Refrigerant radiator and air conditioner with same

Abstract

The utility model discloses a refrigerant radiator and an air conditioner with the same. A heat dissipation channel is arranged in the refrigerant radiator, a refrigerant circulation area for refrigerant circulation is defined by the channel wall of the heat dissipation channel, the channel wall comprises a plurality of protrusions arranged at intervals, a groove is formed between any two adjacent protrusions, the protruding height of the protrusions towards the refrigerant circulation area is L1, and L1 meets the conditions that L1 is larger than or equal to 0.3 mm, and L1 is smaller than or equal to 0.5 mm. According to the refrigerant radiator, the channel wall is arranged to be of the structure that the protrusions and the grooves are alternately arranged, the internal surface area of the channel wall can be increased, and therefore the heat exchange capacity between a refrigerant and the refrigerant radiator is enhanced, and the cooling efficiency of the refrigerant is improved.

Description

Refrigerant radiator and air conditioner having such refrigerant radiator Technical Field

[0001] This application relates to the field of air conditioning technology, and more specifically, to a refrigerant radiator and an air conditioner having the refrigerant radiator. Background Technology

[0002] In related technologies, refrigerant radiators transfer refrigerant through internal heat dissipation channels. The inner walls of these channels are smooth cylindrical or elliptical cylindrical surfaces. The flow resistance of the refrigerant within these channels mainly depends on factors such as fluid viscosity and flow velocity, and is relatively stable. This stable, low-resistance flow state is not conducive to transferring heat from the refrigerant to the radiator. Under some high-temperature conditions, the heat transfer performance requirements are extremely high, and the refrigerant cooling requirements cannot be met. Summary of the Invention

[0003] This application aims to at least partially address one of the aforementioned technical problems in the prior art. To this end, this application proposes a refrigerant radiator that improves the heat dissipation efficiency of the refrigerant.

[0004] This application also proposes an air conditioner having the aforementioned refrigerant radiator.

[0005] According to an embodiment of this application, the refrigerant radiator has a heat dissipation channel inside. The channel wall of the heat dissipation channel encloses a refrigerant flow area for refrigerant flow. The channel wall includes a plurality of spaced protrusions, and a groove is formed between any two adjacent protrusions. The height of the protrusion protruding toward the refrigerant flow area is L1, and L1 satisfies: L1≥0.3mm, L1≤0.5mm.

[0006] The channel walls have protrusions and grooves. When the refrigerant flows within the heat dissipation channel, these protrusions and grooves disrupt the originally smooth laminar flow state of the refrigerant, promoting turbulence. Turbulence allows for more thorough molecular mixing within the refrigerant, enabling the refrigerant near the channel walls to continuously exchange positions with the refrigerant near the center of the heat dissipation channel. This allows the warmer portions of the refrigerant to come into contact with the cooler channel walls more frequently, thereby accelerating heat transfer and improving heat dissipation efficiency.

[0007] The height L1 of the protrusion facing the refrigerant flow area has a significant impact on heat dissipation performance. Appropriately increasing the height L1 can increase the heat exchange area between the protrusion and the refrigerant; however, excessive protrusion height will increase refrigerant flow resistance, affecting the overall system performance. By setting L1 to 0.3mm–0.5mm, the heat exchange area between the protrusion and the refrigerant can be increased without causing excessive refrigerant flow resistance.

[0008] According to the embodiments of this application, the refrigerant radiator can increase the internal surface area of ​​the channel wall by setting the channel wall into a structure with alternating protrusions and grooves, thereby enhancing the heat exchange capacity between the refrigerant and the refrigerant radiator, and thus improving the heat dissipation efficiency of the refrigerant.

[0009] According to some embodiments of this application, the channel wall includes a reference surface, the protrusion is a toothed structure, one end of the toothed structure is connected to the reference surface, and the other end of the toothed structure is separated from the reference surface and protrudes toward the refrigerant flow area.

[0010] According to some embodiments of this application, the minimum circumferential distance between two adjacent protrusions is L2, where L2 satisfies: L2 ≥ 0.1 mm, L2 ≤ 0.3 mm. By setting 0.1 mm ≤ L2 ≤ 0.3 mm, the distance between two adjacent protrusions is more suitable, the processing difficulty of the channel wall is lower, the number of protrusions is more appropriate, resulting in a larger internal surface area of ​​the channel wall, thereby improving the heat exchange efficiency between the refrigerant and the channel wall.

[0011] According to some embodiments of this application, the height of the toothed structure protruding towards the refrigerant flow area is L1, and the maximum circumferential width of the toothed structure is W. L1 and W satisfy: L1 / W ≥ 0.5, L1 / W ≤ 1.5. Appropriately increasing L1 and decreasing W can increase the heat exchange area, but an excessively large L1 may lead to increased refrigerant flow resistance, affecting the overall performance of the system. A ratio of L1 to W between 0.5 and 1.5 is more suitable.

[0012] According to some embodiments of this application, the tooth structure is a conical tooth. The large-diameter end of the tooth structure is connected to the reference surface, and the small-diameter end of the tooth structure is separated from the reference surface and protrudes towards the refrigerant flow area. Connecting the large-diameter end of the tooth structure to the reference surface ensures a relatively firm connection between the tooth structure and the reference surface, making it less likely for the tooth structure to break at the connection point when the refrigerant impacts the tooth structure.

[0013] According to some embodiments of this application, the conical tooth includes a first tooth surface and a second tooth surface, and the included angle between the first tooth surface and the second tooth surface is α, where α satisfies: α ≥ 15°, α ≤ 45°. This ensures that the conical tooth has sufficient strength, preventing breakage when the refrigerant impacts it. Simultaneously, the conical tooth has a significant disturbance effect on the refrigerant without significantly increasing the refrigerant's flow resistance.

[0014] According to some embodiments of this application, the channel wall includes a reference surface, the groove is an arc-shaped groove, and the arc-shaped groove is recessed outward from the reference surface in a direction away from the refrigerant flow area.

[0015] According to some embodiments of this application, the minimum circumferential distance between two adjacent grooves is L4, where L4 satisfies: L4 ≥ 0.1 mm, L4 ≤ 0.3 mm. Therefore, the distance between two adjacent grooves is suitable, the processing difficulty of the channel wall is relatively low, the number of grooves is appropriate, the internal surface area of ​​the channel wall is large, and the heat exchange efficiency between the refrigerant and the channel wall is high.

[0016] According to some embodiments of this application, the radius of the arc-shaped groove is R, where R satisfies: R≥0.3mm, R≤0.5mm. This increases the heat exchange area between the channel wall and the refrigerant, while simultaneously preventing excessive resistance to refrigerant flow from the channel wall.

[0017] According to some embodiments of this application, the aperture of the reference surface is L3, where L3 satisfies: L3≥5mm, L3≤12.7mm. This ensures that the flow area of ​​the heat dissipation channel is moderate, the refrigerant flow rate per unit time is appropriate, and the overall strength of the refrigerant radiator is not significantly weakened.

[0018] According to some embodiments of this application, both the protrusion and the groove extend at least along the extension direction of the heat dissipation channel.

[0019] According to some embodiments of this application, there are multiple heat dissipation channels arranged in parallel. In a plane perpendicular to the extension direction of each heat dissipation channel, the center distance between two adjacent heat dissipation channels is L0, where L0 ≥ 15mm and L0 ≤ 35mm. This ensures that the heat generated by the refrigerant in adjacent heat dissipation channels does not affect each other, resulting in a more suitable overall structure for the refrigerant radiator.

[0020] An air conditioner according to another embodiment of this application includes the refrigerant radiator described above.

[0021] According to the embodiments of the present application, by setting the channel wall of the refrigerant radiator in a structure with alternating protrusions and grooves, the internal surface area of ​​the channel wall can be increased, thereby enhancing the heat exchange capacity between the refrigerant and the refrigerant radiator, and thus improving the heat dissipation efficiency of the refrigerant.

[0022] Additional aspects and advantages of this application will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of this application. Attached Figure Description

[0023] Figure 1 is a schematic diagram of a refrigerant heat sink according to an embodiment of the present application;

[0024] Figure 2 is a partially enlarged schematic diagram of point A of the refrigerant radiator shown in Figure 1;

[0025] Figure 3 is a top view of the refrigerant radiator shown in Figure 1;

[0026] Figure 4 is an enlarged cross-sectional view along the BB section line in Figure 3;

[0027] Figure 5 is an enlarged schematic diagram of the channel wall in Figure 4;

[0028] Figure 6 is a schematic diagram of a refrigerant radiator according to another embodiment of this application;

[0029] Figure 7 is a partially enlarged schematic diagram of point C of the refrigerant radiator shown in Figure 6;

[0030] Figure 8 is a top view of the refrigerant radiator shown in Figure 6;

[0031] Figure 9 is an enlarged cross-sectional view along the DD section line in Figure 8;

[0032] Figure 10 is an enlarged schematic diagram of the channel wall in Figure 9.

[0033] Figure label:

[0034] Refrigerant radiator 10, heat dissipation channel 1, channel wall 11, reference surface 111, protrusion 112, first tooth surface 1121, second tooth surface 1122, groove 113, refrigerant flow area 12. Detailed Implementation

[0035] The embodiments of this application are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and intended to explain this application, and should not be construed as limiting this application.

[0036] In the description of this application, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this application, "multiple" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0037] The refrigerant radiator 10 according to an embodiment of the present application is described in detail below with reference to Figures 1-10. Figures 1-5 show a refrigerant radiator 10 according to one embodiment of the present application, and Figures 6-10 show a refrigerant radiator 10 according to another embodiment of the present application.

[0038] Referring to Figures 1-10, the refrigerant radiator 10 according to the embodiment of this application has a heat dissipation channel 1 inside. The channel wall 11 of the heat dissipation channel 1 encloses a refrigerant flow area 12, which is used for refrigerant flow. The channel wall 11 includes a plurality of protrusions 112, which are spaced apart from each other. A groove 113 is formed between any two adjacent protrusions 112. In other words, the protrusions 112 and the grooves 113 are arranged alternately.

[0039] Compared to related technologies where the channel wall is cylindrical or elliptical, in this application, the protrusions 112 and grooves 113 increase the internal surface area of ​​the channel wall 11. This increases the contact area between the refrigerant and the channel wall 11 as the refrigerant flows through the heat dissipation channel 1, allowing more and faster heat to be transferred to the channel wall 11, which then dissipates heat outwards, thus cooling the refrigerant. The refrigerant can be gaseous, liquid, or a gas-liquid mixture.

[0040] The channel wall 11 has protrusions 112 and grooves 113. When the refrigerant flows within the heat dissipation channel 1, these protrusions 112 and grooves 113 disrupt the originally smooth laminar flow state of the refrigerant, promoting turbulence. Turbulence allows for more thorough molecular mixing within the refrigerant, enabling the refrigerant near the channel wall 11 to continuously exchange positions with the refrigerant near the center of the heat dissipation channel 1. This allows the higher-temperature portions of the refrigerant to come into contact with the lower-temperature channel wall 11 more frequently, thereby accelerating heat transfer and improving heat dissipation.

[0041] Compared to the cylindrical channel wall in related technologies, the channel wall 11 in some embodiments of this application increases the internal surface area of ​​the channel wall 11 by 20% to 40% through the alternating arrangement of protrusions 112 and grooves 113, which greatly increases the contact area between the refrigerant and the channel wall 11 and significantly enhances the heat exchange capacity between the refrigerant and the refrigerant radiator 10.

[0042] The protrusion 112 protrudes to a height L1 towards the refrigerant flow area 12, where L1 satisfies: L1 ≥ 0.3 mm, L1 ≤ 0.5 mm, i.e., 0.3 mm ≤ L1 ≤ 0.5 mm. In other words, the protrusion 112 protrudes to a height of 0.3 mm to 0.5 mm towards the refrigerant flow area 12. For example, L1 can be 0.3 mm, 0.32 mm, 0.35 mm, 0.4 mm, 0.45 mm, 0.5 mm, or other values ​​between 0.3 mm and 0.5 mm.

[0043] The height L1 of the protrusion 112 protruding towards the refrigerant flow area 12 has a significant impact on heat dissipation performance. Appropriately increasing the height L1 of the protrusion 112 towards the refrigerant flow area 12 can increase the heat exchange area between the protrusion 112 and the refrigerant; however, an excessively large protrusion 112 height will increase the refrigerant flow resistance, affecting the overall system performance. By setting L1 to 0.3mm to 0.5mm, the heat exchange area between the protrusion 112 and the refrigerant can be increased, while the refrigerant flow resistance of the protrusion 112 is not excessive. When L1 < 0.3mm, the height of the protrusion 112 is too small, and the increase in the internal surface area of ​​the channel wall 11 is minimal, making it difficult to significantly increase the heat exchange efficiency between the protrusion 112 and the refrigerant; when L1 > 0.5mm, the height of the protrusion 112 is too large, leading to increased refrigerant flow resistance.

[0044] In some embodiments, L1 can be 0.38 mm, which can increase the heat exchange area between the protrusion 112 and the refrigerant, while ensuring that the protrusion 112 does not cause excessive resistance to the flow of the refrigerant.

[0045] According to the embodiments of this application, the refrigerant radiator 10 can increase the internal surface area of ​​the channel wall 11 by setting the channel wall 11 with alternating protrusions 112 and grooves 113, thereby enhancing the heat exchange capacity between the refrigerant and the refrigerant radiator 10 and improving the heat dissipation efficiency of the refrigerant.

[0046] In some embodiments of this application, referring to Figures 4-5, the channel wall 11 includes a reference surface 111 and a protrusion 112 that is a toothed structure. One end of the toothed structure is connected to the reference surface 111, and the other end of the toothed structure is separated from the reference surface 111 and protrudes towards the refrigerant flow area 12. When the refrigerant flows inside the heat dissipation channel 1, the refrigerant is in direct contact with the toothed structure. In addition to heat exchange with the reference surface 111, the refrigerant can also exchange heat with the surface of the toothed structure. Compared with the related art, which only has a reference surface without a toothed structure or groove 113, in this application, the toothed structure increases the heat exchange area between the refrigerant and the channel wall 11, thus improving the heat exchange effect between the refrigerant and the channel wall 11.

[0047] In the example shown in Figures 4-5, the other end of the toothed structure protrudes toward the center of the refrigerant flow area 12.

[0048] In some embodiments of this application, as shown in Figures 4-5, the reference surface 111 is a cylindrical surface, and the toothed structure protrudes radially from the reference surface 111 toward the center.

[0049] In some embodiments of this application, referring to Figures 4-5, the minimum circumferential distance between two adjacent protrusions 112 is L2, which satisfies: L2 ≥ 0.1 mm, L2 ≤ 0.3 mm, that is, 0.1 mm ≤ L2 ≤ 0.3 mm. In other words, the minimum circumferential distance between two adjacent protrusions 112 is 0.1 mm to 0.3 mm. For example, L2 can be 0.1 mm, 0.15 mm, 0.2 mm, 0.25 mm, 0.3 mm, or other values ​​between 0.1 mm and 0.3 mm.

[0050] When L2 < 0.1 mm, the distance between two adjacent protrusions 112 is too small, significantly increasing the processing difficulty of the channel wall 11. When L2 > 0.3 mm, the distance between two adjacent protrusions 112 is too large, reducing the number of protrusions 112 and resulting in a smaller internal surface area of ​​the channel wall 11, thus leading to lower heat exchange efficiency between the refrigerant and the channel wall 11. By setting 0.1 mm ≤ L2 ≤ 0.3 mm, the distance between two adjacent protrusions 112 is more suitable, the processing difficulty of the channel wall 11 is reduced, and the number of protrusions 112 is more suitable, resulting in a larger internal surface area of ​​the channel wall 11, thereby improving the heat exchange efficiency between the refrigerant and the channel wall 11.

[0051] In some embodiments, L2 = 0.18 mm, the distance between two adjacent protrusions 112 is appropriate, the number of protrusions 112 is moderate, the internal surface area of ​​the channel wall 11 is large, and the heat exchange efficiency between the refrigerant and the channel wall 11 is high.

[0052] In some embodiments of this application, referring to Figures 4-5, the height of the toothed structure protruding towards the refrigerant flow area 12 is L1, where L1 is the tooth height of the toothed structure, and the maximum circumferential width of the toothed structure is W, where W is the tooth width of the toothed structure. L1 and W satisfy: L1 / W ≥ 0.5, L1 / W ≤ 1.5, that is, 0.5 ≤ L1 / W ≤ 1.5. In other words, the ratio of the height of the toothed structure protruding towards the refrigerant flow area 12 to the maximum circumferential width of the toothed structure is 0.5 to 1.5. For example, L1 / W can be 0.5, 0.8, 1.0, 1.2, 1.5, or other values ​​between 0.5 and 1.5.

[0053] When L1 / W < 0.5, the tooth structure is too short and wide, resulting in less turbulence of the refrigerant; when L1 / W > 1.5, the tooth structure is too tall and narrow, resulting in poor strength of the tooth structure. When the refrigerant impacts the tooth structure, it is easy for the tooth structure to break, causing debris to mix into the refrigerant. When the refrigerant enters the working equipment (such as an air conditioner), it can easily cause damage to the equipment.

[0054] Appropriately increasing the tooth height L1 and decreasing the tooth width W can increase the heat exchange area, but excessive tooth height may increase the refrigerant flow resistance and affect the overall performance of the system. The ratio of tooth width to tooth height is more suitable between 0.5 and 1.5.

[0055] In some embodiments, L1 / W = 0.9, the distance between two adjacent protrusions 112 is appropriate, the number of protrusions 112 is moderate, the internal surface area of ​​the channel wall 11 is large, and the heat exchange efficiency between the refrigerant and the channel wall 11 is high.

[0056] The height of the toothed structure protruding towards the refrigerant flow area 12 is the same as the depth of the groove 113 recessed in the direction away from the refrigerant flow area 12, both being L1.

[0057] In some embodiments of this application, referring to Figures 4-5, the tooth structure is a conical tooth. The large-diameter end of the tooth structure is connected to the reference surface 111, while the small-diameter end of the tooth structure is separated from the reference surface 111 and protrudes towards the refrigerant flow area 12. In the example shown in Figures 4-5, the small-diameter end of the tooth structure protrudes towards the center of the refrigerant flow area 12. Connecting the large-diameter end of the tooth structure to the reference surface 111 ensures a relatively strong connection between the tooth structure and the reference surface 111, preventing the tooth structure from easily breaking off at the connection point when the refrigerant impacts it.

[0058] In some embodiments of this application, referring to Figures 4-5, the conical tooth includes a first tooth surface 1121 and a second tooth surface 1122. The included angle between the first tooth surface 1121 and the second tooth surface 1122 is α, which satisfies the following conditions: α ≥ 15°, α ≤ 45°, that is, 15° ≤ α ≤ 45°. In other words, the included angle between the first tooth surface 1121 and the second tooth surface 1122 is 15° to 45°. For example, α can be 15°, 20°, 25°, 30°, 35°, 40°, 45°, or other values ​​between 15° and 45°.

[0059] When α < 15°, the conical teeth are thinner and have lower strength. When refrigerant impacts the conical teeth, they are prone to breakage, causing debris to mix into the refrigerant. When the refrigerant enters the working equipment (such as an air conditioner), it can easily cause damage to the equipment. At the same time, the conical teeth have a weak disturbance effect on the refrigerant. When α > 45°, the conical teeth are thicker, which greatly increases the flow resistance of the refrigerant and increases the energy consumption of the system.

[0060] By setting 15°≤α≤45°, the conical teeth can be guaranteed to have sufficient strength. When the refrigerant impacts the conical teeth, they are not easy to break. At the same time, the conical teeth have a greater disturbance effect on the refrigerant and will not significantly increase the flow resistance of the refrigerant.

[0061] In some embodiments, 15°≤α≤25°, so that the flow direction of the refrigerant in the heat dissipation channel 1 changes relatively little and the flow resistance is low.

[0062] In some embodiments, 35°≤α≤45° can enhance the turbulence of the refrigerant and improve the heat exchange efficiency between the refrigerant and the conical teeth.

[0063] In some embodiments, α = 42°, so that the flow direction of the refrigerant in the heat dissipation channel 1 changes relatively little, the flow resistance is low, and the turbulence of the refrigerant is greater, which is beneficial to improving the heat exchange efficiency between the refrigerant and the conical teeth.

[0064] In a plane perpendicular to the extension direction of the heat dissipation channel 1, as shown in Figures 4-5, the first tooth surface 1121 and the second tooth surface 1122 are constructed in a "V" shape, with the apex angle of the "V" shape being α.

[0065] In some embodiments of this application, referring to Figures 6-10, the channel wall 11 includes a reference surface 111, and the groove 113 is an arc-shaped groove that is recessed outward from the reference surface 111 in a direction away from the refrigerant flow area 12. The arc-shaped groove is a circular arc-shaped groove, which has a simple structure and is easy to process.

[0066] In a plane perpendicular to the extension direction of the heat dissipation channel 1, as shown in Figures 9-10, the arc-shaped groove is recessed radially outward from the reference plane 111 toward the center of the refrigerant flow area 12.

[0067] In some embodiments of this application, referring to Figures 9-10, specifically, the minimum circumferential distance between two adjacent grooves 113 is L4, which satisfies: L4 ≥ 0.1 mm, L4 ≤ 0.3 mm, that is, 0.1 mm ≤ L4 ≤ 0.3 mm. In other words, in the circumferential direction of the heat dissipation channel 1, the minimum circumferential distance between two adjacent grooves 113 is 0.1 mm to 0.3 mm. When the reference surface 111 is a cylindrical surface, the circumferential direction of the heat dissipation channel 1 is the circumferential direction of the heat dissipation channel 1. For example, L4 can be 0.1 mm, 0.15 mm, 0.2 mm, 0.25 mm, 0.3 mm, or other values ​​between 0.1 mm and 0.3 mm.

[0068] When L4 < 0.1 mm, the distance between two adjacent grooves 113 is too small, which will significantly increase the processing difficulty of the channel wall 11; when L4 > 0.3 mm, the distance between two adjacent grooves 113 is too large, the number of grooves 113 is reduced, resulting in a smaller internal surface area of ​​the channel wall 11, which in turn leads to a lower heat exchange efficiency between the refrigerant and the channel wall 11.

[0069] By setting 0.1mm≤L4≤0.3mm, the distance between two adjacent grooves 113 is more suitable, the processing difficulty of the channel wall 11 is less, the number of grooves 113 is more suitable, the internal surface area of ​​the channel wall 11 is larger, and the heat exchange efficiency between the refrigerant and the channel wall 11 is higher.

[0070] In some embodiments, L4 = 0.18 mm, the distance between two adjacent grooves 113 is appropriate, the number of grooves 113 is moderate, the internal surface area of ​​the channel wall 11 is large, and the heat exchange efficiency between the refrigerant and the channel wall 11 is high.

[0071] In some embodiments of this application, referring to Figures 9-10, the radius of the arc-shaped groove is R, which satisfies: R ≥ 0.3 mm, R ≤ 0.5 mm, that is, 0.3 mm ≤ R ≤ 0.5 mm. In other words, the radius of the arc-shaped groove is 0.3 mm to 0.5 mm. R and L1 satisfy: R = L1. For example, R can be 0.3 mm, 0.32 mm, 0.35 mm, 0.4 mm, 0.45 mm, 0.5 mm, or other values ​​between 0.3 mm and 0.5 mm.

[0072] When R is too small, the height L1 of the protrusion 112 adjacent to the groove 113 is also too small, resulting in a small increase in the internal surface area of ​​the channel wall 11, making it difficult to significantly increase the heat exchange efficiency between the channel wall 11 and the refrigerant. When R is too large, the height L1 of the protrusion 112 adjacent to the groove 113 is also too large, which will lead to an increase in the refrigerant flow resistance.

[0073] By setting 0.3mm≤R≤0.5mm, the heat exchange area between the channel wall 11 and the refrigerant can be increased, while the resistance of the channel wall 11 to the refrigerant flow will not be too large.

[0074] In some embodiments, R can be 0.39 mm, which can increase the heat exchange area between the channel wall 11 and the refrigerant, while the protrusion 112 does not cause excessive resistance to the flow of the refrigerant.

[0075] In some embodiments of this application, referring to Figures 4-5 and 9-10, the aperture of the reference surface 111 is L3, which satisfies: L3 ≥ 5mm, L3 ≤ 12.7mm, that is, 5mm ≤ L3 ≤ 12.7mm. In other words, the aperture of the reference surface 111 is 5mm to 12.7mm. For example, L3 can be 5mm, 7mm, 9mm, 11mm, 12mm, 12.7mm, or other values ​​between 5mm and 12.7mm.

[0076] When L3 is too small, for example, L3 < 5mm, the flow area of ​​heat dissipation channel 1 is too small, resulting in insufficient refrigerant flow per unit time. When L3 is too large, for example, L3 > 12.7mm, it will weaken the overall strength of the refrigerant radiator 10. By setting 5mm ≤ L3 ≤ 12.7mm, the flow area of ​​heat dissipation channel 1 can be ensured to be moderate, the refrigerant flow per unit time can be appropriate, and the overall strength of the refrigerant radiator 10 will not be significantly weakened.

[0077] In some embodiments, L3 can be 10mm. In this case, the flow area of ​​the heat dissipation channel 1 is moderate, the amount of refrigerant passing through per unit time is appropriate, and it will not significantly weaken the overall strength of the refrigerant radiator 10.

[0078] In some embodiments of this application, both the protrusion 112 and the groove 113 extend at least along the extending direction of the heat dissipation channel 1. In the embodiments shown in Figures 1-2 and 6-7, the heat dissipation channel 1 extends in a straight line, and the extending direction of the heat dissipation channel 1 is the F1-F2 direction, with both the protrusion 112 and the groove 113 extending along the F1-F2 direction.

[0079] In some embodiments not shown in the figure, the heat dissipation channel 1 extends in a straight line along the F1-F2 direction, and the protrusion 112 and the groove 113 both extend in a spiral shape along the F1-F2 direction.

[0080] In some other embodiments not shown in the figure, the heat dissipation channel 1 extends in a straight line along the F1-F2 direction, and the protrusion 112 and the groove 113 both extend in an arc shape along a direction perpendicular to F1-F2.

[0081] In some embodiments of this application, referring to Figures 1, 4, 6, and 9, there are multiple heat dissipation channels 1 arranged in parallel. In a plane perpendicular to the extending direction of the heat dissipation channels 1, the center-to-center distance between two adjacent heat dissipation channels 1 is L0, where L0 satisfies: L0 ≥ 15mm, L0 ≤ 35mm, i.e., 15mm ≤ L0 ≤ 35mm. In other words, the center-to-center distance between two adjacent heat dissipation channels 1 is 15mm to 35mm. For example, L0 can be 15mm, 20mm, 25mm, 30mm, 35mm, or other values ​​between 15mm and 35mm.

[0082] When L0 is too small, for example, L0 < 15mm, the distance between two adjacent heat dissipation channels 1 is too close, causing the refrigerant heat in the two adjacent heat dissipation channels 1 to affect each other, resulting in poor heat dissipation. When L0 is too large, for example, L0 > 35mm, the distance between two adjacent heat dissipation channels 1 is too large, resulting in an overly large overall structure of the refrigerant radiator 10. By setting 15mm ≤ L0 ≤ 35mm, the refrigerant heat in the two adjacent heat dissipation channels 1 will not affect each other, and the overall structure of the refrigerant radiator 10 is more suitable.

[0083] In some embodiments, L0 can be 22mm, so that the distance between two adjacent heat dissipation channels 1 is moderate, so that the heat of the refrigerant in the two adjacent heat dissipation channels 1 will not affect each other, and the overall structure of the refrigerant radiator 10 is moderate.

[0084] In some embodiments of this application, referring to Figures 1-10, the number of protrusions 112 is 30 to 60. When the number of protrusions 112 is too small, the heat exchange area between the channel wall 11 and the refrigerant is small, resulting in poor heat exchange effect; when the number of protrusions 112 is too large, it will significantly increase the processing difficulty and cost of the channel wall 11. Setting the number of protrusions 112 to 30 to 60 results in a larger heat exchange area between the channel wall 11 and the refrigerant, a better heat exchange effect, and does not significantly increase the processing difficulty and cost of the channel wall 11. For example, the number of protrusions 112 can be 30, 35, 40, 45, 50, 55, or 60.

[0085] An air conditioner according to another embodiment of this application includes the refrigerant radiator 10 of the above embodiment.

[0086] According to the embodiments of this application, by setting the channel wall 11 of the refrigerant radiator 10 into a structure in which protrusions 112 and grooves 113 are arranged alternately, the internal surface area of ​​the channel wall 11 can be increased, thereby enhancing the heat exchange capacity between the refrigerant and the refrigerant radiator 10, and thus improving the heat dissipation efficiency of the refrigerant.

[0087] In the description of this application, it should be understood that the terms "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this application.

[0088] In this application, unless otherwise expressly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection, an electrical connection, or a connection that allows communication between them; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication between two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this application according to the specific circumstances.

[0089] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of this application. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. In addition, those skilled in the art can combine and integrate the different embodiments or examples described in this specification.

[0090] Although embodiments of this application have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting this application. Those skilled in the art can make changes, modifications, substitutions and variations to the above embodiments within the scope of this application.

Claims

1. A refrigerant radiator (10), characterized in that, The refrigerant radiator (10) has a heat dissipation channel (1) inside. The channel wall (11) of the heat dissipation channel (1) encloses a refrigerant flow area (12) for refrigerant flow. The channel wall (11) includes a plurality of spaced protrusions (112). A groove (113) is formed between any two adjacent protrusions (112). The height of the protrusion (112) protruding toward the refrigerant flow area (12) is L1, and L1 satisfies: L1≥0.3mm, L1≤0.5mm.

2. The refrigerant radiator (10) according to claim 1, characterized in that, The channel wall (11) includes a reference surface (111), and the protrusion (112) is a toothed structure. One end of the toothed structure is connected to the reference surface (111), and the other end of the toothed structure is separated from the reference surface (111) and protrudes toward the refrigerant flow area (12).

3. The refrigerant radiator (10) according to claim 2, characterized in that, The minimum circumferential distance between two adjacent protrusions (112) is L2, which satisfies: L2≥0.1mm, L2≤0.3mm.

4. The refrigerant radiator (10) according to claim 2, characterized in that, The toothed structure protrudes to the refrigerant flow area (12) at a height of L1, and the maximum circumferential width of the toothed structure is W. L1 and W satisfy: L1 / W≥0.5, L1 / W≤1.

5.

5. The refrigerant radiator (10) according to claim 2, characterized in that, The tooth structure is a tapered tooth. The large-diameter end of the tooth structure is connected to the reference surface (111), and the small-diameter end of the tooth structure is separated from the reference surface (111) and protrudes toward the refrigerant flow area (12).

6. The refrigerant radiator (10) according to claim 5, characterized in that, The conical tooth includes a first tooth surface (1121) and a second tooth surface (1122), and the included angle between the first tooth surface (1121) and the second tooth surface (1122) is α, which satisfies: α≥15°, α≤45°.

7. The refrigerant radiator (10) according to claim 1, characterized in that, The channel wall (11) includes a reference surface (111), and the groove (113) is an arc-shaped groove that is recessed outward from the reference surface (111) in a direction away from the refrigerant flow area (12).

8. The refrigerant radiator (10) according to claim 7, characterized in that, The minimum circumferential distance between two adjacent grooves (113) is L4, which satisfies: L4≥0.1mm, L4≤0.3mm.

9. The refrigerant radiator (10) according to claim 7, characterized in that, The radius of the arc-shaped groove is R, which satisfies: R≥0.3mm, R≤0.5mm.

10. The refrigerant radiator (10) according to claim 2 or 7, characterized in that, The aperture of the reference surface (111) is L3, and L3 satisfies: L3≥5mm, L3≤12.7mm.

11. The refrigerant radiator (10) according to any one of claims 1-9, characterized in that, Both the protrusion (112) and the groove (113) extend at least along the extension direction of the heat dissipation channel (1).

12. The refrigerant radiator (10) according to any one of claims 1-9, characterized in that, There are multiple heat dissipation channels (1), and the multiple heat dissipation channels (1) are arranged in parallel. In a plane perpendicular to the extension direction of the heat dissipation channel (1), the center distance between two adjacent heat dissipation channels (1) is L0, and L0 satisfies: L0≥15mm, L0≤35mm.

13. An air conditioner characterized by comprising: Includes the refrigerant radiator (10) according to any one of claims 1-12.

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