Heat exchange tube, horizontal shell and tube heat exchanger and heat pump air conditioning unit

Abstract

The invention provides a heat exchange tube, a horizontal shell and tube heat exchanger and a heat pump air conditioning unit. The heat exchange tube comprises a first tube body and a plurality of first fins which are connected to the outside of the first tube body and are arranged at intervals on the first tube body. Each first fin comprises a fin root portion, a fin top portion and a transverse fin portion protruding from the top portion of the fin root portion in the direction away from the fin root portion. The transverse fin part is arranged on at least one side of the first fin in the thickness direction of the first fin and comprises a plurality of fin tables arranged in the extending direction of the first fin at intervals. The first fin further comprises a plurality of ailerons, every two ailerons correspond to one fin table, and the ailerons are located on the two sides, in the extending direction of the first fin, of the corresponding fin tables respectively. The ailerons are connected to the fin root part and protrude towards the direction away from the fin root part in the mode that the ailerons and the fin root part form an angle, and each fin table, the two corresponding ailerons, the fin root part and the first pipe body form a semi-closed evaporation cavity with an opening in the side away from the fin root part.

Description

Technical Field

[0001] The present disclosure relates to the technical field of heat exchange equipment, and in particular to a heat exchange tube, a horizontal shell and tube heat exchanger, and a heat pump air-conditioning unit. Background Art

[0002] Both the condenser and the evaporator are heat exchangers, and the refrigerant circulates in the heat exchanger through phase change to achieve heat transfer and transfer. The liquid refrigerant entering the evaporator absorbs external heat in a low-pressure environment and vaporizes into a low-temperature, low-pressure gas. The gaseous refrigerant output from the evaporator is pressurized by the compressor to form a high-temperature, high-pressure gas, and is transported to the condenser. The high-temperature, high-pressure gas releases heat through heat exchange with the external medium in the condenser and gradually condenses into a high-pressure liquid refrigerant. Next, the liquid refrigerant flows through a throttling device (such as an expansion valve) to reduce pressure and temperature. The refrigerant after pressure reduction and temperature reduction returns to the evaporator to start the next cycle. This process continuously completes the absorption, transfer and release of heat through the periodic change of the refrigerant state (liquid → gas → liquid) and pressure regulation, ultimately achieving the cooling or heating goals.

[0003] Evaporation and condensation are inverse processes in the phase-change heat transfer process: Condensation condenses the gaseous refrigerant outside the heat exchange tubes within the heat exchanger into a liquid, while evaporation evaporates the liquid refrigerant outside the heat exchange tubes to form a gas. Evaporators and condensers typically utilize horizontal shell-and-tube heat exchangers, capable of absorbing heat during vaporization and releasing heat during liquefaction, respectively. Due to fundamental differences in the operating parameters and thermodynamic boundary conditions of condensers and evaporators, the fin designs of the evaporation and condensation tubes differ significantly to achieve the respective evaporation and condensation effects.

[0004] In related art, evaporation heat exchange tubes exhibit over 30% lower performance than condensation heat exchange tubes in condensation performance tests, and condensation heat exchange tubes exhibit over 35% lower performance than existing evaporation heat exchange tubes in evaporation performance tests. Therefore, while horizontal shell-and-tube heat exchangers offer high heat exchange efficiency for single-use applications (evaporation or condensation), traditional horizontal shell-and-tube heat exchangers are difficult to use in heat exchange equipment that combines cooling and heating functions (e.g., heat pump air conditioners) to improve heat exchange efficiency, as the heat exchange tubes cannot perform both heat absorption and heat release.

[0005] To address the aforementioned issues, a related art provides a heat exchange tube for both condensation and evaporation. The fins of this heat exchange tube include a fin base, a fin top, and transverse fin sections protruding from the top of the fin base toward the sides of the fin. The transverse fin sections form condensation channels between the fin tops for condensation and channels between the fin bases for evaporation, thereby enabling the heat exchange tube to perform both evaporation and condensation functions. However, this heat exchange tube has low evaporation heat exchange efficiency. Summary of the Invention

[0006] The purpose of the present disclosure is to provide a heat exchange tube, a horizontal shell-and-tube heat exchanger, and a heat pump air conditioner unit, aiming to solve the problem of low evaporation heat exchange efficiency of the heat exchange tube that can be used for both condensation and evaporation.

[0007] The present disclosure provides a heat exchange tube in a first aspect, including a first tube body and a plurality of first fins connected to the outside of the first tube body and spaced apart. The first fins include fin roots, fin tops, and transverse fin parts protruding from the top of the fin roots in a direction away from the fin roots.

[0008] The transverse fin parts are arranged on at least one side in the thickness direction of the first fins, and include a plurality of fin platforms spaced apart along the extending direction of the first fins.

[0009] The first fins further include a plurality of auxiliary wings. Every two auxiliary wings are correspondingly arranged with one fin platform, and are respectively located on both sides of the corresponding fin platform along the extending direction of the first fins. The auxiliary wings are connected to the fin roots and protrude in a direction away from the fin roots at an angle with the fin roots. Each fin platform and the corresponding two auxiliary wings, the fin roots, and the first tube body form a semi-closed evaporation cavity with an opening on the side away from the fin roots.

[0010] In the heat exchange tube of some embodiments,

[0011] The distance between the two auxiliary wings corresponding to the fin platform along the extending direction of the first fin gradually decreases from the side close to the first tube body to the side close to the fin platform; and / or

[0012] The distance between the two auxiliary wings corresponding to the fin platform along the extending direction of the first fin gradually decreases from the side close to the fin roots to the side close to the opening.

[0013] In the heat exchange tube of some embodiments, the two auxiliary wings corresponding to the fin platform bend towards each other.

[0014] In the heat exchange tube of some embodiments, a channel is formed between the fin roots of two adjacent first fins. Wherein, on any cross-section extending along the extending direction of the first fin through the auxiliary wings, the total dimension of the auxiliary wings located in the same channel along the width direction of the channel is less than or equal to 95% of the minimum width of the channel where the auxiliary wings are located.

[0015] In the heat exchange tube of some embodiments,

[0016] The end of the fin platform away from the fin roots bends towards the first tube body; and / or

[0017] One end of the fin platform away from the fin root protrudes beyond one end of the corresponding two ailerons away from the fin root; and / or

[0018] The thickness of the aileron gradually decreases from the direction close to the fin root to the direction away from the fin root.

[0019] In the heat exchange tubes of some embodiments, the thickness of the part of the fin platform bent towards the first tube body gradually decreases from the direction close to the fin root to the direction away from the fin root.

[0020] In the heat exchange tubes of some embodiments, the fin top includes a plurality of fin teeth arranged along the extending direction of the first fin, and the plurality of fin teeth are located at one end of the fin top radially away from the first tube body along the first tube body.

[0021] In the heat exchange tubes of some embodiments, the distance between two adjacent fin teeth along the extending direction of the first fin gradually decreases from one end away from the first tube body to one end close to the first tube body.

[0022] In the heat exchange tubes of some embodiments, both sides of the fin tooth along the extending direction of the first fin include inclined surfaces,

[0023] The included angle between the inclined surface and the extending direction of the first fin on the side towards the fin tooth is an acute angle; and / or

[0024] The included angle between the inclined surface and one of the two side surfaces of the first fin is an acute angle.

[0025] In the heat exchange tubes of some embodiments, the inclined surfaces on both sides of the fin tooth are symmetric or asymmetric; and / or

[0026] The included angle between each inclined surface of each fin tooth of the first fin and the same side surface of the first fin is an acute angle.

[0027] In the heat exchange tubes of some embodiments, there is an interval between two adjacent fin teeth of the fin top.

[0028] In the heat exchange tubes of some embodiments, the tooth shape of the fin tooth is configured as a triangle or a square or a trapezoid or an inverted trapezoid.

[0029] In the heat exchange tubes of some embodiments, the fin top further includes a connecting part, and the connecting part is connected between the plurality of fin teeth and the fin root along the radial direction of the first tube body.

[0030] In the heat exchange tubes of some embodiments, the fin teeth of two adjacent first fins are arranged in a staggered manner along the extending direction of the first fin.

[0031] In the heat exchange tubes of some embodiments,

[0032] The thickness of the fin root forming the evaporation cavity is greater than the thickness of other parts of the fin root; and / or

[0033] The thickness of at least a part of the fin root is greater than the thickness of the fin top.

[0034] In the heat exchange tubes of some embodiments, the first fin includes a first groove, and the surface of the fin root between two adjacent evaporation cavities along the extending direction of the first fin forms the bottom surface of the first groove.

[0035] In the heat exchange tubes of some embodiments,

[0036] The dimension of the first groove along the extending direction of the first fin gradually increases from the position close to the first tube body to the position far from the first tube body; and / or

[0037] The depth of the first groove is less than or equal to 80% of the thickness of the fin root forming the evaporation cavity.

[0038] In the heat exchange tubes of some embodiments, the first tube body includes a second groove, and the surface of the first tube body between two adjacent evaporation cavities along the extending direction of the first fin forms the bottom surface of the second groove.

[0039] In the heat exchange tubes of some embodiments,

[0040] The first fin includes a first groove, and the surface of the fin root between two adjacent evaporation cavities along the extending direction of the first fin forms the bottom surface of the first groove;

[0041] One end of the second groove close to the first groove is connected to one end of the first groove close to the second groove between two adjacent evaporation cavities along the extending direction of the first fin.

[0042] In the heat exchange tubes of some embodiments, the first fins are symmetrically arranged or asymmetrically arranged along their own thickness direction.

[0043] In the heat exchange tubes of some embodiments,

[0044] The evaporation cavities of two adjacent first fins are arranged in alignment or misalignment along the extending direction of the first fin; and / or

[0045] A channel is formed between the fin roots of two adjacent first fins, and evaporation cavities are formed in both of the two adjacent first fins in the channel. The evaporation cavities located in the same channel are arranged in alignment or misalignment along the extending direction of the first fin; and / or

[0046] The evaporation chambers on both sides of the same first fin along its thickness direction are arranged in alignment or misalignment along the extension direction of the first fin.

[0047] In the heat exchange tubes of some embodiments, the heat exchange tubes include:

[0048] Two smooth tube sections located at two ends of the heat exchange tube;

[0049] A main heat exchange section located in the middle of the heat exchange tube, the main heat exchange section includes the first tube body and the first fin; and

[0050] Two transition heat exchange sections respectively located between the two smooth tube sections and the main heat exchange section, the transition heat exchange section includes a second tube body and a second fin provided on the second tube body, the second tube body is connected between the smooth tube section and the first tube body, the second fin is provided on the second tube body, and the second fin has a different structure from the first fin;

[0051] Wherein, the outer surface of the smooth tube section, the outer end surface of the first fin along the radial direction of the first tube body, and the outer end surface of the second fin along the radial direction of the second tube body are on the same cylindrical surface.

[0052] The second aspect of the present disclosure provides a horizontal shell-and-tube heat exchanger including the heat exchange tube of the first aspect of the present disclosure.

[0053] The third aspect of the present disclosure provides a heat pump air conditioner unit including the horizontal shell-and-tube heat exchanger of the second aspect of the present disclosure.

[0054] Based on the heat exchange tube provided by the present disclosure, the transverse fin portion of the first fin includes a plurality of fin platforms arranged at intervals along the extending direction of the first fin, and the first fin includes a plurality of auxiliary wings. Every two auxiliary wings are correspondingly arranged with one fin platform and are respectively located on both sides of the corresponding fin platform along the extending direction of the first fin. The auxiliary wings are connected to the fin root and protrude away from the fin root at an angle. Each fin platform and the corresponding two auxiliary wings, fin root and first tube body form a semi-closed evaporation cavity with an opening on the side away from the fin root. During the evaporation process, the two auxiliary wings are beneficial to intercept the refrigerant distributed on the surface of the heat exchange tube, forming a micro-liquid layer required for evaporation, thereby being beneficial to improving the heat exchange efficiency during the evaporation process; the evaporation cavity is a semi-closed cavity with an opening on one side, which is beneficial to retain the refrigerant required for evaporation. The auxiliary wings and fin platforms are beneficial to intercept the gasification nuclei generated at the tail of the evaporation bubbles, that is, it is beneficial to retain the small bubble points after the evaporation bubbles overflow for the gasification nuclei required for new evaporation bubbles, thereby being beneficial to enhancing the evaporation heat exchange effect. During the condensation process, the fin platforms are beneficial to segmentally enhance condensation, cooperating with the fin top to further thin the thickness of the condensate film condensed on the first fin, thereby being beneficial to enhancing the condensation heat exchange effect; the auxiliary wings are beneficial to thin the condensate film and are also beneficial to guide the refrigerant condensed on the fin top, so that the refrigerant is quickly discharged, thereby improving the heat exchange efficiency. This heat exchange tube is suitable for both evaporation and condensation.

[0055] The horizontal shell-and-tube heat exchanger of the present disclosure includes the heat exchange tube of the present disclosure, and thus has the advantages of the heat exchange tube of the present disclosure.

[0056] The heat pump air conditioner unit of the present disclosure includes the horizontal shell-and-tube heat exchanger of the present disclosure, and thus has the advantages of the heat exchange tube of the present disclosure.

[0057] Through the following detailed description of the exemplary embodiments of the present disclosure with reference to the accompanying drawings, other features and advantages of the present disclosure will become clear. BRIEF DESCRIPTION OF THE DRAWINGS

[0058] The drawings described herein are used to provide a further understanding of the present disclosure and constitute a part of this application. The schematic embodiments of the present disclosure and their descriptions are used to explain the present disclosure and do not constitute an improper limitation to the present disclosure. In the drawings:

[0059] Figure 1 is a schematic structural diagram of a part of the structure of the heat exchange tube according to an embodiment of the present disclosure, which shows that the transverse fin portion is located on both sides of the first fin along the axial direction of the first tube;

[0060] Figure 2 is Figure 1 a schematic circumferential structural diagram of a part of the structure of the heat exchange tube shown;

[0061] Figure 3 is Figure 1Schematic structural diagram of a partial structure of the heat exchange tube shown along the axial direction of the first tube body;

[0062] Figure 4 For Figure 1 Top view structural diagram of a partial structure of the heat exchange tube shown;

[0063] Figure 5 Schematic structural diagram of a partial structure of the heat exchange tube according to another embodiment of the present disclosure, which shows that the transverse fin portion is located on one side of the first fin along the axial direction of the first tube body;

[0064] Figure 6 For Figure 5 Schematic structural diagram of a partial structure of the heat exchange tube shown along the circumferential direction of the first tube body;

[0065] Figure 7 For Figure 5 Schematic structural diagram of a partial structure of the heat exchange tube shown along the axial direction of the first tube body;

[0066] Figure 8 For Figure 5 Top view structural diagram of a partial structure of the heat exchange tube shown;

[0067] Figure 9 Overall structural diagram of the heat exchange tube according to another embodiment of the present disclosure.

[0068] Figures 1 to 9 In the figures, each reference numeral represents respectively:

[0069] 1, first tube body; 13, rib; 19, second groove; 10, evaporation cavity; 21, channel; 4, first fin; 41, fin root; 42, fin top; 421, fin tooth; 422, connecting portion; 43, fin platform; 45, aileron; 49, first groove;

[0070] 110, smooth tube section; 120, transitional heat exchange section; 121, second tube body; 122, second fin; 130, main heat exchange section. Detailed implementation manners

[0071] Next, the technical solutions in the embodiments of the present disclosure will be clearly and completely described in conjunction with the accompanying drawings in the embodiments of the present disclosure. Obviously, the described embodiments are only a part of the embodiments of the present disclosure, rather than all of the embodiments. The following description of at least one exemplary embodiment is actually only illustrative and in no way constitutes a limitation to the present disclosure and its application or use. Based on the embodiments of the present disclosure, all other embodiments obtained by those of ordinary skill in the art without creative efforts shall fall within the scope of protection of the present disclosure.

[0072] Unless otherwise specifically stated, the relative arrangements, numerical expressions, and numerical values of the components and steps set forth in these embodiments do not limit the scope of the present disclosure. At the same time, it should be understood that for the convenience of description, the dimensions of the various parts shown in the drawings are not drawn in actual proportional relationships. Technologies, methods, and devices known to those of ordinary skill in the relevant art may not be discussed in detail, but where appropriate, the said technologies, methods, and devices should be regarded as part of the authorization specification. In all the examples shown and discussed here, any specific value should be construed as merely exemplary and not as a limitation. Therefore, other examples of the exemplary embodiments may have different values. It should be noted that like reference numerals and letters denote like items in the following drawings, and thus, once an item is defined in one drawing, it does not need to be further discussed in subsequent drawings.

[0073] In the description of the present disclosure, it should be understood that the use of terms such as "first" and "second" to define components is merely for the convenience of differentiating the corresponding components. Without additional statements, the above terms have no special meanings, and thus, should not be construed as limiting the scope of the present disclosure.

[0074] In the description of the present disclosure, it should be understood that the orientation or positional relationships indicated by orientation terms such as "front, rear, top, bottom, left, right", "lateral, vertical, upright, horizontal", and "top, bottom" are generally based on the orientation or positional relationships shown in the drawings. These are merely for the convenience of describing the present disclosure and simplifying the description. Without contrary statements, these orientation terms do not indicate or imply that the devices or elements referred to must have a specific orientation or be constructed and operated in a specific orientation, and thus, should not be construed as limiting the scope of the present disclosure; the orientation terms "inner, outer" refer to the inside and outside relative to the contour of each component itself.

[0075] As Figures 1 to 9 shown, an embodiment of the present disclosure provides a heat exchange tube. The heat exchange tube includes a first tube body 1 and a plurality of first fins 4 connected to the outside of the first tube body 1 and spaced apart. The first fins 4 include fin roots 41, fin tops 42, and transverse fin portions protruding from the top of the fin roots 41 in a direction away from the fin roots 41. The transverse fin portions are provided on at least one side in the thickness direction of the first fins 4 and include a plurality of fin platforms 43 spaced apart along the extending direction of the first fins 4. The first fins 4 further include a plurality of sub-wings 45. Every two sub-wings 45 are correspondingly arranged with one fin platform 43 and are respectively located on both sides of the corresponding fin platform 43 along the extending direction of the first fins 4. The sub-wings 45 are connected to the fin roots 41 and protrude from the fin roots 41 at an angle in a direction away from the fin roots 41. Each fin platform 43, the corresponding two sub-wings 45, the fin roots 41, and the first tube body 1 form a semi-closed evaporation chamber 10 having an opening on the side away from the fin roots 41.

[0076] For the heat exchange tube according to this embodiment, the transverse fin portion of the first fin 4 includes a plurality of fin platforms 43 arranged at intervals along the extending direction of the first fin 4, and the first fin 4 includes a plurality of auxiliary wings 45. Every two auxiliary wings 45 are correspondingly arranged with one fin platform 43 and are respectively located on both sides of the corresponding fin platform 43 along the extending direction of the first fin 4. The auxiliary wings 45 are connected to the fin root 41 and protrude from the fin root 41 at an angle towards a direction away from the fin root 41. A semi-closed evaporation cavity 10 with an opening on the side away from the fin root 41 is formed between each fin platform 43 and the corresponding two auxiliary wings 45, the fin root 42 and the first tube body 1. During the evaporation process, the two auxiliary wings 45 are beneficial to intercept the refrigerant distributed by the distributor of the horizontal shell and tube heat exchanger, forming a micro-liquid layer required for evaporation, so as to be beneficial to improving the heat exchange efficiency during the evaporation process; the evaporation cavity 10 is a semi-closed cavity with an opening on one side, which is beneficial to retaining the refrigerant required for evaporation. The auxiliary wings 45 and the fin platforms 43 are beneficial to retaining the gasification cores generated at the tails of evaporation bubbles, that is, beneficial to intercepting the small bubble points left after the evaporation bubbles overflow, which are used as the gasification cores required for new evaporation bubbles, so as to be beneficial to strengthening the evaporation heat exchange effect. During the condensation process, the fin platforms 43 are beneficial to segmentally strengthen condensation, and cooperate with the fin top 42 to further thin the thickness of the condensate film condensed on the first fin 4, so as to be beneficial to strengthening the condensation heat exchange effect; the auxiliary wings 45 are beneficial to thinning the condensate film, and are also beneficial to guiding the refrigerant condensed on the fin top 42, so that the refrigerant is quickly discharged, thereby improving the heat exchange efficiency. This heat exchange tube is suitable for both evaporation and condensation.

[0077] As Figure 1 、 Figure 2 、 Figure 5 and Figure 6 shown, in some embodiments, the distance between the two auxiliary wings 45 corresponding to the fin platform 43 along the extending direction of the first fin 4 gradually decreases from the side close to the first tube body 1 to the side close to the fin platform 43; and / or the distance between the two auxiliary wings 45 corresponding to the fin platform 43 along the extending direction of the first fin 4 gradually decreases from the side close to the fin root 41 to the side close to the opening.

[0078] The distance between the two auxiliary wings 45 corresponding to the fin platform 43 along the extending direction of the first fin 4 gradually decreases from the side close to the first tube body 1 to the side close to the fin platform 43, which is beneficial to making the evaporation cavity 10 form a space structure with a narrow upper part and a wide lower part, so as to be beneficial to making the evaporation cavity 10 form a space structure that gradually converges from the side close to the first tube body 1 to the side close to the fin platform 43, which is beneficial to intercepting the small bubble points after the evaporation bubbles overflow. The small bubble points are beneficial to forming the gasification cores of new evaporation bubbles, so as to be beneficial to improving the heat exchange efficiency of the heat exchange tube during the evaporation process.

[0079] The distance between the two ailerons 45 corresponding to the fin platform 43 along the extension direction of the first fin 4 gradually decreases from the side close to the fin root 41 to the side close to the opening, which is conducive to forming a space structure in the evaporation chamber 10 that gradually converges from the side close to the fin root 41 to the side close to the opening. This is beneficial for intercepting small bubble points after the evaporation bubbles overflow. The small bubble points are conducive to forming the gasification core of new evaporation bubbles, thereby facilitating the improvement of the heat exchange efficiency of the heat exchange tube during the evaporation process.

[0080] In some embodiments (not shown), the distance between the two ailerons 45 corresponding to the fin platform 43 along the extension direction of the first fin 4 may be equal; and / or the two ailerons 45 corresponding to the fin platform 43 may be arranged perpendicular to the fin root 41.

[0081] Such as Figure 1 、 Figure 4 、 Figure 5 and Figure 8 As shown in

[0082] This setting is conducive to forming a space structure that gradually converges towards the opening of the evaporation chamber 10, thereby facilitating the interception of small bubble points after the evaporation bubbles overflow, and is beneficial for improving the heat exchange efficiency of the heat exchange tube during the evaporation process.

[0083] In some embodiments (not shown), the aileron 45 can also be configured as a straight plate.

[0084] Such as Figure 3 and Figure 5 As shown in

[0085] On the one hand, this setting is conducive to setting an appropriate surface area of the aileron 45, thereby facilitating setting an appropriate space size of the evaporation chamber 10 and is also beneficial for increasing the condensation heat exchange area. On the other hand, it is conducive to leaving a flow channel for the condensed refrigerant during the condensation process, which is beneficial for avoiding blocking the circumferential flow of the refrigerant along the heat exchange tube, so as to facilitate maintaining the continuous and efficient progress of the condensation process. Among them, the ailerons 45 located in the same channel 21 can be arranged only on the first fin 4 on one side of the channel 21, or can be arranged on the first fins 4 on both sides of the channel 21 at the same time.

[0086] Such as Figure 3 and Figure 5As shown, in some embodiments, one end of the fin platform 43 away from the fin root 41 is bent towards the first tube body 1; one end of the fin platform 43 away from the fin root 41 protrudes beyond one end of the corresponding two auxiliary fins 45 away from the fin root 41; and / or the thickness of the auxiliary fin 45 gradually decreases from the end close to the fin root 41 to the end away from the fin root 41.

[0087] The bending of one end of the fin platform 43 away from the fin root 41 towards the first tube body 1 is conducive to the fin platform 43 converging towards the evaporation chamber 10 on the side close to the opening of the evaporation chamber 10, which is conducive to intercepting small bubble points after evaporation bubbles overflow.

[0088] One end of the fin platform 43 away from the fin root 41 protrudes beyond one end of the corresponding two auxiliary fins 45 away from the fin root 41. This setting is conducive to providing space for the fin platform 43 to bend towards the first tube body 1, and is also conducive to increasing the condensation heat transfer area, thereby improving the heat transfer efficiency during the condensation process. In addition, this setting is conducive to generating a bending surface at the junction of the auxiliary fin 45 and the fin platform 43, which is conducive to the generation of vaporization nuclei, and thus is conducive to improving the evaporation heat transfer effect.

[0089] The thickness of the auxiliary fin 45 gradually decreases from the direction close to the fin root 41 to the direction away from the fin root 41. This setting is conducive to thinning the condensate film during the condensation process, and is conducive to forming a sharp edge at one end of the auxiliary fin 45 away from the fin root 41, thereby facilitating the puncturing of the condensate film.

[0090] As Figure 1 、 Figure 3 、 Figure 5 and Figure 7 As shown, in some embodiments, the thickness of the part of the fin platform 43 bent towards the first tube body 1 gradually decreases from the direction close to the fin root 41 to the direction away from the fin root 41.

[0091] This setting is conducive to forming a sharp edge at one end of the fin platform 43 away from the fin root 41, thereby facilitating the puncturing of the condensate film.

[0092] As Figures 1 to 8 As shown, in some embodiments, the fin top 42 includes a plurality of fin teeth 421 arranged along the extending direction of the first fin 4. The plurality of fin teeth 421 are located at one end of the fin top 42 radially away from the first tube body 1 along the first tube body 1.

[0093] The fin teeth 421 are conducive to thinning the condensate film and facilitating the heat exchange tube to achieve the condensation function.

[0094] As Figure 1 、 Figure 2 、 Figure 5 and Figure 6As shown, in some embodiments, the distance between two adjacent fin teeth 421 along the extending direction of the first fin 4 gradually decreases from the end far away from the first tube body 1 to the end close to the first tube body 1.

[0095] This setting is conducive to forming a serrated structure at the fin top 42, facilitating thinning of the condensate film, reducing the residence time of the liquid refrigerant at the fin top 41, promoting the flow of the liquid refrigerant along the edge of the fin teeth 421 towards the first tube body 1 and rapid discharge, thereby being conducive to improving the condensation efficiency.

[0096] As Figure 1 , Figure 4 , Figure 5 and Figure 8 As shown, in some embodiments, both sides of the fin teeth 421 along the extending direction of the first fin 4 include inclined surfaces. The angle between the inclined surface and the extending direction of the first fin 4 towards the fin teeth 421 side is an acute angle; and / or the angle between the inclined surface and one of the two side surfaces of the first fin 4 is an acute angle.

[0097] The inclined surface helps the refrigerant to spread on the surface of the heat exchange tube during the evaporation process, is conducive to reducing dry spots, is conducive to reducing the deterioration of falling film evaporation, and thus is conducive to reducing the performance attenuation of the heat exchange tube in the horizontal shell and tube heat exchanger. Compared with the setting where the inclined surface is perpendicular to the two side surfaces of the first fin 4, the angle between the inclined surface and one of the two side surfaces of the first fin 4 being an acute angle is conducive to increasing the area of the inclined surface, thereby further helping the refrigerant to quickly spread on the surface of the heat exchange tube during the evaporation process and also being conducive to thinning the condensate film during the condensation process.

[0098] As Figure 1 , Figure 2 , Figure 4 , Figure 5 , Figure 6 and Figure 8 As shown, in some embodiments, the inclined surfaces on both sides of the fin teeth 421 are symmetric or asymmetric; and / or the angle between each inclined surface of each fin tooth 421 of the first fin 4 and the same side surface of the first fin 4 is an acute angle.

[0099] The symmetrical inclined surfaces on both sides of the fin teeth 421 are beneficial for evenly spreading the refrigerant on the surface of the heat exchange tube, and also for reducing the difficulty of manufacturing the first fin 4, improving the manufacturing efficiency, and reducing the cost. When the inclined surfaces on both sides of the fin teeth 421 are asymmetrical, the parameters of the liquid refrigerant flowing down along the inclined surfaces on both sides of the same tooth groove, such as flow velocity and thickness, have certain differences. During the confluence process of the liquid refrigerant flowing to the bottom of the tooth groove, more disturbances can be generated, which is beneficial for enhancing the heat exchange process. The acute angle between each inclined surface of each fin tooth 421 of the first fin 4 and the same side surface of the first fin 4 is beneficial for the liquid refrigerant to have approximately the same flow area and flow resistance when flowing from between adjacent fin teeth 421 to the two side surfaces of the first fin 4, which is beneficial for the liquid refrigerant to flow synchronously from adjacent fin teeth 421 to the two side surfaces, thereby being beneficial for improving the heat exchange effect.

[0100] As Figure 1 , Figure 2 , Figure 4 , Figure 5 , Figure 6 and Figure 8 shown, in some embodiments, there is a spaced arrangement between two adjacent fin teeth 421 at the fin top 42.

[0101] This setting is beneficial for the refrigerant flowing along the inclined surface to the bottom of the tooth groove to quickly spread along the extending direction of the first fin 4, and is beneficial for the refrigerant to smoothly flow from the bottom of the tooth groove towards the first tube body 1, thereby being beneficial for strengthening the condensation effect.

[0102] As Figure 2 and Figure 6 shown, in some embodiments, the tooth shape of the fin teeth 421 is configured as a triangle. In other embodiments (not shown), the tooth shape of the fin teeth 421 is configured as a square or a trapezoid or an inverted trapezoid.

[0103] The triangular tooth shape is beneficial for the fin teeth 421 to form a tip on the side away from the fin root 41, thereby being beneficial for piercing the condensate film. The square, trapezoid or inverted trapezoid tooth shape is beneficial for the refrigerant to spread along the extending direction of the first fin 4, and is beneficial for thinning the condensate film.

[0104] As Figure 2 and Figure 6 shown, in some embodiments, the fin top 42 further includes a connecting portion 422. The connecting portion 422 is connected radially to the first tube body 1 between a plurality of fin teeth 421 and the fin root 41.

[0105] The connecting portion 422 is beneficial for expanding the heat exchange area of the heat exchange tube, enabling the refrigerant flowing through the fin teeth 421 to quickly spread along the extending direction of the first fin 4, and being beneficial for the liquid refrigerant flowing down from the fin top 42 to be quickly and evenly distributed on the fin platform 43 and the fin root 41 between adjacent evaporation chambers 10 to form a liquid film, thereby being beneficial for improving the heat exchange efficiency.

[0106] As Figure 4 and Figure 8 shown, in some embodiments, the fin teeth 421 of two adjacent first fins 4 are arranged in a staggered manner along the extending direction of the first fin 4.

[0107] This setting is conducive to the spreading of the liquid refrigerant on the surface of the fin tops 42 of multiple first fins 4, and is also conducive to the liquid refrigerant flowing from the tooth grooves between adjacent fin teeth 421 along the surface of the fin roots 41 to the surface of the first tube body 1, and finally being discharged from the channel 21 between two adjacent first fins 4. During this process, the liquid refrigerants flowing on two adjacent first fins 4 do not interfere with each other substantially before reaching the first tube body 1, thus being conducive to the rapid discharge of the liquid refrigerant.

[0108] As Figure 1 , Figure 3 , Figure 5 and Figure 7 shown, in some embodiments, the thickness of the fin roots 41 forming the evaporation cavity 10 is greater than the thickness of other parts of the fin roots 41; and / or the thickness of at least part of the fin roots 41 is greater than the thickness of the fin tops 42.

[0109] The fact that the thickness of the fin roots 41 forming the evaporation cavity 10 is greater than the thickness of other parts of the fin roots 41 is conducive to increasing the distance between the surface of the fin roots 41 and the end of the aileron 45 far from the fin roots 41, conducive to expanding the heat exchange area, helpful for the superheating of the refrigerant in the channel 21, conducive to the formation of evaporation bubbles, and conducive to the smooth flow of the liquid refrigerant on the fin tops 42 along the surface of the fin roots 41 between two adjacent evaporation cavities 10 towards the first tube body 1.

[0110] The thickness of at least part of the fin roots 41 is greater than the thickness of the fin tops 42, that is, the thickness of the fin tops 41 is reduced, which is conducive to thinning and piercing the condensate film, thus being conducive to enhancing the condensation effect.

[0111] As Figure 1 , Figure 2 , Figure 5 and Figure 6 shown, in some embodiments, the first fin 4 includes a first groove 49, and the surface of the fin roots 41 between two adjacent evaporation cavities 10 along the extending direction of the first fin 4 forms the bottom surface of the first groove 49.

[0112] The side surfaces of the first groove 49 (including the opposite side surfaces of the opposite two wing portions 45 of two adjacent evaporation chambers 10, and when the thickness of the fin root portion 41 forming the evaporation chamber 10 is greater than the thickness of other portions of the fin root portion 41, also including the stepped surface formed between the two fin root portions 41) and the bottom surface are conducive to expanding the heat exchange area during evaporation and condensation, and are conducive to providing the superheat required for evaporation. During the evaporation process, the fold angle at the bottom of the first groove 49 is conducive to the formation of gasification nuclei; during the condensation process, the first groove 49 is conducive to thinning the thickness of the liquid film, and is also conducive to guiding the refrigerant condensed at the fin top 42 to flow between two adjacent first fins 4 to discharge the condensate.

[0113] As Figure 2 and Figure 6 shown, in some embodiments, the dimension of the first groove 49 in the extending direction of the first fin 4 gradually increases from near the first tube body 1 to away from the first tube body 1; and / or the depth of the first groove 49 is less than or equal to 80% of the thickness of the fin root portion 41 forming the evaporation chamber 10.

[0114] The dimension of the first groove 49 in the extending direction of the first fin 4 gradually increasing from near the first tube body 1 to away from the first tube body 1 is conducive to forming an inverted trapezoidal structure of the first groove 49, is conducive to expanding the effective heat exchange area, and is also conducive to enabling the refrigerant condensed at the fin top 42 to quickly flow along the inclined side wall of the first groove 49 to the channel 21 and be discharged, thereby being conducive to improving the heat exchange efficiency.

[0115] The thickness of the first groove 49 being less than or equal to 80% of the thickness of the fin root portion 41 forming the evaporation chamber 10 is conducive to avoiding the thickness of some regions of the fin root portion 41 being too small and weakening the connection strength between the first fin 4 and the first tube body 1.

[0116] As Figure 1 、 Figure 2 、 Figures 4 to 6 and Figure 8 shown, in some embodiments, the first tube body 1 includes a second groove 19. The bottom surface of the second groove 19 is formed on the surface of the first tube body 1 between two adjacent evaporation chambers 10 along the extending direction of the first fin 4.

[0117] Providing the second groove 19 is conducive to expanding the heat exchange area. In addition, since the bottom surface of the second groove 19 is closer to the heat source inside the heat exchange tube in the radial direction, it is conducive to providing the superheat required for evaporation, thereby being conducive to improving the heat exchange effect during the evaporation process. In addition, the liquid refrigerant in the heat exchange tube flows circumferentially, and the second groove 19 is conducive to disturbing the liquid refrigerant on the flow path of the refrigerant, is conducive to triggering the formation of bubbles, providing the energy or trigger point for the formation of bubbles, and enabling the bubbles to start growing, thereby being conducive to promoting the evaporation process.

[0118] As Figure 1, Figure 2 , Figure 5 and Figure 6 As shown in Figure 2 , Figure 5 and Figure 6 , in some embodiments, the second groove 19 and the first groove 49 between two adjacent evaporation chambers 10 along the extension direction of the first fin 4 are connected at their ends close to each other.

[0119] The second groove 19 and the first groove 49 together form a path for guiding the condensate to drain out of the heat exchange tube, which is beneficial to improving the speed of the condensate draining out of the heat exchange tube, and thus beneficial to improving the condensation heat exchange efficiency.

[0120] In some embodiments, the first fin 4 is symmetrically arranged or asymmetrically arranged along its own thickness direction.

[0121] The symmetrical arrangement of the first fin 4 along its own thickness direction is beneficial to convenient manufacturing, beneficial to improving manufacturing efficiency and reducing costs.

[0122] The asymmetric arrangement of the first fin 4 along its own thickness direction is beneficial to dispersing the spatial distribution of the fin top 42 and the evaporation chamber 10 and the like, and thus beneficial to enabling the refrigerant to fully evaporate or condense and reducing local dry spots or liquid accumulation phenomena.

[0123] For example, by making at least one of the structure and size of the evaporation chambers 10 on both sides of the same first fin 4 along its own thickness direction the same or different, symmetric or asymmetric evaporation chambers 10 can be formed.

[0124] Such as Figure 1 , Figure 4 , Figure 5 and Figure 8 As shown in Figure 1 , Figure 4 , Figure 5 and Figure 8 , in some embodiments, the evaporation chambers 10 of two adjacent first fins 4 are arranged in alignment or offset along the extension direction of the first fin 4; and / or a channel 21 is formed between the fin roots 41 of two adjacent first fins 4, and evaporation chambers 10 are formed in both of the two adjacent first fins 4 in the channel 21, and the evaporation chambers 10 located in the same channel 21 are arranged in alignment or offset along the extension direction of the first fin 4; and / or the evaporation chambers 10 on both sides of the same first fin 4 along its own thickness direction are arranged in alignment or offset along the extension direction of the first fin 4.

[0125] The alignment of the evaporation chambers 10 of two adjacent first fins 4 along the extension direction of the first fin 4 is beneficial to making the evaporation chambers 10 locally relatively concentrated, and thus beneficial to improving the evaporation heat exchange efficiency in the relatively concentrated area. The offset arrangement of the evaporation chambers 10 of two adjacent first fins 4 along the extension direction of the first fin 4 is beneficial to dispersing the spatial distribution of the fin top 42 and the evaporation chambers 10 and the like, and thus beneficial to reducing local dry spots or liquid accumulation phenomena.

[0126] The evaporating chambers 10 located within the same channel 21 being arranged in alignment along the extending direction of the first fin 4 is conducive to enabling two opposite evaporating chambers 10 within the same channel 21 to form a larger evaporation space, which is beneficial to improving the evaporation heat exchange efficiency. When the evaporating chambers 10 located within the same channel 21 are arranged in a circumferential stagger along the first tube body 1, the openings of the evaporating chambers 10 face the fin roots 41 of the adjacent first fins 4, thereby being conducive to the evaporating chambers 10 intercepting the refrigerant, thus being beneficial to improving the evaporation heat exchange efficiency, and this setting is conducive to increasing the number of evaporating chambers 10 along the circumference of the first tube body 1.

[0127] The evaporating chambers 10 located on both sides of the same first fin 4 along its thickness direction being arranged in alignment along the extending direction of the first fin 4 is conducive to simplifying the manufacturing process of the first fin 4 and improving the manufacturing efficiency. The evaporating chambers 10 located on both sides of the same first fin 4 along its thickness direction being arranged in a stagger along the extending direction of the first fin 4 is conducive to dispersing the spatial distribution of the fin tops 42 and the evaporating chambers 10, etc., thereby being beneficial to reducing local dry spots or liquid accumulation phenomena.

[0128] As Figure 9 shown, in some embodiments, the heat exchange tube includes two smooth tube sections 110, a main heat exchange section 130, and two transition heat exchange sections 120. The two smooth tube sections 110 are located at the two ends of the heat exchange tube. The main heat exchange section 130 is located in the middle of the heat exchange tube, and the main heat exchange section 130 includes a first tube body 1 and a first fin 4. The two transition heat exchange sections 120 are respectively located between the two smooth tube sections 110 and the main heat exchange section 130. The transition heat exchange section 120 includes a second tube body 121 and a second fin 122 provided on the second tube body. The second tube body 121 is connected between the smooth tube section 110 and the first tube body 1. The second fin 122 is provided on the second tube body 121. The second fin 122 has a different structure from the first fin 4. Among them, the outer surface of the smooth tube section 110, the outer end surface of the first fin 4 along the radial direction of the first tube body 1, and the outer end surface of the second fin 122 along the radial direction of the second tube body 121 are on the same cylindrical surface.

[0129] The heat exchange tube includes two smooth tube sections 110, a main heat exchange section 130, and two transition heat exchange sections 120, and the outer surface of the smooth tube section 110, the outer end surface of the first fin 4 along the radial direction of the first tube body 1, and the outer end surface of the second fin 122 along the radial direction of the second tube body 121 are on the same cylindrical surface. On the basis of the heat exchange tube having a relatively high evaporation and condensation heat exchange efficiency, it has a regular outer surface, which is conducive to the installation and arrangement of the heat exchange tube, reducing the possibility of the first fin 4 and the second fin 122 being deformed due to external forces such as being knocked, etc., thereby being conducive to the heat exchange tube stably exerting its heat exchange function.

[0130] Another aspect of the embodiments of the present disclosure provides a horizontal shell-and-tube heat exchanger, and this horizontal shell-and-tube heat exchanger includes the heat exchange tube provided by the embodiments of the present disclosure.

[0131] The horizontal shell-and-tube heat exchanger according to an embodiment of the present disclosure has the advantages of the heat exchange tubes according to the embodiments of the present disclosure.

[0132] On the other hand, an embodiment of the present disclosure provides a heat pump air conditioner unit, including the horizontal shell-and-tube heat exchanger according to the embodiment of the present disclosure.

[0133] The heat pump air conditioner unit according to the embodiment of the present disclosure has the advantages of the heat exchange tubes of the present disclosure.

[0134] The following Figures 1 to 9 will describe in detail the horizontal shell-and-tube heat exchanger and the heat exchange tubes according to the embodiments of the present disclosure.

[0135] As Figures 1 to 9 shown, the heat exchange tube includes a first tube body 1 and a plurality of first fins 4 that are connected to the outside of the first tube body 1 and are arranged at intervals. The plurality of first fins may be arranged at intervals along the axial direction of the first tube body 1 as a plurality of annular first fins. The plurality of first fins 4 may also form a spiral around the axis of the first tube body 1.

[0136] The first fin 4 includes a fin root 41, a fin top 42, a transverse fin portion protruding axially from the top of the fin root 41 toward the first tube body 1, and a plurality of auxiliary wings 45.

[0137] The transverse fin portion may be respectively arranged on both axial sides of the first fin 4 along the axial direction of the first tube body 1 as Figures 1 to 4 shown, or may be arranged on the same side of each first fin 4 along the axial direction of the first tube body 1 as Figures 1 to 8 shown. Each transverse fin portion includes a plurality of fin platforms 43, and the plurality of fin platforms 43 are arranged at intervals along the circumferential direction of the first tube body 1. Every two auxiliary wings 45 are correspondingly arranged with one fin platform 43, and are respectively located on both sides of the corresponding fin platform 43 along the extending direction of the first fin 4. The auxiliary wings 45 are connected to the fin root 41 and are arranged at an angle with the fin root 41, protruding in a direction away from the fin root 41. A semi-closed evaporation cavity 10 with an opening on the side away from the fin root 41 is formed between each fin platform 43 and the corresponding two auxiliary wings 45, fin root 41 and first tube body 1. The thickness of the fin root 41 forming the evaporation cavity 10 is greater than the thickness of other parts of the fin root 41.

[0138] The first fin 4 includes a plurality of first grooves 49. The surface of the fin root 41 between two adjacent evaporation cavities 10 along the extending direction of the first fin 4 forms the bottom surface of the first groove 49.

[0139] The fin top 42 of the heat exchange tube is conducive to thinning the condensate film, enabling the refrigerant to spread on the surface of the first fin 4, thereby facilitating the improvement of the condensation heat transfer effect. At the same time, the evaporation cavity 10 of the heat exchange tube is conducive to the formation of vaporization nuclei, thus facilitating the improvement of the evaporation heat transfer effect. This heat exchange tube can be compatible with the dual functions of heat absorption and heat release, and is suitable for horizontal shell-and-tube heat exchangers with both refrigeration and heating functions to enhance the heat transfer energy efficiency. During the evaporation process, the two ailerons 45 are conducive to intercepting the refrigerant distributed on the surface of the heat exchange tube, forming a micro-liquid layer required for evaporation, thereby facilitating the improvement of the heat transfer efficiency during the evaporation process; the evaporation cavity 10 is conducive to retaining the refrigerant required for evaporation, and the ailerons 45 and fin platforms 43 are conducive to intercepting the vaporization nuclei generated at the tails of the evaporation bubbles. During the condensation process, the fin platforms 43 are conducive to segmental enhancement of condensation, and in cooperation with the fin tops 42, further thin the thickness of the condensate film condensed on the first fins 4, thereby facilitating the enhancement of the condensation heat transfer effect; the ailerons 45 are conducive to guiding the refrigerant condensed on the fin tops 42 as the side surfaces of the first grooves 49. In addition, the first grooves 49 are conducive to expanding the heat transfer area. During the evaporation process, the fold angle at the bottom of the first grooves 49 is conducive to the formation of vaporization nuclei. During the condensation process, the first grooves 49 are conducive to guiding the refrigerant condensed on the fin tops 42 to flow between two adjacent first fins 4 to discharge the liquid refrigerant.

[0140] As Figure 9 shown, the heat exchange tube includes two smooth tube sections 110, a main heat exchange section 130, and two transition heat exchange sections 120. The two smooth tube sections 110 are located at the two ends of the heat exchange tube. The main heat exchange section 130 is located in the middle of the heat exchange tube, and the main heat exchange section 130 includes a first tube body 1 and first fins 4. The two transition heat exchange sections 120 are respectively located between the two smooth tube sections 110 and the main heat exchange section 130. The transition heat exchange section 120 includes a second tube body 121 and second fins 122 provided on the second tube body 121. The second tube body 121 is connected between the smooth tube section 110 and the first tube body 1. The second fins 122 have a different structure from the first fins 4. The outer surface of the smooth tube section 110, the outer end surface of the first fins 4 along the radial direction of the first tube body 1, and the outer end surface of the second fins 122 along the radial direction of the second tube body 121 are on the same cylindrical surface. The second fins 122 can be, for example, ordinary fins, or only have a partial fin structure of the first fins 4.

[0141] The two light pipe sections 110 may be of equal or unequal lengths along the axial direction of the heat exchange pipe. The two transition heat exchange sections 120 may be of equal or unequal lengths along the axial direction of the heat exchange pipe. The radial dimension of the first pipe body 1 is smaller than that of the light pipe section 110, and the radial dimension of the second pipe section 121 gradually decreases along the axial direction of the heat exchange pipe from one end close to the light pipe section 110 to the end far from the light pipe section 110. Two or more of the light pipe section 110, the first pipe body 1, the first fin 4, the second pipe body 121 and the second fin 121 may be configured as an integrally formed structure to facilitate improving the structural strength of the heat exchange pipe.

[0142] As Figures 1 to 8 shown, the two ailerons 45 corresponding to the fin platform 43 are respectively connected to the fin roots 41 that jointly form the evaporation chamber 10 with the fin platform 43 and are bent towards each other. The distance between the two ailerons 45 corresponding to the fin platform 43 along the extension direction of the first fin 4 gradually decreases from the side close to the first pipe body 1 to the side close to the fin platform 43. And the distance between the two ailerons 45 along the extension direction of the first fin 4 gradually decreases from the side close to the fin root 41 to the side close to the opening, so that the ailerons 45 are both inclined and bent, which is beneficial to thinning the condensate film and enhancing the condensation heat transfer effect. The thickness of the aileron 45 gradually decreases from the end close to the fin root 41 to the end far from the fin root 41, which is beneficial to piercing the condensate film.

[0143] As Figures 1 to 8 shown, the dimension of the part of the fin root 41 forming the evaporation chamber 10 along the axial direction of the first pipe body 1 is larger than the dimensions of the other parts of the fin root 41 and the fin top 41 along the axial direction of the first pipe body 1. The distance of the fin root 41 forming the evaporation chamber 10 along the extension direction of the first fin 4 gradually decreases from the side close to the pipe body 1 to the side close to the fin platform 43 to cooperate with the shapes of the two connected ailerons 45. The intersection lines of the two side surfaces of the fin root 41 forming the same evaporation chamber 10 along the circumferential direction of the first pipe body 1 with the side surfaces of the corresponding fin platform 43 on one side and the corresponding side surfaces of the root of the aileron 45 and the fin root 41 are located in the same plane.

[0144] As Figures 1 to 8 shown, the end of the fin platform 43 far from the fin root 41 is bent towards the first pipe body 1, and the thickness of the part of the fin platform 43 bent towards the first pipe body 1 gradually decreases from the side close to the fin root 41 to the side far from the fin root 41. The dimension of the part of the fin platform 43 bent towards the first pipe body 1 along the axial direction of the first pipe body 1 is larger than the dimensions of the corresponding two ailerons 45.

[0145] As Figures 1 to 8As shown, the top of the fin 42 includes a plurality of fin teeth 421 arranged along the extension direction of the first fin 4 and a connecting portion 422. The plurality of fin teeth 421 are located at one end of the top of the fin 42 that is radially away from the first tube body 1 along the extension direction of the first fin 4. The tooth shape of the fin teeth 421 is triangular. Both sides of the fin teeth 421 along the extension direction of the first fin 4 include inclined surfaces. The included angle between the inclined surface and the extension direction of the first fin 4 towards the side of the fin teeth 421 is an acute angle, and the included angles between the inclined surfaces on both sides and one of the two side surfaces of the first fin 4 are acute angles respectively. Adjacent fin teeth 421 are spaced apart along the extension direction of the first fin 4. The fin teeth 421 of two adjacent first fins 4 are arranged in a staggered manner along the extension direction of the first fin 4.

[0146] As Figure 1 , Figure 2 , Figure 5 and Figure 6 shown, the connecting portion 422 is connected between the plurality of fin teeth 421 and the root of the fin 41, and extends from the end of the fin teeth 421 close to the first tube body 1 to the end of the root of the fin 41 away from the first tube body 1 along the radial direction of the first tube body 1.

[0147] As Figures 1 to 8 shown, the first tube body 1 includes ribs 13 located on the inner wall of the first tube body 1 and second grooves 19 located on the outer wall of the first tube body 1. The second grooves 19 extend axially along the first tube body 1 between two adjacent first fins 4 and are located between two adjacent evaporation chambers 10 along the extension direction of the first fin 4. One end of the second groove 19 along the axial direction of the first tube body 1 is connected to one end of the corresponding first groove 49 close to the first tube body 1.

[0148] As Figures 1 to 4 shown in the embodiment, a plurality of fin platforms 43 of the heat exchange tube are spaced apart along the extension direction of the first fin 4 on both sides of the first fin 4 along the axial direction of the first tube body 1. The evaporation chambers 10 of two adjacent first fins 4 are arranged in circumferential alignment along the circumferential direction of the first tube body 1, and the evaporation chambers 10 located on both sides of the same first fin 4 along the axial direction of the first tube body 1 are arranged in circumferential alignment along the circumferential direction of the first tube body 1. A channel 21 is formed between the roots 41 of two adjacent first fins 4. In any cross-section extending circumferentially along the first tube body 1 through the aileron 45, the sum of the axial dimensions of the ailerons 45 on both sides of the first tube body 1 located in the same channel 21 is less than or equal to 95% of the minimum axial dimension of the channel 21 along the first tube body 1.

[0149] Among them, the minimum axial dimension of the channel 21 corresponds to the axial dimension of the first tube body 1 between the roots 41 of two adjacent fins 4 that form the evaporation chambers 10.

[0150] As Figures 5 to 8In the illustrated embodiment, a plurality of fin platforms 43 on the transverse fin portions of each first fin 4 are arranged at intervals in the circumferential direction of the first tube body 1 on the same side of the first fin 4 along the axial direction of the first tube body 1. The evaporation chambers 10 of two adjacent first fins 4 are arranged in circumferential alignment along the first tube body 1. A channel 21 is formed between the fin roots 41 of two adjacent first fins 4. In any cross-section extending in the circumferential direction of the first tube body 1 through the aileron 45, the axial dimension of the aileron 45 along the first tube body 1 is less than or equal to 95% of the minimum axial dimension of the channel 21 where the aileron 45 is located along the first tube body 1.

[0151] In the embodiment of the present application, the heat exchange tube is made of a metal material, such as copper or copper alloy. The first fins 4 of the heat exchange tube can be formed by extrusion using a combined die. For example, the aileron 45 is formed by extruding the portion of the first fin 4 close to the first tube body 1, and the two ailerons 45 corresponding to the fin platforms 43 form the fin platforms 43 during the extrusion deformation process.

[0152] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present disclosure and are not intended to limit them; although the present disclosure has been described in detail with reference to the preferred embodiments, those of ordinary skill in the art should understand that it is still possible to modify the specific implementation manners of the present disclosure or make equivalent replacements for some technical features, and they should all be covered by the scope of the technical solutions claimed in the present disclosure.

Claims

1. A heat exchange tube, comprising a first tube body (1) and a plurality of first fins (4) connected to the outside of the first tube body (1) and arranged at intervals, the first fins (4) comprising a fin root (41), a fin top (42), and a transverse fin portion protruding from the top of the fin root (41) in a direction away from the fin root (41), characterized in that, the transverse fin portion is arranged on at least one side in the thickness direction of the first fin (4), and comprises a plurality of fin platforms (43) arranged at intervals along the extending direction of the first fin (4); the first fin (4) further comprises a plurality of auxiliary wings (45), every two of the auxiliary wings (45) are arranged corresponding to one fin platform (43), and are respectively located on both sides of the corresponding fin platform (43) along the extending direction of the first fin (4), the auxiliary wings (45) are connected to the fin root (41) and protrude from the fin root (41) at an angle in a direction away from the fin root (41), and each fin platform (43) and the corresponding two auxiliary wings (45), the fin root (41), and the first tube body (1) form a semi-enclosed evaporation cavity (10) having an opening on the side away from the fin root (41).

2. The heat exchange tube according to claim 1, characterized in that, the distance between the two auxiliary wings (45) corresponding to the fin platform (43) along the extending direction of the first fin (4) gradually decreases from the side close to the first tube body (1) to the side close to the fin platform (43); and / or the distance between the two auxiliary wings (45) corresponding to the fin platform (43) along the extending direction of the first fin (4) gradually decreases from the side close to the fin root (41) to the side close to the opening.

3. The heat exchange tube according to claim 1, wherein The two auxiliary wings (45) corresponding to the fin platform (43) are bent towards each other.

4. The heat exchange tube according to claim 1, characterized in that, A channel (21) is formed between the fin roots (41) of two adjacent first fins (4), wherein, on any cross-section extending along the extending direction of the first fin (4) of the auxiliary wings (45), the total dimension of the auxiliary wings (45) located in the same channel (21) along the width direction of the channel (21) is less than or equal to 95% of the minimum width of the channel (21) where the auxiliary wings (45) are located.

5. The heat exchange tube according to claim 1, characterized in that, one end of the fin platform (43) away from the fin root (41) is bent towards the first tube body (1); and / or one end of the fin platform (43) away from the fin root (41) protrudes from one ends of the corresponding two auxiliary wings (45) away from the fin root (41); and / or the thickness of the auxiliary wings (45) gradually decreases from the side close to the fin root (41) to the side away from the fin root (41).

6. The heat exchange tube according to claim 5, wherein, The thickness of the portion of the fin platform (43) bent towards the first tube body (1) gradually decreases from the side close to the fin root (41) to the side away from the fin root (41).

7. The heat exchange tube according to claim 1, characterized in that, The top of the fin (42) includes a plurality of fin teeth (421) arranged along the extending direction of the first fin (4), and the plurality of fin teeth (421) are located at one end of the top of the fin (42) that is radially away from the first tube body (1) along the radial direction of the first tube body (1).

8. The heat exchange tube according to claim 7, wherein, The distance between two adjacent fin teeth (421) along the extending direction of the first fin (4) gradually decreases from the end away from the first tube body (1) to the end close to the first tube body (1).

9. The heat exchange tube according to claim 8, wherein, Both sides of the fin tooth (421) along the extending direction of the first fin (4) include inclined surfaces. The included angle between the inclined surface and the extending direction of the first fin (4) on the side facing the fin tooth (421) is an acute angle; and / or The included angle between the inclined surface and one of the two side surfaces of the first fin (4) is an acute angle.

10. The heat exchange tube according to claim 9, wherein The inclined surfaces on both sides of the fin tooth (421) are symmetric or asymmetric; and / or The included angle between each inclined surface of each fin tooth (421) of the first fin (4) and the same side surface of the first fin (4) is an acute angle.

11. The heat exchange tube according to claim 7, wherein, The adjacent two fin teeth (421) on the top of the fin (42) are spaced apart.

12. The heat exchange tube according to claim 7, wherein, The tooth shape of the fin tooth (421) is configured as a triangle, a square, a trapezoid, or an inverted trapezoid.

13. The heat exchange tube according to claim 7, characterized in that, The top of the fin (42) further includes a connecting portion (422), and the connecting portion (422) is radially connected to the plurality of fin teeth (421) and the root of the fin (41) along the first tube body (1).

14. The heat exchange tube according to claim 7, wherein, The fin teeth (421) of two adjacent first fins (4) are arranged in a staggered manner along the extending direction of the first fin (4).

15. The heat exchange tube according to any one of claims 1-14, wherein The thickness of the root of the fin (41) forming the evaporation cavity (10) is greater than the thickness of other parts of the root of the fin (41); and / or The thickness of at least part of the root of the fin (41) is greater than the thickness of the top of the fin (42).

16. The heat exchange tube according to claim 15, wherein, The first fin (4) includes a first groove (49), and the bottom surface of the first groove (49) is formed on the surface of the root of the fin (41) between two adjacent evaporation cavities (10) along the extending direction of the first fin (4).

17. The heat exchange tube according to claim 16, wherein The dimension of the first groove (49) along the extending direction of the first fin (4) gradually increases from the side close to the first tube body (1) to the side away from the first tube body (1); and / or The depth of the first groove (49) is less than or equal to 80% of the thickness of the root of the fin (41) forming the evaporation cavity (10).

18. The heat exchange tube according to any one of claims 1-14, characterized in that, The first tube body (1) includes a second groove (19), and the bottom surface of the second groove (19) is formed on the surface of the first tube body (1) between two adjacent evaporation cavities (10) along the extending direction of the first fin (4).

19. The heat exchange tube according to claim 18, wherein The first fin (4) includes a first groove (49), and the bottom surface of the first groove (49) is formed on the surface of the fin root (41) between two adjacent evaporation chambers (10) along the extension direction of the first fin (4). The second groove (19) between two adjacent evaporation chambers (10) along the extension direction of the first fin (4) is connected to one end of the first groove (49) close to each other.

20. The heat exchange tube according to any one of claims 1-14, characterized in that, The first fin (4) is symmetrically arranged or asymmetrically arranged along its own thickness direction.

21. The heat exchange tube according to claim 20, wherein the evaporation chambers (10) of two adjacent first fins (4) are arranged in alignment or misalignment along the extension direction of the first fin (4); and / or a channel (21) is formed between the fin roots (41) of two adjacent first fins (4), and evaporation chambers (10) are formed in both of the two adjacent first fins (4) within the channel (21), and the evaporation chambers (10) located in the same channel (21) are arranged in alignment or misalignment along the extension direction of the first fin (4); and / or the evaporation chambers (10) on both sides of the same first fin (4) along its own thickness direction are arranged in alignment or misalignment along the extension direction of the first fin (4).

22. The heat exchange tube according to any one of claims 1-14, characterized in that, The heat exchange tube includes: two smooth tube sections (110) located at two ends of the heat exchange tube; a main heat exchange section (130) located in the middle of the heat exchange tube, the main heat exchange section (130) includes the first tube body (1) and the first fin (4); and two transition heat exchange sections (120) respectively located between the two smooth tube sections (110) and the main heat exchange section (130), the transition heat exchange section (120) includes a second tube body (121) and a second fin (122) provided on the second tube body, the second tube body (121) is connected between the smooth tube section (110) and the first tube body (1), the second fin (122) is provided on the second tube body (121), and the second fin (122) has a different structure from the first fin (4); wherein, the outer surface of the smooth tube section (110), the outer end surface of the first fin (4) along the radial direction of the first tube body (1), and the outer end surface of the second fin (122) along the radial direction of the second tube body (121) are on the same cylindrical surface.

23. A horizontal shell-and-tube heat exchanger, characterized in that, The horizontal shell-and-tube heat exchanger includes the heat exchange tube according to any one of claims 1 to 22.

24. A heat pump air conditioner unit, characterized in that, It includes the horizontal shell-and-tube heat exchanger according to claim 23.

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