange tube has the best effect.

[0076] In some embodiments, the spacing L8 between adjacent two second fins 3 satisfies L8 = 0.3 mm - 1.2 mm.

[0077] In some embodiments, L8 = 0.9 mm, and at this time, the heat exchange tube has the best effect.

[0078] In some embodiments, the first incision portion 6 is at least one of a trapezoid, an arc, and a V shape, so that the condensate can flow down quickly after being punctured by the second fin 3 and the fin tip portion 7.

[0079] In some embodiments, a diversion groove 11 is provided on the side of the fin portion 5 facing away from the tube base 1, and the diversion groove 11 is at least one of a straight shape, a V shape, and an X shape. Under the heating condition, the fin tip portion 7 can quickly puncture the condensate film, and the generated condensate can be quickly discharged to the outer wall surface of the tube base 1 through the diversion groove 11.

[0080] In some embodiments, the diversion grooves 11 are uniformly distributed on the surface of the fin tip portion 7, and the FPI satisfies 50 - 300, and at this time, the heat exchange tube has the best effect.

[0081] In some embodiments, an internal rib structure 12 is provided on the inner wall surface of the tube base 1. There are a plurality of internal rib structures 12, and the plurality of internal rib structures 12 are arranged circumferentially along the inner wall surface of the tube base 1 and helically extend along the axis of the tube base 1 on the inner wall surface of the tube base 1. The internal rib structure increases the heat transfer area of the inner wall surface of the heat exchange tube, enhances the disturbance effect of the medium inside the tube, strengthens the heat exchange effect inside the tube, and further enhances the overall performance of the heat exchange tube.

[0082] A heat exchanger employs the above heat exchange tube.

[0083] An air conditioner employs the above heat exchange tube.

[0084] It is easy for those skilled in the art to understand that, on the premise of no conflict, the above advantageous ways can be freely combined and superimposed.

[0085] The above are only the preferred embodiments of the present disclosure, and are not intended to limit the present disclosure. Any modifications, equivalent replacements, and improvements made within the spirit and principle of the present disclosure shall be included within the protection scope of the present disclosure. The above is only the preferred implementation manner of the present disclosure. It should be noted that for those of ordinary skill in the art in this technical field, several improvements and modifications can be made without departing from the technical principle of the present disclosure, and these improvements and modifications should also be regarded as within the protection scope of the present disclosure.

Claims

1. A heat exchange tube, characterized in that, Comprising: A tube base body (1); A first fin (2) and a second fin (3) are provided on the outer wall surface of the tube base body (1); The first fin (2) includes a fin root portion (4) perpendicular to the outer wall surface of the tube base body (1), and a fin portion (5) parallel to the outer wall surface of the tube base body (1), and the fin portion (5) is provided at the end of the fin root portion (4); The second fin (3) is provided on the tube base body (1) covered by the fin portion (5), and the end of the second fin (3) penetrates to the outside of the fin portion (5), and a first cut portion (6) for the second fin (3) to pass through is provided on the fin portion (5); A fin tip portion (7) is provided on the side surface of the fin portion (5) facing away from the tube base body (1), and the fin tip portion (7) is arranged perpendicular to the outer wall surface of the tube base body (1); The dimension of the fin root portion (4) along the axial direction of the tube base body (1) is the thickness L1 of the fin root portion (4), and it satisfies L1 = 0.05 mm - 0.2 mm; the dimension of the second fin (3) along the axial direction of the tube base body (1) is the thickness L2 of the second fin (3), and it satisfies L2 = 0.05 mm - 0.2 mm; the dimension of the fin tip portion (7) along the axial direction of the tube base body (1) is the thickness L6 of the fin tip portion (7), and it satisfies L6 = 0.05 mm - 0.2 mm.

2. The heat exchange tube according to claim 1, wherein, The dimension of the fin tip portion (7) in the direction perpendicular to the outer wall surface of the tube base body (1) is the thickness H4 of the fin tip portion (7), and it satisfies H4 = 0.05 mm - 0.2 mm.

3. The heat exchange tube according to claim 1, wherein The dimension of the first fin (2) along the axial direction of the tube base body (1) is the thickness L3 of the first fin (2), and it satisfies L3 = 0.1 mm - 0.4 mm.

4. The heat exchange tube according to claim 1, wherein The distance from the end of the second fin (3) to the outer wall surface of the tube base body (1) is the height H2 of the second fin (3), and the distance from the end of the fin tip portion (7) to the outer wall surface of the tube base body (1) is the height H1 of the first fin (2), and it satisfies H1 = H2 = 0.5 mm - 1.2 mm.

5. The heat exchange tube according to claim 1, characterized in that, The distance from the end of the fin tip portion (7) to the side surface of the fin portion (5) facing away from the tube base body (1) is the height H3 of the fin tip portion (7), and it satisfies H3 = 0.1 mm - 0.5 mm.

6. The heat exchange tube according to claim 1, wherein The distance L4 along the axial direction of the tube base body (1) of the projection of the fin tip portion (7) and the fin root portion (4) on the outer wall surface of the tube base body (1) satisfies L4 = 0.055 mm - 0.2 mm.

7. The heat exchange tube according to claim 1, wherein, The distance L5 along the axial direction of the tube base body (1) of the projection of the second fin (3) and the fin root portion (4) on the outer wall surface of the tube base body (1) satisfies L5 = 0.125 mm - 0.25 mm.

8. The heat exchange tube according to claim 1, characterized in that, The dimension of the first cut portion (6) along the axial direction of the tube base body (1) is the depth L7 of the first cut portion (6), and it satisfies L7 = 0.05 mm - 0.35 mm.

9. The heat exchange tube according to claim 1, characterized in that, A second cut portion (8) is provided on the fin tip portion (7).

10. The heat exchange tube according to claim 9, wherein, The dimension of the second cut portion (8) in the direction perpendicular to the outer wall surface of the tube base body (1) is the depth H5 of the second cut portion (8), satisfying H5 = 0.05 mm - 0.5 mm; the dimension of the bottom of the second cut portion (8) in the circumferential direction of the tube base body (1) is the bottom width L11 of the second cut portion (8), satisfying L11 = 0.02 mm - 0.2 mm; the included angle θ1 between the two side walls of the second cut portion (8) satisfies θ1 = 0 - 90°.

11. The heat exchange tube according to claim 1, wherein A pit structure (9) is further provided on the outer wall surface of the tube base body (1) covered by the fin portion (5).

12. The heat exchange tube according to claim 1, characterized in that, There are multiple first fins (2), and the multiple first fins (2) are arranged circumferentially on the outer wall surface of the tube base body (1) and respectively extend spirally on the outer wall surface of the tube base body (1) along the axis of the tube base body (1); there are multiple second fins (3), and the multiple second fins (3) are arranged circumferentially on the outer wall surface of the tube base body (1) and respectively extend spirally on the outer wall surface of the tube base body (1) along the axis of the tube base body (1). The number of the first fins (2) is equal to the number of the second fins (3).

13. The heat exchange tube according to claim 12, characterized in that, A third cut portion (10) is provided between two adjacent fin tip portions (7). The dimension of the third cut portion (10) in the direction perpendicular to the outer wall surface of the tube base body (1) is the depth H6 of the third cut portion (10), satisfying H6 = 0.05 mm - 0.5 mm; the dimension of the bottom of the third cut portion (10) in the circumferential direction of the tube base body (1) is the bottom width L12 of the third cut portion (10), satisfying L12 = 0.02 mm - 0.2 mm; the included angle θ2 between the two side walls of the third cut portion (10) satisfies θ2 = 0 - 90°.

14. The heat exchange tube according to claim 12, characterized in that, The center distance L10 between two adjacent second cut portions (8) satisfies L10 = 0.3 mm - 1.2 mm.

15. The heat exchange tube according to claim 12, wherein, The spacing L8 between two adjacent second fins (3) satisfies L8 = 0.3 mm - 1.2 mm.

16. The heat exchange tube according to claim 1, characterized in that, The first cut portion (6) is at least one of a trapezoid, an arc, and a V shape.

17. The heat exchange tube according to claim 1, wherein, A flow guiding groove (11) is provided on the side surface of the fin portion (5) facing away from the tube base body (1), and the flow guiding groove (11) is at least one of a straight shape, a V shape, and an X shape.

18. The heat exchange tube according to any one of claims 1-17, characterized in that, Internal rib structures (12) are provided on the inner wall surface of the tube base body (1). There are multiple internal rib structures (12), and the multiple internal rib structures (12) are arranged circumferentially on the inner wall surface of the tube base body (1) and respectively extend spirally on the inner wall surface of the tube base body (1) along the axis of the tube base body (1).

19. A heat exchanger, characterized in that, Use the heat exchange tube according to any one of claims 1 - 18.

20. An air conditioner, characterized in that, Use the heat exchange tube according to any one of claims 1 - 18.

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