A siphon heat pipe radiator for an air conditioner outdoor unit

Abstract

This invention discloses a siphon heat pipe radiator for an outdoor unit of an air conditioner, relating to the field of energy-saving air conditioning. It includes an evaporator and a condenser connected together. The evaporator is mounted on the outdoor unit of the air conditioner. The condenser includes a manifold connected to the outlet of the condenser. A first partition plate is arranged inside the manifold along a first direction and is connected to the evaporator. The first partition plate divides the manifold into an upper chamber and a lower chamber, which are sequentially distributed along a second direction. A connecting area is formed between the side of the first partition plate away from the evaporator and the side wall of the manifold, connecting the upper and lower chambers. Through holes are formed on the first partition plate. A proximal region, a middle region, and a distal region are formed on the first partition plate along the first direction, with the density of through holes corresponding to the proximal, middle, and distal regions increasing sequentially. This invention solves the problems of gas-liquid entrainment and uneven vapor distribution.

Description

Technical Field

[0001] This invention relates to the field of energy-saving air conditioning, and more particularly to a siphon heat pipe radiator for outdoor units of air conditioners. Background Technology

[0002] The controller of the outdoor unit of an air conditioner, as the core electronic control unit, integrates power modules such as IGBTs and MOSFETs, as well as drive circuits. It generates a significant amount of heat during operation. Insufficient heat dissipation can lead to overheating of components, resulting in increased switching losses, compressor frequency reduction, and even shutdown protection. Existing technologies include heat pipe-based solutions for controller cooling. Siphon heat pipes, in particular, have attracted attention due to their ability to utilize gravity for refrigerant circulation and eliminate the need for a capillary wick structure. For example, the refrigerant absorbs heat from the heating element in the evaporator, causing it to vaporize and rise to the condenser for heat release and condensation. Then, it flows back to the evaporator by gravity, forming a siphon cycle.

[0003] The controller of an air conditioner's outdoor unit, as the core electronic control unit, integrates power modules such as IGBTs and MOSFETs, as well as drive circuits. It generates a significant amount of heat during operation. Inadequate heat dissipation can lead to overheating of components, resulting in increased switching losses, compressor frequency reduction, and even shutdown protection. In energy-efficient air conditioners and dual-mode solar heat pump air conditioning units, where energy efficiency is paramount, the controller's heat dissipation efficiency directly impacts the overall energy-saving performance. Existing technologies utilize heat pipe principles for controller heat dissipation. Siphon heat pipes, in particular, have attracted attention due to their ability to achieve working fluid circulation using gravity and eliminating the need for a capillary wick structure. For example, the evaporator absorbs heat from the heating element, causing the working fluid to vaporize and rise to the condenser for heat release and condensation, before returning to the evaporator by gravity, forming a siphon cycle. These heat pipe-based heat dissipation solutions can serve as an important component of energy-saving heat exchange devices, improving heat dissipation efficiency while helping to reduce the overall energy consumption of the air conditioning system.

[0004] Existing siphon heat pipe radiators have some drawbacks in practical applications, such as gas-liquid entrainment and uneven steam distribution. Specifically, during application, the steam generated in the evaporation section easily carries unevaporated liquid working fluid when entering the manifold, resulting in insufficient steam dryness entering the condenser. The liquid working fluid occupies the internal space of the condenser, significantly reducing heat exchange efficiency and disrupting the gas-liquid balance of the siphon cycle. At the same time, due to the simple internal structure of existing manifolds, the flow rate is high near the evaporation point and low far from the evaporation point, causing significant differences in the surface temperature distribution of the condenser. This leads to a prominent risk of localized overheating, making it impossible for the siphon-driven circulation head to effectively act on the entire condenser.

[0005] Therefore, a siphon heat pipe radiator for outdoor units of air conditioners is proposed to solve the problems of gas-liquid entrainment and uneven steam distribution. Summary of the Invention

[0006] The purpose of this invention is to provide a siphon heat pipe radiator for outdoor units of air conditioners, which solves the problems of gas-liquid entrainment and uneven steam distribution.

[0007] To achieve this objective, the present invention adopts the following technical solution: A siphon heat pipe radiator for an outdoor unit of an air conditioner includes an evaporator and a condenser connected together. The evaporator is disposed on the outdoor unit of the air conditioner. The condenser includes a manifold connected to the outlet of the condenser. A first partition plate is disposed inside the manifold along a first direction and is connected to the evaporator. The first partition plate divides the manifold into an upper chamber and a lower chamber, which are sequentially distributed along a second direction. A communication area is formed between the side of the first partition plate away from the evaporator and the side wall of the manifold, which connects the upper chamber and the lower chamber. A through hole is formed on the first partition plate. When the gas-liquid mixture discharged from the outlet of the condenser enters the upper chamber, the gas and liquid respectively enter the lower chamber through the through hole and the communication area. The first partition plate has a proximal region, a middle region and a distal region formed along a first direction. The proximal region and the distal region are respectively close to the air outlet and the connecting region. The distribution density of the through holes on the first partition plate corresponding to the proximal region, the middle region and the distal region increases sequentially.

[0008] The inner diameter of the through hole in the proximal region gradually decreases along the second direction, while the inner diameter of the through hole in the distal region gradually increases along the second direction.

[0009] A second partition plate is provided inside the manifold corresponding to the first partition plate. A middle chamber is formed between the first partition plate and the second partition plate. The second partition plate has the same structure as the first partition plate. The through holes in the middle section of the first partition plate and the second partition plate are inclined towards the distal section.

[0010] The inclination angle of the through hole in the middle section of the first partition plate is 10-20°, and the inclination angle of the through hole in the middle section of the second partition plate is 25-45°.

[0011] The inlet and outlet of the corresponding through holes in the proximal, middle and distal regions of the first partition plate are all larger than the inlet and outlet of the corresponding through holes in the second partition plate.

[0012] The through holes in the proximal region of the first partition plate and the corresponding through holes in the proximal region of the second partition plate are axially aligned and circumferentially misaligned; the through holes in the middle region of the first partition plate and the corresponding through holes in the middle region of the second partition plate are axially misaligned and circumferentially misaligned; the through holes in the distal region of the first partition plate and the corresponding through holes in the distal region of the second partition plate are axially aligned and circumferentially misaligned.

[0013] The second partition plate is inclined toward the connecting area, and the inclination angle of the second partition plate is 5-10°.

[0014] The height of the middle chamber gradually increases along the first direction.

[0015] The condensation section further includes a condenser and a liquid storage pipe. The manifold, the condenser, and the liquid storage pipe are connected in sequence along the second direction. The end of the evaporation section away from the manifold is connected to the liquid storage pipe.

[0016] The condenser includes several guide tubes that connect the collecting tube and the liquid storage tube, and heat dissipation fins are provided between two adjacent guide tubes.

[0017] Compared with the prior art, the present invention has the following beneficial effects: This invention provides a siphon heat pipe radiator for an outdoor unit of an air conditioner. A first partition plate divides the manifold into an upper chamber and a lower chamber. A connecting zone is formed between the side of the first partition plate away from the evaporator and the side wall of the manifold. This allows steam and its entrained liquid working fluid to enter the upper chamber. The liquid working fluid, due to inertia, impacts the surface of the first partition plate or is intercepted by its edge, and then flows directly into the lower chamber along the connecting zone by gravity. The steam, however, enters the lower chamber through through holes in the first partition plate. This achieves physical separation of the gas and liquid phases, effectively solving the problem of gas-liquid entrainment in existing technologies. This addresses the issues of insufficient steam dryness and reduced heat exchange efficiency entering the condenser. Simultaneously, by setting near-end, middle-end, and far-end zones along a first direction on the first partition plate, and increasing the density of through-holes in these zones sequentially, the steam experiences maximum flow resistance in the near-end zone, forcing some steam to flow towards the middle and far-end zones. This results in a more uniform axial flow distribution of steam entering the lower chamber, effectively solving the problem of significant differences in condenser surface temperature distribution and prominent local overheating risks caused by uneven steam distribution in existing technologies. Furthermore, this structure integrates gas-liquid separation and axial flow equalization functions within the manifold, eliminating the need for additional external gas-liquid separation devices or control components. This simplifies the overall structure, reduces manufacturing costs and assembly complexity, and achieves passive steam flow regulation without relying on moving parts or external sensors, enhancing the radiator's adaptability to fluctuations in the operating conditions of the outdoor air conditioning unit. Attached Figure Description

[0018] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0019] The structures, proportions, sizes, etc., shown in the accompanying drawings of this specification are only for the purpose of assisting those skilled in the art in understanding and reading the content disclosed in the specification, and are not intended to limit the conditions under which the present invention can be implemented. Therefore, they have no substantial technical significance. Any modifications to the structure, changes in the proportions, or adjustments to the size, without affecting the effects and objectives that the present invention can produce, should still fall within the scope of the technical content disclosed in the present invention.

[0020] Figure 1 This is a schematic diagram of the overall structure of the present invention; Figure 2 This is a schematic diagram of the internal structure of the manifold in this invention; Figure 3 In this invention Figure 2 Enlarged schematic diagram of the structure at point A; Figure 4 This is a cross-sectional view of the first partition plate in this invention; Figure 5 This is a schematic diagram of the distribution structure of the first partition plate and the second partition plate in this invention; Figure 6 This is a top view of the structure of the first partition plate in this invention.

[0021] Diagram description: 1. Condensation section; 11. Manifold; 111. Upper chamber; 112. Middle chamber; 113. Lower chamber; 114. Connecting area; 12. First partition plate; 121. Proximal area; 122. Middle area; 123. Distal area; 124. Through hole; 13. Second partition plate; 14. Condensation component; 141. Guide pipe; 142. Heat dissipation fins; 15. Liquid storage pipe; 2. Evaporation section. Detailed Implementation

[0022] To make the objectives, features, and advantages of this invention more apparent and understandable, the technical solutions of the embodiments of this invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the embodiments described below are only some embodiments of this invention, and not all embodiments. Based on the embodiments of this invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this invention.

[0023] In the description of this invention, it should be understood that the terms "upper," "lower," "top," "bottom," "inner," and "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 the invention 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 the invention. It should be noted that when a component is considered to be "connected" to another component, it can be directly connected to the other component or there may be a component positioned centrally in the connection.

[0024] Example 1: Please see Figure 1-6 This embodiment of a siphon heat pipe radiator for an outdoor unit of an air conditioner includes an evaporator 2 and a condenser 1 connected together. The evaporator 2 is disposed on the outdoor unit of the air conditioner. The condenser 1 includes a manifold 11 connected to the outlet end of the condenser 1. A first partition plate 12 is disposed in the manifold 11 along a first direction and is connected to the evaporator 2. The first partition plate 12 divides the manifold 11 into an upper chamber 111 and a lower chamber 113, which are distributed sequentially along a second direction. A connecting area 114 is formed between the side of the first partition plate 12 away from the evaporator 2 and the side wall of the manifold 11. The connecting area 114 connects the upper chamber 111 and the lower chamber 113. A through hole 124 is formed on the first partition plate 12. When the gas-liquid mixture discharged from the outlet end of the condenser 1 enters the upper chamber 111, the gas and liquid respectively enter the lower chamber 113 through the through hole 124 and the connecting area 114. The first partition plate 12 has a proximal region 121, a middle region 122 and a distal region 123 formed along the first direction. The connecting region 114 is formed by a pre-reserved gap between the side of the first partition plate 12 near the distal region 123 and the side wall of the manifold 11. The proximal region 121 and the distal region 123 are close to the gas outlet and the connecting region 114, respectively. The distribution density of the through holes 124 on the first partition plate 12 corresponding to the proximal region 121, the middle region 122 and the distal region 123 increases sequentially.

[0025] When in use, after the siphon heat pipe radiator absorbs heat from the outdoor unit of the air conditioner, it will evaporate the liquid working fluid in the radiator into gas through the evaporation section 2. At this time, the steam and the entrained liquid working fluid enter the manifold 11 of the condensation section 1, and first enter the upper chamber 111 formed by the first partition plate 12. Since a connecting area 114 is formed between the side of the first partition plate 12 away from the evaporation section 2 and the side wall of the manifold 11, the connecting area 114 connects the upper chamber 111 and the lower chamber 113. Driven by the thermosiphon effect, the steam and the entrained liquid working medium flow along the upper chamber 111 towards the far end region 123. Since the density of the gaseous working medium is much smaller than that of the liquid working medium, the gas and liquid phases generate a velocity difference during the flow. The liquid working medium with a higher density is difficult to turn synchronously with the steam flow line due to inertia, so it continuously impacts the surface of the first partition plate 12 or is intercepted along the edge of the first partition plate 12. The intercepted liquid working medium gathers along the surface of the first partition plate 12 towards the connecting area 114 under the action of gravity, and directly enters the lower chamber 113 through the connecting area 114, thereby realizing the physical separation of the gas and liquid phases and preventing the liquid working medium from continuing to be transported forward to the condensation section 1 with the steam, thus solving the gas-liquid entrainment problem.

[0026] Meanwhile, after being separated in the above manner, the steam continues to flow along the upper chamber 111 and enters the lower chamber 113 through the through-holes 124 formed on the first partition plate 12. Since the first partition plate 12 has a proximal region 121, a middle region 122, and a distal region 123 formed along the first direction, the proximal region 121 is near the connection between the evaporator 2 and the manifold 11, i.e., the steam inlet end, while the distal region 123 is near the connecting region 114. Furthermore, the distribution density of the corresponding through-holes 124 on the proximal region 121, middle region 122, and distal region 123 increases sequentially, i.e., the proximal region 121 has the lowest distribution density of through-holes 124, the middle region 122 has a moderate distribution density, and the distal region 123 has the highest density. The through-holes 124 have the highest distribution density, which causes the steam to encounter the greatest flow resistance in the near-end region 121. This forces some of the steam to flow in the upper chamber 111 towards the middle region 122 and the far-end region 123. The steam then enters the lower chamber 113 through the through-holes 124, which have a higher distribution density in the middle region 122 and the far-end region 123. This makes the axial flow distribution of the steam entering the lower chamber 113 more uniform, thus solving the problem of uneven steam distribution caused by excessive flow in the near-end region 121 and insufficient flow in the far-end region 123.

[0027] Under the aforementioned structure, on the one hand, in the directional flow formed by the thermosiphon effect, the connecting area 114 acts as an independent liquid phase channel, allowing the liquid working fluid intercepted by the inertial impact of the first partition plate 12 to flow separately from the steam in the manifold 11 under the action of gravity. This avoids the shearing and entrainment of the return liquid by the high-speed steam, improves the dryness of the steam entering the condenser 1, and thus solves the gas-liquid entrainment problem. On the other hand, the increasing density of the through holes 124 along the first direction enables the steam to be evenly distributed in the axial direction of the manifold 11, eliminating the uneven heat exchange load caused by the difference in steam flow rate in each area of ​​the condenser 1. This solves the problem of uneven steam distribution, improves the overall heat exchange efficiency of the condenser 1, and enhances the stability of the siphon heat pipe radiator during the operation of the outdoor unit of the air conditioner.

[0028] Furthermore, the aforementioned structure divides the manifold 11 into an upper chamber 111 and a lower chamber 113 via the first partition plate 12, and utilizes the connecting area 114 as an independent return channel for the liquid working fluid. This achieves physical isolation between steam and liquid working fluid within the manifold 11, eliminating the need for additional gas-liquid separation devices or control components outside the manifold 11. This simplifies the overall structure and reduces manufacturing costs and assembly complexity. Since the distribution density of the through holes 124 in the near-end region 121, middle region 122, and far-end region 123 of the first partition plate 12 increases sequentially, this structure can passively regulate the steam flow rate by axially varying the distribution density of the through holes 124 without relying on moving parts or external sensors. This ensures that the manifold 11 maintains a relatively uniform steam distribution under different load conditions, enhancing the radiator's adaptability to fluctuations in the operating conditions of the outdoor air conditioning unit. The connecting zone 114 is located on the side of the first partition plate 12 away from the evaporator section 2, allowing the intercepted liquid working fluid to flow directly back to the lower chamber 113 under gravity and eventually return to the evaporator section 2. This return path is independent of the steam flow path, avoiding the risk of the return liquid being re-entrained by high-speed steam in traditional structures. This maintains high heat transfer efficiency during long-term operation and reduces performance degradation caused by gas-liquid interference. This structure integrates gas-liquid separation, axial flow equalization, and gravity return within the manifold 11, resulting in a compact overall structure that does not increase the space occupied inside the outdoor unit of the air conditioner and is compatible with existing outdoor unit condenser and duct layouts.

[0029] Furthermore, such as Figure 4 As shown, the inner diameter of the through hole 124 at the proximal region 121 gradually decreases along the second direction, while the inner diameter of the through hole 124 at the distal region 123 gradually increases along the second direction.

[0030] Because the inner diameter of the through-hole 124 at the distal region 123 gradually increases along the second direction, that is, the inner diameter of the inlet of the through-hole 124 in the direction of working fluid flow is smaller than the inner diameter of the outlet, a gradually expanding structure is formed. This gradually expanding structure reduces the flow resistance of steam at the through-hole 124 at the distal region 123, compensates for the pressure drop loss caused by the extension of the steam flow path from the upper chamber 111 to the distal region 123, and further improves the uniformity of steam distribution in the axial direction of the manifold 11; on the other hand, when the steam and the entrained non-condensable gas pass through the through-hole 124 at the distal region 123, the non-condensable gas preferentially enters the lower chamber 113 through the gradually expanding structure and is discharged through the subsequent path, avoiding the heat transfer performance degradation caused by the accumulation of non-condensable gas in the distal region 123 of the manifold 11.

[0031] Furthermore, the gradually expanding structure formed by the above method ensures gas-liquid separation efficiency by making the connecting zone 114 the main channel. The through hole 124 at the near end zone 121 achieves passive adaptive adjustment to prevent drying and liquid blockage. The through hole 124 at the far end zone 123 further optimizes the uniformity of steam distribution and provides a non-condensable gas discharge channel. The synergistic effect of the connecting zone 114, the through hole 124 at the near end zone 121, and the through hole 124 at the far end zone 123 enables the siphon heat pipe radiator to significantly improve the operational stability and long-term reliability under variable load conditions while maintaining high gas-liquid separation efficiency.

[0032] Furthermore, because the inner diameter of the through-hole 124 at the proximal region 121 gradually decreases along the second direction, that is, the inner diameter of the inlet of the through-hole 124 in the direction of working fluid flow is larger than the inner diameter of the outlet, a tapering structure is formed. In addition to undertaking the function of steam flow, this tapering structure also serves as an auxiliary channel for the return of liquid working fluid, solving the problem of adaptive regulation under variable load conditions. Specifically, when the outdoor unit of the air conditioner is under low load, the steam flow rate is small, and the pressure difference on both sides of the through hole 124 at the near end zone 121 is small. A portion of the liquid working fluid in the upper chamber 111 near the near end zone 121 can gather along the surface of the first partition plate 12 towards the near end zone 121 and enter the lower chamber 113 by gravity through the through hole 124 at the near end zone 121 to replenish the working fluid for the evaporation section 2 and prevent the evaporation section from drying out due to insufficient working fluid circulation power. When the outdoor unit of the air conditioner is under high load, the steam flow rate is large, the steam velocity in the through hole 124 at the near end zone 121 increases, and a steam pad is formed in the through hole 124, which automatically blocks the passage of liquid working fluid and prevents excessive liquid working fluid from entering the condensation section 1 and causing liquid blockage.

[0033] Under the effect of the above structure, not only is the uniformity of steam distribution in the axial direction of the manifold 11 further improved, but the heat pipe radiator can also automatically adjust the liquid supply of the evaporation section 2 according to the load change without relying on external sensors or moving parts. Thus, while solving the problem of uneven steam distribution, it also solves the problem of poor adaptability of traditional siphon heat pipe radiators under variable load conditions.

[0034] It should be noted that the through-hole 124 at the near end region 121 serves as an auxiliary supplement to the main channel of the connecting region 114. Its liquid originates from the residual working fluid in the upper chamber 111 that was not promptly discharged by the connecting region 114. Under low load, it enters the lower chamber 113 through the through-hole 124 at the near end region 121 by gravity to replenish the evaporator section 2. Under high load, a vapor pad forms within the through-hole 124 at the near end region 121, automatically blocking the liquid flow. This creates a primary-secondary division of labor with the connecting region 114, jointly maintaining a stable liquid supply to the evaporator section 2. The through-hole 124 at the far end region 123 utilizes its small inlet and large outlet structure to preferentially allow non-condensable gases (non-condensable gases refer to gases that cannot be converted into liquid through condensation under the operating temperature and pressure conditions inside the heat pipe) to enter and distribute in the lower chamber 113. This prevents accumulation and gas blockage in the far end region 123 of the manifold 11, thereby maintaining uniform steam distribution and delaying the decline in heat transfer performance.

[0035] Furthermore, the condenser section 1 also includes a condenser element 14 and a liquid storage pipe 15. The manifold 11, the condenser element 14, and the liquid storage pipe 15 are connected sequentially along the second direction. The end of the evaporator section 2 away from the manifold 11 is connected to the liquid storage pipe 15. The condenser element 14 includes a plurality of guide pipes 141, which connect the manifold 11 and the liquid storage pipe 15. Heat dissipation fins 142 are provided between two adjacent guide pipes 141.

[0036] When this siphon heat pipe radiator is working, the evaporator 2 absorbs heat from the outdoor unit of the air conditioner, causing the internal working fluid to vaporize. The density of the gaseous working fluid decreases and it naturally rises to the manifold 11. After distribution, it enters the guide pipe 141 of the condenser 14. Through the heat dissipation fins 142 arranged between adjacent guide pipes 141, it releases heat to the outside air. The gaseous working fluid condenses and transforms into a liquid working fluid, increasing its density. Relying on gravity, it descends along the guide pipe 141 and collects in the storage pipe 15. Then, it flows back to the heat absorption area of ​​the evaporator 2 through the end of the evaporator 2 away from the manifold 11, completing the circulation of the working fluid. The above process is driven by the density difference generated by the phase change of the working fluid and gravity, forming a thermosiphon effect that does not require external power. This allows the evaporator 2 to continuously transfer heat from the outdoor unit of the air conditioner to the condenser 1 and release it into the environment, thus achieving heat dissipation for the outdoor unit of the air conditioner.

[0037] It should be noted that this siphon heat pipe radiator uses the thermosiphon effect, the working principle of which is well known to those skilled in the art and will not be described in detail in this embodiment. Furthermore, the first direction is the length direction of the manifold 11, and the second direction is the height direction of the manifold 11, i.e., the flow direction of the working fluid within the manifold 11.

[0038] Understandably, the above structure effectively solves the problems of gas-liquid entrainment and uneven steam distribution. However, in some application scenarios with higher requirements for gas-liquid separation efficiency, such as when the outdoor unit of an air conditioner operates under high load or high humidity for extended periods, the number of tiny liquid droplets entrained in the steam increases, and a single-stage separation structure may be insufficient to completely intercept all droplets. To further improve separation efficiency, a second partition plate 13 with the same or similar structure as the first partition plate 12 can be added to the manifold 11 based on the first partition plate 12, forming a central chamber 112 between the first partition plate 12 and the second partition plate 13. Through multi-stage separation, the tiny droplets are intercepted and settled step by step, thereby achieving higher steam dryness. This will be illustrated below with Example 2.

[0039] Example 2: The basic content is the same as in Example 1, except that: Please see Figure 4-6 In this embodiment, a second partition plate 13 is provided in the manifold 11 corresponding to the first partition plate 12. A middle chamber 112 is formed between the first partition plate 12 and the second partition plate 13. The second partition plate 13 has the same structure as the first partition plate 12. The through holes 124 corresponding to the middle section 122 of the first partition plate 12 and the second partition plate 13 are inclined towards the distal section 123.

[0040] In application, the steam and entrained liquid working fluid from the evaporation section 2 enter the manifold 11 of the condensation section 1 and first enter the upper chamber 111 formed by the first partition plate 12. After the gas-liquid separation is initially achieved by the method described in Example 1, the steam continues to flow along the upper chamber 111 and enters the middle chamber 112 through the through hole 124 formed on the first partition plate 12. Since the second partition plate 13 has the same structure as the first partition plate 12, and the through holes 124 corresponding to the middle section 122 of the first partition plate 12 and the second partition plate 13 are inclined towards the far section 123, the steam entering the middle chamber 112 is intercepted again by the second partition plate 13 during the flow process. The tiny liquid droplets remaining in the steam impact the surface of the second partition plate 13 due to inertia and are intercepted. The intercepted liquid working fluid gathers along the surface of the second partition plate 13 towards the connecting section 114 and enters the lower chamber 113 through the connecting section 114, thereby realizing multi-stage separation of the gas and liquid phases and further improving the dryness of the steam entering the lower chamber 113.

[0041] Since a middle chamber 112 is formed between the first partition plate 12 and the second partition plate 13, and the through holes 124 corresponding to the middle section 122 of the first partition plate 12 and the second partition plate 13 are all inclined towards the distal section 123, this structure allows the steam to flow in the middle chamber 112 after passing through the first partition plate 12. The flow direction is guided by the inclined through holes 124, forming a flow path extending towards the distal section 123 in the middle chamber 112. This prolongs the residence time of the steam in the middle chamber 112, allowing the tiny droplets remaining in the steam to settle under gravity for a longer time. At the same time, the inclined through holes 124 prevent high-speed steam from directly impacting the surface of the second partition plate 13 and causing droplet splashing, thereby further improving the gas-liquid separation efficiency. Furthermore, since the second partition plate 13 has the same structure as the first partition plate 12, the second partition plate 13 also has a proximal region 121, a middle region 122 and a distal region 123 formed along the first direction. The distribution density of the corresponding through holes 124 on the proximal region 121, the middle region 122 and the distal region 123 increases sequentially. This distribution density makes the steam entering the middle chamber 112 uniformly distributed in the axial direction again. This, combined with the axial flow equalization effect of the first partition plate 12, further eliminates the problem of uneven heat exchange load caused by the difference in steam flow rate.

[0042] Based on the gas-liquid separation and uniform steam distribution functions achieved in Example 1, the above structure utilizes the central chamber 112 formed between the first partition plate 12 and the second partition plate 13 to construct a multi-stage separation path. As the steam passes through the first partition plate 12 and the second partition plate 13 in sequence, the entrained liquid working fluid is intercepted and settled step by step, significantly improving the dryness of the steam entering the condenser 14, thereby further improving the gas-liquid separation efficiency. At the same time, the through holes 124 corresponding to the middle section 122 of the first partition plate 12 and the second partition plate 13 are inclined towards the distal section 123, so that the steam forms a flow path extending to the distal section 123 in the central chamber 112. This increases the droplet settling time and avoids secondary entrainment of settled droplets by high-speed steam, thereby further improving the gas-liquid separation efficiency and the uniformity of steam distribution.

[0043] Furthermore, since the through holes 124 corresponding to the middle section 122 of the first partition plate 12 and the second partition plate 13 are all inclined towards the distal section 123, and this inclination direction is consistent with the mainstream direction of steam in the manifold 11, firstly, the steam carries non-condensable gas towards the distal section 123 when passing through the through holes 124. The non-condensable gas enters the lower chamber 113 through the through holes 124 with a higher distribution density in the distal section 123, and is discharged through the subsequent path, avoiding the accumulation of non-condensable gas in the middle chamber 112 or the distal section 123 of the manifold 11 to form air resistance, thereby delaying the performance degradation of the radiator during long-term operation; secondly, the through holes 124 inclined towards the distal section 123 make the steam flow more smoothly when passing through the partition plate, reducing the impact of flow channel deflection. The local resistance loss caused by the folding allows steam to pass through the first partition plate 12 and the second partition plate 13 with a smaller pressure drop, thereby reducing the overall flow resistance of the siphon cycle and helping to maintain the driving force of the working fluid circulation. Especially under low load conditions, it can effectively prevent the cycle from being interrupted. Finally, the inclined through hole 124 guides the steam into the middle chamber 112 at a certain angle, so that the steam forms a certain sweeping effect on the lower wall of the middle chamber 112 during the flow process. This sweeping effect can promptly remove the liquid film deposited on the lower wall of the middle chamber 112, preventing the liquid film from being entrained again by the high-speed steam after it becomes too thick. At the same time, it promotes the collection of the removed liquid film along the surface of the second partition plate 13 towards the connecting area 114, thereby further reducing the risk of gas-liquid interference at the fine separation level.

[0044] Furthermore, the inclination angle of the upper middle section 122 of the first partition plate 12 corresponding to the through hole 124 is 10-20°, and the inclination angle of the upper middle section 122 of the second partition plate 13 corresponding to the through hole 124 is 25-45°.

[0045] In this structure, there is a significant angular difference between the through holes 124 in the middle section 122 of the first partition plate 12 and the through holes 124 in the middle section 122 of the second partition plate 13. This angular difference causes the steam to deflect twice at different angles as it passes through the first partition plate 12 and the second partition plate 13 in sequence, thereby creating a specific flow field distribution within the middle chamber 112. Preferably, the inclination angle of the upper middle section 122 of the first partition plate 12 corresponding to the through hole 124 is 15°, and the inclination angle of the upper middle section 122 of the second partition plate 13 corresponding to the through hole 124 is 35°. Specifically, when steam enters the middle chamber 112 through the first partition plate 12 at a relatively small angle of 15°, the steam flows towards the distal section 123 with a relatively gentle trajectory. This gentle 15° flow trajectory reduces the impact of steam on the settled droplets in the middle chamber 112, and avoids the droplets being resuspended and re-entrained due to high-speed airflow disturbance. When the steam continues to flow and passes through the second partition plate 13 at a larger angle of 35°, the steam enters the lower chamber 113 with a relatively steep trajectory. This steep 35° flow trajectory causes the steam to generate a downward velocity component when leaving the second partition plate 13, forming a sweeping effect on the liquid surface of the lower chamber 113, promoting the separation of the residual tiny droplets in the steam from the steam under inertia and settling at the bottom of the lower chamber 113. The through-hole 124 in the middle section 122 of the first partition plate 12, which is inclined at 15°, and the through-hole 124 in the middle section 122 of the second partition plate 13, which is inclined at 35°, ensure that the steam flows in the middle chamber 112 with a gentle trajectory of 15° to facilitate droplet sedimentation, and ensure that the steam has a sufficient downward velocity component with a steep trajectory of 35° when entering the lower chamber 113 to enhance the final separation effect. Thus, without adding any additional structure, the gas-liquid separation efficiency is improved by the layered design of the inclined angle of the through-hole 124.

[0046] The different tilt angles mentioned above can further solve the problem of steam distribution. Specifically, the through hole 124 in the middle section 122 of the first partition plate 12 is tilted at a small angle of 15°, so that the steam enters the middle chamber 112 with a relatively gentle trajectory. This gentle trajectory reduces the flow resistance of the steam in the middle chamber 112, allowing the steam to diffuse more smoothly towards the distal section 123, avoiding local pressure loss and flow attenuation caused by excessive flow channel bends. The through hole 124 in the middle section 122 of the second partition plate 13 is tilted at a larger angle of 35°, so that the steam enters the lower chamber 113 with a relatively steep trajectory. The downward velocity component generated by this steep trajectory helps the steam to be evenly distributed axially to each guide pipe 141, especially providing compensating flow replenishment to the guide pipe 141 near the distal section 123. The angle difference between the smaller tilt angle of the first partition plate 12 and the larger tilt angle of the second partition plate 13 causes the steam to undergo a flow transition from gentle diffusion to steep distribution as it passes through the two partition plates. This ensures that the steam can diffuse sufficiently towards the distal region 123 to improve the axial distribution uniformity, and also ensures that the steam has sufficient downward momentum after entering the lower chamber 113 to be evenly distributed to each guide pipe 141. Thus, without adding any additional structure, the layered design of the tilt angle of the through hole 124 improves the axial distribution uniformity of the steam and solves the problem of uneven steam distribution caused by the large flow rate at the near end and the small flow rate at the far end.

[0047] Furthermore, the inlet and outlet of the through holes 124 corresponding to the proximal region 121, middle region 122, and distal region 123 on the first partition plate 12 are all larger than the inlet and outlet of the through holes 124 corresponding to the regions on the second partition plate 13. Specifically, the diameter of the through hole 124 corresponding to the middle region 122 on the first partition plate 12 is larger than the diameter of the through hole 124 corresponding to the middle region 122 on the second partition plate 13; the inlet and outlet of the through hole 124 corresponding to the proximal region 121 on the first partition plate 12 are both larger than the diameter of the through hole 124 corresponding to the proximal region 121 on the second partition plate 13; and the inlet and outlet of the through hole 124 corresponding to the distal region 123 on the first partition plate 12 are both larger than the diameter of the through hole 124 corresponding to the distal region 123 on the second partition plate 13.

[0048] In application, the steam and entrained liquid working fluid from the evaporation section 2 enter the manifold 11 of the condensation section 1 and first enter the upper chamber 111 formed by the first partition plate 12. Since the inlet and outlet of the corresponding through holes 124 in the near end region 121, middle end region 122 and far end region 123 of the first partition plate 12 are larger than the through holes 124 in the corresponding regions of the second partition plate 13, the through holes 124 on the first partition plate 12 are larger in size, which allows the steam and entrained larger diameter liquid droplets to pass smoothly through the first partition plate 12 and enter the middle chamber 112, avoiding premature blockage of the through holes 124. At the same time, the large-sized through holes 124 on the first partition plate 12 undertake the coarse separation function, intercepting most of the liquid working fluid in the upper chamber 111 and returning it to the lower chamber 113 through the connecting area 114.

[0049] After the steam and the entrained residual micro-droplets enter the middle chamber 112, they need to further pass through the through holes 124 on the second partition plate 13 to enter the lower chamber 113. Since the inlet and outlet of the through holes 124 corresponding to the proximal region 121, middle region 122 and distal region 123 on the second partition plate 13 are smaller than the through holes 124 of the corresponding regions on the first partition plate 12, the through holes 124 on the second partition plate 13 are smaller in size, forming a fine interception of residual micro-droplets. Only steam with a high dryness can pass through the second partition plate 13 to enter the lower chamber 113, while the intercepted micro-droplets settle by gravity in the middle chamber 112 and flow back to the lower chamber 113 through the connecting area 114. With the above structure, the first partition plate 12 and the second partition plate 13 have a clear division of functions. The large through hole 124 on the first partition plate 12 is used for coarse separation, allowing steam and larger droplets to pass through but blocking ultra-large droplets. The small through hole 124 on the second partition plate 13 is used for fine separation, allowing only steam to pass through while blocking tiny droplets, thereby significantly improving the gas-liquid separation efficiency compared to the single-stage separation structure.

[0050] In the middle section 122, since the diameter of the through hole 124 corresponding to the middle section 122 on the first partition plate 12 is larger than that of the through hole 124 corresponding to the middle section 122 on the second partition plate 13, and the through holes 124 corresponding to the middle section 122 on both the first partition plate 12 and the second partition plate 13 are inclined towards the distal section 123, this structure reduces the flow resistance of steam when it passes through the first partition plate 12 and enters the middle chamber 112. This avoids the droplets being blown away due to excessively high steam velocity caused by the through hole 124 being too small. Steam enters the middle chamber After chamber 112, because the diameter of the through hole 124 corresponding to the middle section 122 on the second partition plate 13 is small and it is also inclined towards the distal section 123, the steam needs to change its flow direction in the middle chamber 112 in order to pass through the small through hole 124 on the second partition plate 13. This process increases the flow path length of the steam in the middle chamber 112, allowing the residual tiny droplets to settle under gravity for a longer time. At the same time, the inclined through hole 124 guides the steam to flow towards the distal section 123, avoiding local accumulation of steam in the middle chamber 112. In the proximal region 121, the inlet and outlet of the corresponding through hole 124 on the first partition plate 12 are larger than the inlet and outlet of the corresponding through hole 124 on the second partition plate 13. This makes the proximal region 121 form a series structure of the large through hole 124 of the first partition plate 12 and the small through hole 124 of the second partition plate 13. This structure ensures that steam can pass smoothly through the first partition plate 12 into the middle chamber 112 in the proximal region 121, while restricting the steam flow in the proximal region 121 through the small through hole 124 of the second partition plate 13. This forces some steam to flow towards the middle region 122 and the distal region 123, which works synergistically with the gradual opening ratio of the first partition plate 12 itself to further improve the uniformity of steam distribution in the axial direction. In the distal region 123, the inlet and outlet of the corresponding through hole 124 on the first partition plate 12 are larger than the inlet and outlet of the corresponding through hole 124 on the second partition plate 13. This makes the distal region 123 also form a series structure of the large through hole 124 of the first partition plate 12 and the small through hole 124 of the second partition plate 13. This structure ensures that there is enough steam entering the middle chamber 112 at the distal end through the large through hole 124 of the first partition plate 12, thereby compensating for the pressure drop loss caused by the extension of the flow path. At the same time, it maintains the interception capability of small droplets through the small through hole 124 of the second partition plate 13, so that the distal region 123 can obtain sufficient steam flow without reducing the gas-liquid separation efficiency.

[0051] Through the above structure, the first partition plate 12 and the second partition plate 13 form aperture differences in the near-end region 121, the middle region 122, and the far-end region 123, respectively, enabling the first partition plate 12 and the second partition plate 13 to perform coarse separation and fine separation functions. The large-sized through-hole 124 on the first partition plate 12 ensures smooth steam flow and undertakes the coarse separation function, while the small-sized through-hole 124 on the second partition plate 13 achieves fine separation and improves steam dryness. Through the synergistic cooperation of the near-end region 121, the middle region 122, and the far-end region 123 in the axial direction, the uniformity of steam distribution and the gas-liquid separation efficiency are improved simultaneously, thereby further enhancing the overall heat exchange performance and operational stability of the siphon heat pipe radiator.

[0052] In one specific embodiment, the through holes 124 corresponding to the proximal region 121 of the first partition plate 12 and the through holes 124 corresponding to the proximal region 121 of the second partition plate 13 are axially aligned and circumferentially misaligned; the through holes 124 corresponding to the middle region 122 of the first partition plate 12 and the through holes 124 corresponding to the middle region 122 of the second partition plate 13 are axially misaligned and circumferentially misaligned; the through holes 124 corresponding to the distal region 123 of the first partition plate 12 and the through holes 124 corresponding to the distal region 123 of the second partition plate 13 are axially aligned and circumferentially misaligned.

[0053] It should be noted that axial alignment means that the projected positions in the first direction coincide; axial misalignment means that the projected positions in the first direction are offset, and the offset amount is half the hole spacing; axial misalignment means that the position is offset in the horizontal direction perpendicular to the first direction, and the offset amount is the corresponding circumferential angle.

[0054] By staggering the through holes 124 in different areas on the first partition plate 12 and the second partition plate 13, the siphon heat pipe radiator is further enhanced in solving the problems of gas-liquid entrainment and uneven steam distribution.

[0055] In addressing the issue of gas-liquid entrainment, the near-end region 121, through axial alignment and circumferential misalignment, forces the steam to change its flow direction within the middle chamber 112, increasing the residence time of residual micro-droplets in the steam and preventing secondary entrainment of droplets caused by high-speed steam directly impacting the inlet of the second partition plate 13 through the through hole 124. The middle-end region 122, through a combination of axial and circumferential misalignment, creates the longest flow path for steam within the middle chamber 112, significantly increasing the droplet settling time and completely preventing secondary entrainment of already settled droplets by high-speed steam. The far-end region 123, through axial alignment and circumferential misalignment, maintains the ability to intercept micro-droplets while ensuring far-end flow compensation. To address uneven steam distribution, the near-end region 121, through its axial alignment and circumferential misalignment, works in conjunction with its low orifice ratio to limit steam flow. The middle-end region 122, through its complete misalignment, forces steam to change its flow path both axially and circumferentially within the middle chamber 112, guiding steam towards the far-end region 123 and improving the uniformity of steam distribution in the axial direction. The far-end region 123, through its axial alignment and circumferential misalignment, works in conjunction with its high orifice ratio to ensure smooth steam replenishment and compensate for pressure drop losses caused by the extended flow path. Through these misalignments and their coordination with other structures, the uniformity of steam distribution in the axial direction of the manifold 11 is further optimized.

[0056] In application, the steam and entrained liquid working fluid from the evaporation section 2 enter the manifold 11 of the condensation section 1 and first enter the upper chamber 111 formed by the first partition plate 12. Through the above-mentioned gas-liquid separation method, most of the liquid working fluid is intercepted and flows back to the lower chamber 113 through the connecting area 114. The steam continues to flow along the upper chamber 111 and enters the middle chamber 112 through the through hole 124 formed on the first partition plate 12.

[0057] In the proximal region 121, since the corresponding through holes 124 on the first partition plate 12 and the corresponding through holes 124 on the second partition plate 13 are axially aligned and circumferentially misaligned, after the steam enters the middle chamber 112 through the through holes 124 on the first partition plate 12, its flow direction is offset from that of the through holes 124 on the second partition plate 13 in the circumferential direction. This makes it impossible for the steam to pass directly through the through holes 124 on the second partition plate 13 in a straight line. Instead, the steam must change its flow direction in the middle chamber 112 before it can enter the through holes 124 on the second partition plate 13. This circumferential misalignment forces the steam in the proximal region 121 to form a transverse flow path within the middle chamber 112. On the one hand, this increases the residence time of residual micro-droplets in the steam within the middle chamber 112, allowing the micro-droplets more time to settle by gravity. On the other hand, it prevents high-speed steam from directly impacting the inlet of the through hole 124 on the second partition plate 13, preventing the droplets at the inlet of the through hole 124 from being blown apart and forming secondary entrainment, thereby further improving the separation efficiency of the proximal region 121.

[0058] In the middle section 122, because the corresponding through holes 124 on the first partition plate 12 and the corresponding through holes 124 on the second partition plate 13 are axially and circumferentially misaligned, after steam enters the middle chamber 112 through the through holes 124 on the first partition plate 12, its flow direction is offset from the through holes 124 on the second partition plate 13 in both the axial and circumferential directions. This combination of axial and circumferential misalignment forces the steam to change its flow path in both the axial and circumferential directions simultaneously in the middle chamber 112 to pass through the through holes 124 on the second partition plate 13, forming a longer flow path. This significantly increases the residence time of the steam in the middle chamber 112, allowing the tiny droplets entrained in the steam to settle fully under gravity. At the same time, it completely avoids the possibility of high-speed steam directly impacting the inlet of the through holes 124 on the second partition plate 13, effectively preventing secondary entrainment of droplets. Since the middle section 122 is the area where the steam flow rate changes most frequently, the combination of axial and circumferential misalignment enables the middle section 122 to maintain a stable gas-liquid separation effect under variable load conditions. When combined with the structures in Examples 1 and 2, it forms a synergy, which significantly improves both the gas-liquid separation efficiency and the uniformity of steam distribution in the middle section 122.

[0059] In the distal region 123, since the corresponding through hole 124 on the distal region 123 of the first partition plate 12 and the corresponding through hole 124 on the distal region 123 of the second partition plate 13 are axially aligned and circumferentially misaligned, after the steam enters the middle chamber 112 through the through hole 124 on the first partition plate 12, its flow direction is axially aligned with the through hole 124 on the second partition plate 13, but is offset in the circumferential direction. This axial alignment ensures that the steam in the distal region 123 can flow from the through-hole 124 on the first partition plate 12 to the through-hole 124 on the second partition plate 13 via the shortest path, reducing the pressure drop loss caused by the extended flow path. This allows the distal region 123 to still receive sufficient steam supply even when the steam flow rate is low. This works in conjunction with the structure in Embodiment 1 where the through-hole 124 distribution density in the distal region 123 is the highest, and in Embodiment 2 where both the inlet and outlet of the through-hole 124 in the distal region 123 are larger than the second partition plate 13. Together, they compensate for the pressure drop loss caused by the steam flowing from the manifold 11 to the distal end, ensuring sufficient steam flow in the guide pipe 141 of the distal region 123. The circumferential misalignment means that the steam still needs to undergo a certain degree of lateral flow in the middle chamber 112 before entering the through-hole 124 on the second partition plate 13. This ensures flow compensation in the distal region 123 while maintaining the interception capability of small droplets, avoiding a decrease in gas-liquid separation efficiency due to axial alignment.

[0060] Furthermore, the second partition plate 13 is inclined toward the connecting area 114, and the inclination angle of the second partition plate 13 is 5-10°.

[0061] Furthermore, the height of the middle chamber 112 gradually increases along the first direction.

[0062] Preferably, the tilt angle of the second partition plate 13 is 7°.

[0063] Because the second partition plate 13 is inclined downwards towards the connecting area 114 at an angle of 7°, the second partition plate 13 as a whole presents an inclined posture that gradually decreases from the end away from the connecting area 114 towards the connecting area 114. The liquid working fluid intercepted and settled in the middle chamber 112 by the first partition plate 12 and the second partition plate 13, as well as the condensate collected along the surface of the second partition plate 13, flows towards the connecting area 114 under the action of gravity along the surface of the second partition plate 13 at an inclination angle of 7°. This downwardly inclined structure allows the liquid working fluid in the middle chamber 112 to collect more quickly into the connecting area 114 and enter the lower chamber 113, avoiding the risk of the liquid working fluid remaining in the middle chamber 112 for a long time or being re-entrained by high-speed steam. Meanwhile, the second partition plate 13 is inclined downwards towards the connecting area 114 at a 7° angle, so that the liquid working fluid return path in the middle chamber 112 forms a certain angle with the steam flow path, further reducing the mutual interference between the two. This works in conjunction with the structures in Examples 1 and 2, allowing the condensate formed after gas-liquid separation to return to the evaporation section 2 more efficiently, thereby maintaining a stable working fluid supply to the evaporation section 2 under variable load conditions. The 7° inclination angle of the second partition plate 13 ensures smooth liquid return while preventing excessive compression of the middle chamber 112 due to an excessively large inclination angle, which would affect the normal flow of steam, thus achieving a balance between return efficiency and flow performance.

[0064] Because the height of the middle chamber 112 gradually increases along the first direction, that is, the height of the middle chamber 112 is smaller in the proximal region 121 and larger in the distal region 123. In the proximal region 121, due to the smaller height of the middle chamber 112, after the steam enters the middle chamber 112 through the through holes 124 on the first partition plate 12, the space inside the middle chamber 112 is compressed, which increases the steam velocity in the proximal region 121. This increased velocity helps to push the steam towards the middle region 122 and the distal region 123. This works in conjunction with the lowest distribution density of the through holes 124 in the proximal region 121 in Embodiment 1 and the fact that the through holes 124 of the first partition plate 12 in the proximal region 121 are larger than the through holes 124 of the second partition plate 13 in Embodiment 2, together limiting the steam flow in the proximal region 121 and forcing some of the steam to flow towards the distal region 123. In the distal region 123, due to the larger height of the middle chamber 112, more space is provided within the middle chamber 112, allowing steam to diffuse fully in the distal region 123. This compensates for the pressure drop loss caused by the steam flowing to the distal end along the manifold 11. At the same time, the larger space provides a longer residence time for the liquid working fluid settling in the distal region 123, allowing the tiny droplets to settle more fully and flow back to the connecting region 114 through the surface of the second partition plate 13 with an inclination angle of 7°. This works in conjunction with the highest distribution density of the through holes 124 in the distal region 123 in Example 1 and the larger through holes 124 of the first partition plate 12 in the distal region 123 than the through holes 124 of the second partition plate 13 in Example 2, together ensuring that the distal region 123 maintains a high gas-liquid separation efficiency while obtaining sufficient steam flow.

[0065] In the above structure, the second partition plate 13 is inclined downwards at a 7° angle toward the connecting area 114, which allows the liquid working fluid in the middle chamber 112 to flow back quickly. At the same time, the structure in which the height of the middle chamber 112 gradually increases along the first direction compresses the flow channel in the near end area 121 to push the steam to flow to the far end, and expands the space in the far end area 123 to compensate for pressure drop loss and promote droplet sedimentation. Thus, the siphon heat pipe radiator is further improved in terms of gas-liquid separation efficiency, steam distribution uniformity, condensate reflux efficiency, and operational stability under variable load conditions.

[0066] The above-described embodiments are only used to illustrate the technical solutions of the present invention, and are not intended to limit it. Although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some of the technical features. Such modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the spirit and scope of the technical solutions of the embodiments of the present invention.

Claims

1. A siphon heat pipe radiator for an outdoor unit of an air conditioner, characterized in that, The unit includes an evaporator (2) and a condenser (1) connected together. The evaporator (2) is installed on the outdoor unit of the air conditioner. The condenser (1) includes a manifold (11) connected to the outlet of the condenser (1). A first partition plate (12) is provided inside the manifold (11) along a first direction and is connected to the evaporator (2). The first partition plate (12) divides the manifold (11) into an upper chamber (111) and a lower chamber (113). Distributed sequentially along the second direction, the first partition plate (12) has a connecting area (114) between the side away from the evaporation section (2) and the side wall of the manifold (11). The connecting area (114) connects the upper chamber (111) and the lower chamber (113). A through hole (124) is formed on the first partition plate (12). When the gas-liquid mixture discharged from the outlet of the condensation section (1) enters the upper chamber (111), the gas and liquid enter the lower chamber (113) through the through hole (124) and the connecting area (114), respectively. The first partition plate (12) has a proximal region (121), a middle region (122) and a distal region (123) formed along the first direction. The proximal region (121) and the distal region (123) are close to the air outlet and the connecting region (114) respectively. The distribution density of the through holes (124) on the first partition plate (12) corresponding to the proximal region (121), the middle region (122) and the distal region (123) increases sequentially.

2. The siphon heat pipe radiator for an outdoor unit of an air conditioner according to claim 1, characterized in that, The inner diameter of the through hole (124) in the proximal region (121) gradually decreases along the second direction, and the inner diameter of the through hole (124) in the distal region (123) gradually increases along the second direction.

3. The siphon heat pipe radiator for an outdoor unit of an air conditioner according to claim 1, characterized in that, The manifold (11) is provided with a second partition plate (13) corresponding to the first partition plate (12). A middle chamber (112) is formed between the first partition plate (12) and the second partition plate (13). The second partition plate (13) has the same structure as the first partition plate (12). The through holes (124) corresponding to the middle section (122) of the first partition plate (12) and the second partition plate (13) are inclined towards the distal section (123).

4. The siphon heat pipe radiator for an outdoor unit of an air conditioner according to claim 3, characterized in that, The inclination angle of the upper middle section (122) of the first partition plate (12) corresponding to the through hole (124) is 10-20°, and the inclination angle of the upper middle section (122) of the second partition plate (13) corresponding to the through hole (124) is 25-45°.

5. The siphon heat pipe radiator for an outdoor unit of an air conditioner according to claim 3, characterized in that, The inlet and outlet of the corresponding through holes (124) in the proximal region (121), middle region (122) and distal region (123) of the first partition plate (12) are larger than the inlet and outlet of the corresponding through holes (124) in the second partition plate (13).

6. The siphon heat pipe radiator for an outdoor unit of an air conditioner according to claim 3, characterized in that, The through hole (124) in the proximal region (121) of the first partition plate (12) and the through hole (124) in the proximal region (121) of the second partition plate (13) are axially aligned and circumferentially misaligned. The through hole (124) in the middle region (122) of the first partition plate (12) and the through hole (124) in the middle region (122) of the second partition plate (13) are axially misaligned and circumferentially misaligned. The through hole (124) in the distal region (123) of the first partition plate (12) and the through hole (124) in the distal region (123) of the second partition plate (13) are axially aligned and circumferentially misaligned.

7. The siphon heat pipe radiator for an outdoor unit of an air conditioner according to claim 3, characterized in that, The second partition plate (13) is inclined toward the connecting area (114), and the inclination angle of the second partition plate (13) is 5-10°.

8. The siphon heat pipe radiator for an outdoor unit of an air conditioner according to claim 7, characterized in that, The height of the middle chamber (112) gradually increases along the first direction.

9. The siphon heat pipe radiator for an outdoor unit of an air conditioner according to claim 1, characterized in that, The condensing section (1) further includes a condensing element (14) and a liquid storage pipe (15). The collecting pipe (11), the condensing element (14) and the liquid storage pipe (15) are connected in sequence along the second direction. The end of the evaporating section (2) away from the collecting pipe (11) is connected to the liquid storage pipe (15).

10. The siphon heat pipe radiator for an outdoor unit of an air conditioner according to claim 9, characterized in that, The condenser (14) includes several guide tubes (141), which connect the collecting tube (11) and the liquid storage tube (15), and heat dissipation fins (142) are provided between two adjacent guide tubes (141).

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