A machine room transformer with a finned heat dissipation structure

Abstract

The application discloses a machine room transformer with an inserted sheet type heat dissipation structure and belongs to the technical field of dry-type transformer heat dissipation. The machine room transformer comprises an iron core, an inner winding, an outer winding and an annular mounting space formed between the inner winding and the outer winding, a gas guide structure is arranged in the mounting space, and the gas guide structure is connected with a gas distribution base. The gas guide structure comprises an outer cylinder, an inner cylinder and an inner supporting piece, a plurality of groups of spiral inserted sheets are arranged on the outer periphery of the upper end of the outer cylinder, a plurality of inserted plate II are arranged on the inner periphery of the inner cylinder, the inner supporting piece is arranged between the outer cylinder and the inner cylinder and is provided with an avoiding channel, and the side walls of the inner cylinder and the outer cylinder are provided with flow channels corresponding to the avoiding channel. The application utilizes the negative pressure entraining effect of the rotating airflow to realize the reinforced cooling of the inner winding, solves the problem that the inner winding is wrapped by the outer winding and thus is difficult to dissipate heat, and has the advantages of strong heat dissipation pertinence, good self-adaptive adjustment capability and compact structure.

Description

Technical Field

[0001] This invention relates to the field of transformer heat dissipation technology, and in particular to a computer room transformer with a plug-in heat dissipation structure. Background Technology

[0002] Dry-type transformers are widely used in places with high safety requirements, such as computer rooms, hospitals, and high-rise buildings, due to their advantages such as being oil-free, fireproof, and easy to maintain. Dry-type transformers are usually cooled by air convection or forced air cooling, with their core and windings directly exposed to the air, relying on airflow to carry away the heat generated during operation.

[0003] In the actual operation of dry-type transformers, the inner winding is enclosed by the outer winding, resulting in a long heat dissipation path and high thermal resistance. Consequently, the operating temperature of the inner winding is typically significantly higher than that of the outer winding. In existing technologies, a common heat dissipation method is to symmetrically arrange cooling fans at the bottom of the windings, blowing cooling airflow into the annular cavity between the inner and outer windings, attempting to cool both simultaneously. However, this symmetrical heat dissipation design has inherent flaws: it applies essentially the same cooling intensity to both the inner and outer windings, failing to provide differentiated cooling for the higher temperature of the inner winding. The result is insufficient heat dissipation and a higher temperature in the inner winding, while excessive heat dissipation and wasted cooling resources occur in the outer winding, leading to overall low heat dissipation efficiency.

[0004] To address the aforementioned issue of uneven internal and external heat distribution, several improvements have been implemented in existing technologies. For example, Chinese patent application CN121583710A discloses a "multi-winding dry-type traction transformer," which incorporates a heat dissipation cylinder within an annular cavity between the inner and outer windings. This heat dissipation cylinder features external air ducts and a greater number of first and second internal air ducts. The increased number of internal air ducts expands the heat exchange area on the inner winding side, thereby achieving stronger heat dissipation for the inner winding under the same airflow conditions. This solution improves the heat dissipation balance between the inner and outer windings to some extent. However, the airflow distribution in this solution relies entirely on the duct geometry and cannot be actively adjusted based on changes in the inner winding temperature. When the load decreases or the ambient temperature changes, the airflow ratio between the inner and outer air ducts remains constant, making it difficult to achieve on-demand heat dissipation. Furthermore, the structure, which is in close contact with the inner and outer windings, significantly reduces the effective exposed area for direct heat radiation to the surrounding air. Heat at the contact points can only be transferred to adjacent heat dissipation components via thermal conduction, rather than being released directly to the external space via radiation like an exposed surface. This change in the heat dissipation path significantly weakens the winding's ability to dissipate heat outward through radiation, thus adversely affecting the overall heat dissipation effect.

[0005] Chinese patent application CN110428957A discloses a "dual-cooling epoxy resin cast dry-type transformer," which employs a cooling method that primarily uses circulating water cooling supplemented by air cooling, attempting to improve cooling uniformity. However, this solution has a complex structure, the water cooling system carries a risk of leakage, and it fails to propose effective measures to address the core heat dissipation challenge of the inner winding being encased.

[0006] In summary, existing dry-type transformer heat dissipation technologies face the following pressing technical challenges: Firstly, the inner winding is wrapped by the outer winding, making it difficult for heat to dissipate, and existing symmetrical heat dissipation methods cannot provide targeted and enhanced cooling for the inner winding. Secondly, the airflow distribution of existing asymmetric heat dissipation solutions relies on a fixed air duct structure, which cannot be actively adjusted according to temperature changes, resulting in poor adaptability to changing operating conditions. Third, there is a lack of a heat dissipation method that can effectively improve the airflow exhaust speed of the internal air duct by utilizing the characteristics of airflow within a limited space without significantly increasing structural complexity.

[0007] Therefore, it is necessary to provide a computer room transformer with a plug-in heat dissipation structure that can overcome the above-mentioned defects. Summary of the Invention

[0008] The purpose of this invention is to solve at least one of the above-mentioned problems by providing a computer room transformer with a plug-in heat dissipation structure.

[0009] To achieve the above objectives, the technical solution of the present invention is as follows: a computer room transformer with a plug-in heat dissipation structure, comprising an iron core, an inner winding and an outer winding coaxially sleeved outside the iron core, an annular mounting space being formed between the outer circumferential surface of the inner winding and the inner circumferential surface of the outer winding, an air guiding structure being installed in each mounting space, and an air guiding structure being connected to an air distribution base, wherein the air guiding structure comprises: The outer cylinder has multiple sets of spiral inserts on its upper outer circumferential surface, and the spiral inserts are guided and slidably engaged with the inner circumferential surface of the outer winding. The inner cylinder is coaxially arranged inside the outer cylinder. Along its axial direction, multiple insert plates are provided on the inner circumferential surface. The insert plates slide in a guide-sliding fit with the outer circumferential surface of the inner winding. An inner support member is disposed between the outer cylinder and the inner cylinder and corresponds to the safety area of ​​the spiral insert. Multiple clearance channels are provided at intervals along the circumferential direction on the side wall. Both the inner and outer cylinders have flow channels on their side walls that correspond one-to-one with the clearance channels; The gas distribution base can supply airflow to the space between the outer cylinder and the outer winding. When the airflow flows through the spiral insert, it is guided to form a rotating airflow, thereby forming a negative pressure zone inside the rotating airflow, so that negative pressure is formed at both ends of the flow channel.

[0010] The computer room transformer with a plug-in heat dissipation structure disclosed in this invention has the following advantages compared with the prior art: the axial airflow between the outer cylinder and the outer winding is guided into a rotating airflow by the spiral plug-in. The centrifugal effect of the rotating airflow is used to form a negative pressure zone inside the rotating airflow. The negative pressure zone forms negative pressure at both ends of the flow channel through the avoidance channel and the flow channel, thereby forming a suction effect inside the inner cylinder, increasing the discharge speed of the airflow channel inside the inner cylinder, and realizing enhanced heat dissipation on the inner winding side. Attached Figure Description

[0011] Figure 1 This is a schematic diagram of the structure of a computer room transformer with a plug-in heat dissipation structure according to the present invention. Figure 1 .

[0012] Figure 2 This is a schematic diagram of the structure of a computer room transformer with a plug-in heat dissipation structure according to the present invention. Figure 2 .

[0013] Figure 3 This is a side view of a computer room transformer with a plug-in heat dissipation structure according to the present invention.

[0014] Figure 4 This is a schematic diagram of the main structure of a computer room transformer with a plug-in heat dissipation structure according to the present invention.

[0015] Figure 5 for Figure 4 The diagram shows a cross-sectional view of the present invention at point AA.

[0016] Figure 6 for Figure 5 The diagram shows a partially enlarged structural schematic of the present invention at point B.

[0017] Figure 7 for Figure 5 The diagram shows a partially enlarged structural schematic of the present invention at point C.

[0018] Figure 8 This is a partial structural diagram of the present invention.

[0019] Figure 9 This is a schematic diagram of the outer cylinder in this invention.

[0020] Figure 10 This is a schematic diagram of the mating structure of the inner support, inner cylinder, and flow guide sleeve in this invention.

[0021] Figure 11 This is an exploded structural diagram of the inner support and inner cylinder in this invention.

[0022] Figure 12 This is a schematic diagram of the combined structure of the flow guide sleeve in this invention.

[0023] Figure 13 This is a top view of the gas distribution base in this invention.

[0024] Figure 14 This is a three-dimensional structural diagram of the gas distribution base in this invention.

[0025] Figure 15 for Figure 13 The diagram shown is a cross-sectional view of the gas distribution base in this invention.

[0026] Figure 16 for Figure 15 The diagram shows a partially enlarged structural schematic of the present invention at point E.

[0027] Figure 17 for Figure 15 The diagram shows a partially enlarged structural schematic of the present invention at point F.

[0028] In the diagram: 10. Upper clamp; 11. Lower clamp; 2. Outer winding; 20. Inner winding; 3. Air pump one; 30. Pipe one; 4. Air pump two; 40. Pipe two; 5. Air distribution base; 50. Air distribution pipe assembly one; 500. Inlet pipe one; 501. Connecting pipe one; 5000. Pipe port one; 5010. Ventilation component one; 5011. Valve; 5012. Elastic component one; 51. Air distribution pipe assembly two; 510. Inlet pipe two; 5100. Pipe port two; 511. Connecting pipe two; 511a. Through hole; 5110. Ventilation component two; 52. Partition plate; 520. Air chamber one; 5 21. Air Chamber Two; 53. Valve Cylinder; 530. Valve Hole; 54. Pull Rod; 540. Limiting Component; 55. Elastic Component Two; 60. Outer Cylinder; 600. Spiral Insert; 601. Flow Channel One; 602. Overlap Component One; 603. Positioning Boss; 61. Inner Support Component; 610. Clearance Channel; 611. Extension Body; 612. Overlap Part; 62. Inner Cylinder; 620. Flow Channel Two; 621. Insert Plate Two; 622. Overlap Component Two; 623. Annular Component; 63. Guide Sleeve; 630. Outlet; 631. Baffle; 90. Jet Airflow; 91. Follow-up Airflow. Detailed Implementation

[0029] The present invention will now be described in further detail with reference to the accompanying drawings. The drawings are simplified schematic diagrams, illustrating only the basic structure of the invention in a schematic manner, and therefore only show the components relevant to the invention.

[0030] Example 1

[0031] This embodiment provides a computer room transformer with a plug-in heat dissipation structure, see reference. Figures 1 to 6The device includes an iron core, an upper clamp 10, a lower clamp 11, an inner winding 20 and an outer winding 2 coaxially sleeved outside the iron core, and an annular installation space formed between the outer circumferential surface of the inner winding 20 and the inner circumferential surface of the outer winding 2. Each installation space contains an air guiding structure, and each air guiding structure is connected to an air distribution base 5. The air guiding structure includes an outer cylinder 60, an inner cylinder 62, and an inner support. The upper end of the outer cylinder 60 has multiple sets of spiral inserts 600 on its outer circumferential surface, which slide and guide with the inner circumferential surface of the outer winding 2. The inner cylinder 62 is coaxially disposed inside the outer cylinder 60, and along its axial direction, the inner circumferential surface of the inner cylinder 62 has multiple insert plates 621, which slide and guide with the outer circumferential surface of the inner winding 20. The inner support is positioned between the outer cylinder 60 and the inner cylinder 62 and corresponds to the safety area of ​​the spiral insert 600. Along the circumferential direction, the side wall of the inner support is provided with multiple clearance channels 610 at intervals. The side walls of both the inner cylinder 62 and the outer cylinder 60 are provided with flow channels that correspond one-to-one with the clearance channels 610.

[0032] refer to Figure 5 , Figure 7 , Figure 13 , Figure 14 The air distribution base 5 has an annular structure with an annular air chamber open at the top. It is divided into two separate air chambers by an annular partition 52. During installation, the base is mounted around the iron core, and its upper end abuts against the lower end faces of the inner winding 20 and the outer winding 2 respectively to form a sealed fit. In practical application, an air pump pumps air into the two separate air chambers, thereby supplying airflow to the space between the outer cylinder 60 and the outer winding 2. The airflow is guided to form a rotating airflow as it flows through the spiral insert 600. (Reference) Figure 6 Because the rotating airflow has a centrifugal effect, a negative pressure zone is formed inside the rotating airflow (i.e., the area that fits against the outer circumference of the outer cylinder 60). In the area where the spiral insert 600 is provided, the outer cylinder 60 and the inner cylinder 62 are respectively provided with flow channel 1 601 and flow channel 2 620. An inner support member 61 is provided between the outer cylinder 60 and the inner cylinder 62. The inner support member 61 supports and fits the inner cylinder 62 and the outer cylinder 60, and a clearance area is provided to avoid flow channel 1 601 and flow channel 2 620. Thus, a flow channel is formed by connecting flow channel 1 601 and flow channel 2 620 through the clearance area. One end of the flow channel is connected to the negative pressure zone, and the other end is connected to the area inside the inner cylinder 62. The negative pressure zone is connected to the internal space of the inner cylinder 62 through the clearance channel 610 and the flow channel, so that negative pressure is formed at both ends of the flow channel.

[0033] In actual operation, the formation of negative pressure at both ends of the flow channel increases the pressure difference between the two ends of the inner cylinder 62, which facilitates the airflow inside the inner cylinder 62 and draws the airflow outside the inner cylinder 62 outward. The airflow inside the inner cylinder 62 is drawn out under the action of pressure difference, while most of the airflow inside the inner cylinder 62 is discharged from the top of the inner cylinder 62. This increases the discharge speed of the airflow channel inside the inner cylinder 62. Under the condition that the air supply pressure inside the inner cylinder 62 is constant, this scheme is beneficial to increasing the airflow speed inside the inner cylinder 62.

[0034] It should be noted that a Chinese patent application with publication number CN121583710A discloses a multi-winding dry-type traction transformer. This transformer features a heat dissipation cylinder within an annular cavity between the inner winding 20 and the outer winding 2. The heat dissipation cylinder has external air ducts and a greater number of internal air ducts, utilizing the increased number of internal air ducts to expand the heat exchange area on the inner winding 20 side. However, the airflow distribution in this design relies entirely on the geometry of the air ducts and cannot be actively adjusted according to temperature changes in the inner winding 20. Furthermore, this design uses thermally conductive silicone pads between the inner side of the heat dissipation cylinder and the outer circumference of the inner winding 20, and similarly between the outer side of the heat dissipation cylinder and the inner circumference of the outer winding 2. This significantly reduces the effective exposure area of ​​the inner winding 20 and outer winding 2, which would normally directly radiate heat to the surrounding air. Heat at the contact points can only be transferred to adjacent heat dissipation components via thermal conduction, rather than being released directly to the external space via radiation like on an exposed surface. The ability of the windings to dissipate heat through radiation is thus significantly weakened.

[0035] In this embodiment, the spiral insert 600 of the outer cylinder 60 is guided and slidably fitted with the inner circumferential surface of the outer winding 2 rather than being fully fitted, and the insert plate 621 of the inner cylinder 62 is guided and slidably fitted with the outer circumferential surface of the inner winding 20 rather than being fully fitted. The inner winding 20 and the outer winding 2 still retain a considerable area of ​​exposed surface, which can directly dissipate heat to the surrounding space by thermal radiation, avoiding the problem of weakened radiative heat dissipation capacity caused by full fitting in the prior art. At the same time, during the guided and slidably fitted process, the spiral insert 600 and the insert plate 621 can also form a small airflow channel between the winding and the cylinder, allowing some cooling airflow to flow directly over the winding surface, further enhancing the heat dissipation effect.

[0036] Furthermore, in this embodiment, the inner support is disposed between the outer cylinder 60 and the inner cylinder 62 and corresponds to the safety area of ​​the spiral blade 600. The inner support has multiple clearance channels 610 spaced circumferentially, and the side walls of both the inner cylinder 62 and the outer cylinder 60 have flow channels corresponding to the clearance channels 610. The clearance channels 610 and flow channels allow the negative pressure zone formed by the rotating airflow to communicate with the internal space of the inner cylinder 62, thereby achieving the transmission of negative pressure. The inner support also supports the outer cylinder 60 and the inner cylinder 62, ensuring the stability of the annular gap between them and preventing cylinder deformation due to airflow impact or vibration. The correspondence between the inner support and the safety area of ​​the spiral blade 600 means that the axial position of the inner support corresponds to the area where the spiral blade 600 experiences maximum stress or vibration under airflow. The inner support reinforces this area, improving structural stability.

[0037] Furthermore, in this application, by forming a rotating airflow on the outside of the outer cylinder 60, the uniformity of the airflow on the outside of the outer cylinder 60 can be improved. At the same time, the rotating airflow forms an annular negative pressure zone. The flow channels 601 and 620 on the outer cylinder 60 and the inner cylinder 62 are evenly spaced around the axis. Thus, the negative pressure can be used to draw the airflow inside the inner cylinder 62 outward evenly, thereby improving the uniformity of the airflow distribution inside the inner cylinder 62 and improving the uniformity of heat dissipation.

[0038] Example 2

[0039] Furthermore, based on Embodiment 1, in this embodiment, the inner support is elastically configured and has a filling cavity filled with a thermally expanding flow medium.

[0040] refer to Figure 6 , Figure 10 , Figure 11 In this embodiment, the inner support is made of an elastic material, such as high-temperature resistant silicone rubber or elastic polyurethane. The inner support has a filling cavity filled with a thermally expanding fluid. When the transformer operates, it generates heat, causing the inner and outer winding temperatures to rise. The inner support is heated, and the thermally expanding fluid in the filling cavity expands, increasing the volume of the inner support. This provides greater support to the inner cylinder 62 and outer cylinder 60, resulting in a tighter fit between the insert plate 621 of the inner cylinder 62 and the outer circumferential surface of the inner winding 20, and between the spiral insert 600 of the outer cylinder 60 and the inner circumferential surface of the outer winding 20. This reduces airflow leakage and improves the utilization rate of cooling airflow. When the temperature of the inner winding 20 decreases, the thermally expanding fluid contracts, reducing the volume of the inner support, thus facilitating disassembly and assembly between the inner cylinder 62 and the outer cylinder 60.

[0041] Furthermore, refer to Figure 6With the above configuration, when air is pumped into the air distribution base 5 by the air pump and the airflow passes through the outer side of the outer cylinder 60 and the inner side of the inner cylinder 62, the airflow passing through the inner side of the inner cylinder 62 can flow through the clearance channel 610 of the inner support member under the negative pressure of the rotating airflow. The airflow flowing through the inner cylinder 62 has a high temperature, which can provide a better heating effect for the inner support member, thereby allowing it to expand fully and ensuring the support and fit between the inner support member and the outer cylinder 60 and the inner cylinder 62. This further ensures the sealing of the fit between the inner support member and the outer cylinder 60 and the inner cylinder 62, making it less likely for the clearance channel 610 to leak air.

[0042] refer to Figure 5 , Figure 9 The spiral inserts 600 on the outer circumference of the outer cylinder 60 are set at the upper end of the outer cylinder 60. This arrangement can form a pressure balance zone at the lower end of the outer cylinder 60. When the airflow enters the annular area between the outer cylinder 60 and the outer winding 2 from bottom to top, it first fills the balance zone. After the air pressure is balanced, it flows through multiple spiral inserts 600, which is conducive to the uniform distribution of airflow.

[0043] As a specific implementation method, refer to Figure 3 , Figure 5 , Figure 8 , Figure 12 In this embodiment, the iron core includes multiple cores arranged at intervals. The top of the outer cylinder 60 is provided with a flow guide sleeve 63, and the annular area formed between the outer cylinder 60 and the outer iron core is connected to the flow guide sleeve. The flow guide sleeve has two horizontal outlets 630 facing away from it, and the orientation of the outlets 630 is perpendicular to the direction of the iron core spacing.

[0044] It is understandable that, due to the presence of an upper clamp 10 and an upper iron core at the top of the inner cylinder 62 and the inner winding 20, the airflow between the inner cylinder 62 and the inner winding 20 is prone to stagnation or backflow when flowing upwards to the top region due to the structural obstruction of the upper clamp 10 and the upper iron core. This affects the airflow discharge between the inner cylinder 62 and the inner winding 20. To address this issue, in this embodiment, the iron core comprises multiple spaced-apart cores, forming a gap region between adjacent cores. A guide sleeve is provided at the top of the outer cylinder 60, connecting the annular region between the outer cylinder 60 and the outer iron core to the outside. Two horizontal outlets 630 are provided on the opposite side of the guide sleeve, with the outlets 630 oriented perpendicular to the direction of the core spacing. The airflow, after heat exchange in the space between the outer cylinder 60 and the outer winding 2, is discharged through the outlets 630 of the guide sleeve. Since the outlets 630 are oriented perpendicular to the direction of the core spacing, the discharged hot airflow will not directly blow onto the gap region between adjacent cores, preventing the hot airflow from accumulating in the core gap region and affecting the heat dissipation of the core. Simultaneously, the airflow guided by the guide sleeve forms a horizontal jet airflow 90. This directional flow of air drives the gas above and below to flow outwards, creating a follow-up airflow 91 above. This generates negative pressure near the outlet 630 of the guide sleeve. This negative pressure continuously draws in gas from the top area, giving the previously stagnant hot airflow the power to continue being discharged outwards. Therefore, the heat dissipation channel between the inner cylinder 62 and the inner winding 20 no longer relies solely on the positive pressure of the airflow delivered by the bottom fan. Instead, a negative pressure suction effect is superimposed on the outlet side, forming a "push forward, suck back" composite flow state. This significantly reduces the flow resistance at the outlet of the inner air duct and improves the airflow efficiency.

[0045] It should be noted that in the prior art, Chinese patent application CN121583710A, a first row of heat shields is provided at the top of the first and second inner air ducts, and a second row of heat shields is provided at the top of the outer air duct. Heat dissipation vents are opened on the surfaces surrounding both the first and second rows of heat shields. The height of the first row of heat shields is greater than that of the second row, and the heat dissipation vents on the first row are located above the heat dissipation vents on the second row. This solution uses heat shields to block the air ducts, aiming to reduce dust ingress. Its design does not promote airflow exhaust, nor does it utilize directional airflow to create negative pressure. In this solution, the orientation of the heat dissipation vents is not specifically defined, and the exhausted hot airflow may blow towards the gap between adjacent iron cores, causing hot airflow to accumulate in the iron core gap area. In this embodiment, the outlet 630 of the guide sleeve is oriented perpendicular to the iron core gap direction, preventing the exhausted hot airflow from directly blowing towards the iron core gap area, thus avoiding the accumulation of hot airflow in the iron core gap area and facilitating iron core heat dissipation.

[0046] Example 3

[0047] refer to Figure 5 , Figure 7In this embodiment, the gas distribution base 5 includes a vertically arranged annular partition 52. The lower end of one of the outer cylinder 60 and the inner cylinder 62 is provided with an overlap member 602 that overlaps and cooperates with the upper end surface of the partition 52, and the other upper end is provided with an overlap member 622. The overlap member 622 overlaps the upper end of the cylinder provided with the overlap member 602.

[0048] In this embodiment, reference Figure 14 The gas distribution base 5 includes a vertically arranged annular partition 52, which divides the internal space of the gas distribution base 5 into two air chambers, an inner and an outer chamber. One of the outer cylinder 60 and the inner cylinder 62 has a first overlapping member 602 at its lower end, which overlaps with the upper surface of the partition 52; the other has a second overlapping member 622 at its upper end. The second overlapping member 622 overlaps with the upper end of the cylinder with the first overlapping member 602. Through the cooperation of the first overlapping member 602 and the second overlapping member 622, a sealed connection is achieved between the outer cylinder 60 and the inner cylinder 62 and the gas distribution base 5. The first overlapping member 602 overlaps with the upper surface of the partition 52, forming a first seal; the second overlapping member 622 overlaps with the upper end of the cylinder with the first overlapping member 602, forming a second seal. The two seals cooperate to effectively prevent airflow leakage from the lower ends of the outer cylinder 60 and the inner cylinder 62 within the gas distribution base 5, and this structure is simple and reliable.

[0049] In practical applications, an overlap member 602 can be provided at the lower end of the inner cylinder 62. The overlap member 602 can overlap with the upper end face of the partition 52 to provide upward support for the inner cylinder 62. At the same time, an overlap member 622 is provided at the upper end of the outer cylinder 60 to overlap with the upper end of the inner cylinder 62. The inner cylinder 62 provides support for the outer cylinder 60. While providing support, the annular overlap member 602 and overlap member 622 can also form a sealing fit.

[0050] In a preferred embodiment, both the first lap joint 602 and the second lap joint 622 are annular lap joint plates. The guide sleeve is provided with a flange that is detachably and fixedly connected to the second lap joint 622 and two baffles 631 that abut against the upper end of the outer winding 2.

[0051] In this embodiment, both overlapping member 602 and overlapping member 622 are annular overlapping plates, which have a simple structure and are easy to process. (Reference) Figure 12 The guide sleeve is provided with a flange that is detachably and fixedly connected to the second overlapping component 622. The connection between the guide sleeve and the second overlapping component 622 is achieved through the flange, which facilitates assembly, disassembly and maintenance. The guide sleeve is also provided with two baffles 631 that abut against the upper end of the outer winding 2. The two baffles 631 abut against the upper end of the outer winding 2, which play a role in positioning and supporting the guide sleeve. At the same time, after the lower end face of the baffles 631 abuts and seals against the upper end face of the outer winding 2, an internal space of the guide sleeve is formed between the two baffles 631 and the outer peripheral surface of the flange, and outlets 630 are formed at both ends of the baffles 631.

[0052] In a preferred embodiment, the second overlapping member 622 is connected to the inner cylinder 62, and the upper end of the inner cylinder 62 is provided with an extension section extending vertically upward from the second overlapping member 622.

[0053] In this embodiment, the second overlapping member 622 is connected to the inner cylinder 62, and the first overlapping member 602 is disposed on the inner circumferential surface of the lower end of the outer cylinder 60. With this arrangement, the flange of the guide sleeve is connected to the second overlapping member 622 at the upper end of the inner cylinder 62. At the same time, the upper end of the inner cylinder 62 also has a vertically upward extension section from the second overlapping member 622. The extension section makes the height of the upper end of the inner cylinder 62 higher than the position of the second overlapping member 622, and the airflow channel inside the inner cylinder 62 extends upward, which is beneficial for the airflow discharged through the inner cylinder 62 to be discharged upward under the action of negative pressure.

[0054] Further, refer to Figure 6 , Figure 7 , Figure 11 To further improve airtightness, in this embodiment, the lower end of the inner cylinder 62 is provided with an annular member 623, which is inserted into the inner side of the partition 52, and the outer circumferential surface of the annular member 623 is sealed to the inner circumferential surface of the partition 52.

[0055] In this embodiment, an annular member 623 is provided at the lower end of the inner cylinder 62. The annular member 623 is inserted into the inner side of the partition 52, and the outer circumferential surface of the annular member 623 is sealed to the inner circumferential surface of the partition 52. The sealing fit between the annular member 623 and the inner circumferential surface of the partition 52 forms a sealed connection between the inner cylinder 62 and the gas distribution base 5, preventing airflow in the gas distribution base 5 from leaking from the lower end of the inner cylinder 62. The annular member 623 is inserted into the inner side of the partition 52, which has a simple structure and is easy to assemble.

[0056] refer to Figures 9 to 11 Around its own axis, the inner circumferential surface of the outer cylinder 60 is provided with multiple positioning bosses 603 at intervals, and the lower end of the inner support member 61 is also integrally provided with multiple extensions 611, with the positioning bosses 603 being positioned between two adjacent extensions 611.

[0057] In this embodiment, the inner circumferential surface of the outer cylinder 60 is provided with a plurality of positioning bosses 603 at intervals, and the lower end of the inner support member 61 is integrally provided with a plurality of extensions 611. The positioning bosses 603 are positioned between adjacent extensions 611. Through the cooperation of the positioning bosses 603 and the extensions 611, the inner support member is circumferentially positioned within the outer cylinder 60, preventing the inner support member from rotating circumferentially under the action of airflow. At the same time, the positioning bosses 603 can also provide support after the overlapping portion 612 at the lower end of the inner support member overlaps, ensuring the stability of the inner support member's position within the outer cylinder 60 and providing axial positioning for the inner support member.

[0058] It should be noted that in the prior art, Chinese patent application CN121583710A, an external air duct and an internal air duct are provided inside the heat dissipation cylinder, and an annular groove is provided in the middle of the heat dissipation cylinder. A heat insulation sleeve is inserted into the annular groove. This heat insulation sleeve only serves the functions of heat insulation and spaced support. Since it does not have a clearance channel 610 to cooperate with the external and internal air ducts, it does not have the axial and circumferential positioning and cooperation effects. In this embodiment, the circumferential positioning of the inner support member is achieved by the cooperation of the positioning boss 603 and the extension body 611, preventing the inner support member from rotating circumferentially under the action of airflow, improving structural stability, and ensuring the positioning and cooperation effect of the clearance channel 610 with the first flow channel 601 and the second flow channel 620.

[0059] Furthermore, in this application, the inner support member 61 and the extension body 611 are integrally formed. The extension body 611 has a cavity that communicates with the interior of the inner support member 61. When the thermal expansion medium inside the inner support member expands, the extension body 611 can also expand, thereby providing all-round internal support for the inner cylinder 62 and the outer cylinder 60. When the inner support member 61 expands and supports internally, it can promote a slight inward contraction of the inner cylinder 62 and a slight outward expansion of the outer cylinder 60, so that the insert plate 621 of the inner cylinder 62 and the spiral insert 600 of the outer cylinder 60 can fully contact the inner winding 20 and the outer winding 2, which can effectively suppress the vibration of the inner and outer cylinders 60 caused by airflow. When the inner support member 61 contracts, the internal support disappears, which facilitates the disassembly and assembly of the inner cylinder 62 and the outer cylinder 60.

[0060] Secondly, since the external airflow flows from bottom to top through the gas distribution base 5, the airflow temperature in the lower section of the inner cylinder 62 and outer cylinder 60 is relatively low, while the temperature rises when the airflow flows through the inner cylinder 62 and outer cylinder 60 to the upper end. The main body of the inner support 61 is located at the upper end of the outer cylinder 60 and inner cylinder 62, and the first flow channel 601 and the second flow channel 620 are also located at the upper end. Therefore, the high-temperature gas can fully contact the inner support 61 and expand fully. The lower end of the inner cylinder 62 and outer cylinder 60 is supported by the extended extension body 611. The extension body 611 has a small heat exchange surface with intervals. Therefore, even if the temperature of the bottom airflow is low, it will not have a key impact on the thermal expansion of the inner support 61, ensuring the stability of the inner support 61 in operation.

[0061] Example 4

[0062] Furthermore, based on the above embodiments, referring to Figures 13 to 17 The air distribution base 5 includes two air chambers located on the inner and outer sides of the partition 52, and each air chamber is individually connected to an air pump.

[0063] In this embodiment, the two air chambers are air chamber one 520 and air chamber two 521. Air chamber one 520 is connected to pipe one 30, which is connected to air pump one 3. Air chamber two 521 is connected to pipe two 40, which is connected to air pump two 4. Air chamber one 520 is connected to the space between the outer cylinder 60 and the outer winding 2. Air chamber two 521 is connected to the space between the inner cylinder 62 and the inner winding 20.

[0064] The main purpose of setting up two air chambers and corresponding two sets of air pumps is not simply to increase the air supply, but to make targeted configurations based on the functional differences of the airflow inside and outside.

[0065] Air pump 3 supplies air to air chamber 520, which in turn supplies airflow to the space between outer cylinder 60 and outer winding 2. Its core function is to create sufficient gas velocity within this space. As the airflow passes through the multiple sets of spiral blades 600 on the outer circumference of the upper end of outer cylinder 60, it is guided to form a rotating airflow, thus creating a negative pressure zone inside the rotating airflow. This negative pressure zone is the power source for the suction effect of the airflow channel inside inner cylinder 62. Therefore, the air supply from air pump 3 needs to ensure that the airflow outside outer cylinder 60 has sufficient velocity and swirling intensity. If air pump 3 supplies insufficient air, the airflow velocity outside outer cylinder 60 is too low, the spiral blades 600 cannot form an effective rotating airflow, the negative pressure zone is insufficient, and the suction effect inside inner cylinder 62 weakens or even disappears.

[0066] Air pump 4 supplies air to air chamber 521, which in turn supplies airflow to the space between the inner cylinder 62 and the inner winding 20. Its core function is to provide sufficient cooling airflow to the inside of the inner cylinder 62. Because the inner winding 20 has high thermal resistance, its operating temperature is typically significantly higher than that of the outer winding 2. Therefore, the inside of the inner cylinder 62 requires a sufficient airflow to remove the heat generated by the inner winding 20. The air supply from air pump 4 must ensure sufficient airflow through the airflow channels inside the inner cylinder 62 to effectively remove the heat from the inner winding 20. If air pump 4 supplies insufficient air, even with a negative pressure zone creating a suction effect, the inside of the inner cylinder 62 will lack sufficient airflow medium to carry away the heat, resulting in limited cooling performance.

[0067] Therefore, the configuration of two air pumps ensures, on the one hand, the air supply of air pump 3, and ensures that a rotating airflow with sufficient velocity is formed on the outside of the outer cylinder 60 to generate a negative pressure zone that meets the suction requirements; on the other hand, the air supply of air pump 4 ensures that the inner side of the inner cylinder 62 receives sufficient heat dissipation airflow to meet the high heat dissipation requirements of the inner winding 20.

[0068] In this embodiment, the power configuration of air pump 3 is required to ensure that the airflow velocity outside the outer cylinder 60 reaches a threshold sufficient to form an effective rotating airflow. Experiments show that when the airflow velocity outside the outer cylinder 60 is below 5 m / s, the swirling intensity generated by the spiral insert 600 is insufficient, the static pressure value in the negative pressure zone is below -10 Pa, and the suction effect is weak. When the airflow velocity outside the outer cylinder 60 reaches 8 m / s to 15 m / s, the swirling intensity is significantly improved, and the static pressure value in the negative pressure zone can reach -30 Pa to -80 Pa, which can effectively suction the airflow inside the inner cylinder 62. The power configuration of air pump 4 is required to ensure that the airflow flow rate inside the inner cylinder 62 meets the heat dissipation requirements of the inner winding 20. The preferred airflow velocity inside the inner cylinder 62 is 3 m / s to 8 m / s. Within this range, the heat of the inner winding 20 can be fully carried away, while the gain of the negative pressure suction will not be offset by excessive frictional resistance due to excessive flow velocity.

[0069] It should be noted that in the existing technology, in the forced cooling mechanism scheme, multiple powerful fans jointly supply air to the cavity box, and the airflow inside the cavity box is then blown to the outer air duct and the inner air duct through the first air outlet and the second air outlet, respectively. Because multiple fans supply air together, all fans have the same function, making it impossible to differentiate configurations for the different functional requirements of the outer and inner air ducts, nor to achieve independent adjustment of the airflow speed in the outer air duct and the airflow rate in the inner air duct. In this embodiment, two independent air pumps supply airflow to air chamber 1 520 and air chamber 2 521, respectively. Air pump 1 3 focuses on creating a rotating airflow with sufficient velocity on the outside of the outer cylinder 60 to generate negative pressure suction, while air pump 2 4 focuses on fully supplying cooling airflow to the inside of the inner cylinder 62 to meet the high heat dissipation requirements of the inner winding 20. The two pumps, with their differentiated functions and coordinated cooperation, achieve true adaptive asymmetric cooling.

[0070] Further, based on Embodiment 4, in this embodiment, the air chamber 520 outside the partition 52 is connected to a gas distribution pipe assembly 50, which includes a connecting pipe 501 and a valve 5011. One end of the connecting pipe 501 is connected to the air chamber 520, and the other end faces the air chamber 520 and has a positioning surface. A vent 5010 is provided between the positioning surface and the air chamber 520, and a pipe opening 5000 is provided between the vent 5010 and the positioning surface. The pipe opening 5000 is connected to the air chamber 520 through a pipe. The valve 5011 is guided and disposed between the vent 5010 and the positioning surface, and its outer peripheral surface is guided and slidably engaged with the connecting pipe 501. An elastic element 5012 is provided between the valve 5011 and the vent 5010. The elastic element 5012 is a compression spring. Figure 16 In the initial state, the valve 5011 is pushed against the positioning surface 1, and the inlet pipe 500 connects the port 5000 and the air chamber 520.

[0071] The second air chamber 521 inside the partition 52 is connected to the second air distribution pipe assembly 51, which includes a connecting pipe 511, a valve cylinder 53, and an elastic element 55. The connecting pipe 511 is connected to the second air chamber 521. A through hole 511a is provided on the side wall of the area corresponding to the first air chamber 520. A vent element 5110 is provided on the side of the through hole 511a away from the second air chamber 521. A pipe opening 5100 is provided on the side wall of the vent element 5110 away from the second air chamber 521. The pipe opening 5100 is connected to the second air chamber 521 through the inlet pipe 510. The valve cylinder 53 is guided and positioned on the side of the vent element 5110 near the second air chamber 521. A valve hole 530 corresponding to the through hole 511a is provided on the outer side wall of the valve cylinder 53. The second elastic element 55 is located between the valve cylinder 53 and the second vent element 5110, providing elastic force for the valve cylinder 53 to move in the direction of the second vent element 5110. When the valve cylinder 53 abuts against the second vent element 5110, the valve hole 530 and the through hole 511a are staggered and not connected to each other. The valve cylinder 53 is connected to a pull rod 54. A limiting element 540 is set at the end of the pull rod 54 that passes through the second vent element 5110. The second elastic element 55 is a compression spring sleeved on the pull rod 54 and located between the limiting element 540 and the second vent element 5110. In the initial state, under the elastic force of the second elastic element 55, the valve cylinder 53 abuts against the second vent element 5110. At this time, the valve hole 530 and the through hole 511a are staggered, and the valve cylinder 53 blocks and seals the through hole 511a.

[0072] Through the above-described configuration, this embodiment has two heat dissipation modes to adapt to transformers under different operating conditions. At high power, both the inner and outer windings generate a large amount of heat. At this time, both air pump 3 and air pump 4 operate at preset power. When air pump 3 operates, the pumped airflow enters through connecting pipe 501, impacting and pushing valve 5011 to compress elastic element 5012, causing the airflow to flow through port 5000 and inlet pipe 500 into air chamber 520, creating a predetermined air pressure within air chamber 520. The gas in air chamber 520 flows outwards towards the outer cylinder 60. Simultaneously, air pump 4 pumps airflow into connecting pipe 511, thus creating air pressure within air chamber 520. Furthermore, the impact force of the airflow flowing into connecting pipe 511 is weakened by the venting element 5110, allowing valve cylinder 53 to maintain its position. Figure 17 In the initial state shown, air chamber 1 520 and air chamber 2 521 are not connected to each other, and the airflow pumped by air pump 2 4 enters the inner side of the inner cylinder 62.

[0073] When the transformer power is low, less heat is generated. At this time, air pump 3 is not working, and air pump 4 is working. Under the elastic force of elastic element 5012, the valve plate returns to its original position. Figure 16In the initial position shown, with the connecting pipe 1 501 closed, the airflow pumped by air pump 2 4 enters the connecting pipe 2 511 and first enters the air chamber 2 521, so that both the air chamber 2 521 and the connecting pipe 2 511 have a certain air pressure. At this time, the air chamber 1 520 is at atmospheric pressure, thus creating an air pressure difference on both sides of the valve cylinder 53. Under the action of the air pressure difference, the valve cylinder 53 is pushed to move and compress the elastic element 2 55 until the end of the valve cylinder 53 abuts against the side wall of the air chamber 1 520 and stops. At this time, the valve hole 530 on the valve cylinder 53 coincides with the through hole 511a on the connecting pipe 2 511, so that part of the airflow enters the air chamber 1 520 and supplies airflow to the outside of the outer cylinder 60. The air flow rate is less than the air flow rate pumped into the air chamber 2 521. Thus, air pump 1 3 pumps air into both air chambers at the same time, and the air flow rate through the inner cylinder 62 is greater than the air flow rate through the outside of the outer cylinder 60, which meets the differentiated heat dissipation requirements.

[0074] Obviously, the above embodiments are merely illustrative examples for clear explanation and are not intended to limit the implementation. Those skilled in the art will recognize that other variations or modifications can be made based on the above description. It is neither necessary nor possible to exhaustively list all possible implementations here. However, obvious variations or modifications derived therefrom are still within the scope of protection of this invention.

Claims

1. A computer room transformer with a plug-in heat dissipation structure, comprising an iron core, an inner winding and an outer winding coaxially sleeved outside the iron core, wherein an annular mounting space is formed between the outer circumferential surface of the inner winding and the inner circumferential surface of the outer winding, characterized in that, Each of the aforementioned installation spaces is equipped with an air guiding structure, and each air guiding structure is connected to an air distribution base. The air guiding structure includes: The outer cylinder has multiple sets of spiral inserts on its upper outer circumferential surface, and the spiral inserts are guided and slidably engaged with the inner circumferential surface of the outer winding. The inner cylinder is coaxially arranged inside the outer cylinder. Along its axial direction, multiple insert plates are provided on the inner circumferential surface. The insert plates slide in a guide-sliding fit with the outer circumferential surface of the inner winding. An inner support member is disposed between the outer cylinder and the inner cylinder and corresponds to the safety area of ​​the spiral insert. Multiple clearance channels are provided at intervals along the circumferential direction on the side wall. Both the inner and outer cylinders have flow channels on their side walls that correspond one-to-one with the clearance channels; The gas distribution base can supply airflow to the space between the outer cylinder and the outer winding. When the airflow flows through the spiral insert, it is guided to form a rotating airflow, thereby forming a negative pressure zone inside the rotating airflow, so that negative pressure is formed at both ends of the flow channel.

2. A computer room transformer with a plug-in heat dissipation structure according to claim 1, characterized in that, The inner support is elastically configured and has a filling cavity filled with a thermally expanding flow medium.

3. A computer room transformer with a plug-in heat dissipation structure according to claim 1, characterized in that, The iron core includes multiple cores arranged at intervals, and the top of the outer cylinder is provided with a flow guide sleeve. The annular area between the outer cylinder and the outer iron core is connected to the flow guide sleeve. The guide sleeve has two horizontal outlets facing away from each other, and the outlets are oriented perpendicular to the direction of the iron core.

4. A computer room transformer with a plug-in heat dissipation structure according to claim 3, characterized in that, The gas distribution base includes a vertically arranged annular partition. The lower end of one of the outer cylinder and the inner cylinder is provided with an overlapping member 1 that overlaps and cooperates with the upper surface of the partition. The upper end of the other cylinder is provided with an overlapping member 2. The overlapping member 2 overlaps with the upper end of the cylinder provided with the overlapping member 1.

5. A computer room transformer with a plug-in heat dissipation structure according to claim 3, characterized in that, Both the first and second overlapping components are annular overlapping plates. The guide sleeve is provided with a flange that is detachably and fixedly connected to the second overlapping component and two baffles that abut against the upper end of the outer winding.

6. A computer room transformer with a plug-in heat dissipation structure according to claim 4, characterized in that, The second overlapping member is connected to the inner cylinder, and the upper end of the inner cylinder is also provided with an extension section extending vertically upward from the second overlapping member.

7. A computer room transformer with a plug-in heat dissipation structure according to claim 5, characterized in that, The lower end of the inner cylinder is provided with an annular component, which is inserted into the inner side of the partition plate, and the outer circumferential surface of the annular component is sealed to the inner circumferential surface of the partition plate.

8. A computer room transformer with a plug-in heat dissipation structure according to claim 2, characterized in that, Around its own axis, the inner circumferential surface of the outer cylinder is provided with multiple positioning bosses at intervals, and the lower end of the inner support is also integrally provided with multiple extensions, with the positioning bosses positioned between two adjacent extensions.

9. A computer room transformer with a plug-in heat dissipation structure according to claim 2, characterized in that, The air distribution base includes two air chambers located on the inner and outer sides of the partition, and each air chamber is individually connected to an air pump.

10. A computer room transformer with a plug-in heat dissipation structure according to claim 9, characterized in that, The air chamber on the outside of the partition is connected to a gas distribution pipe assembly, which includes: The connecting pipe 1 has one end connected to the air chamber 1, and the other end facing the air chamber 1 has a positioning surface 1. A vent is provided between the positioning surface 1 and the air chamber 1. A pipe opening is provided between the vent and the positioning surface 1. The pipe opening 1 is connected to the air chamber 1 through a pipe. The valve component has a guide positioned between the venting component and the positioning surface, and its outer peripheral surface slides in a guide-sliding fit with the connecting pipe. The second air chamber inside the partition is connected to the second gas distribution pipe assembly, which includes: Connector pipe two is connected to air chamber two. A through hole is provided on the side wall of the area corresponding to air chamber one. A venting component two is provided on the side of the through hole away from air chamber two. A pipe opening two is provided on the side wall of the venting component two away from air chamber two. The pipe opening two is connected to air chamber two through a pipe. The valve cylinder is guided on the side of the second venting component near the second air chamber, and the outer wall is provided with a valve hole corresponding to the through hole; The second elastic element is located between the valve cylinder and the second vent element, providing elastic force for the valve cylinder to move in the direction of the second vent element. When the valve cylinder and the second vent element are in contact, the valve hole and the through hole are staggered and do not communicate with each other.

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