An inverter

Abstract

The application provides an inverter, first inductors, a heat dissipation fan and a first heat exchange part of a first heat exchanger are sequentially and spacedly arranged in a first direction in a through air cavity, and an axis of the heat dissipation fan extends in the first direction; a length direction of the first inductors is a second direction; the through air cavity is provided with a first air inlet for air inlet in the first direction and a second air inlet for air inlet in a third direction; the first air inlet is located upstream of the first inductors, and the second air inlet is located upstream of the heat dissipation fan and at least partially faces the space between the first inductors and the heat dissipation fan. The application can improve the heat dissipation efficiency of each device in the through air cavity.

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 between the heat-generating components in the protective cavity is achieved through heat sinks. The heat-absorbing portion of the heat sink is located in the protective cavity, while the heat-exchanging portion is located in the air-flow cavity. A fan in the air-flow cavity removes the heat from the heat-exchanging portion of the heat sink. The heat sink can be a finned heat sink, an air-to-air heat exchanger, an air-to-liquid heat exchanger, or a phase-change heat sink, etc.

[0004] In existing designs, the air ducts within the air chamber are arranged vertically, with the boost inductor typically located near the air inlet and the inverter inductor near the air outlet. The heat exchange section of the radiator is generally located downstream of the boost inductor. This not only causes a sharp decrease in the heat dissipation performance of the radiator due to receiving preheated air, creating a heat dissipation bottleneck, but also amplifies this bottleneck as the inverter's power increases. 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 each device in the air cavity.

[0006] Through continuous observation, analysis and experimentation, the applicant intends to find the reasons for the low heat dissipation efficiency of inverters in the background technology. On the one hand, the heat exchange part of the heat sink located downstream of the boost inductor receives hot air that has passed through the boost inductor. On the other hand, when the power of the inverter increases, finned heat sinks and heat exchangers are often set up simultaneously for combined heat dissipation, and the disadvantage of the unreasonable layout in the air passage of the existing inverter will be further highlighted.

[0007] The aforementioned defects in the background technology were first discovered by the applicant. Based on this, and in order to improve upon the defects in the background technology and achieve the objective of this application, the applicant adopts the following technical solution to solve the problem: Technical solution one relates to an inverter, wherein a first inductor, a cooling fan, and a first heat exchanger are sequentially and spaced apart in an air passage cavity along a first direction, and the axis of the cooling fan extends along the first direction; the length direction of the first inductor is a second direction; the air passage cavity is provided with a first air inlet that enters air along the first direction and a second air inlet that enters air in a third direction; the first air inlet is located upstream of the first inductor, and the second air inlet is located upstream of the cooling fan and at least partially faces the gap between the first inductor and the cooling fan; the first direction, the second direction, and the third direction are orthogonal.

[0008] Technical Solution 2 based on Technical Solution 1: The first heat dissipation fin group in the air passage is located upstream of the heat dissipation fan. The first heat dissipation fin group includes several first heat dissipation fins that are spaced apart along the second direction and extend along the first direction. The number of first inductors is at least two and they are symmetrically distributed on both sides of the first heat dissipation fin group along the second direction. The second air inlet is at least partially oriented towards the gap between the heat dissipation fan and the first heat dissipation fin group. Technical Solution 3 based on Technical Solution 1: The second heat dissipation fin group in the air passage is located downstream of the heat dissipation fan. The second heat dissipation fin group includes several second heat dissipation fins that are spaced apart along the second direction and extend along the first direction. The number of first heat exchange sections is at least two and they are symmetrically distributed on both sides of the second heat dissipation fin group along the second direction.

[0009] Technical Solution 4 based on Technical Solution 3: The third heat dissipation fin group in the air passage is located downstream of the second heat dissipation fin group. The third heat dissipation fin group includes a plurality of third heat dissipation fins that are spaced apart along the second direction and extend along the first direction. The length of the third heat dissipation fin group along the second direction is greater than the length of the second heat dissipation fin group along the second direction, and the middle parts of the second heat dissipation fin group and the third heat dissipation fin group correspond to each other along the second direction. The first heat exchange section is located in the angle region between the second heat dissipation fin group and the third heat dissipation fin group. Technical solution five based on technical solution four: The cavity wall of the air passage is provided with a first wall that is opposite to the second heat dissipation fin group and the third heat dissipation fin group in a third direction; the tooth height of the third heat dissipation fin is higher than the tooth height of the second heat dissipation fin group; the air guide cover is provided on the third heat dissipation fin group and is provided with a first baffle plate connected to the first wall.

[0010] Technical solution six based on technical solution five: The first air guide plate extends inclinedly from the first wall toward the direction close to the second heat dissipation fin group. Technical solution seven based on technical solution six: the first air guide plate is suspended above the second heat dissipation fin group, and its end and the third heat dissipation fin group are spaced apart along the first direction to guide the air to the second heat dissipation fin group. Technical solution eight based on technical solution four: a plurality of second inductors arranged along the second direction are disposed in the air passage cavity downstream of the third heat dissipation fin assembly; the second heat exchange section of at least one second heat exchanger is located on at least one side of each second inductor along the second direction; an air passage gap is formed between the two ends of the third heat dissipation fin assembly along the first direction and the cavity wall of the air passage cavity. Technical solution nine based on technical solution eight: the projection of the second heat exchange section and the air passage along the first direction at least partially overlaps. Based on technical solution eight, technical solution ten: the second air inlet is also opposite to the first inductor; the first inductor has several first teeth arranged at intervals along a third direction and perpendicular to the third direction on both sides along the second direction, and several second teeth arranged at intervals along the second direction and perpendicular to the second direction on the side of the first inductor facing the second air inlet; the second inductor has several third teeth arranged at intervals along the second direction and perpendicular to the second direction on the side facing the third heat dissipation fin group, and several fourth teeth arranged at intervals along a third direction and perpendicular to the third direction on both sides along 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, "upstream" and "downstream" refer to the direction of the airflow, that is, along the airflow path, the position that is first passed by the airflow is upstream, and the position that is later passed by the airflow is downstream.

[0011] To address the issue that the first inductor is located upstream of the cooling fan, causing it to heat the airflow and thus resulting in excessively high inlet air temperature in the downstream first heat exchange section, a dual air inlet with airflow in different directions is installed upstream of the cooling fan. The cold air from the second air inlet is then allowed to enter at least part of the gap between the first inductor and the cooling fan, thereby relatively reducing the mixed air temperature flowing to the first heat exchange section while also taking into account the cooling requirements of the first inductor itself.

[0012] Specifically, a main airflow path is formed within the air passage cavity along a first direction, and the airflow passes sequentially through each device along the first direction. The length direction of the first inductor is the second direction, which increases the area of ​​the windward surface of the first inductor and helps to improve the convective heat transfer conditions on the surface of the first inductor.

[0013] The first and second air inlets bring in cool air from the axial and lateral directions, respectively, enriching the airflow sources, which helps to increase the total air volume and reduce the air resistance of the cooling fan. The first air inlet is located upstream of the first inductor, so that the cool air flows through the first inductor first before it is heated, which helps to reduce the heating temperature of the first inductor.

[0014] The second air inlet is at least partially oriented towards the gap between the first inductor and the cooling fan. Lateral cool air entering this gap helps to relatively reduce the temperature of the air flowing towards the first heat exchanger, thus improving its heat exchange efficiency. Therefore, the combination of the dual air inlets and the gap creates a composite flow field in the main airflow path, which not only enhances the heat dissipation intensity of the first inductor itself but also optimizes the airflow conditions of the first heat exchanger. The overall heat dissipation path is compact and has low air resistance.

[0015] In technical solution two, the first heat dissipation fin assembly is located upstream of the cooling fan, increasing the heat dissipation surface area at the front of the fan and helping to improve the overall heat dissipation capacity of the upstream area. Simultaneously, the first heat dissipation fins extend along the main airflow direction, limiting their impact on wind resistance. At least two first inductors are symmetrically distributed on both sides of the first heat dissipation fin assembly along the second direction. This disperses the heat load along the second direction, preventing heat accumulation on one side and improving the uniformity of heat dissipation conditions for each inductor. Furthermore, the symmetrical arrangement of the first inductors on both sides, together with the centrally located first heat dissipation fin assembly, forms a stable weight distribution, balancing the weight along the second direction in the upstream area of ​​the cooling fan. This helps maintain the center of gravity of the entire unit in the middle of the airflow cavity along the second direction, improving balance during handling and installation and reducing the risk of tilting or installation misalignment caused by uneven weight distribution. The second air inlet is at least partially oriented towards the gap between the first inductors and the first heat dissipation fin assembly. Lateral cold air not only continues to mix and cool within the gap area but also penetrates into the air inlet side of the first heat dissipation fin array, improving the convective heat transfer environment on the surface of the first heat dissipation fins.

[0016] In technical solution three, the second heat dissipation fin group is located downstream of the cooling fan, utilizing the pressurized airflow of the cooling fan for forced convection heat transfer, which helps to further improve the heat dissipation capacity of the air cavity. The number of first heat exchange sections is at least two and symmetrically distributed on both sides of the second heat dissipation fin group along the second direction. On the one hand, this allows the heat exchange area to expand along the second direction, matching the relatively uniform airflow distribution downstream of the cooling fan and improving the uniformity of the heating conditions of each first heat exchange section. On the other hand, the symmetrical arrangement of the first heat exchange sections on both sides matches the central layout of the second heat dissipation fin group, making the weight of the downstream area of ​​the cooling fan evenly distributed along the second direction. This echoes the symmetrical layout of the first inductor upstream, helping to further stabilize the center of gravity of the whole machine along the second direction in the middle of the cavity, and improving the anti-tipping ability of the whole machine in different scenarios such as wall mounting and bracket fixing.

[0017] In technical solution four, the third heat dissipation fin group is located downstream of the second heat dissipation fin, forming a two-stage fin array connected one after the other downstream of the cooling fan. The airflow passes through the two stages of fins in sequence, and the heat dissipation area is progressively superimposed along the main air path, which helps to absorb heat in stages and increase the total heat dissipation downstream.

[0018] The length of the third heat dissipation fin group along the second direction is greater than that of the second heat dissipation fin group along the second direction, so that the downstream heat dissipation area covers a wider lateral range, which helps to absorb the residual heat that is still spreading laterally after the heat dissipation of the front stage; at the same time, the heat dissipation fin layout that is narrow at the front and wide at the back, together with the symmetrical arrangement of the first inductor and the first heat exchange section upstream and downstream, makes the weight distribution of the whole machine from front to back along the first direction and from left to right along the second direction more reasonable, and the center of gravity is closer to the geometric center of the air passage, which helps to improve the stability of the whole machine under various installation postures.

[0019] The first heat exchange section is located in the angled area between the second and third heat dissipation fin groups, rather than occupying additional air duct space. This improves space utilization without increasing the overall size of the unit and reduces the overall size of the unit along the second direction.

[0020] In technical solution five, the tooth height of the third heat dissipation fin is higher than that of the second heat dissipation fin group. By increasing the heat exchange area of ​​the downstream heat dissipation fin, the heat exchange capacity attenuation caused by the decrease in dynamic pressure after the airflow passes through the front fin is compensated, which helps to maintain the stability of the downstream heat dissipation capacity.

[0021] The air guide cover is installed on the third heat dissipation fin assembly and has a first baffle plate connected to the first wall. It restricts the airflow above the third heat dissipation fin assembly to a predetermined air duct, reduces the short-circuit overflow of airflow from the top of the third heat dissipation fin, increases the proportion of effective airflow through the gap of the third heat dissipation fin, and improves the heat exchange efficiency of the third heat dissipation fin assembly.

[0022] In technical solution six, the first air guide plate extends obliquely from the first wall toward the direction of the second heat dissipation fin group to guide the air to the second heat dissipation fin group, which helps to confine the airflow in the second heat dissipation fin group and increase the effective air volume flowing through the second heat dissipation fin group.

[0023] In technical solution seven, the first air guide plate is suspended above the second heat dissipation fin group, and its end is spaced from the third heat dissipation fin group along the first direction. Because the tooth height of the downstream third heat dissipation fin is higher than that of the upstream second heat dissipation fin, the airflow, after flowing out of the upstream channel, mainly adheres to the lower part of the channel due to flow inertia, making it difficult to fill the higher part of the downstream channel with its higher tooth height. This results in a low-speed vortex zone or even a dead flow zone in the higher part of the downstream fin. By suspending the end of the first air guide plate and creating a gap, a third-direction diffusion space is provided for the airflow, allowing it to fully fill the entire tooth height range of the downstream third heat dissipation fin, thus truly converting the increased heat exchange area into an effective heat exchange area. Simultaneously, the suspended structure avoids direct contact between the first air guide plate and the fins, reducing assembly precision requirements.

[0024] In technical solution eight, the second inductor is positioned downstream of the third heat sink fin assembly. This allows cool air to preferentially flow through the heat sink fin assembly corresponding to the IGBT, which has higher heat dissipation requirements, and then through the second inductor, which has relatively lower heat dissipation. This improves the rationality of heat distribution and increases the utilization efficiency of the cold source. A gap is formed between the two ends of the third heat sink fin assembly along the first direction and the cavity wall of the air passage. Cool air can flow through this gap to the second heat exchange section, making it possible to arrange multiple heat exchange sections within the air passage.

[0025] In technical solution nine, the projections of the second heat exchange section and the air passage along the first direction at least partially overlap. The air passage allows a portion of the cold air delivered by the cooling fan to be directly transported to the second heat exchange section without passing through the heat dissipation fins of the preceding stage. On the one hand, this reduces the inlet air temperature of the second heat exchange section, increases the heat exchange temperature difference, and improves the heat exchange performance of the second heat exchanger. On the other hand, this path of cold air does not need to pass through the wind resistance of the heat dissipation fins, reducing the overall wind resistance of the system and improving the energy efficiency of the fan.

[0026] In technical solution ten, the second air inlet is connected to the first air inlet and is opposite to the first inductor. After the two streams of cold air converge on the windward side of the first inductor, they concentrate on impacting the surface of the first inductor, which improves the cooling intensity of the windward side of the first inductor. This allows the tooth height of the first and second teeth of the first inductor to be reduced, thereby reducing production costs. The arrangement of the third and fourth teeth of the second inductor improves the heat dissipation efficiency of the second inductor. Attached Figure Description

[0027] 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.

[0028] Figure 1 This is a schematic diagram of the inverter according to an embodiment of this application; Figure 2 for Figure 1 Top view; Figure 3 for Figure 2 Sectional view along the AA direction; Figure 4 for Figure 2 Sectional view in the BB direction; Figure 5 for Figure 2 Sectional view in the CC direction; Figure 6 This is a schematic diagram showing the arrangement of various components in the air passage cavity according to an embodiment of this application; Figure 7 for Figure 6 Top view.

[0029] Explanation of key figure labels: Box 10; Protective cavity 11; Air passage 12; First wall 120; First air inlet 121; Second air inlet 122; First air outlet 123; Second air outlet 124; First inductor 20; First toothed plate 21; Second toothed plate 22; Cooling fan 30; First heat exchange section 41; Second heat exchange section 42; First heat dissipation fin assembly 51; First heat dissipation fin 511; Second heat dissipation fin assembly 52; Second heat dissipation fin 521; Third heat dissipation fin group 53; Third heat dissipation fin 531; Second inductor 60; Third tooth 61; Fourth tooth 62; Air guide shroud 70; First air baffle 71; First air guide plate 80; Airflow interval 01; Detailed Implementation 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.

[0030] 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.

[0031] 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.

[0032] 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.

[0033] 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."

[0034] 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.

[0035] Example The high-power photovoltaic inverter in this embodiment is suitable for outdoor power generation scenarios with high temperatures and high dust levels. Figure 1-5 , Figure 1 This is a schematic diagram of the inverter in this embodiment. Figure 2 for Figure 1 Top view, Figure 3 for Figure 2 Cross-sectional view along the AA direction, Figure 4 for Figure 2 Cross-sectional view in the BB direction, Figure 5 for Figure 2 Sectional view in the CC direction.

[0036] See Figure 3 The 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. Environmentally sensitive components such as IGBT power modules and capacitors are encapsulated within the protective cavity 11, while heat-generating components with strong weather resistance, such as boost inductors and inverter inductors, and heat dissipation ducts are centrally located 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, with the airflow generally flowing 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, perpendicular to the first direction Y in the horizontal plane; and the third direction Z is the up-to-down direction of the air passage cavity 12, perpendicular to the plane formed by the first direction Y and the second direction X. The first direction Y, the second direction X, and the third direction Z are perpendicular to each other.

[0037] See Figure 6 and Figure 7 , Figure 6 A schematic diagram showing the layout of the components within the air passage 12 is provided. Figure 7 It shows Figure 6 Top view. Figure 6 Within the air passage 12, a main airflow path extending along the first direction Y is formed. The first inductor 20, the cooling fan 30, the first heat exchange section 41 of the first heat exchanger, the first heat dissipation fin group 51, the second heat dissipation fin group 52, the third heat dissipation fin group 53, the second inductor 60, and the second heat exchange section 42 of the second heat exchanger are all located within the air passage 12. Each component is positioned and fixed through the cavity wall of the air passage 12, the mounting bracket, and the connecting parts.

[0038] join Figure 3 The air passage 12 forms air inlets at both ends along the first direction Y. Figure 3 (left end) and air outlet ( Figure 3 The air inlet of the air passage 12 (located at the right end) has two independent air inlets. The first air inlet 121 is located on the front wall of the air passage 12 and allows air to enter along the first direction Y. The second air inlet 122 is located on the top wall of the air passage 12 and allows air to enter along the third direction Z. The first air inlet 121 is located at the uppermost part of the air passage 12 and is also located upstream of the first inductor 20 mentioned below. The second air inlet 122 is located upstream of the cooling fan 30 and is at least partially oriented towards the gap between the first inductor 20 and the cooling fan 30. The second air inlet 122 is also opposite to the first inductor 20 and the first heat dissipation fin group 51 mentioned below along the third direction Z.

[0039] See Figure 3 The air outlet of the air passage 12 is provided with a first air outlet 123 that discharges air in the first direction Y, see [reference]. Figure 1 The air outlet of the air passage 12 is also provided with a second air outlet 124 that discharges air in the second direction X. In other embodiments, the air outlet of the air passage 12 may also be provided with a third air outlet that discharges air in the third direction Z. However, it should be understood that the air outlet of the air passage 12 may also be provided with only one or both of the first air inlet 121, the second air outlet 124, or the third air outlet.

[0040] The walls of the air passage 12 form the boundary of the main air duct and participate in... Figure 4 The top wall, serving as the first wall 120 facing downstream heat dissipation fin assemblies along the third direction Z, together with the upper surface of the fin assemblies, defines the top boundary of the air outlet duct. See [reference needed]. Figure 5 The left and right cavity walls and the two ends of the fin assembly along the second direction X form an air passage gap 01, which is a closed or semi-closed air passage space enclosed by the bottom wall and the front and rear end walls.

[0041] See Figure 6The first inductor 20 is positioned upstream of the air passage 12. In this embodiment, the first inductor 20 is the boost inductor of the inverter, and its length direction is the second direction X. That is, the body of the first inductor 20 is horizontally placed along the left-right direction, with its long side perpendicular to the main air passage direction, maximizing the projected area of ​​the windward surface. The first inductor 20 and the cooling fan 30 are arranged at intervals along the first direction Y. See [reference needed]. Figure 3 The first inductor 20 and the second air inlet 122 are opposite each other along the third direction Z.

[0042] See also Figure 6-7 There are two first inductors 20, which are symmetrically distributed on the left and right sides of the air passage cavity 12 along the second direction X. There are at least two first inductors 20 and they are symmetrically distributed on both sides of the first heat dissipation fin group 51 along the second direction X. The weight of the upstream area is evenly distributed along the second direction X. The center of gravity of the whole machine falls on the left and right symmetrical center line of the air passage cavity 12.

[0043] See Figure 6 The first inductor 20 has several first toothed plates 21 arranged at intervals along the third direction Z and perpendicular to the third direction Z on both sides of the second direction X. The first inductor 20 has several second toothed plates 22 arranged at intervals along the second direction X and perpendicular to the second direction X on the side facing the second air inlet 122. The first inductor 20 can also have several toothed plates arranged at intervals along the third direction Z and perpendicular to the third direction Z on the side opposite to the first air inlet 121. The arrangement direction of each type of toothed plate is matched with the axial flow of the first air inlet 121 and the lateral flow of the second air inlet 122, so that each surface of the first inductor 20 can obtain good convective heat transfer conditions.

[0044] A cooling fan 30 is fixed in the middle of the air passage cavity 12, with its axis extending along the first direction Y. An axial flow fan is used to drive the airflow throughout its length. In this embodiment, there are multiple cooling fans 30, which are spaced apart along the second direction X. The cooling fans 30 are located downstream of the first inductor 20 and upstream of the first heat exchange section 41 of the first heat exchanger. That is, the first inductor 20, the cooling fan 30, and the first heat exchange section 41 of the first heat exchanger are sequentially spaced apart along the first direction Y in the air passage cavity 12. The cooling fan 30 pressurizes the upstream airflow and then delivers it downstream along the first direction Y. The second air inlet 122 is at least partially oriented towards the gap between the first inductor 20 and the cooling fan 30, allowing lateral cold air to enter this area, relatively reducing the air temperature flowing towards the cooling fan 30 and the downstream area. At the same time, some of the cold air directly washes over the second toothed fins 22 of the first inductor 20, improving the inductor's own heat dissipation intensity.

[0045] The first heat exchange section 41 of the first heat exchanger is located downstream of the cooling fan 30, between the cooling fan 30 and the subsequent heat dissipation fin assembly along the first direction Y. The first heat exchanger is a cross-chamber heat exchange device. In addition to the first heat exchange section 41 located in the air passage 12, it also includes a heat absorption end disposed 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 compromised. The first heat exchanger can be selected from different types according to the 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 first heat exchange section 41 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 first heat exchange section 41 and is cooled by the airflow in the air passage 12 before flowing 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 first heat exchange section 41 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] See Figure 7 There are at least two first heat exchange sections 41, symmetrically distributed on the left and right sides of the main airflow along the second direction X, so that the weight of the downstream area is evenly distributed along the second direction X, forming a counterweight system that echoes the symmetrical layout of the upstream first inductor 20. The first heat exchange section 41 is located in the angled area between the subsequent second heat dissipation fin group 52 and the third heat dissipation fin group 53, without occupying additional lateral space of the main airflow, thus maximizing the utilization of the heat exchange area within the limited cavity volume. The first heat exchange section 41 receives the mixed airflow pressurized by the cooling fan 30, completes the heat exchange, and continues to transport the hot air downstream.

[0047] See Figure 6 The first heat dissipation fin assembly 51 is located upstream of the cooling fan 30, between the first inductor 20 and the cooling fan 30. It comprises several first heat dissipation fins 511 spaced apart along the second direction X and extending along the first direction Y, and is centrally positioned. Two first inductors 20 are symmetrically distributed along the second direction X on both sides of the first heat dissipation fin assembly 51 along the second direction X, together forming the upstream heat dissipation unit. (See [reference]). Figure 4 The second air inlet 122 is at least partially oriented toward the gap between the cooling fan 30 and the first cooling fin group 51, allowing lateral cold air to penetrate into the gap of the first cooling fin 511 to enhance fin heat exchange and improve the overall heat dissipation capacity of the upstream area.

[0048] See Figure 6 The second heat dissipation fin group 52 is located downstream of the cooling fan 30, after the cooling fan 30 and before the third heat dissipation fin group 53. It includes several second heat dissipation fins 521 arranged at intervals along the second direction X and extending along the first direction Y. The second heat dissipation fin group 52 is centrally located, and the two aforementioned first heat exchange sections 41 are symmetrically distributed on its left and right sides along the second direction X. The second heat dissipation fin group 52 and the first heat exchange sections 41 together constitute the first-stage heat dissipation unit downstream of the fan.

[0049] See Figure 6 The third heat dissipation fin group 53 is located downstream of the second heat dissipation fin group 52, behind the second heat dissipation fin group 52 and the first heat exchange section 41. It includes several third heat dissipation fins 531 arranged at intervals along the second direction X and extending along the first direction Y. The total length of the third heat dissipation fin group 53 along the second direction X is greater than the total length of the second heat dissipation fin group 52 along the second direction X, that is, the lateral coverage of the downstream fin group is wider. Moreover, the second heat dissipation fin group 52 and the third heat dissipation fin group 53 are aligned at the middle along the second direction X, so that the energy of the mainstream airflow is concentrated in the left and right central areas of the air passage cavity 12. The tooth height of the third heat dissipation fin 531 is higher than that of the second heat dissipation fin group 52. By increasing the heat exchange area of ​​the downstream fins, the heat exchange capacity attenuation caused by the decrease in dynamic pressure after the airflow passes through the front fins is compensated. The third heat dissipation fin group 53 and the second heat dissipation fin group 52 are connected front and rear along the first direction Y, forming a two-stage fin array downstream of the fan. The airflow passes through the two stages of fins sequentially, and the heat dissipation area gradually overlaps along the main airflow path, which helps to absorb heat in stages. See also Figure 5 The two ends of the second heat dissipation fin group 52 in the first direction Y are respectively provided with air passage gaps 01 that run through the first direction Y between the left and right cavity walls of the air passage cavity 12. These gaps are not blocked by fins, providing a low-resistance bypass channel for airflow.

[0050] See Figure 6 The second inductor 60 is located downstream of the third heat dissipation fin group 53. In this embodiment, the second inductor 60 is an inverter inductor, arranged at intervals along the second direction X in the downstream region of the air passage cavity 12. Several third toothed fins 61, arranged at intervals along the second direction X and perpendicular to the second direction X, are arranged on the side of the second inductor 60 facing the third heat dissipation fin group 53. Several fourth toothed fins 62, arranged at intervals along the third direction Z and perpendicular to the third direction Z, are arranged on the left and right sides respectively, matching the incoming flow direction of the downstream region to enhance heat dissipation. The second inductor 60 is dispersed along the second direction X, working together with the symmetrically distributed upstream and downstream devices to maintain the overall weight balance along the second direction X.

[0051] The second heat exchange section 42 of the second heat exchanger is arranged on at least one side of each second inductor 60 along the second direction X, located in the downstream region of the third heat dissipation fin group 53. The second heat exchanger is also a cross-chamber heat exchange device. In addition to the second heat exchange section 42 located in the air passage 12, it also includes an auxiliary heat absorption end disposed in the protective cavity 11, which will not be described in detail here. In this embodiment, there are two second heat exchange sections 42, respectively located on both sides of each second inductor 60 along the second direction X. The projection of the second heat exchange section 42 along the first direction Y at least partially overlaps with the aforementioned air passage 01, so that the cold air flowing through the air passage 01 does not need to be preheated by the upstream fins and directly washes over the second heat exchange section 42. This reduces the inlet air temperature of the second heat exchange section 42, increases the heat exchange temperature difference, and avoids the wind resistance in the fin area. The second heat exchange section 42 and the second inductor 60 are staggered along the second direction X, so that the downstream region simultaneously has two thermal management paths: inductive heat dissipation and independent heat exchange, preventing heat from flowing back upstream and affecting the heat dissipation effect of the upstream stage.

[0052] See Figure 4 An air guide shroud 70 is installed above the third heat dissipation fin assembly 53, covering the top area of ​​the third heat dissipation fin assembly 53 in a Z-direction, restricting the airflow above the third heat dissipation fin assembly 53 within a predetermined air duct, reducing airflow short-circuiting and overflowing from the top of the fins. A first baffle plate 71 is provided on the side of the air guide shroud 70 facing the top wall of the air passage 12. The first baffle plate 71 extends upward and connects with the top wall, i.e., the first wall 120, increasing the effective airflow ratio through the gaps of the third heat dissipation fins 531. A first air guide plate 80 is also integrally formed on the air guide shroud 70, extending obliquely from the first wall 120 towards the second heat dissipation fin assembly 52. Figure 4 The middle section extends downwards and to the right.

[0053] The first air guide plate 80 adopts a suspended design, with a gap between its end and the upper surface of the second heat dissipation fin group 52, and a continuous interval space along the first direction Y between its end and the front end of the third heat dissipation fin group 53. Since the airflow has the inertia of flowing along the original lower flow channel when flowing out of the second heat dissipation fin group 52, if there is a lack of diffusion space, the airflow will continuously adhere to the lower part of the flow channel and cannot fill the higher part of the third heat dissipation fin 531 with its higher tooth height, forming a low-speed dead zone. The suspension and spacing of the first air guide plate 80 provide vertical diffusion space for the airflow. The airflow guided by the air guide plate gains an upward velocity component in the interval area, gradually rising to the tooth tip area of ​​the third heat dissipation fin 531, and finally filling the entire tooth height range of the third heat dissipation fin 531, so that the increased tooth height is truly converted into effective heat exchange area. The suspended design also avoids direct contact between the air guide plate and the fins, reducing the requirements for assembly precision and reducing vibration noise during operation.

[0054] During operation, the cooling fan 30 starts, and cold air simultaneously enters the air passage cavity 12 from the first air inlet 121 along the first direction Y and the second air inlet 122 along the third direction Z. The two streams of cold air impact the surface of the first inductor 20, first completing the cooling of the first inductor 20. Part of the cold air from the second air inlet 122 cools the first heat dissipation fin assembly 51, and part of the cold air enters the gap between the first inductor 20 and the cooling fan 30. After being pressurized by the cooling fan 30, part of the airflow flows synchronously through the second heat dissipation fin assembly 52 and the first heat exchange section 41 and then flows to the third heat dissipation fin assembly 53. After being guided by the first air guide plate 80, it fills the tooth height of the third heat dissipation fin 531, completing the heat exchange. Then it flows through the gap of the third heat dissipation fin 531 and cools the second inductor 60; another part flows through the air passage gap 01 to the second heat exchange section 42. Finally, the hot air is discharged from the air outlet of the air passage cavity 12.

[0055] In this embodiment, to address the problem that the first inductor 20 is located upstream of the cooling fan 30, causing it to heat up the airflow and thus making the inlet temperature of the downstream first heat exchange section 41 too high, a dual air inlet with airflow in different directions is provided upstream of the cooling fan 30, and the cold air from the second air inlet 122 is allowed to at least partially enter the gap area between the first inductor 20 and the cooling fan 30, thereby relatively reducing the mixed air temperature flowing to the first heat exchange section 41, while also taking into account the cooling requirements of the first inductor 20 itself.

[0056] Specifically, a main airflow path along the first direction Y is formed within the air passage 12, and the airflow passes through each device sequentially along the first direction Y. The length direction of the first inductor 20 is the second direction X, which increases the area of ​​the windward surface of the first inductor 20 and helps to improve the convective heat transfer conditions on the surface of the first inductor 20.

[0057] The first air inlet 121 and the second air inlet 122 bring in two streams of cold air from the axial and lateral directions, respectively, enriching the air intake sources, helping to increase the total air volume and reduce the wind resistance of the cooling fan 30. The first air inlet 121 is located upstream of the first inductor 20, so that the cold air flows through the first inductor 20 first before it is heated, which helps to reduce the temperature of the first inductor 20.

[0058] The second air inlet 122 is at least partially oriented towards the gap between the first inductor 20 and the cooling fan 30. When lateral cool air enters this gap, it helps to relatively reduce the air temperature flowing towards the first heat exchanger 41, thus improving the heat exchange efficiency of the first heat exchanger 41. Therefore, the combination of the dual air inlets and the gap creates a composite flow field in the main airflow path, which not only enhances the heat dissipation intensity of the first inductor 20 itself but also optimizes the airflow conditions of the first heat exchanger 41. The overall heat dissipation path is compact and has low air resistance.

[0059] In this embodiment, the first heat dissipation fin group 51 is located upstream of the cooling fan 30, increasing the heat dissipation surface area at the front of the cooling fan 30, which helps to improve the overall heat dissipation capacity of the upstream area. At the same time, the first heat dissipation fin group 511 extends along the main airflow direction, so its impact on wind resistance is relatively limited. The number of first inductors 20 is at least two and they are symmetrically distributed on both sides of the first heat dissipation fin group 51 along the second direction X. On the one hand, this disperses the heat load along the second direction X, avoids heat accumulation on one side, and improves the uniformity of heat dissipation conditions for each first inductor 20. On the other hand, the symmetrical arrangement of the first inductors 20 on both sides and the centrally located first heat dissipation fin group 51 forms a stable weight distribution, making the weight of the upstream area of ​​the cooling fan 30 along the second direction X more balanced. This helps to keep the center of gravity of the whole machine in the middle of the air passage 12 along the second direction X, improves the balance during handling and installation, and reduces the risk of hoisting tilt or installation offset caused by unilateral weight imbalance. The second air inlet 122 is at least partially oriented toward the gap between the first inductor 20 and the first heat dissipation fin group 51. The lateral cold air not only continues to mix and cool in the gap area, but can also penetrate into the air inlet side of the array of the first heat dissipation fin group 51, improving the convective heat transfer environment on the surface of the first heat dissipation fin group.

[0060] In this embodiment, the second heat dissipation fin group 52 is located downstream of the heat dissipation fan 30, and uses the pressurized airflow of the heat dissipation fan 30 for forced convection heat exchange, which helps to further improve the heat dissipation capacity of the air cavity 12. The number of the first heat exchange parts 41 is at least two and they are symmetrically distributed on both sides of the second heat dissipation fin group 52 along the second direction X. On the one hand, the heat exchange area is expanded along the second direction X, which matches the relatively uniform wind speed distribution downstream of the heat dissipation fan 30 and improves the balance of the heating conditions of each first heat exchange part 41. On the other hand, the symmetrical arrangement of the first heat exchange parts 41 on both sides matches the central layout of the second heat dissipation fin group 52, which makes the weight of the downstream area of ​​the heat dissipation fan 30 evenly distributed along the second direction X. This forms an upstream and downstream echo with the symmetrical layout of the upstream first inductor 20, which helps to further stabilize the center of gravity of the whole machine along the second direction X in the middle of the cavity and improve the anti-tipping ability of the whole machine in different scenarios such as wall mounting and bracket fixing.

[0061] In this embodiment, the third heat dissipation fin group 53 is located downstream of the second heat dissipation fin 521, forming a two-stage fin array connected in series downstream of the heat dissipation fan 30. The airflow passes through the two-stage fins in sequence, and the heat dissipation area is progressively superimposed along the main air path, which helps to absorb heat in stages and increase the total heat dissipation downstream.

[0062] The length of the third heat dissipation fin group 53 along the second direction X is greater than that of the second heat dissipation fin group 52 along the second direction X, so that the downstream heat dissipation area covers a wider lateral range, which helps to absorb the residual heat that is still spreading laterally after the heat dissipation of the front stage; at the same time, the heat dissipation fin layout that is narrow in the front and wide in the back, together with the symmetrical distribution of the first inductor 20 and the first heat exchange section 41 upstream and downstream, makes the weight distribution of the whole machine from front to back along the first direction Y and from left to right along the second direction X more reasonable, and the center of gravity is closer to the geometric center of the air passage 12, which helps to improve the stability of the whole machine under various installation postures.

[0063] The first heat exchange section 41 is located in the angled area between the second heat dissipation fin group 52 and the third heat dissipation fin group 53, rather than occupying additional air duct space. This improves space utilization without increasing the overall size of the machine and reduces the overall size of the machine along the second direction X.

[0064] In this embodiment, the tooth height of the third heat dissipation fin 531 is higher than that of the second heat dissipation fin group 52. By increasing the heat exchange area of ​​the downstream heat dissipation fins, the heat exchange capacity attenuation caused by the decrease in dynamic pressure after the airflow passes through the front fins is compensated, which helps to maintain the stability of the downstream heat dissipation capacity.

[0065] The air guide shroud 70 is placed on the third heat dissipation fin group 53 and is provided with a first baffle plate 71 connected to the first wall 120. It restricts the airflow above the third heat dissipation fin group 53 to a predetermined air duct, reduces the short-circuit overflow of airflow from the top of the third heat dissipation fin 531, increases the effective airflow ratio flowing through the gap of the third heat dissipation fin 531, and improves the heat exchange efficiency of the third heat dissipation fin group 53.

[0066] In this embodiment, the first air guide plate 80 extends obliquely from the first wall 120 toward the direction close to the second heat dissipation fin group 52 to guide the air to the second heat dissipation fin group 52, which helps to limit the airflow in the second heat dissipation fin group 52 and increase the effective air volume flowing through the second heat dissipation fin group 52.

[0067] In this embodiment, the first air guide plate 80 is suspended above the second heat dissipation fin group 52, and its end is spaced from the third heat dissipation fin group 53 along the first direction Y. Since the tooth height of the downstream third heat dissipation fin 531 is higher than that of the upstream second heat dissipation fin 521, the airflow, after flowing out of the upstream channel, mainly adheres to the lower part of the channel due to flow inertia, making it difficult to fill the higher part of the downstream channel with its higher tooth height. This results in a low-speed vortex zone or even a dead flow zone in the higher part of the downstream fin. By suspending the end of the first air guide plate and creating a gap, a vertical diffusion space is provided for the airflow, allowing the airflow to fully fill the entire tooth height range of the downstream third heat dissipation fin 531, thus truly converting the increased heat exchange area into an effective heat exchange area. Simultaneously, the suspended structure avoids direct contact between the first air guide plate and the fins, reducing assembly precision requirements.

[0068] In this embodiment, the second inductor 60 is positioned downstream of the third heat dissipation fin group 53. This allows cold air to preferentially flow through the heat dissipation fin group corresponding to the IGBT, which has higher heat dissipation requirements, and then through the second inductor 60, which has relatively lower heat dissipation. This improves the rationality of cold air distribution and increases the utilization efficiency of the cold source. The three heat dissipation fin group 53 forms a gap between its two ends along the first direction Y and the cavity wall of the air passage 12. Cold air can flow through this gap to the second heat exchange section 42, making it possible to arrange multiple heat exchange sections within the air passage 12.

[0069] In this embodiment, the projection of the second heat exchange section 42 and the air passage 01 along the first direction Y at least partially overlaps. The air passage 01 delivers a portion of the cold air sent out by the cooling fan 30 directly to the second heat exchange section 42 without passing through the heat dissipation fins of the preceding stage. On the one hand, this reduces the inlet air temperature of the second heat exchange section 42, increases the heat exchange temperature difference, and improves the heat exchange performance of the second heat exchanger. On the other hand, this cold air does not need to pass through the wind resistance of the heat dissipation fins, reducing the overall wind resistance of the system and improving the energy efficiency of the fan.

[0070] In this embodiment, the second air inlet 122 is connected to the first air inlet 121 and is opposite to the first inductor 20. After the two streams of cold air converge on the windward side of the first inductor 20, they concentrate on impacting the surface of the first inductor 20, which improves the cooling intensity of the windward side of the first inductor 20. This allows the tooth height of the first tooth 21 and the second tooth 22 of the first inductor 20 to be reduced, thereby reducing production costs. The arrangement of the third tooth 61 and the fourth tooth 62 of the second inductor 60 improves the heat dissipation efficiency of the second inductor 60.

[0071] 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, firstly The inductor (20), the cooling fan (30) and the first heat exchange section (41) of the first heat exchanger are arranged sequentially and spaced apart in the air passage cavity (12) along the first direction, and the axis of the cooling fan (30) extends along the first direction; the length direction of the first inductor (20) is the second direction; The air passage (12) is provided with a first air inlet (121) for air intake in a first direction and a second air inlet (122) for air intake in a third direction; the first air inlet (121) is located upstream of the first inductor (20), and the second air inlet (122) is located upstream of the cooling fan (30) and is at least partially oriented toward the gap between the first inductor (20) and the cooling fan (30); The first direction, the second direction, and the third direction are orthogonal.

2. The inverter as described in claim 1, characterized in that, The first heat dissipation fin group (51) in the air passage (12) is located upstream of the heat dissipation fan (30). The first heat dissipation fin group (51) includes a number of first heat dissipation fins (511) spaced apart along the second direction and extending along the first direction. The number of first inductors (20) is at least two and they are symmetrically distributed on both sides of the first heat dissipation fin group (51) along the second direction. The second air inlet (122) is at least partially facing the gap between the heat dissipation fan (30) and the first heat dissipation fin group (51).

3. An inverter as described in claim 1, characterized in that, The second heat dissipation fin group (52) in the air passage (12) is located downstream of the heat dissipation fan (30). The second heat dissipation fin group (52) includes a number of second heat dissipation fins (521) spaced apart along the second direction and extending along the first direction. The number of first heat exchange parts (41) is at least two and they are symmetrically distributed on both sides of the second heat dissipation fin group (52) along the second direction.

4. An inverter as described in claim 3, characterized in that, The third heat dissipation fin group (53) in the air passage (12) is located downstream of the second heat dissipation fin group (52). The third heat dissipation fin group (53) includes a plurality of third heat dissipation fins (531) that are spaced apart along the second direction and extend along the first direction. The length of the third heat dissipation fin group (53) along the second direction is greater than the length of the second heat dissipation fin group (52) along the second direction, and the second heat dissipation fin group (52) and the third heat dissipation fin group (53) correspond to each other at the middle of the second direction. The first heat exchange section (41) is located in the angle region between the second heat dissipation fin group (52) and the third heat dissipation fin group (53).

5. An inverter as described in claim 4, characterized in that, The cavity wall of the air passage (12) is provided with a first wall (120) that is opposite to the second heat dissipation fin group (52) and the third heat dissipation fin group (53) in a third direction. The tooth height of the third heat dissipation fin (531) is higher than that of the second heat dissipation fin group (52); The air guide cover (70) is placed on the third heat dissipation fin group (53) and is provided with a first wind deflector (71) that is connected to the first wall (120).

6. An inverter as described in claim 5, characterized in that, The first air guide plate (80) extends obliquely from the first wall (120) toward the second heat dissipation fin group (52) to direct the airflow to the second heat dissipation fin group (52).

7. An inverter as described in claim 6, characterized in that, The first air guide plate (80) is suspended above the second heat dissipation fin group (52), and its end is spaced from the third heat dissipation fin group (53) along the first direction.

8. An inverter as described in claim 4, characterized in that, A number of second inductors (60) arranged along the second direction are disposed in the air passage cavity (12) downstream of the third heat dissipation fin assembly (53); at least one second heat exchanger's second heat exchange section (42) is located on at least one side of each second inductor (60) along the second direction; the two ends of the third heat dissipation fin assembly (53) along the first direction form an air passage gap (01) between the cavity wall of the air passage cavity (12) and the two ends of the third heat dissipation fin assembly (53) along the first direction.

9. An inverter as described in claim 8, characterized in that, The projection of the second heat exchange section (42) and the air passage (01) along the first direction at least partially overlaps.

10. An inverter as described in claim 8, characterized in that, The second air inlet (122) is also opposite to the first inductor (20); the first inductor (20) has a plurality of first toothed plates (21) arranged at intervals along the third direction and perpendicular to the third direction on both sides along the second direction, and a plurality of second toothed plates (22) arranged at intervals along the second direction and perpendicular to the second direction on the side of the first inductor (20) facing the second air inlet (122); the second inductor (60) has a plurality of third toothed plates (61) arranged at intervals along the second direction and perpendicular to the second direction on the side of the second inductor (60) facing the third heat dissipation fin group (53), and a plurality of fourth toothed plates (62) arranged at intervals along the third direction and perpendicular to the third direction on both sides along the second direction.

Images