An inverter

Abstract

The application provides an inverter, at least two groups of heat dissipation fins are arranged in the air passing direction in the air passing cavity, and the tooth height of the downstream heat dissipation fin group is greater than that of the upstream heat dissipation fin group in the two groups of heat dissipation fins adjacent in the air passing direction; the air guide cover is connected between any two groups of heat dissipation fins adjacent in the air passing direction and at least partially adheres to the tooth top of the two groups of heat dissipation fins, so as to form the air cavity together with the downstream tooth top of the upstream heat dissipation fin group and the windward end surface of the downstream heat dissipation fin group. The application can improve the heat dissipation efficiency of the downstream heat dissipation fin.

Description

Technical Field

[0001] This invention relates to the field of inverter technology, and more specifically to an inverter. Background Technology

[0002] In high-power-density inverters, heat dissipation is one of the key factors restricting product performance and reliability. In existing technologies, to adapt to harsh environments such as high temperature, high humidity, and high dust, the internal cavity of the equipment is often divided into a closed protective cavity with a high protection level and an open ventilation cavity with a low protection level.

[0003] High-power photovoltaic inverters integrate numerous heat-generating components, including IGBT power modules, boost inductors, inverter inductors, capacitors, and various magnetic components. The IGBT power modules and capacitors are typically housed in a protective cavity, while the boost inductors and inverter inductors are housed in an air-flow cavity. Heat transfer within the protective cavity is achieved through finned heat sinks. The IGBT power modules are primarily mounted on the heat sink's substrate, and the heat sink fins are located within the air-flow cavity, where a fan removes heat from the fins.

[0004] As inverter power density continues to increase, the total heat dissipation within the air cavity also increases. As the airflow moves from the inlet to the outlet, it continuously absorbs heat from various heat-generating components and the heat dissipation fins themselves, causing the air temperature to rise continuously along the way. This leads to a gradual decrease in the heat exchange temperature difference of the downstream heat dissipation fins. When the power is further increased, the temperature rise widens, amplifying the aforementioned disadvantages and making it a systemic bottleneck restricting the improvement of overall power density. Summary of the Invention

[0005] The purpose of this application is to improve the above-mentioned defects in the prior art to a certain extent, and to provide an inverter that can improve the heat dissipation efficiency of the downstream heat sink fins.

[0006] Through continuous observation, analysis, and experimentation, the applicant aims to identify the reasons for the low heat dissipation efficiency of inverters in the background technology. On the one hand, the heat dissipation fins in the air passage generally adopt a uniform tooth height design, and the heat exchange area of ​​each heat dissipation fin group along the airflow direction is basically the same. The heat dissipation capacity distribution of the uniform tooth height heat dissipation fins along the airflow direction is basically constant. When the downstream air temperature rises and the heat exchange temperature difference decreases, the heat dissipation capacity of the downstream heat dissipation fins decreases accordingly, resulting in insufficient heat dissipation efficiency in the downstream area. On the other hand, if the tooth height of the downstream heat dissipation fins is higher than that of the adjacent upstream heat dissipation fins, due to the inertia of the airflow flowing out of the upstream channel along its original height, the airflow will mainly adhere to the lower area of ​​the channel and will be difficult to fill the higher area of ​​the downstream channel with higher tooth height. This easily forms a low-speed vortex area or even a flow dead zone in the higher part of the downstream heat dissipation fins, resulting in the increased heat exchange area not being effectively utilized and failing to improve the heat dissipation efficiency of the downstream heat dissipation fins.

[0007] Based on the above, in order to improve the deficiencies of the prior art and achieve the purpose of this invention, the applicant adopts the following technical solution to solve the problem: Technical solution one relates to an inverter, in which at least two heat dissipation fin groups are provided in the air passage cavity along the air passage direction, and in the two adjacent heat dissipation fin groups along the air passage direction, the tooth height of the downstream heat dissipation fin group is greater than the tooth height of the upstream heat dissipation fin group; the air guide shroud spans between any two adjacent heat dissipation fin groups along the air passage direction and is at least partially in contact with the tooth tips of the two heat dissipation fin groups, so as to form an air passage with the downstream tooth tip of the upstream heat dissipation fin group and the windward end face of the downstream heat dissipation fin group.

[0008] Technical Solution 2 based on Technical Solution 1: Each heat dissipation fin group includes several heat dissipation fins extending along a first direction and spaced apart along a second direction; the first direction is the airflow direction; each air cavity has a rectangular cross-section perpendicular to the second direction. Technical Solution 3 based on Technical Solution 2: The length of each air cavity along the airflow direction is at least half the length of the air cavity along a third direction; the third direction is perpendicular to the first direction and the second direction. Technical Solution 4 based on Technical Solution 3: The length of each air cavity along the airflow direction shall not exceed twice the length of the air cavity along the third direction.

[0009] Technical Solution 4 based on Technical Solution 1: The air guide shroud also has a first air guide plate that is inclined relative to the airflow direction for the upstream heat dissipation fin group, so as to guide the airflow to the upstream heat dissipation fin group. Technical Solution Six based on Technical Solution One: Each heat dissipation fin group includes several heat dissipation fins extending along a first direction and spaced apart along a second direction; the first direction is the airflow direction; at least two first inductors are respectively disposed on both sides of at least one heat dissipation fin group along the second direction; the length direction of the first inductor is the first direction. Technical solution seven based on technical solution six: the heat exchange sections of at least two heat exchangers are respectively disposed on both sides of at least one heat dissipation fin group along the second direction, and the heat exchange sections are located upstream of the first inductor. Technical solution eight based on technical solution seven: each first inductor is evenly distributed on both sides of at least one heat dissipation fin group along the second direction; the heat exchange section of each heat exchanger is evenly distributed on both sides of at least one heat dissipation fin group along the second direction. Technical solution nine based on technical solution six: Several second inductors arranged along the second direction are provided downstream of each heat dissipation fin assembly; the air guide shroud is also provided with a second air guide plate extending downstream relative to the downstream heat dissipation fin assembly to guide the air to the second inductors. Based on technical solution 8 or 9, technical solution 10: any two adjacent heat dissipation fin groups have the same length along the second direction; the first inductor also overlaps at least partially with the second inductor on the projection surface of the second inductor in the second direction. As can be seen from the above description of the present invention, compared with the prior art, the present invention has the following beneficial effects: In technical solution one, the air passage cavity refers to the cavity space within the chassis used to house heat dissipation fins and heat-generating components such as inductors, and to allow cooling airflow. This cavity is typically equipped with an airflow fan for forced convection heat transfer. The airflow direction refers to the macroscopic direction in which the cooling airflow, driven by the fan, flows within the air passage cavity during inverter operation. "Upstream" and "downstream" are based on this airflow direction; that is, along the airflow path, the position first passed by the airflow is upstream, and the position subsequently passed by the airflow is downstream. "Tooth tip" refers to the highest edge of the heat dissipation fins perpendicular to the airflow direction, and is the main bearing boundary of the fin's heat dissipation area. "Air-facing end face" is the side of the heat dissipation fin assembly facing the incoming airflow along the airflow direction, that is, the upstream end face of each fin in the heat dissipation fin assembly in the airflow direction. This end face is the inlet interface for airflow into the interfinal flow channel.

[0010] "The windward side of the downstream heat dissipation fin assembly" refers to the side of the downstream heat dissipation fin assembly that extends beyond the tooth tip of the upstream heat dissipation fin assembly in the height direction and faces the incoming flow along the wind direction.

[0011] In two adjacent heat dissipation fin groups along the airflow direction, the tooth height of the downstream heat dissipation fin group is greater than that of the upstream heat dissipation fin group. This causes the heat exchange area of ​​the heat dissipation fins to gradually increase along the airflow direction, which helps to compensate for the attenuation of heat dissipation capacity caused by the temperature rise along the airflow path and improves the uneven heat dissipation phenomenon along the airflow direction. The air guide shroud spans between any two adjacent heat dissipation fin groups along the airflow direction and is at least partially in contact with the tooth tips of the two heat dissipation fin groups. It forms an air cavity by enclosing the downstream tooth tip of the upstream heat dissipation fin group and the windward end face of the downstream heat dissipation fin group. On the one hand, the air guide shroud acts as a cap on the two adjacent heat dissipation fin groups, preventing airflow from overflowing from the tooth tips of the heat dissipation fins. On the other hand, it also allows airflow to enter the air cavity, providing the necessary expansion space for the airflow to transition from the upstream low-tooth fin flow channel to the downstream high-tooth fin flow channel. Because airflow has inertia along its original height when exiting the upstream channel, without a transition space, the airflow will mainly adhere to the lower part of the channel and will be unable to fill the higher part of the downstream channel with its higher tooth height. This can easily lead to the formation of low-speed vortex zones or even dead zones in the higher part of the downstream heat dissipation fins, resulting in the increased heat transfer area not being effectively utilized. The existence of the air cavity allows the airflow to enter a relatively open transition space before entering the downstream high heat dissipation fins. The flow velocity decreases and the static pressure increases, allowing the airflow to redistribute and climb to a higher channel height under lower inertial constraints. This fills the entire cross-section of the downstream high heat dissipation fins, reduces ineffective heat transfer areas, improves the actual utilization rate of the heat transfer area gain brought about by the increased tooth height, and enables the increased heat transfer area downstream to truly participate in effective heat transfer, thereby improving the heat dissipation efficiency of the downstream heat dissipation fins.

[0012] In technical solution two, each air cavity has a rectangular cross-section perpendicular to the second direction, resulting in clear cavity boundaries, low processing difficulty, and low mold cost. Simultaneously, the smooth inner wall of the rectangular cross-section ensures a more uniform static pressure distribution within the cavity, avoiding localized low-pressure areas or additional eddies induced by irregular cross-sections. This provides a stable flow field environment for airflow deceleration, static pressure recovery, and vertical ascent within the cavity. Furthermore, the downstream end face of the rectangular cross-section (i.e., the windward end face of the downstream heat dissipation fin assembly) faces the airflow, allowing the airflow to uniformly enter the downstream flow channel along the entire end face when exiting the air cavity, further improving the airflow uniformity of the downstream high heat dissipation fin flow channel.

[0013] In technical solution three, the length of each air cavity along the airflow direction is at least half the length of the air cavity along the third direction, providing the necessary axial distance for the airflow to decelerate, recover static pressure, and redistribute height within the air cavity. If the length of the air cavity along the airflow direction is too short, the airflow will be forced into the downstream high-heat-dissipation fin channel before it has completed sufficient deceleration and static pressure recovery. At this time, the airflow still retains strong flow inertia along its original height, making it difficult to fully climb to the full height of the downstream channel. Low-speed vortex zones may still exist in the higher part of the downstream heat dissipation fins, and the area gain brought by the increase in tooth height cannot be fully realized.

[0014] In technical solution four, the length of each air cavity along the airflow direction does not exceed twice its length along the third direction. On the one hand, when the length of the air cavity exceeds a certain limit, the improvement in the airflow distribution in the height direction tends to saturate. Further increasing the length will result in excessive cold air volume that does not pass through the heat dissipation fins, thus reducing the benefits. Furthermore, an excessively long length along the airflow direction leads to an excessively long residence time of the airflow within the cavity, which is detrimental to heat dissipation. On the other hand, an excessively long axial dimension will increase the overall length of the inverter, which is not conducive to improving power density. Therefore, by setting an upper limit on the length, the overall size of the unit is avoided from being excessively increased while ensuring that the airflow fully fills the downstream flow channel, thus balancing the relationship between heat dissipation performance and structural compactness.

[0015] In technical solution five, the air guide shroud is provided with a first air guide plate that is inclined relative to the airflow direction for the upstream heat dissipation fin group, so as to guide the airflow to the upstream heat dissipation fin group, improve the airflow direction entering the upstream heat dissipation fin group, help improve the uniformity of incoming flow and heat exchange efficiency of the upstream fin group, and at the same time help reduce airflow noise.

[0016] In technical solution six, at least two first inductors are respectively located on both sides of at least one heat dissipation fin assembly along the second direction. The length direction of the first inductor is the first direction, and the length direction of the first inductor is aligned with the airflow direction. This reduces the windward projection area of ​​the first inductor, effectively reducing the wind resistance along the air duct and improving the air delivery efficiency of the fan. It also makes the space occupied by the first inductor and the heat dissipation fins in the second direction smaller. The first inductors are respectively located on both sides of at least one heat dissipation fin assembly, rather than concentrated on one side of the heat dissipation fin assembly. This effectively balances the weight distribution of the whole machine along the second direction, improves the stability during hoisting and installation, and reduces the risk of tipping. Moreover, compared with the solution where the first inductor is located upstream of the heat dissipation fin assembly, the airflow is not preheated by the first inductor before flowing to the heat dissipation fin assembly, and the overall airflow resistance of the air duct is reduced, improving the air intake of the heat dissipation fin assembly and alleviating the heat dissipation bottleneck pressure under high power.

[0017] In technical solution seven, the heat exchange sections of at least two heat exchangers are respectively located on both sides of at least one heat dissipation fin assembly along the second direction. The heat exchange sections are located upstream of the first inductor, making full use of the space on both sides of the heat dissipation fin assembly along the second direction. Since the first inductor has relatively high temperature resistance, its temperature sensitivity is lower than that of other semiconductor devices in the inverter. This allows the heat exchanger to preferentially utilize the lower-temperature incoming air entering the air passage for heat exchange, which helps to improve the heat exchange efficiency of the heat exchanger itself and improve the heat exchanger's ability to share the heat load of the whole machine.

[0018] In technical solution eight, "equal distribution" means that in terms of quantity, the number of first inductors on both sides of the second direction is the same, and the number of heat exchange sections is the same.

[0019] Each first inductor is evenly distributed on both sides of at least one heat dissipation fin assembly along the second direction; the heat exchange sections of each heat exchanger are also evenly distributed on both sides of at least one heat dissipation fin assembly along the second direction. From a thermal management perspective, the heat generation of the first inductors on both sides is evenly matched with the cooling capacity of the heat exchange sections along the second direction, helping to reduce thermal deformation or thermal stress concentration caused by unilateral heat accumulation and improving the lateral uniformity of the overall thermal field. Furthermore, since the first inductors and the heat exchange sections of the heat exchangers are components with a relatively high mass proportion in the entire machine, their even distribution effectively balances the weight distribution of the entire machine along the second direction, avoiding unilateral load imbalance, improving the posture stability during hoisting, handling, and installation, reducing the risk of tipping during operation, and enhancing the convenience and safety of installation operations.

[0020] In technical solution nine, a second inductor is set downstream of each heat dissipation fin assembly, and a second air guide plate extending from the air guide shroud is used to guide the airflow to the second inductor. This reduces the diffusion and separation of the airflow after it leaves the heat dissipation fin channel due to the loss of boundary constraints, allowing the second inductor to be cooled by the residual velocity airflow downstream, which helps to improve the heat dissipation efficiency of the second inductor.

[0021] In technical solution ten, any two adjacent heat dissipation fin groups have the same length along the second direction, making the shape of the heat dissipation fin groups regular and facilitating the integrated design and assembly of the air guide cover; at the same time, the first inductor and the second inductor at least partially overlap on the projection surface of the second inductor in the second direction, which helps to make reasonable use of the space in the air passage cavity. Attached Figure Description

[0022] To more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings used in the following description of the embodiments are briefly introduced. Obviously, the drawings described below are some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0023] Figure 1 This is an overall schematic diagram of the inverter in this embodiment; Figure 2 for Figure 1 Top view; Figure 3 for Figure 2 Sectional view along the AA direction; Figure 4 This is a schematic diagram of the air passage cavity and its internal components in the inverter of this embodiment; Figure 5 for Figure 4 Top view.

[0024] Figure 6 This is a schematic diagram of the heat dissipation fin assembly and air guide shroud in this embodiment.

[0025] Explanation of key figure labels: Box body 10; protective cavity 11; air passage cavity 12; air inlet 121; first air outlet 122; cooling fan 20; heat dissipation fin assembly 30; heat dissipation fin 31; first heat dissipation fin assembly 32; second heat dissipation fin assembly 33; air guide shroud 40; first air guide plate 41; second air guide plate 42; air cavity 01; first inductor 50; heat exchange section 60; second inductor 70. Detailed Implementation

[0026] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are preferred embodiments of the present invention and should not be considered as excluding other embodiments. All other embodiments obtained by those skilled in the art based on the embodiments of the present invention without creative effort are within the scope of protection of the present invention.

[0027] Unless otherwise expressly defined, the use of terms such as "first," "second," or "third" in the claims, description, and accompanying drawings of this invention is for distinguishing different objects and not for describing a specific order.

[0028] Unless otherwise expressly defined, in the claims, description, and accompanying drawings of this invention, the use of directional terms such as "center," "lateral," "longitudinal," "horizontal," "vertical," "top," "bottom," "inner," "outer," "upper," "lower," "front," "rear," "left," "right," "clockwise," and "counterclockwise" to indicate orientation or positional relationships is based on the orientation and positional relationships shown in the accompanying drawings and is only for the convenience of describing the invention and simplifying the description, and is not intended to 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 limiting the specific scope of protection of this invention.

[0029] Unless otherwise expressly defined, the terms "fixed connection" or "fixed connection" used in the claims, description and drawings of this invention should be interpreted broadly to refer to any connection in which there is no displacement or relative rotation relationship between the two parties, including non-removable fixed connection, detachable fixed connection, integral connection and fixed connection by other means or components.

[0030] In the claims, description and accompanying drawings of this invention, the terms "comprising," "having," and variations thereof are used to mean "including but not limited to."

[0031] In the claims and the description other than the embodiments, the terms "first direction," "second direction," and "third direction" only refer to a feature having one of the aforementioned directions being perpendicular to a feature having another direction, and do not require that they be implemented according to the "first direction," "second direction," and "third direction" described in the embodiments. In the embodiments, the first direction is perpendicular to both the second direction and the third direction. The first direction can be divided into front and back, the second direction into left and right, and the third direction into up and down.

[0032] In the claims and the description except for the embodiments, the term "tooth tip" refers to the highest edge of the heat dissipation fin perpendicular to the airflow direction, which is the main bearing boundary of the fin's heat dissipation area. The term "airflow-facing end face" refers to the side of the heat dissipation fin assembly facing the incoming flow along the airflow direction, that is, the upstream end face of each fin in the heat dissipation fin assembly in the airflow direction, which is the inlet interface for airflow into the flow channel between the fins. The term "airflow-facing end face of the downstream heat dissipation fin assembly" refers to the side of the downstream heat dissipation fin assembly facing the incoming flow along the airflow direction, which extends beyond the tooth tip of the upstream heat dissipation fin assembly in the height direction of the fin.

[0033] Example The high-power photovoltaic inverter in this embodiment is suitable for outdoor power generation scenarios with high temperatures and high dust levels. See [link / reference]. Figure 1-3 , Figure 1 A schematic diagram of the inverter in this embodiment is shown. Figure 2 It shows Figure 1 Top view; Figure 3 A cross-sectional view of the inverter of this embodiment is shown.

[0034] See Figure 3The enclosure 10 of the entire unit consists of a high-protection-level enclosed protective cavity 11 and a low-protection-level open air passage cavity 12. The air passage cavity 12 refers to the cavity space inside the enclosure used to accommodate heat dissipation fins and inductors and other heat-generating devices, while allowing cooling airflow. This cavity is usually equipped with an airflow fan for forced convection heat transfer. IGBT power modules, capacitors, and other environmentally sensitive devices are encapsulated in the protective cavity 11. The heat-generating surface of the IGBT power module is attached to the back of the heat dissipation substrate of the finned heat sink, and the front of the heat dissipation substrate forms heat dissipation fins 30 extending into the air passage cavity 12. Heat-generating devices with strong weather resistance, such as boost inductors and inverter inductors, as well as the heat dissipation air ducts, are concentrated in the air passage cavity 12. To clarify the spatial assembly relationship and airflow direction of each component, this embodiment visualizes the three orthogonal directions within the air passage cavity 12 as follows: the first direction Y is the front-to-back direction of the air passage cavity 12, and the airflow generally flows from front to back along the first direction Y; the second direction X is the left-to-right direction of the air passage cavity 12, which is perpendicular to the first direction Y in the horizontal plane; the third direction Z is the up-to-down direction of the air passage cavity 12, which is perpendicular to the plane formed by the first direction Y and the second direction X, and the first direction Y, the second direction X, and the third direction Z are perpendicular to each other.

[0035] See Figure 4-5 , Figure 4 A schematic diagram of the air passage 12 and its internal components in the inverter of this embodiment is shown. Figure 5 It shows Figure 4 From the top view, a main airflow path extending along the first direction Y is formed within the air passage 12. The first inductor 50, the cooling fan 20, the heat exchange section 60 of the heat exchanger, the heat dissipation fin assembly 30, and the second inductor 70 are all located within the air passage 12, collectively constituting the main heat dissipation load of the air passage 12. Each component is positioned and fixed through the cavity wall, mounting bracket, and connectors of the air passage 12.

[0036] The air passage 12 forms air inlets at both ends along the first direction Y. Figure 4 (front end) and air outlet ( Figure 4 The air inlet 121, which allows air to enter along the first direction Y, is located at the rear end of the air passage cavity 12. The air outlet 12 has a first air outlet 122, which allows air to exit along the first direction Y. In practical applications, a second air outlet along the second direction X and a third air outlet along the third direction Z can be provided at the air outlet 12 as needed. However, it should be understood that the air outlet 12 can also have only one or two of the first air inlet 121, the second air outlet, or the third air outlet. In this embodiment, multiple cooling fans 20 are located at the air inlet 121 to drive airflow from the air inlet 121 to the first air outlet 122. The cooling fans 20 can be axial flow fans.

[0037] At least two heat dissipation fin groups 30 are provided in the air passage cavity 12 along the air passage direction. Among two adjacent heat dissipation fin groups 30 along the air passage direction, the tooth height of the downstream heat dissipation fin group 30 is greater than that of the upstream heat dissipation fin group 30. The air passage direction refers to the macroscopic direction of the cooling airflow driven by the cooling fan 20 in the air passage cavity 12 during inverter operation. "Downstream" and "downstream" are based on this air passage direction. That is, along the airflow path, the position first passed by the airflow is upstream, and the position second passed by the airflow is downstream.

[0038] See Figure 6 , Figure 6 A schematic diagram of the heat dissipation fin assembly and air guide shroud 40 of this embodiment is shown. Each heat dissipation fin assembly 30 includes a plurality of heat dissipation fins 31 extending along a first direction Y and spaced apart along a second direction X, where the first direction Y is the airflow direction. Any two adjacent heat dissipation fin assemblies 30 have the same length along the second direction X, making the overall shape of the heat dissipation fin assembly 30 regular and facilitating the integrated design and assembly of the supporting structure.

[0039] Specifically, in this embodiment, see Figure 3 The first heat dissipation fin group 32 and the second heat dissipation fin group 33 are arranged sequentially along the first direction Y in the air passage cavity 12. The tooth height of the second heat dissipation fin group 33 is greater than that of the first heat dissipation fin group 32. This tooth height gradient makes the heat exchange area of ​​the downstream heat dissipation fin group 30 larger than that of the upstream, which can compensate for the heat exchange temperature difference attenuation caused by the temperature rise along the airflow and improve the heat dissipation uniformity along the air passage direction.

[0040] See Figure 6 The air guide shroud 40 spans between any two adjacent heat dissipation fin groups 30 along the airflow direction and at least partially abuts the tooth tips of the two heat dissipation fin groups 30, so as to form an air cavity 01 by surrounding the downstream tooth tips of the upstream heat dissipation fin group 30 and the windward end face of the downstream heat dissipation fin group 30. "Tooth tip" refers to the highest edge of the heat dissipation fin perpendicular to the airflow direction, which is the main bearing boundary of the fin's heat dissipation area; "windward end face" is the side of the heat dissipation fin group facing the incoming flow along the airflow direction, that is, the upstream end face of each fin in the heat dissipation fin group in the airflow direction, which is the inlet interface for airflow into the interfin channel. "Windward end face of the downstream heat dissipation fin group" refers to the side of the downstream heat dissipation fin group facing the incoming flow along the airflow direction, which extends beyond the tooth tips of the upstream heat dissipation fin group in the height direction of the heat dissipation fin.

[0041] In this embodiment, the air guide shroud 40 is integrally fastened to the downstream portion of the first heat dissipation fin group 32 and the upper portion of the second heat dissipation fin group 33. The middle part of the air guide shroud 40 expands outward between the first heat dissipation fin group 32 and the second heat dissipation fin group 33, thereby forming an air cavity 01 located between the two groups of fins. Each air cavity 01 has a rectangular cross-section perpendicular to the second direction X, with a smooth inner wall and clear boundaries, providing a stable flow field environment for airflow within the cavity. The length of each air cavity 01 along the airflow direction is at least half the length of the air cavity 01 along the third direction Z, while the length of each air cavity 01 along the airflow direction does not exceed twice the length of the air cavity 01 along the third direction Z.

[0042] It should be understood that the number of heat dissipation fin groups 30 can be expanded to three or more. Among the heat dissipation fin groups 30 arranged sequentially along the first direction Y, any two adjacent heat dissipation fin groups 30 along the airflow direction satisfy the condition that the tooth height of the downstream heat dissipation fin group 30 is greater than the tooth height of the upstream heat dissipation fin group 30, forming a tooth height gradient that increases step by step along the airflow direction. The tooth tip of the downstream of each upstream heat dissipation fin group 30, together with the windward end face of the adjacent downstream heat dissipation fin group 30 and the air guide shroud 40, form an air cavity 01. When the number of heat dissipation fin groups 30 is three or more, the tooth tips of the air guide shroud 30 and the middle heat dissipation fin group 30 (except for the first heat dissipation fin group 31 at the very upstream and the second heat dissipation fin group 31 at the very downstream) are all in contact with the air cavity 01 except for the part. Thus, the air guide shroud 40 and each adjacent heat dissipation fin group 30 cooperate to form multiple air cavities 01 arranged at intervals along the first direction Y.

[0043] See also Figure 6 The air guide shroud 40 has a first air guide plate 41 inclined relative to the airflow direction, corresponding to the upstream heat dissipation fin assembly 30, to guide the airflow to the upstream heat dissipation fin assembly 30. In this embodiment, the first air guide plate 41 is located at the foremost end of the air guide shroud 40 and is inclined relative to the first direction Y. Figure 6 The first air guide plate 41 slopes backward from top to bottom, with its lower end extending to the fin tip of the first heat dissipation fin assembly 32. The first air guide plate 41 smoothly guides the airflow entering from the air inlet 121 to the windward end face of the first heat dissipation fin assembly 32, improving the uniformity of the incoming airflow to the uppermost fin assembly and reducing airflow impact noise. The air guide shroud 40 also has a second air guide plate 42 extending downstream relative to the lowermost heat dissipation fin assembly 33 to guide the airflow to the second inductor 70.

[0044] See Figure 5-6At least two first inductors 50 are respectively disposed on both sides of at least one heat dissipation fin group 30 along the second direction X. The length direction of the first inductor 50 is the first direction Y, aligned with the airflow direction, reducing the windward projection area in the airflow direction and lowering the friction resistance along the air duct. At least two heat exchanger heat exchange sections 60 are respectively disposed on both sides of at least one heat dissipation fin group 30 along the second direction X. The heat exchange section 60 is located upstream of the first inductor 50, preferentially utilizing the low-temperature incoming air entering the airflow cavity 12 for heat exchange, thereby improving the heat exchange efficiency of the heat exchanger itself. In this embodiment, there are two first inductors 50 and two heat exchangers. The first inductor 50 is a step-up inductor. Each first inductor 50 is evenly distributed on both sides of at least one heat dissipation fin group 30 along the second direction X, and the heat exchange section 60 of each heat exchanger is evenly distributed on both sides of at least one heat dissipation fin group 30 along the second direction X, so as to balance the heat load distribution and weight distribution of the whole machine along the second direction X and avoid one-sided load. "Equal distribution" means that, in terms of quantity, the number of first inductors 50 on both sides of the second direction is the same, and the number of heat exchange sections 60 is the same.

[0045] The heat exchanger is a cross-chamber heat exchange device. In addition to the heat exchange section 60 located in the air passage 12, it also includes a heat absorption end set in the protective cavity 11. The two parts are connected by a connecting channel through a partition plate between the air passage 12 and the protective cavity 11. A sealing element is provided between the connecting channel and the partition plate to ensure that the high protection level of the protective cavity 11 is not damaged. Different types of heat exchangers can be selected according to heat dissipation requirements: When an air-to-air heat exchanger is used, the heat-absorbing end in the protective cavity 11 can be a finned heat dissipation structure. The heat from the IGBT power module, capacitor and other heat-generating devices is absorbed by the air convection in the protective cavity 11. The heat is transferred to the heat exchange section 60 through the connecting channel and carried away by the airflow in the air passage 12. When an air-to-liquid heat exchanger is used, the heat-absorbing end in the protective cavity 11 is a liquid-cooled flow channel with coolant flowing inside. It absorbs the heat from the heat-generating devices in the protective cavity 11. The heated coolant flows through the liquid-cooled fins in the heat exchange section 60, is cooled by the airflow in the air passage 12 and then flows back to the protective cavity 11 for recycling. When a phase change heat exchanger is used, the heat-absorbing end in the protective cavity 11 is a sealed phase change working fluid chamber. The working fluid absorbs the heat in the protective cavity 11 and vaporizes. The vapor enters the heat exchange section 60 through the connecting channel and condenses and releases heat. The condensed liquid working fluid flows back to the phase change working fluid chamber to complete the cycle.

[0046] It should be understood that the number of first inductors 50 can be adjusted according to the rated power level of the inverter. There can be one or more first inductors 50 arranged on each side. Multiple sets of first inductors 50 are arranged in parallel along the second direction X, and the number of first inductors 50 on both sides along the second direction X is always consistent and the arrangement position is basically corresponding. Similarly, the number of heat exchange sections 60 can be set to match the heat load requirements of the inverter. One or more heat exchange sections 60 can be set on each side of the heat dissipation fin assembly 30 along the second direction X. Each heat exchange section 60 is arranged sequentially upstream of the first inductor 50 on the same side along the first direction Y, and the number and arrangement position of the heat exchange sections 60 on both sides correspond one-to-one.

[0047] See also Figure 5-6 Downstream of each heat dissipation fin assembly 30, several second inductors 70 are also provided, arranged along the second direction X. See [reference needed]. Figure 3 The second inductor 70 protrudes along the third direction Z relative to the free end of the downstream heat sink fin assembly 30. The first inductor 50 at least partially overlaps with the downstream second inductor 70 on the projection plane of the second direction X, making full use of the three-dimensional space within the air cavity 12 and improving space utilization.

[0048] During operation, the cooling fan 20 drives external airflow from the air inlet 121 into the air passage 12. After being guided by the first air guide plate 41, the airflow flows to the uppermost first heat dissipation fin group 32, carrying away the heat from the first heat dissipation fin group 32. The airflow then enters the air passage 01, where the flow velocity decreases, the static pressure increases, and it is redistributed in the height direction, gradually rising to a height matching the tooth height of the second heat dissipation fin group 33. It then evenly fills the entire flow channel cross-section of the second heat dissipation fin group 33, completing the second fin heat exchange. At the same time, as the airflow flows through the heat dissipation fin group 30, it simultaneously flows through the heat exchange section 60 of the heat exchanger arranged along both sides of the second direction X and the first inductor 50 located downstream of the heat exchange section 60, cooling the heat exchange section 60 and the first inductor 50 in sequence. After exiting the second heat dissipation fin group 33, the airflow continues to flow along the first direction Y, reaching the downstream area of ​​the second heat dissipation fin group 33, and flowing through the second inductor 70 arranged along the second direction X. Because the second inductor 70 protrudes upward relative to the free end of the second heat sink fin assembly 33 along the third direction Z, and there is still a relatively high residual airflow downstream of the second heat sink fin assembly 33, the airflow sweeps across the surface of the second inductor 70 from below and side, using the residual airflow downstream to cool the second inductor 70. Finally, the heated airflow is discharged from the exhaust port from the chassis, completing the entire heat dissipation cycle.

[0049] In this embodiment, among two adjacent heat dissipation fin groups 30 along the airflow direction, the tooth height of the downstream heat dissipation fin group 30 is greater than that of the upstream heat dissipation fin group 30. This causes the heat exchange area of ​​the heat dissipation fins 31 to gradually increase along the airflow direction, which helps to compensate for the attenuation of heat dissipation capacity caused by the temperature rise along the airflow path and improves the uneven heat dissipation phenomenon along the airflow direction. The air guide shroud 40 spans between any two adjacent heat dissipation fin groups 30 along the airflow direction and is at least partially in contact with the tooth tips of the two heat dissipation fin groups 30. It forms an air cavity 01 by surrounding the downstream tooth tip of the upstream heat dissipation fin group 30 and the windward end face of the downstream heat dissipation fin group 30. On the one hand, the air guide shroud 40 acts as a capping effect on the two adjacent heat dissipation fin groups, preventing airflow from overflowing from the tooth tips of the heat dissipation fins. On the other hand, it also allows airflow to enter the air cavity 01, providing the necessary expansion space for the airflow to transition from the upstream low-tooth fin flow channel to the downstream high heat dissipation fin 31 flow channel. Because the airflow has inertia along its original height when flowing out of the upstream channel, without a transition space, the airflow will mainly adhere to the lower part of the channel and will be difficult to fill the higher part of the downstream channel with a higher tooth height. This can easily lead to the formation of low-speed vortex zones or even dead zones in the higher part of the downstream heat dissipation fins 31, resulting in the increased heat exchange area not being effectively utilized. The existence of the air cavity 01 allows the airflow to enter a relatively open transition space before entering the downstream high heat dissipation fins 31. The flow velocity decreases and the static pressure increases, allowing the airflow to redistribute and climb to a higher channel height under lower inertial constraints. This fills the entire cross-section of the downstream high heat dissipation fins 31, reduces the ineffective heat exchange area, improves the actual utilization rate of the heat exchange area gain brought about by the increase in tooth height, and enables the increased heat exchange area downstream to truly participate in effective heat exchange, thereby improving the heat dissipation efficiency of the downstream heat dissipation fins.

[0050] In this embodiment, each air cavity 01 has a rectangular cross-section perpendicular to the second direction X, making the boundaries of the air cavity 01 clear, reducing processing difficulty and mold cost. At the same time, the flat inner wall of the rectangular cross-section of the air cavity 01 makes the static pressure distribution within the air cavity 01 more uniform, avoiding local low-pressure areas or additional eddies induced by irregular cross-sections, and providing a stable flow field environment for airflow deceleration, static pressure recovery, and vertical ascent within the cavity. Meanwhile, the downstream end face of the rectangular cross-section (i.e., the windward end face of the downstream heat dissipation fin assembly 30) faces the airflow, allowing the airflow to uniformly enter the downstream flow channel along the entire end face when flowing out of the air cavity 01, further improving the airflow uniformity of the downstream high heat dissipation fin 31 flow channel.

[0051] In this embodiment, the length of each air cavity 01 along the airflow direction is at least half the length of the air cavity 01 along the third direction, providing the necessary axial distance for the deceleration, static pressure recovery, and height redistribution of the airflow within the air cavity 01. If the length of the air cavity 01 along the airflow direction is too short, the airflow will be forced into the downstream high heat dissipation fin 31 flow channel before it has completed sufficient deceleration and static pressure recovery. At this time, the airflow still retains a strong flow inertia along the original height, making it difficult to fully climb to the full height of the downstream flow channel. Low-speed vortex areas may still exist in the higher part of the downstream heat dissipation fin 31, and the area gain brought by the increase in tooth height cannot be fully realized.

[0052] In this embodiment, the length of each air cavity 01 along the airflow direction does not exceed twice the length of the air cavity 01 along the third direction. On the one hand, when the length of the air cavity 01 exceeds a certain limit, the improvement in the airflow height distribution tends to saturate. Further increasing the length will result in excessive cold air volume that does not pass through the heat dissipation fins, thus reducing the benefits. Furthermore, an excessively long length of the air cavity 01 along the airflow direction leads to an excessively long residence time of the airflow within the cavity, which is detrimental to heat dissipation. On the other hand, an excessively long axial dimension will increase the overall length of the inverter, which is not conducive to improving power density. Therefore, by setting an upper limit on the length, the overall size of the unit is avoided from being excessively increased while ensuring that the airflow fully fills the downstream flow channel, thus balancing the relationship between heat dissipation performance and structural compactness.

[0053] In this embodiment, the air guide shroud 40 is provided with a first air guide plate 41 that is inclined relative to the airflow direction to the upstream heat dissipation fin group 30, so as to guide the airflow to the upstream heat dissipation fin group 31, improve the airflow direction entering the upstream heat dissipation fin group 30, help improve the uniformity of the incoming flow and heat exchange efficiency of the upstream fin group, and at the same time help reduce airflow noise.

[0054] In this embodiment, at least two first inductors 50 are respectively disposed on both sides of at least one heat dissipation fin assembly 30 along the second direction X. The length direction of the first inductor 50 is the first direction Y, and the length direction of the first inductor 50 is aligned with the airflow direction, which reduces the windward projection area of ​​the first inductor 50, effectively reduces the wind resistance along the air duct, and improves the air delivery efficiency of the fan. It also makes the space occupied by the first inductor 50 and the heat dissipation fins 31 in the second direction X smaller. The first inductors 50 are respectively disposed on both sides of at least one heat dissipation fin assembly 30, rather than concentrated on one side of the heat dissipation fin assembly 30, which effectively balances the weight distribution of the whole machine along the second direction X, improves the stability during hoisting and installation, and reduces the risk of tipping. Moreover, compared with the scheme where the first inductor 50 is located upstream of the heat dissipation fin assembly 30, the airflow will not be preheated by the first inductor 50 before flowing to the heat dissipation fin assembly 30, and the overall airflow resistance of the air duct is reduced, the air intake of the heat dissipation fin assembly 30 is improved, and the heat dissipation bottleneck pressure under high power is alleviated.

[0055] In this embodiment, the heat exchange sections 60 of at least two heat exchangers are respectively disposed on both sides of at least one heat dissipation fin assembly 30 along the second direction X. The heat exchange sections 60 are located upstream of the first inductor 50, making full use of the space on both sides of the heat dissipation fin assembly 30 along the second direction X. Since the first inductor 50 has relatively high temperature resistance, its temperature sensitivity is lower than that of other semiconductor devices in the inverter. This allows the heat exchanger to preferentially utilize the lower-temperature incoming air entering the air passage 12 for heat exchange, which helps to improve the heat exchange efficiency of the heat exchanger itself and improve the heat exchanger's ability to share the heat load of the whole machine.

[0056] In this embodiment, each first inductor 50 is evenly distributed on both sides of at least one heat dissipation fin group 30 along the second direction X; the heat exchange section 60 of each heat exchanger is evenly distributed on both sides of at least one heat dissipation fin group 30 along the second direction X. From a thermal management perspective, the heat generation of the first inductors 50 on both sides and the cooling capacity of the heat exchange section 60 of the heat exchanger are evenly matched along the second direction X, which helps to reduce thermal deformation or thermal stress concentration caused by heat accumulation on one side, and improves the lateral uniformity of the overall thermal field. Furthermore, since the first inductors 50 and the heat exchange section 60 of the heat exchanger are components with a relatively high mass proportion in the whole machine, their even distribution effectively balances the weight distribution of the whole machine along the second direction X, avoids unilateral load imbalance, improves the posture stability during hoisting, handling, and installation, reduces the risk of tipping during operation, and improves the convenience and safety of installation operations.

[0057] In this embodiment, a second inductor 70 is provided downstream of each heat dissipation fin assembly 30, and the airflow is directed to the second inductor 70 by the second air guide plate 42 extending from the air guide shroud 40. This reduces the diffusion and separation of the airflow after it leaves the heat dissipation fin channel due to the loss of boundary constraints, which helps to improve the heat dissipation efficiency of the second inductor 70.

[0058] In this embodiment, any two adjacent heat dissipation fin groups 30 have the same length along the second direction X, making the heat dissipation fin group 30 have a regular shape, which facilitates the integrated design and assembly of the air guide shroud 40; at the same time, the first inductor 50 and the second inductor 70 at least partially overlap on the projection surface of the second direction X, which helps to make reasonable use of the space in the air passage cavity 12.

[0059] The foregoing description of the specifications and embodiments is intended to explain the scope of protection of this invention, but does not constitute a limitation on the scope of protection of this invention. Modifications, equivalent substitutions, or other improvements to the embodiments of this invention or a portion thereof that can be obtained by those skilled in the art through logical analysis, reasoning, or limited experimentation, based on the teachings of this invention or the foregoing embodiments, in conjunction with common knowledge, general technical knowledge, and / or existing technology, should all be included within the scope of protection of this invention.

Claims

1. An inverter, characterized in that, At least two heat dissipation fin groups (30) are provided in the air passage cavity (12) along the air passage direction, and in the two adjacent heat dissipation fin groups (30) along the air passage direction, the tooth height of the downstream heat dissipation fin group (30) is greater than the tooth height of the upstream heat dissipation fin group (30). The air guide shroud (40) spans between any two adjacent heat dissipation fin groups (30) along the wind direction and is at least partially in contact with the tooth tips of the two heat dissipation fin groups (30) to form an air cavity (01) by surrounding the downstream tooth tips of the upstream heat dissipation fin group (30) and the windward end face of the downstream heat dissipation fin group (30).

2. The inverter as described in claim 1, characterized in that, Each heat dissipation fin assembly (30) includes several heat dissipation fins (31) extending along a first direction and spaced apart along a second direction; the first direction is the airflow direction; each air cavity (01) has a rectangular cross-section perpendicular to the second direction.

3. An inverter as described in claim 2, characterized in that, The length of each air cavity (01) along the first direction is at least half the length of the air cavity (01) along the third direction; the third direction is perpendicular to the first direction and the second direction.

4. An inverter as described in claim 3, characterized in that, The length of each air cavity (01) along the airflow direction shall not exceed twice the length of the air cavity (01) along the third direction.

5. An inverter as described in claim 1, characterized in that, The air guide shroud (40) also has a first air guide plate (41) that is inclined relative to the airflow direction to the upstream heat dissipation fin group (30) to guide the airflow to the upstream heat dissipation fin group (30).

6. An inverter as described in claim 1, characterized in that, Each heat dissipation fin group (30) includes a plurality of heat dissipation fins (31) extending along a first direction and spaced apart along a second direction; the first direction is the airflow direction; at least two first inductors (50) are respectively disposed on both sides of at least one heat dissipation fin group (30) along the second direction; the length direction of the first inductor (50) is the first direction.

7. An inverter as described in claim 6, characterized in that, At least two heat exchangers have heat exchange sections (60) respectively disposed on both sides of at least one heat dissipation fin group (30) along the second direction, and the heat exchange sections (60) are located upstream of the first inductor (50).

8. An inverter as described in claim 7, characterized in that, Each first inductor (50) is evenly distributed on both sides of at least one heat dissipation fin group (30) along the second direction; the heat exchange section (60) of each heat exchanger is evenly distributed on both sides of at least one heat dissipation fin group (30) along the second direction.

9. An inverter as described in claim 6, characterized in that, Downstream of each heat dissipation fin assembly (30), there are also several second inductors (70) arranged along the second direction; the air guide shroud (40) is also provided with a second air guide plate (42) extending downstream relative to the downstream heat dissipation fin assembly (30) to guide the air to the second inductor (70).

10. An inverter as described in claim 8 or 9, characterized in that, Any two adjacent heat dissipation fin groups (30) have the same length along the second direction; the first inductor (50) also overlaps at least partially with the second inductor (70) on the projection surface of the second direction.

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