JPS6239523B2 - - Google Patents
Info
- Publication number
- JPS6239523B2 JPS6239523B2 JP1342380A JP1342380A JPS6239523B2 JP S6239523 B2 JPS6239523 B2 JP S6239523B2 JP 1342380 A JP1342380 A JP 1342380A JP 1342380 A JP1342380 A JP 1342380A JP S6239523 B2 JPS6239523 B2 JP S6239523B2
- Authority
- JP
- Japan
- Prior art keywords
- tank
- panel
- oil
- fin
- overhang
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
- 238000005452 bending Methods 0.000 claims description 18
- 229910000831 Steel Inorganic materials 0.000 claims description 10
- 239000010959 steel Substances 0.000 claims description 10
- 230000009977 dual effect Effects 0.000 claims 1
- 238000003466 welding Methods 0.000 description 30
- 230000017525 heat dissipation Effects 0.000 description 15
- 238000010586 diagram Methods 0.000 description 10
- 238000004519 manufacturing process Methods 0.000 description 9
- 238000013461 design Methods 0.000 description 5
- 239000000463 material Substances 0.000 description 5
- 238000000034 method Methods 0.000 description 4
- 230000003014 reinforcing effect Effects 0.000 description 4
- 230000001133 acceleration Effects 0.000 description 3
- 230000002787 reinforcement Effects 0.000 description 3
- 238000009751 slip forming Methods 0.000 description 3
- 230000015572 biosynthetic process Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 230000005484 gravity Effects 0.000 description 2
- 230000005855 radiation Effects 0.000 description 2
- 238000004891 communication Methods 0.000 description 1
- 238000007796 conventional method Methods 0.000 description 1
- 238000005520 cutting process Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 230000006866 deterioration Effects 0.000 description 1
- 238000009413 insulation Methods 0.000 description 1
- 238000005304 joining Methods 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 238000000465 moulding Methods 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 238000010008 shearing Methods 0.000 description 1
- 238000012546 transfer Methods 0.000 description 1
- 239000013585 weight reducing agent Substances 0.000 description 1
Classifications
-
- H—ELECTRICITY
- H01—ELECTRIC ELEMENTS
- H01F—MAGNETS; INDUCTANCES; TRANSFORMERS; SELECTION OF MATERIALS FOR THEIR MAGNETIC PROPERTIES
- H01F27/00—Details of transformers or inductances, in general
- H01F27/02—Casings
- H01F27/025—Constructional details relating to cooling
Landscapes
- Engineering & Computer Science (AREA)
- Power Engineering (AREA)
- Transformer Cooling (AREA)
Description
【発明の詳細な説明】
本発明は、変圧器等の油入電気機器用タンクに
かかり、特にシート状の薄鋼板を波形に折曲げて
ひれ状の張出部を形成し、その張出部によつて張
出油室を形成した放熱板兼側板を有する油入電気
機器用タンクに関する。Detailed Description of the Invention The present invention relates to a tank for oil-filled electrical equipment such as a transformer, and in particular, a sheet-like thin steel plate is bent into a corrugated shape to form a fin-like overhang. The present invention relates to an oil-filled electrical equipment tank having a heat sink and side plate with an overhanging oil chamber formed therein.
一般に、油入電気機器では機器内部で発生した
熱を絶縁油を媒体としてタンク表面から放熱する
ようにしている。このため油入電気機器のタンク
は放熱効果を高め得るような構造とされている。
すなわち、側板にフインを取付ける方法、側板に
上下連通の放熱パイプを取付ける方法、２枚のパ
ネル板の外周をシーム溶接してパネルエレメント
を構成し上下のヘツダーをタンクに取付ける方
法、および側板を波形に折曲げて放熱面積を拡大
する方法等があり、特に近年は後者の２つが多く
採用されている。 Generally, in oil-filled electrical equipment, heat generated inside the equipment is radiated from the tank surface using insulating oil as a medium. For this reason, the tanks of oil-filled electrical equipment are designed to enhance the heat dissipation effect.
In other words, there are two methods: attaching fins to the side panels, attaching heat dissipation pipes that communicate with the top and bottom to the side panels, forming a panel element by seam welding the outer periphery of two panel plates and attaching the upper and lower headers to the tank, and corrugating the side panels. There are methods to expand the heat dissipation area by bending the tube, and the latter two methods have been particularly popular in recent years.
ところで、前記２枚のパネル板の外周をシーム
溶接して形成したパネルエレメントを必要放熱量
に応じてそれらを複数個溶接により連結固着させ
て構成したいわゆるパネル形放熱器（図示せず）
は、その製造に多くの工程を要し、その製作に長
時間を要する等の不都合がある。すなわち、その
製作には、フープ材の所定寸法の切断、プレス成
形、パネル板中溝スポツト溶接、パネル板外周シ
ーム溶接、パネルエレメントひねり矯正、パネル
エレメント間組合せ溶接、ヘツダー挿入、ヘツダ
ーとパネルとの溶接、パネル外部補強溶接、パネ
ル放熱器のタンクへの取付等の多数の工程を必要
とする。 By the way, a so-called panel type heat radiator (not shown) is constructed by welding and fixing a plurality of panel elements formed by seam welding the outer peripheries of the two panel plates according to the required amount of heat radiation.
However, there are disadvantages in that the manufacturing process requires many steps and takes a long time. In other words, the manufacturing process involves cutting the hoop material to predetermined dimensions, press forming, spot welding in the grooves in the panel plates, welding the outer circumference seam of the panel plates, correcting the twist of the panel elements, welding combinations between panel elements, inserting the header, and welding the header and the panel. , requires numerous steps such as welding the panel's external reinforcement and attaching the panel radiator to the tank.
また、パネル板外周シーム溶接やパネルエレメ
ント間のステツチ溶接等溶接全長は非常に長くな
り、かつ溶接雰囲気として必ずしも十分でない抵
抗溶接部分が殆どであり、溶接欠陥による油洩れ
の可能性があり信頼性にも欠ける等の問題点もあ
る。 In addition, the total length of welds such as panel panel outer circumference seam welding and stitch welding between panel elements is very long, and most of the welding parts are resistance welded where the welding atmosphere is not necessarily sufficient, and there is a possibility of oil leakage due to welding defects, reducing reliability. There are also problems such as lack of.
さらに、放熱器は諭送時に加わる上下、前後、
左右方向の振動加速度の繰返し疲労に対し耐え得
る強度を有しなければならないが、パネル放熱器
は油を含む放熱器重量、加熱器重心部に加わる振
動加速度、およびタンク側壁部から放熱器重心位
置までの距離の相乗積のモーメントが、放熱器上
下部に設けたヘツダーの根元すなわちタンク側壁
取付部に生じ、またパネルエレメント連結溶接部
にも曲げねじり、せん断等の合成力が作用する。
したがつて、多量の熱を発生する機器において
は、パネルエレメントの枚数が多くかつ長さが大
なるものが必要となるため、前述部位に非常に大
きな応力が発生して諭送時に破損に至ることがあ
る。そこで、これらの発生応力を許容値以下にお
さえるため、パネル放熱器の外側にてタンクと連
結する補強を必要とし、さらにそのための製作工
数が増大する。 Furthermore, the radiator is used for the upper and lower, front and back
Panel radiators must have the strength to withstand repeated fatigue caused by vibration acceleration in the left and right directions, but the panel radiator must have the strength to withstand the weight of the radiator including oil, the vibration acceleration applied to the center of gravity of the heater, and the position of the center of gravity of the radiator from the side wall of the tank. A moment due to the multiplicative product of the distances is generated at the base of the header installed at the top and bottom of the radiator, that is, at the tank side wall attachment part, and a resultant force such as bending, twisting, shearing, etc. also acts on the panel element connection weld.
Therefore, for equipment that generates a large amount of heat, a large number of panel elements and a large length are required, which creates extremely large stress in the above-mentioned parts, leading to damage during transport. Sometimes. Therefore, in order to suppress these generated stresses to below a permissible value, it is necessary to provide reinforcement to connect the panel radiator to the tank on the outside, which further increases the number of manufacturing steps.
なお、この種放熱器はプレスによりパネル板を
成形しており、プレス型の関係でパネル幅、長
さ、パネル間ピツチの種類が限定され、このため
機器毎に最適のパネル幅、長さ、パネル間ピツチ
を選定することができず、設計自由度に制約をう
け最適設計ができない等の欠点をも有している。 Note that this type of heatsink is formed into a panel board by pressing, and the type of panel width, length, and pitch between panels is limited due to the press type. Therefore, the optimal panel width, length, and It also has the disadvantage that it is not possible to select the pitch between panels, and the degree of freedom in design is restricted, making it impossible to perform an optimal design.
一方、側板を波形に折曲げて放熱面積を拡大す
る方法には、第１図に示すような波形放熱板が使
用される。すなわち、第２図に断面図で示すよう
に、薄いシート状の鋼板１を波形に屈曲せしめ一
定間隔毎にひれ状突出部１ａを形成し、そのひれ
状突出部１ａの先端部を複数個の補強片２によつ
て互いに連結するとともに、上記突出部の上下両
端縁を、第３図のようにそれぞれ圧接し、例えば
MAG溶接などで融着させ一個の放熱板３とする
ものである。しかして、この放熱板を使つて油入
電気機器のタンクを構成する場合には、第４図に
示すように、上記放熱板３の上下両端縁をそれぞ
れタンクの上部側板４および下部側板兼底板５に
溶接等により固着することによつてタンクの側壁
が構成されている。 On the other hand, in a method of expanding the heat dissipation area by bending the side plates into a corrugated shape, a corrugated heat dissipation plate as shown in FIG. 1 is used. That is, as shown in the cross-sectional view in FIG. 2, a thin sheet-like steel plate 1 is bent into a corrugated shape to form fin-like protrusions 1a at regular intervals, and the tips of the fin-like protrusions 1a are bent into a plurality of wavy shapes. They are connected to each other by reinforcing pieces 2, and the upper and lower edges of the protrusion are pressed together as shown in FIG. 3, for example.
They are fused together by MAG welding or the like to form a single heat sink 3. When this heat sink is used to construct a tank for oil-filled electrical equipment, as shown in FIG. The side wall of the tank is constituted by fixing it to 5 by welding or the like.
この場合、開放形油入電気機器においては、タ
ンクに加わる内圧として油頭があるため、このタ
ンク内圧に対して上記放熱板のひれ状張出部にお
ける壁面の応力および変形量が許容量以下となる
ことが要求される。 In this case, in open-type oil-filled electrical equipment, there is an oil head as the internal pressure applied to the tank, so the stress and deformation of the wall surface at the fin-like extensions of the heat sink are below the allowable amount for this tank internal pressure. It is required to become.
また、絶縁油の劣化を防止するため密封形のタ
ンクとする場合には、油頭の他の中身の温度上昇
に伴なう絶縁油の膨張とガス室内の温度上昇によ
つてガス室の圧力上昇が起り、これにより張出部
の一部に加わる圧力がその降伏応力を超えると上
記張出部に残留歪が発生する。また弾性限度内で
あつても常時加わる圧力によつて上記張出部に変
形が生じてタンクの内容積が増加し、そのためタ
ンク内に必要油面を保たせるためその容積増加に
応じて予め絶縁油を増加する必要があり、さらに
張出部の変形により隣接するひれ状突出部の対向
する側板間の距離が小さくなり、側板から大気へ
の対流熱伝達率が低下し放熱量の減少をきたすこ
とがある。また、機器の容量が大きくなれば当然
放熱面積を増加させなければならず、そのため張
出油室の張出量を大きくしなければならない。 In addition, if a sealed tank is used to prevent deterioration of the insulating oil, the pressure in the gas chamber will increase due to the expansion of the insulating oil due to the rise in temperature of other contents of the oil head and the rise in temperature in the gas chamber. When this rise occurs and the pressure exerted on a portion of the overhang exceeds its yield stress, residual strain occurs in the overhang. In addition, even if the elasticity is within the limit, the pressure constantly applied causes deformation of the above-mentioned overhang, increasing the internal volume of the tank. Therefore, in order to maintain the necessary oil level in the tank, insulation is required in advance to accommodate the increase in volume. It is necessary to increase the amount of oil, and furthermore, due to the deformation of the overhang, the distance between the opposing side plates of adjacent fin-like protrusions becomes smaller, reducing the convective heat transfer coefficient from the side plates to the atmosphere and reducing the amount of heat dissipated. Sometimes. Furthermore, as the capacity of the device increases, the heat dissipation area must naturally be increased, and therefore the amount of overhang of the overhanging oil chamber must be increased.
ところが、上記張出部の応力は、その張出量す
なわち波の深さの自乗に比例し、板厚の自乗に反
比例して発生し、また変形量は波の深さの４乗に
比例し板厚の３乗に反比例して増減するので、張
出部の応力、変形量をそれぞれ許容値以下に押え
るには張出量の大きさに応じて板厚を厚くする必
要があり、また板厚が大きくなれば当然材料費お
よび製品重量が増大する不都合がある。 However, the stress in the overhang is proportional to the amount of overhang, that is, the square of the wave depth, and is inversely proportional to the square of the plate thickness, and the amount of deformation is proportional to the fourth power of the wave depth. It increases or decreases in inverse proportion to the cube of the plate thickness, so in order to keep the stress and deformation in the overhang below the respective allowable values, it is necessary to increase the plate thickness according to the size of the overhang. As the thickness increases, the material cost and product weight naturally increase.
さらに、第４図の如くタンクの四辺の側壁に波
形状放熱板を構成させた構造では、フロアスペー
スの面で四隅にデツドスペースを生じるだけでな
く、ひれ状張出部を放熱効率の点より適切なピツ
チで設ける必要上、タンクサイズに応じて張出油
室総個数に制限があり、より大きな放熱量を必要
とする場合には、張出油室の張出量にも当然製造
上制限があるので、このタンク構造は採用できな
い等の問題がある。 Furthermore, in the structure in which corrugated heat sinks are formed on the four side walls of the tank as shown in Figure 4, not only does it create dead space at the four corners in terms of floor space, but the fin-like overhangs are also designed to improve heat dissipation efficiency. Due to the necessity of providing them at a suitable pitch, there is a limit to the total number of overhanging oil chambers depending on the tank size, and if a larger amount of heat dissipation is required, there is of course a manufacturing limit to the amount of overhanging oil chambers. Therefore, there are problems such as not being able to adopt this tank structure.
本発明はこのような点に鑑み、ひれ状張出部の
板厚を厚くすることなく、機械的強度が大きく放
熱面積を自由に選択することができ、小形軽量で
かつ経済的な油入電気機器タンクを提供すること
を目的とする。 In view of these points, the present invention has been developed to provide a compact, lightweight, and economical oil-filled electrical appliance that has high mechanical strength and can freely select the heat dissipation area without increasing the plate thickness of the fin-like protruding parts. The purpose is to provide equipment tanks.
以下、第５図乃至第２４図を参照して本発明の
実施例について説明する。 Embodiments of the present invention will be described below with reference to FIGS. 5 to 24.
第５図および第６図はタンクの長辺側の側壁を
形成するパネル状波形放熱板１０の平断面図およ
び側面図であつて、第７図に示すように、シート
状の薄鋼板１１を波形に屈曲せしめることによつ
て一定間隔毎にひれ状張出部１１ａを連続的に複
数個形成した２つの張出部群１２，１３を構成す
るとともに、両張出部群１２，１３の中央部に１
個のひれ状張出部１４を構成し、その両張出部群
１２，１３と上記ひれ状張出部１４との間に平板
状部１５，１５を設けるとともに両端部に平板状
部１６，１６を設け、上記平板状部１５，１５を
直角状に折曲げることにより、両張出部群１２，
１３のひれ状張出部１１ａの先端が互いに対向す
るように形成され、さらに両端の平板状部１６，
１６も字状に折曲して隣接する他のパネル状波
形放熱板との溶着を行なうためのフランジ部１６
ａが形成されている。なお、図中符号１７は各張
出部群毎のひれ状張出部１１ａの先端部を互いに
連結する補強片である。 5 and 6 are a plan sectional view and a side view of a panel-shaped corrugated heat sink 10 forming the long side wall of the tank, and as shown in FIG. 7, a sheet-like thin steel plate 11 is Two overhang groups 12 and 13 are formed in which a plurality of fin-like overhangs 11a are continuously formed at regular intervals by bending in a waveform, and the center of both overhang groups 12 and 13 is formed. Part 1
The fin-like overhanging portions 14 are constructed, and flat plate-like portions 15, 15 are provided between both of the overhanging portion groups 12, 13 and the fin-like overhanging portion 14, and flat plate-like portions 16, 16 are provided at both ends. 16, and by bending the flat plate portions 15, 15 at right angles, both projecting portion groups 12,
The tips of the 13 fin-like protruding parts 11a are formed so as to face each other, and the flat plate-like parts 16 at both ends,
16 A flange portion 16 which is bent into a letter shape and is welded to another adjacent panel-shaped corrugated heat sink.
a is formed. In addition, the reference numeral 17 in the figure is a reinforcing piece that connects the tips of the fin-like projections 11a of each group of projections to each other.
一方、第８図および第９図は、タンクの短辺側
の側壁を形成するパネル状波形放熱板２０の平断
面図および側面図であつて、第１０図に示すよう
に、シート状の薄鋼板１１を波形に屈曲せしめる
ことによつて一定間隔毎にひれ状張出部１１ａを
連続的に複数個形成した２つの張出部群２１，２
２を構成し、その両張出部群２１，２２間に所定
長さの平板状部２３を構成するとともに、両端に
もそれぞれ短かい平板状部２４，２４を設け、上
記中央の平板状部２３を第８図のようにほゞ直角
に折曲し、張出部群２１と張出部群２２のひれ状
張出部１１ａの軸線方向が互いに直角方向に向く
ように形成し、さらに両端部の平板状部２４，２
４にフランジ部２４ａをそれぞれ形成することに
よつてパネル状波形放熱板２０が形成されてい
る。 On the other hand, FIGS. 8 and 9 are a plan sectional view and a side view of the panel-shaped corrugated heat sink 20 forming the side wall on the short side of the tank, and as shown in FIG. Two overhang groups 21, 2 in which a plurality of fin-like overhangs 11a are continuously formed at regular intervals by bending the steel plate 11 in a waveform.
2, and a flat plate portion 23 of a predetermined length is formed between both projecting portion groups 21 and 22, and short flat portions 24 and 24 are provided at both ends, respectively, and the central flat portion is 23 is bent at a substantially right angle as shown in FIG. The flat plate portion 24, 2 of the
A panel-shaped corrugated heat sink 20 is formed by forming a flange portion 24a on each of the flange portions 24a.
しかして、この場合上述のように形成されたパ
ネル状波形放熱板２０を２個隣接して配設し、一
方の張出部群２２のひれ状張出部１１ａの基部を
互いに所定間隔をおいて対向せしめ、対応するフ
ランジ部２４ａ同志を溶着することによつて、一
つのタンク短辺側側壁が形成されている。 In this case, two panel-shaped corrugated heat sinks 20 formed as described above are arranged adjacently, and the bases of the fin-like projections 11a of one of the projection group 22 are spaced apart from each other by a predetermined distance. One short side side wall of the tank is formed by welding the corresponding flange portions 24a facing each other.
なお、上記実施例においては２つの張出部群１
２と１３のそれぞれの張出部の数は同一として形
成し、またこれらの張出部群１２と１３の張出部
深さD1，D2は同一寸法として図示しているけれ
ども、異なる張出部数、異なる張出部深さで構成
してもよい。 In addition, in the above embodiment, two overhang group 1
Although the number of protruding parts 2 and 13 is the same, and the protruding part depths D 1 and D 2 of these protruding part groups 12 and 13 are shown as having the same dimensions, different protruding parts are formed. The number of protrusions and the depth of the protrusions may be different.
そこで、第１１図は上記パネル状波形放熱板１
０，２０によつて形成されたタンク側壁を示す平
面図であつて、それぞれ２個のパネル状波形放熱
板１０をその張出部の基端が互いに所定間隔だけ
離間するように隣接して配設し、両者のフランジ
部１６ａ同志を互いに溶着することによつてタン
クの長辺側の２側壁を構成するとともに、その２
側壁の両端部間に前述のようにして構成された短
辺側の側壁を配設し、そのフランジ部２４ａと他
方のパネル状波形放熱板１０のフランジ部１６ａ
とをそれぞれ溶着することによつてタンク側壁が
構成される。しかして、上述のようにして構成さ
れたタンク側壁の上下両端部に、第１２図および
第１３図に示すように上部側板２５および下部側
板兼底板２６を装着するとともに、互いに対向す
る各張出部１１ａ間に形成される連通路２７の上
下部に蓋板２８が溶接により固着され、一個のタ
ンクが構成される。 Therefore, FIG. 11 shows the panel-shaped corrugated heat sink 1.
0 and 20, in which two panel-shaped corrugated heat sinks 10 are arranged adjacently so that the base ends of their projecting portions are spaced apart from each other by a predetermined distance. By welding the flange portions 16a of both to each other, two side walls on the long sides of the tank are constructed.
The side wall on the short side configured as described above is disposed between both ends of the side wall, and the flange portion 24a of the side wall and the flange portion 16a of the other panel-shaped corrugated heat sink 10 are connected to each other.
The tank side wall is constructed by welding these together. As shown in FIGS. 12 and 13, an upper side plate 25 and a lower side plate/bottom plate 26 are attached to both upper and lower ends of the tank side wall constructed as described above, and each overhang facing each other is A lid plate 28 is fixed by welding to the upper and lower portions of the communication passage 27 formed between the portions 11a, thereby forming one tank.
なお、上記実施例においては第５図に示すよう
にひれ状張出部の二つの群が対向する面に設けら
れた放熱板を使用したものを示したが、第１４図
に示すように一枚の薄鋼板に四つの張出部群を形
成し、その折曲によつて第１５図に示すようなパ
ネル状波形放熱板１０が２個一体的に連接したよ
うな形状としてもよい。 In the above embodiment, as shown in FIG. 5, a heat dissipation plate in which two groups of fin-like protrusions are provided on opposing surfaces is used, but as shown in FIG. It is also possible to form a shape in which four groups of projecting parts are formed on a sheet of thin steel plate, and by bending the projecting parts, two panel-shaped corrugated heat sinks 10 as shown in FIG. 15 are integrally connected.
また、第１６図或は第１７図に示すように、パ
ネル状波形放熱板２０における張出部群２１と２
２間の屈曲部を多角形状に折曲したり彎曲状に折
曲することによつて、例えば第１８図に示すよう
なタンクを構成することができ、タンク隅部の絶
縁油の節約さらには重量の軽減を計ることもでき
る。 Further, as shown in FIG. 16 or 17, the projecting portion groups 21 and 2 of the panel-shaped corrugated heat sink 20 are
By bending the bent portion between the two into a polygonal shape or a curved shape, a tank as shown in FIG. You can also measure weight reduction.
第１９図はタンクの短辺側の側壁を形成するパ
ネル状波形放熱板の他の実施例を示す図であり、
シート状の薄い鋼板を波形に屈曲せしめることに
よつてほゞその全長にわたつて多数のひれ状張出
部１１ａが連続的に形成され、その両端部に長辺
側の側壁と接合するためのフランジ部３０ａが形
成されて、一つのパネル状波形放熱板３０が構成
されており、これと前記構成の長辺側側壁との組
合わせによつて第２０図に示すようなタンク側壁
を構成することもできる。 FIG. 19 is a diagram showing another embodiment of the panel-shaped corrugated heat sink forming the side wall on the short side of the tank,
By bending a sheet-like thin steel plate into a corrugated shape, a large number of fin-like protruding parts 11a are continuously formed over almost its entire length, and a plurality of fin-like protruding parts 11a are formed at both ends of the fin-like protruding parts 11a for joining with the long side walls. A flange portion 30a is formed to constitute one panel-shaped corrugated heat sink 30, and a tank side wall as shown in FIG. 20 is constituted by the combination of this and the long side side wall of the above structure. You can also do that.
さらに、第２１図はタンクの長辺側の側壁を形
成するパネル状波形放熱板の他の実施例を示す図
であり、第２２図に示すように、２つの張出部群
１２，１３との中間部に複数のひれ状張出部から
なる他の張出部群１４ａを形成し、中央の張出部
群１４ａと両側の張出部群１２，１３間の平板状
部１５を直角状に折曲げることにより、両張出部
群１２，１３のひれ状張出部１１ａの先端が互い
に対向するように形成され、一つのパネル状波形
放熱板４０が形成されている。 Furthermore, FIG. 21 is a diagram showing another embodiment of the panel-shaped corrugated heat sink forming the side wall on the long side of the tank, and as shown in FIG. Another projecting part group 14a consisting of a plurality of fin-like projecting parts is formed in the middle part of By bending it, the tips of the fin-like protruding parts 11a of both protruding part groups 12 and 13 are formed so as to face each other, and one panel-shaped corrugated heat sink 40 is formed.
しかして、これらのパネル状波形放熱板４０を
数個連接することによつてタンクの長辺側側壁を
構成することができ、前記短辺側の側壁と組合わ
せることによつて第２３図の如きタンク側壁を形
成することができる。 By connecting several of these panel-shaped corrugated heat sinks 40, the long side side wall of the tank can be constructed, and by combining with the short side side wall, the structure shown in FIG. The tank side wall can be formed as follows.
さらに、各放熱板間の溶接部は、第２４図ａ〜
ｆに示すような色々な形状にしてその溶接を行な
うこともできる。 Furthermore, the welded parts between each heat sink are as shown in Fig. 24a-
It is also possible to weld them into various shapes as shown in f.
本発明においては油入電気機器用タンクを上述
のように構成したので、パネル状波形放熱板自体
の製造工程が、フープ材の波形折曲げ、波状部両
端縁のスクイズ溶接、補強片溶接、波形状放熱板
の平板状部折曲げ、タンク側板組立溶接となり、
加熱器とタンクを含めて従来のタンクの半分以下
の工程で安価にしかも短時間で製作することがで
きる。 In the present invention, since the tank for oil-filled electrical equipment is configured as described above, the manufacturing process of the panel-shaped corrugated heat sink itself includes corrugated bending of the hoop material, squeeze welding of both edges of the corrugated part, reinforcing piece welding, and corrugation. Bending the flat plate part of the shaped heat sink, assembling and welding the tank side plate,
It can be manufactured inexpensively and in a short time, with less than half the steps required for conventional tanks, including the heater and tank.
また、パネル加熱器に比し溶接部全長は約1/4
と大幅に減少し、溶接個所に対する信頼性が増
し、さらにシールドガスを用いた溶接雰囲気の良
好なMAG溶接等で固着できるので、シーム溶
接、ステツチ溶接等の抵抗溶接に比し一層溶接の
信頼性が向上する。 Also, the total length of the welded part is approximately 1/4 of that of a panel heater.
The reliability of the welding area is increased, and it can be fixed by MAG welding in a good welding atmosphere using shielding gas, making the welding more reliable than resistance welding such as seam welding and stitch welding. will improve.
なお、輸送時における上下、前後、左右方向の
振動加速度に対する疲労度においても、このパネ
ル状波形放熱器は連続した板を折曲することによ
つてパネル放熱板兼タンク側壁を構成しているの
で、パネル相互間およびタンク側壁に対する連結
面積、断面形数、断面二次モーメントは従来のパ
ネル形放熱器に比し、非常に大きくなり、従つて
垂直、水平方向振動加速度に対し、タンク側壁連
結部の最大モーメント発生部位および放熱器各部
位に対する曲げ、ねじり、せん断等の合成力作用
による発生応力は激減し大幅な機械的強度アツプ
による品質の向上も計れ、かつ多くの発生熱量を
有する機器でパネル枚数が増加しても特別にタン
クに対して補強する必要もなく、その分一層製作
工数の低減を計ることができる。さらに、特定の
サイズ専用のプレス型を必要とせず、パネル長さ
およびパネル間ピツチを機器毎に最適のものに選
択することができ、設計自由度を大幅に向上する
ことができるという大きな利点をも有する。 In addition, this panel-shaped corrugated heatsink has a panel heatsink that also functions as a tank side wall by bending a continuous plate, so that it can withstand fatigue due to vibration acceleration in the vertical, longitudinal, and horizontal directions during transportation. , the connection area, cross-sectional shape, and moment of inertia between panels and to the tank side wall are much larger than those of conventional panel radiators. The stress generated by the combined forces such as bending, torsion, and shear on the maximum moment generation area and each area of the radiator is drastically reduced, and the quality can be improved by significantly increasing the mechanical strength. Even if the number of plates increases, there is no need to specially reinforce the tank, and the number of manufacturing steps can be further reduced accordingly. Furthermore, there is no need for a press mold dedicated to a specific size, and the panel length and pitch between panels can be optimally selected for each device, greatly increasing the degree of design freedom. It also has
また、本発明においては、第１１図に示した平
面図のように、タンク四隅にも自由にひれ状張出
部を形成することができ、一定熱量においては、
機器外形寸法の縮少化すなわちフロアースペース
の減少を計ることができる。 In addition, in the present invention, as shown in the plan view shown in FIG.
It is possible to reduce the external dimensions of the equipment, that is, to reduce the floor space.
シート状の薄鋼板を波形に折曲げ連続的に張出
油室を形成するタンク構造の適用範囲について
は、従来の波形タンクでは機器の発熱量に応じ、
その発熱量が大となれば張出量を大きくして放熱
面積を増すことを行なうが、この張出量すなわち
波の深さには波形成形や両端縁のスクイズ成形に
おいて製造設備の能力あるいは製品の加工精度等
当然ながら製造上の制限があり、また空気側の効
果的な放熱特性を得るために張出部ピツチも波の
深さに応じて制約でき、張出油室の数も同一タン
クサイズにおいては限られてくる。したがつて、
おのずから最大放熱量すなわち適用機器容量が限
定される。 Regarding the applicability of a tank structure in which a sheet-like thin steel plate is bent into a corrugated shape to form a continuous overhanging oil chamber, conventional corrugated tanks are
If the amount of heat generated is large, the heat dissipation area is increased by increasing the amount of overhang, but the amount of overhang, that is, the depth of the waves, depends on the capacity of the manufacturing equipment in the corrugation shape and the squeeze molding of both edges. Of course, there are manufacturing limitations such as machining accuracy, and in order to obtain effective heat dissipation characteristics on the air side, the pitch of the overhang can also be restricted depending on the depth of the waves, and the number of overhang oil chambers can also be reduced in the same tank. It is limited in size. Therefore,
Naturally, the maximum heat dissipation amount, that is, the applicable equipment capacity is limited.
しかも、開放油入電気機器においては油頭、ま
た密封形油入電気機器ではさらに中身の温度上昇
に伴なう絶縁油の膨張とガス室内温度上昇による
タンク内圧上昇が加わり、これらのタンク内圧に
対し応力、変形量とも許容値以下としなければな
らないが、このため波の深さが大きくなると当然
波の深さに応じて板厚を厚くしなければならな
い。 Moreover, in open oil-filled electrical equipment, the oil head, and in sealed oil-filled electrical equipment, the tank internal pressure increases due to the expansion of the insulating oil due to the temperature rise of the contents and the rise in gas chamber temperature. On the other hand, both the stress and the amount of deformation must be kept below permissible values, but for this reason, as the depth of the waves increases, it is natural that the plate thickness must be increased in accordance with the depth of the waves.
ところが、本発明においては、同一張出部群の
張出部数を増加させて波形パネルを構成すること
によつて、特に制限を受けることなく所要放熱面
積を確保することができる。 However, in the present invention, by increasing the number of protrusions in the same group of protrusions to form a corrugated panel, the required heat dissipation area can be secured without any particular restriction.
しかも、タンク内圧に応じて張出部の応力およ
び変形量が許容値以下となるように、タンク内圧
の大なるものについては波の深さを小さくして板
厚をあげることなく対応がとれ、従来のタンクに
比し材料費の低減、製品の軽量化を計ることがで
きる利点がある。すなわち、一般にタンクを構成
する板場の強度は、
変形量δ＝１２（１−ν２）αｑａ４／Ｅｈ３……(1
)
応 力σ＝６βｑａ２／ｈ２ ……(2)
で、表わされる。なお、ここで、
ｑ ：圧力
Ｅ ：ヤング率
ｈ ：板厚
ν ：ポアツソン比
ａ ：板場の巾
α，β：板場の長さと巾の比、および板場周辺
条件により定まる係数
したがつて、板場の変形量および応力を許容値
以下とするためには、(1)式および(2)式でａ，ｈの
値を決定することになる。 In addition, in order to keep the stress and deformation of the overhang part below the allowable value depending on the tank internal pressure, we can deal with large tank internal pressures by reducing the depth of the waves without increasing the plate thickness. Compared to conventional tanks, this has the advantage of reducing material costs and making the product lighter. That is, in general, the strength of the board that constitutes a tank is the amount of deformation δ=12(1-ν 2 ) αqa 4 /Eh 3 ...(1
) Stress σ=6βqa 2 /h 2 ...(2) It is expressed as follows. Here, q: Pressure E: Young's modulus h: Plate thickness ν: Poisson's ratio a: Width of the plate field α, β: Coefficients determined by the ratio of the length and width of the plate field and the surrounding conditions of the plate field. In order to keep the deformation and stress of the board field below the allowable values, the values of a and h are determined using equations (1) and (2).
ところで、本発明によるタンクの側壁は、一枚
の板を折曲げて形成した複数個のパネル状波形放
熱板によつて形成されており、板厚ｈに応じてひ
れ状張出部１１ａの高さa1を適切な値として選定
すると、１個のひれ状張出部１４がない場合には
平板状部の長さa3は強度上に問題があり、補強を
施こす必要がある。また逆に平板状部の長さa3に
応じて板厚ｈを選定すると、a1に対しては余裕が
あり過ぎる無駄な設計となり重量アツプともな
る。 By the way, the side wall of the tank according to the present invention is formed by a plurality of panel-shaped corrugated heat sinks formed by bending a single plate, and the height of the fin-like protruding portion 11a is adjusted according to the plate thickness h. If the length a 1 is selected as an appropriate value, the length a 3 of the flat plate-like portion has a problem in terms of strength when one fin-like overhang portion 14 is not provided, and it is necessary to provide reinforcement. On the other hand, if the plate thickness h is selected according to the length a3 of the flat plate portion, the design will be wasteful as it will have too much margin for a1 , resulting in an increase in weight.
ところが、本発明では、平板状部に少なくとも
１個のひれ状張出部が形成してあるため、ひれ状
張出部の両側の平板部の長さをほぼひれ状張出部
１１ａの高さと同じにすることができ、バランス
のとれた設計ができ、ひれ状張出部が補強条とな
り、単に放熱面積の増大ばかりでなく上記板場す
なわちタンク側壁の強度を大巾に増大することが
できる。 However, in the present invention, since at least one fin-like overhang is formed on the flat plate, the length of the flat plate on both sides of the fin-like overhang is approximately equal to the height of the fin-like overhang 11a. They can be made the same, a well-balanced design is possible, and the fin-like overhangs serve as reinforcing strips, which not only increases the heat dissipation area but also greatly increases the strength of the plate area, that is, the tank side wall. .
以上説明したように、本発明においては従来の
タンクに比しその製作工程を半分以下に大幅に削
減でき、安価にしかも短時間で製作することがで
き、また溶接品質の向上さらに輸送時の振動、衝
撃に対する機械的強度を大幅に増大することがで
きる。また、タンクの四辺に波形状放熱板を構成
させる従来の方法に比し、機器の小形化を計るこ
とができ放熱面積の増大が容易にでき、従来と同
一放熱量のタンクの場合には板厚の減少を行なう
ことができ、材料費の低減、製品の軽量化をも計
ることができる等の効果を奏する。 As explained above, in the present invention, compared to conventional tanks, the manufacturing process can be significantly reduced to more than half, the tank can be manufactured at low cost and in a short time, and it also improves welding quality and reduces vibration during transportation. , the mechanical strength against impact can be significantly increased. In addition, compared to the conventional method of configuring corrugated heat sinks on the four sides of the tank, it is possible to downsize the equipment and easily increase the heat radiation area. It is possible to reduce the thickness, which has the effect of reducing material costs and making the product lighter.
第１図は従来の波形状放熱板の概略斜視図、第
２図はその張出油室部の横断面図、第３図はその
縦断面図、第４図は上記波形状放熱板を使用した
油入電気機器タンクの斜視図、第５図は長辺側の
パネル状波形放熱板の平断面図、第６図は同上側
面図、第７図はその成形説明図、第８図は短辺側
のパネル状波形放熱板の平断面図、第９図は同上
側面図、第１０図はその成形説明図、第１１図は
パネル状波形放熱板によるタンク側壁組立壁構成
図、第１２図は本発明の油入電気機器タンクの平
面図、第１３図は第１２図の−線に沿う
断面図、第１４図は他の実施例におけるパネル状
波形放熱板の成形説明図、第１５図は同上パネル
状波形放熱板の平断面図、第１６図、第１７図、
第１９図はそれぞれパネル状波形放熱板の他の実
施例を示す平断面図、第１８図は、第２０図はそ
れぞれ本発明の他の実施例におけるタンク側壁組
立構成図、第２１図はパネル状波形放熱板のさら
に他の実施例を示す平断面図、第２２図は同上形
成説明図、第２３図はさらに他の実施例における
タンク側壁組立構成図、第２４図ａ〜ｆはそれぞ
れパネル状波形放熱板間の連結部の実施例を示す
図である。
１０，２０，３０，４０……パネル状波形放熱
板、１１ａ……ひれ状張出部、１２，１３，１４
ａ……張出部群、１５……平板状部、２５……上
部側板、２６……下部側板兼底板。
Fig. 1 is a schematic perspective view of a conventional corrugated heat sink, Fig. 2 is a cross-sectional view of its overhanging oil chamber, Fig. 3 is a vertical cross-section thereof, and Fig. 4 is a use of the above-mentioned corrugated heat sink. Fig. 5 is a plan cross-sectional view of the panel-shaped corrugated heat sink on the long side, Fig. 6 is a side view of the same, Fig. 7 is an explanatory diagram of its forming, and Fig. 8 is a short sectional view of the panel-shaped corrugated heat sink on the long side. 9 is a side view of the panel-shaped corrugated heat sink on the side, FIG. 10 is an explanatory diagram of its formation, FIG. 11 is a configuration diagram of the tank side wall assembled with the panel-shaped corrugated heat sink, and FIG. 12 is 13 is a plan view of an oil-filled electrical equipment tank of the present invention, FIG. 13 is a sectional view taken along the - line in FIG. 12, FIG. 14 is an explanatory diagram of forming a panel-shaped corrugated heat sink in another embodiment, and FIG. 15 are plan sectional views of the same panel-shaped corrugated heat sink as above, FIGS. 16 and 17,
FIG. 19 is a plan sectional view showing another embodiment of the panel-shaped corrugated heat sink, FIG. 18 is a plan sectional view, FIG. 20 is a tank side wall assembly configuration diagram in another embodiment of the present invention, and FIG. 21 is a panel diagram. 22 is a plan sectional view showing still another embodiment of the corrugated heat sink, FIG. 22 is an explanatory diagram of the formation of the same as above, FIG. 23 is a tank side wall assembly configuration diagram in still another embodiment, and FIGS. 24 a to 24 are panels, respectively. It is a figure which shows the Example of the connection part between shaped corrugated heat sinks. 10, 20, 30, 40...Panel-shaped corrugated heat sink, 11a...Fin-shaped overhang, 12, 13, 14
a... Projection group, 15... Flat plate-shaped part, 25... Upper side plate, 26... Lower side plate/bottom plate.
Claims (1)
よつてひれ状張出部を形成し、そのひれ状張出部
によつて張出油室を構成した放熱器兼側板を有す
る油入電気機器用タンクにおいて、シート状の薄
鋼板に、複数個のひれ状張出部を有する少なくと
も２個の張出部群とその張出部群間に平板状部を
介して少なくとも１個のひれ状張出部とを形成
し、上記少なくとも１個のひれ状張出部の左右の
張出部群における張出油室の先端が互いに対向す
るように上記平板状部を折曲してパネル状波形放
熱板を構成し、この複数個のパネル状波形放熱板
によつてタンク側壁を形成したことを特徴とす
る、油入電気機器用タンク。 ２ 張出部群間の平板状部を折曲げることによつ
て互いに張出部群の張出油室の先端が対向するよ
うに形成された複数のパネル状波形放熱板によつ
て、タンクの長辺側側壁を構成したことを特徴と
する、特許請求の範囲第１項記載の油入電気機器
用タンク。 ３ タンクの短辺側側壁は、長辺側側壁を構成す
るパネル状波形放熱板の先端間に延びる波形放熱
板によつて構成されていることを特徴とする、特
許請求の範囲第２項記載の油入電気機器用タン
ク。 ４ シート状の薄鋼板に複数個のひれ状張出部を
有する２個の張出部群を形成し、その張出部群間
の平板状部をほぼ直角に折曲したパネル状波形放
熱板によつて、タンクの隅角部側壁を構成したこ
とを特徴とする、特許請求の範囲第２項記載の油
入電気機器用タンク。[Claims] 1. A radiator in which a fin-like overhang is formed by bending a sheet-like thin steel plate into a wave shape, and an overhang oil chamber is formed by the fin-like overhang. In a tank for oil-filled electrical equipment having dual side plates, a sheet-like thin steel plate is provided with at least two groups of overhangs each having a plurality of fin-like overhangs, and a flat plate-like section interposed between the groups of overhangs. forming at least one fin-like projecting part, and the flat plate-like part is arranged such that the tips of the projecting oil chambers in the left and right projecting part groups of the at least one fin-like projecting part face each other. 1. A tank for oil-filled electrical equipment, characterized in that a panel-shaped corrugated heat sink is formed by bending, and a side wall of the tank is formed by the plurality of panel-shaped corrugated heat sinks. 2. The tank is heated by a plurality of panel-shaped corrugated heat sinks formed by bending the flat plate-shaped parts between the overhang groups so that the tips of the overhanging oil chambers of the overhang group are facing each other. The tank for oil-filled electrical equipment according to claim 1, characterized in that the tank has long side walls. 3. Claim 2, characterized in that the short-side side wall of the tank is constituted by a corrugated heat sink extending between the tips of the panel-shaped corrugated heat sink forming the long-side side wall. Tank for oil-filled electrical equipment. 4 A panel-shaped corrugated heat sink in which two groups of overhangs each having a plurality of fin-like overhangs are formed on a sheet-like thin steel plate, and the flat plate-like portion between the groups of overhangs is bent at a substantially right angle. 3. The tank for oil-filled electrical equipment according to claim 2, wherein the corner side wall of the tank is constructed by:
Priority Applications (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1342380A JPS56110211A (en) | 1980-02-06 | 1980-02-06 | Tank for oil-filled electric equipment |
| GB8102267A GB2068647B (en) | 1980-01-30 | 1981-01-26 | Tanks for oil-cooled electrical induction apparatus |
| SE8100589A SE452520B (en) | 1980-01-30 | 1981-01-29 | TANK FOR CONTAINING AN OIL COOLED, ELECTROMAGNETIC INDUCTION DEVICE |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1342380A JPS56110211A (en) | 1980-02-06 | 1980-02-06 | Tank for oil-filled electric equipment |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS56110211A JPS56110211A (en) | 1981-09-01 |
| JPS6239523B2 true JPS6239523B2 (en) | 1987-08-24 |
Family
ID=11832716
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1342380A Granted JPS56110211A (en) | 1980-01-30 | 1980-02-06 | Tank for oil-filled electric equipment |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS56110211A (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4535841A (en) * | 1983-10-24 | 1985-08-20 | International Business Machines Corporation | High power chip cooling device and method of manufacturing same |
-
1980
- 1980-02-06 JP JP1342380A patent/JPS56110211A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS56110211A (en) | 1981-09-01 |
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