[go: up one dir, main page]

JP2006003011A - Top plate structure of a high-altitude air conditioner - Google Patents

Top plate structure of a high-altitude air conditioner Download PDF

Info

Publication number
JP2006003011A
JP2006003011A JP2004179871A JP2004179871A JP2006003011A JP 2006003011 A JP2006003011 A JP 2006003011A JP 2004179871 A JP2004179871 A JP 2004179871A JP 2004179871 A JP2004179871 A JP 2004179871A JP 2006003011 A JP2006003011 A JP 2006003011A
Authority
JP
Japan
Prior art keywords
top plate
fan
reinforcing ribs
heat exchanger
air conditioner
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.)
Pending
Application number
JP2004179871A
Other languages
Japanese (ja)
Inventor
Keiko Ryu
継紅 劉
Naoyuki Ota
直之 太田
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Daikin Industries Ltd
Original Assignee
Daikin Industries Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Daikin Industries Ltd filed Critical Daikin Industries Ltd
Priority to JP2004179871A priority Critical patent/JP2006003011A/en
Priority to CNB2005800170393A priority patent/CN100483034C/en
Priority to EP05751179.2A priority patent/EP1775518B1/en
Priority to PCT/JP2005/010961 priority patent/WO2005124238A1/en
Publication of JP2006003011A publication Critical patent/JP2006003011A/en
Pending legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/20—Casings or covers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/008—Indoor units, e.g. fan coil units with perfuming or deodorising means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0043—Indoor units, e.g. fan coil units characterised by mounting arrangements
    • F24F1/0047—Indoor units, e.g. fan coil units characterised by mounting arrangements mounted in the ceiling or at the ceiling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/02—Ducting arrangements
    • F24F13/06—Outlets for directing or distributing air into rooms or spaces, e.g. ceiling air diffuser
    • F24F2013/0616—Outlets that have intake openings

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Air-Conditioning Room Units, And Self-Contained Units In General (AREA)
  • Other Air-Conditioning Systems (AREA)
  • Air Filters, Heat-Exchange Apparatuses, And Housings Of Air-Conditioning Units (AREA)

Abstract

【課題】 ファン駆動時における天板の挙動を含めて、薄肉化して、なおかつ必要な剛性、強度、振動特性等を得ることができる高所設置型空気調和機の天板構造を提供することを目的とする。
【解決手段】 ファンおよびファンモータ、熱交換器、ドレインポンプ、スイッチボックス等を収納する本体ケーシングと、該本体ケーシングの天面にあって、上記ファンおよびファンモータ、熱交換器、ドレインポンプ、スイッチボックス等を吊設支持する天板とを備えてなる空気調和機において、上記天板の板厚を所定の厚さ以下に薄肉化し、同天板の上記ファンおよびファンモータが支持される略中央部から上記熱交換器が支持される半径方向外周部にかけて、複数本の補強リブを放射状に延設するとともに、それら各補強リブの間をフラットに形成し、該複数本の補強リブの本数および断面形状（絞り形状）、深さ、幅などを最適に調整、設定することにより、従来のように多数の副補強リブ等を設けることなく、剛性、強度、たわみ特性、振動特性等を必要なレベルに改善することができるようにした。
【選択図】 図２
PROBLEM TO BE SOLVED: To provide a top plate structure of an air conditioner installed at a high place, which can be thinned and include necessary rigidity, strength, vibration characteristics, etc., including the behavior of the top plate when a fan is driven. Objective.
A main body casing that houses a fan, a fan motor, a heat exchanger, a drain pump, a switch box, and the like, and a fan casing, a fan motor, a heat exchanger, a drain pump, and a switch on the top surface of the main body casing. An air conditioner comprising a top plate for hanging and supporting a box or the like, wherein the thickness of the top plate is reduced to a predetermined thickness or less so that the fan and fan motor of the same top plate are supported. A plurality of reinforcing ribs extending radially from the outer periphery to the radial outer periphery where the heat exchanger is supported, and between the reinforcing ribs are formed flat, and the number of the plurality of reinforcing ribs and By adjusting and setting the cross-sectional shape (drawer shape), depth, width, etc. optimally, rigidity, strength, and deflection can be achieved without providing many secondary reinforcing ribs, etc. The characteristics and vibration characteristics can be improved to the required level.
[Selection] Figure 2

Description

本願発明は、高所設置型空気調和機の天板構造に関するものである。   The present invention relates to a top plate structure of an altitude installation type air conditioner.

天井埋込型又は天井吊設型等の高所設置型の空気調和機（室内機ユニット）は、例えばカセット型の本体ケーシングの天面部に金属製の天板を備え、該天板に対して、熱交換器、ファンおよびファンモータ、ドレインポンプ、スイッチングボックスなどの重量物を吊設支持した上で、本体ケーシングを吊り下げボルト等で吊り下げて天井部内に埋設するか、又は天井部下面に吊設することにより接地されるようになっている。   An altitude installation type air conditioner (indoor unit) such as a ceiling-embedded type or a ceiling-suspended type includes, for example, a metal top plate on the top surface of a cassette-type main body casing, After suspending and supporting heavy objects such as heat exchangers, fans and fan motors, drain pumps, switching boxes, etc., suspend the main body casing with hanging bolts etc. and embed it in the ceiling or on the bottom of the ceiling It is designed to be grounded by hanging.

このような高所設置型空気調和機の中の天井埋込型空気調和機の一例を、図１３〜図１５に示す。   An example of the ceiling-embedded air conditioner in such an altitude installation type air conditioner is shown in FIGS.

この空気調和機は、同図１３〜図１５に示すように、天井Ｃに形成された開口部７の上方に空気調和機本体１を配置し、該空気調和機本体１に対して上記開口部７を覆う化粧パネル２を取り付けて構成されており、上記空気調和機本体１のカセット型の本体ケーシング３内には、略環状の熱交換器４と、該熱交換器４の中心部にあって吸込側を下向きとし、かつ空気吹出側を上記熱交換器４の側面方向としたファン（羽根車）５およびファンモータ９と、上記ファン５の吸込側に配置された合成樹脂製のベルマウス６が配設されている。   In this air conditioner, as shown in FIGS. 13 to 15, the air conditioner body 1 is disposed above the opening 7 formed in the ceiling C, and the opening is formed with respect to the air conditioner body 1. A decorative panel 2 covering 7 is attached. In the cassette-type main body casing 3 of the air conditioner main body 1, there is a substantially annular heat exchanger 4 and a central portion of the heat exchanger 4. The fan (impeller) 5 and the fan motor 9 with the suction side facing downward and the air blowing side facing the side of the heat exchanger 4, and a synthetic resin bell mouth arranged on the suction side of the fan 5 6 is disposed.

この場合、ファン５は例えばハブ５ａとシュラウド５ｃとの間に多数枚のブレード５ｂ，５ｂ・・・を備えた遠心ファンにより構成されている。   In this case, the fan 5 is constituted by a centrifugal fan provided with a plurality of blades 5b, 5b,... Between the hub 5a and the shroud 5c, for example.

なお、符号８は上記熱交換器４の下方に配置されたドレンパン、１０は上記熱交換器４の外周側に形成された空気吹出通路である。   In addition, the code | symbol 8 is the drain pan arrange | positioned under the said heat exchanger 4, 10 is the air blowing path formed in the outer peripheral side of the said heat exchanger 4. FIG.

上記カセット型の本体ケーシング３は、例えば略六角形形状とされており、断熱材からなる側壁３１と、該側壁３１の上部を覆う天板３２とからなっている。   The cassette-type main body casing 3 has, for example, a substantially hexagonal shape, and includes a side wall 31 made of a heat insulating material and a top plate 32 that covers the top of the side wall 31.

上記熱交換器４の両開放端には各々管板１１，１１が設けられ、これら各管板１１，１１間は、所定の仕切り板１２により連結されている。   Tube plates 11, 11 are provided at both open ends of the heat exchanger 4, and the tube plates 11, 11 are connected by a predetermined partition plate 12.

上記本体ケーシング３の天板３２、上記管板１１，１１、上記仕切り板１２および上記ベルマウス６の下面に取り付けられるスイッチボックス１３は、共に板金製品により構成されている。そして、上記天板３２と上記スイッチボックス１３は、例えば図１４に示すように、上記仕切り板１２の上下両端部に対してビス止めされている。   The top plate 32 of the main body casing 3, the tube plates 11, 11, the partition plate 12, and the switch box 13 attached to the lower surface of the bell mouth 6 are all made of sheet metal products. The top plate 32 and the switch box 13 are screwed to the upper and lower ends of the partition plate 12 as shown in FIG.

一方、上記ベルマウス６には、上記スイッチボックス１３を収納する凹部１４が形成されており、該凹部１４の天面１４ａには、上記仕切り板１２の下端部に形成されたスイッチボックス結合部１５が臨まされる開口１６が形成されている。   On the other hand, the bell mouth 6 is formed with a recess 14 for accommodating the switch box 13, and a switch box coupling portion 15 formed at the lower end of the partition plate 12 is formed on the top surface 14 a of the recess 14. Is formed.

また、上記仕切り板１２の上端には、その両端部に位置して上記天板３２への結合部となる取付片１７，１７が一体に突設されており、該取付片１７は、上記天板３２に対してビス１８により下方から固着される。   Further, at the upper end of the partition plate 12, mounting pieces 17, 17 that are located at both ends of the partition plate 12 and serve as coupling portions to the top plate 32 are integrally projected. The plate 32 is fixed from below with screws 18.

また、上記仕切り板１２の下端には、その両端部に位置して上記管板１１，１１の下端への結合部となる取付片１９，１９が一体に突設され、その中間部に位置して上記スイッチボックス１３への結合部となる取付片１５が溶接により固着されている。上記取付片１９は、上記管板１１に対してビス２０により下方から固着され、上記取付片１５は、上記仕切り板１２への結合部となるＬ字状の基部１５ａと、該基部１５ａの先端から下向きに一体に延設された取付部１５ｂとからなっており、該取付部１５ｂを上記開口１６から上記凹部１４内に臨ました状態でスイッチボックス１３の天面１３ａに対してビス２１により下方から固着されている。   Also, at the lower end of the partition plate 12, mounting pieces 19 and 19 that are located at both end portions thereof and serve as coupling portions to the lower ends of the tube plates 11 and 11 are integrally projected and positioned at the intermediate portion thereof. An attachment piece 15 which is a connecting portion to the switch box 13 is fixed by welding. The mounting piece 19 is fixed to the tube plate 11 with screws 20 from below, and the mounting piece 15 includes an L-shaped base portion 15a serving as a coupling portion to the partition plate 12, and a distal end of the base portion 15a. And a mounting portion 15b integrally extending downward from the opening 16 and facing the top surface 13a of the switch box 13 with screws 21 in a state where the mounting portion 15b faces the recess 14 from the opening 16. It is fixed from.

また、符号２２はドレンポンプ、２３はフロートスイッチ、２４はドレンポンプ２２が配置されるドレンポンプ収容部、２５はドレンポンプ収容部を仕切る仕切り板、２６は上記スイッチボックス１３の蓋カバーである。   Reference numeral 22 is a drain pump, 23 is a float switch, 24 is a drain pump accommodating portion in which the drain pump 22 is disposed, 25 is a partition plate for partitioning the drain pump accommodating portion, and 26 is a lid cover of the switch box 13.

ところで、上記天板３２は、上記空気調和機１の本体ケーシング３の形状に対応して略六角形状に形成され、その外周には、同本体ケーシング３の上端部外周側に冠合させるための鉤状の縁部３２ｃが設けられている。   By the way, the top plate 32 is formed in a substantially hexagonal shape corresponding to the shape of the main body casing 3 of the air conditioner 1, and the outer periphery thereof is meshed with the outer peripheral side of the upper end portion of the main body casing 3. A bowl-shaped edge 32c is provided.

また、該天板３２は、上述したファン５およびファンモータ９が支持される略中央部３３から略環状の熱交換器４が支持される半径方向外周部にかけて、放射状に延びる下方側に凹んだ所定幅、所定深さの複数本の主補強リブ３２ａ，３２ａ・・・が設けられている。そして、これら主補強リブ３２ａ，３２ａ・・・外周側の熱交換器支持部には、下方への凹み深さが小さくなった段差部３２ｂ，３２ｂ・・・が形成されている。   The top plate 32 is recessed downward from the substantially central portion 33 where the fan 5 and the fan motor 9 are supported to the radially outer peripheral portion where the substantially annular heat exchanger 4 is supported. A plurality of main reinforcing ribs 32a, 32a,... Having a predetermined width and a predetermined depth are provided. The main reinforcing ribs 32a, 32a,... On the outer peripheral side are formed with stepped portions 32b, 32b,.

そして、これら主補強リブ３２ａ，３２ａ・・・によって天板３２の基本的な剛性、強度、たわみ特性、振動特性を必要なレベルに設定している。   The basic rigidity, strength, deflection characteristics, and vibration characteristics of the top plate 32 are set to necessary levels by these main reinforcing ribs 32a, 32a.

また、天板３２の外周側では、主補強リブ３２ａ，３２ａ・・・相互の間隔が広くなり、その分剛性、強度等が不足する。   Moreover, the space | interval of main reinforcement rib 32a, 32a ... mutual becomes wide in the outer peripheral side of the top plate 32, and rigidity, intensity | strength, etc. are insufficient for it.

そこで、それら複数本の主補強リブ３２ａ，３２ａ・・・の間には、図１５に示すように、想定される荷重の大きさ等に対応して所望の形状、大きさの複数の副補強リブ３４，３４・・・が隣接する形で設けられている。   Therefore, between the plurality of main reinforcing ribs 32a, 32a..., As shown in FIG. Ribs 34, 34... Are provided adjacent to each other.

そして、これらによって、設計時、天板３２の静たわみを一定値以下にし、またファンモータ９回転による共振を避けるため、天板３２の１次固有振動数を一定値以上に維持するようにしていた。   Thus, at the time of design, the static deflection of the top plate 32 is kept below a certain value, and in order to avoid resonance due to the rotation of the fan motor 9, the primary natural frequency of the top plate 32 is kept above a certain value. It was.

また、上記天板３２には、上記略中央部３３のファン５およびファンモータ９支持部にも、内側に平面略三角形状の補強リブ３２ａが設けられている。そして、それによりファンおよびファンモータ支持部の剛性および強度、たわみ特性、振動特性を向上改善するようにしていた。   Further, the top plate 32 is provided with reinforcing ribs 32a having a substantially triangular plane on the inner side of the fan 5 and fan motor 9 support portions of the substantially central portion 33. As a result, the rigidity and strength, deflection characteristics, and vibration characteristics of the fan and fan motor support are improved and improved.

該平面略三角形状の補強リブ３３ａによって補強されたファン５およびファンモータ９支持部には、それぞれその底辺および頂点の各コーナ部位置に円形の凹溝部が設けられ、該凹溝部の中心軸部分に３つのファンモータ９の取付部ａ，ｂ，ｃが形成されている。そして、該ファンモータ取付部ａ，ｂ，ｃに対して吸振性のあるマウント部材１１，１１，１１および取付ブラケット９ｂを介してファンモータ９が吊設固定されている。また、これにより上記ファン５もモータ軸９ａを介して回転可能に支持されている。   The fan 5 and fan motor 9 support portions reinforced by the plane substantially triangular reinforcing ribs 33a are provided with circular concave grooves at the corners of the bottom and apex, respectively, and the central axis portion of the concave grooves The mounting portions a, b, and c of the three fan motors 9 are formed. The fan motor 9 is suspended and fixed via mount members 11, 11, 11 and a mounting bracket 9 b having a vibration absorbing property with respect to the fan motor mounting portions a, b, c. Thereby, the fan 5 is also rotatably supported via the motor shaft 9a.

特開平１１−２０１４９６号公報（明細書第１−３頁、図１−３）Japanese Patent Laid-Open No. 11-201496 (Specification, page 1-3, FIG. 1-3)

ところで、最近では各種の観点から、上記のような空気調和機のコストダウンを図ることが検討されており、上記天板３２もその例外ではない。   By the way, recently, from various viewpoints, it has been studied to reduce the cost of the air conditioner as described above, and the top plate 32 is no exception.

上記天板３２の場合、そのコストダウンの手法として、例えば現行（例えば０．８ｍｍ）のものよりも全体の板厚を薄くし（例えば０．７〜０．６ｍｍ程度に）、材料費を安くするとともに、リブ等形成のための加工性を向上させることが考えられる。   In the case of the top plate 32, as a method for reducing the cost, for example, the entire plate thickness is made thinner (for example, about 0.7 to 0.6 mm) than the current one (for example, 0.8 mm), and the material cost is reduced. In addition, it is conceivable to improve workability for forming ribs and the like.

しかし、その場合に問題となるのが、剛性や強度の低下であり、さらにはファン駆動時の振動対策である。   However, the problem in that case is a decrease in rigidity and strength, and further measures against vibrations when the fan is driven.

板厚を現行のものよりも薄くすれば材料費が低減され、変形も容易になるのでプレス成形時の加圧力も小さくて済み、加工性は向上する。   If the plate thickness is made thinner than the current thickness, the material cost is reduced and deformation is facilitated, so that the pressurizing force at the time of press molding can be reduced and the workability is improved.

しかし、実際に薄肉化して見ると、上記従来の構造の場合、静たわみ量が増大するとともにファンモータ９の回転に伴う１次固有振動数の低下により、上記従来品レベルの設計基準を満たすができなくなった。   However, when viewed in actual thinning, in the case of the conventional structure described above, the amount of static deflection increases and the primary natural frequency associated with the rotation of the fan motor 9 decreases. I can't.

また、補強リブの数が多く、形状も複雑であるため、プレス加工時、金型コストがかさむだけでなく、しわや亀裂、反り等が発生しやすい問題が生じた。   In addition, since the number of reinforcing ribs is large and the shape is complicated, not only the cost of the mold is increased but also a problem that wrinkles, cracks, warpage, etc. are likely to occur.

本願発明は、以上のような事情に鑑み、上記ファン駆動時における天板の挙動を含めて、薄肉化して、なおかつ必要な剛性、強度、振動特性を得ることができる高所設置型空気調和機の天板構造を提供することを目的とするものである。   In view of the circumstances as described above, the present invention is an altitude installation type air conditioner that can be thinned and include necessary rigidity, strength, and vibration characteristics including the behavior of the top plate when the fan is driven. The object is to provide a top plate structure.

本願発明は、上記の目的を達成するために、次のような課題解決手段を備えて構成されている。   In order to achieve the above object, the present invention is configured with the following problem solving means.

（１） 第１の課題解決手段
この発明の第１の課題解決手段は、ファンおよびファンモータ、熱交換器、ドレインポンプ、スイッチボックス等を収納する本体ケーシングと、該本体ケーシングの天面にあって、上記ファンおよびファンモータ、熱交換器、ドレインポンプ、スイッチボックス等を吊設支持する天板とを備えてなる空気調和機において、上記天板の上記ファンモータが支持される略中央部から上記熱交換器が支持される半径方向外周部にかけて、複数本の補強リブを放射状に延設するとともに、それら各補強リブの間をフラットに形成したことを特徴としている。 (1) First Problem Solving Means The first problem solving means of the present invention is a main casing that houses a fan, a fan motor, a heat exchanger, a drain pump, a switch box, and the like, and a top surface of the main casing. And an air conditioner comprising a top plate for suspending and supporting the fan and fan motor, heat exchanger, drain pump, switch box and the like, from a substantially central portion where the fan motor of the top plate is supported. A plurality of reinforcing ribs are radially extended toward the outer periphery in the radial direction where the heat exchanger is supported, and the space between the reinforcing ribs is formed flat.

このような高所設置型空気調和機の天板構造によると、仮に従来よりも天板の板厚を薄くしたとしても、複数本の補強リブの本数および断面形状（絞り形状）、深さ、幅などを最適に調整、設定することにより、従来のような多数の複雑な形状の副補強リブを設けることなく、剛性、強度、たわみ特性、振動特性等を必要なレベルに改善することができるようになる。   According to the top plate structure of such an altitude installation type air conditioner, even if the thickness of the top plate is made thinner than before, the number of the plurality of reinforcing ribs, the cross-sectional shape (drawing shape), the depth, By adjusting and setting the width and the like optimally, the rigidity, strength, deflection characteristics, vibration characteristics, etc. can be improved to the required level without providing a number of complicated reinforcing sub-reinforcement ribs as in the past. It becomes like this.

したがって、多くの副補強リブ等を組み合わせる場合に比べて、加工性が良く、プレス金型の構造も簡単になり、加工後の歪みや不要な変形、亀裂、反り等を伴わなくて済む。   Therefore, compared with the case where many sub-reinforcing ribs are combined, the workability is good, the structure of the press die is simplified, and there is no need for distortion, unnecessary deformation, cracks, warpage, and the like after processing.

そして、板厚を薄くでき、かつ加工性が向上する分、製品コストの削減が可能となる。   Further, since the plate thickness can be reduced and the workability is improved, the product cost can be reduced.

（２） 第２の課題解決手段
この発明の第２の課題解決手段は、上記第１の課題解決手段の構成において、補強リブ外周側の熱交換器支持部には、段差部が形成されていることを特徴としている。 (2) Second Problem Solving Means According to a second problem solving means of the present invention, in the configuration of the first problem solving means, a step portion is formed in the heat exchanger support portion on the outer peripheral side of the reinforcing rib. It is characterized by being.

このような高所設置型空気調和機の天板構造の場合、天板に対して熱交換器を支持する適正な位置決めを図ることができ、適正に位置決めした状態で確実に支持することができるので、より支持状態が安定する。   In the case of such a top plate structure of an altitude installation type air conditioner, proper positioning for supporting the heat exchanger with respect to the top plate can be achieved, and it can be reliably supported in a properly positioned state. Therefore, the support state becomes more stable.

その結果、さらに振動特性が改善される。   As a result, the vibration characteristics are further improved.

また、同段差部が補強リブの幅方向の強度を向上させるので、より天板のたわみ特性も改善される。   Further, since the step portion improves the strength in the width direction of the reinforcing rib, the deflection characteristics of the top plate are further improved.

（３） 第３の課題解決手段
この発明の第３の課題解決手段は、上記第１又は第２の課題解決手段の構成において、天板略中央部のファンモータ支持部には、補強リブが設けられていることを特徴としている。 (3) Third Problem Solving Means According to the third problem solving means of the present invention, in the configuration of the first or second problem solving means, a reinforcing rib is provided on the fan motor support portion at the substantially central portion of the top plate. It is characterized by being provided.

このような構成によると、天板中央部のファンモータ支持部の剛性、強度、振動特性も改善向上される。   According to such a configuration, the rigidity, strength, and vibration characteristics of the fan motor support at the center of the top plate are improved and improved.

（４） 第４の課題解決手段
この発明の第４の課題解決手段は、上記第１，第２又は第３の課題解決手段の構成において、天板の板厚は、０．６ｍｍ以上０．８ｍｍ未満の厚さであることを特徴としている。 (4) Fourth Problem Solving Means According to a fourth problem solving means of the present invention, in the configuration of the first, second or third problem solving means, the thickness of the top plate is 0.6 mm or more and 0.0. The thickness is less than 8 mm.

天板の板厚は、薄いほど材料コストは低下し、プレス成形も容易になる。   The thinner the top plate, the lower the material cost and the easier the press molding.

しかし、逆に強度、剛性は低下し、たわみ特性、振動特性は悪化する。これを補うのに、上記構成の補強リブは有効であるが、しかし補強リブのみでは限界があり、やはり一定の板厚は必要である。   However, on the contrary, the strength and rigidity are lowered, and the deflection characteristics and the vibration characteristics are deteriorated. In order to compensate for this, the reinforcing rib having the above-described configuration is effective, but there is a limit only with the reinforcing rib, and a certain plate thickness is still necessary.

従来の製品の板厚および上述の補強リブの効果との関係を考慮して、材料コストの低減、加工性の向上、必要な品質性能の確保を図ることができる適度な板厚は、０．６ｍｍ以上０．８ｍｍ未満が好ましい。   Considering the relationship between the thickness of the conventional product and the effect of the above-mentioned reinforcing rib, an appropriate thickness that can reduce the material cost, improve the workability, and ensure the necessary quality performance is 0. It is preferably 6 mm or more and less than 0.8 mm.

以上の結果、本願発明の高所設置型空気調和機の天板構造によると、天板の薄肉化、低コスト化を図りながら、その安定した支持剛性、支持強度、低騒音性能を実現することができる。   As a result of the above, according to the top plate structure of the high altitude installation type air conditioner of the present invention, it is possible to achieve stable support rigidity, support strength, and low noise performance while reducing the thickness and cost of the top plate. Can do.

図１〜図５は、本願発明の最良の実施の形態に係る高所設置型空気調和機の天板の構造を示している。   1-5 has shown the structure of the top plate of the high place installation type air conditioner based on the best embodiment of this invention.

この最良の実施の形態における天板３２は、すでに述べた図１３〜図１５に示した従来例の場合と略同様の天井埋込型空気調和機（室内機ユニット）の本体ケーシング３に適用するに最適なものとして構成されている。   The top plate 32 in this best embodiment is applied to the main body casing 3 of the ceiling-embedded air conditioner (indoor unit) that is substantially the same as that of the conventional example shown in FIGS. It is configured as an optimal one.

そして、その板厚Ｄ4は従来のもの０．８ｍｍよりも薄く０．７ｍｍ程度に形成されているとともに、その形状は、例えば図１および図２示すように、同空気調和機のカセット型本体ケーシング３の形状に対応して略六角形状に形成され、その外周には、同本体ケーシング３の上端部外周側に冠合させるための鉤状の縁部３２ｃが設けられている。 The plate thickness D 4 is thinner than the conventional 0.8 mm and is about 0.7 mm, and the shape thereof is, for example, as shown in FIGS. 1 and 2, the cassette type main body of the air conditioner. Corresponding to the shape of the casing 3, it is formed in a substantially hexagonal shape, and on its outer periphery, a bowl-shaped edge portion 32 c for engaging with the outer peripheral side of the upper end portion of the main body casing 3 is provided.

また、該天板３２には、図１３〜図１５のものと同様の構成のファン５およびファンモータ９が支持される略中央部３３から略環状の熱交換器４が支持される半径方向外周部にかけて、放射状に延びる下方側に凹んだ図４および図５に示すような断面が逆台形状で、底面の幅がＷ1、上端側の幅がＷ2、深さがＤ2、傾斜角がθ2の複数本の補強リブ３２ａ，３２ａ・・・が設けられ、それらの間はフラット部に形成されている。そして、それら補強リブ３２ａ，３２ａ・・・外周端側の熱交換器支持部には、下方への凹み深さＤ3が上記Ｄ2よりも所定寸法だけ小さくなった段差部３２ｂ，３２ｂ・・・が形成されている。 Further, the top plate 32 has a radial outer periphery in which a substantially annular heat exchanger 4 is supported from a substantially central portion 33 where the fan 5 and the fan motor 9 having the same configuration as those of FIGS. 13 to 15 are supported. 4 and 5, which are recessed downward in a radially extending direction, have an inverted trapezoidal shape, the bottom width is W 1 , the upper end width is W 2 , the depth is D 2 , and the inclination angle There theta 2 of the plurality of reinforcing ribs 32a, 32a · · · are provided, between which are formed on the flat portion. And those reinforcing ribs 32a, 32a · · · in the heat exchanger support portion of the outer peripheral end side, the stepped portion 32b which is recessed a depth D 3 downward becomes smaller by a predetermined dimension than the D 2, 32b · · -Is formed.

また、上記天板３２には、上記略中央部３３のファン５およびファンモータ９支持部にも、深さＤ1の補強リブ３３ａが設けられている（Ｄ1＝Ｄ2）。該補強リブ３３ａは、３点および４点支持が可能な５ケ所のファンモータ支持部ａ〜ｅの各々間に入り込み、内接する形で配設されている。 Further, the top plate 32, the fans 5 and the fan motor 9 supporting portion of the substantially central portion 33, the reinforcing rib 33a of a depth D 1 is provided (D 1 = D 2). The reinforcing ribs 33a are arranged so as to enter between the five fan motor support portions a to e that can support three and four points and to be inscribed therein.

そして、それによりファン５およびファンモータ９支持部の剛性および強度、たわみ特性、振動特性を有効に向上改善するようにしている。   As a result, the rigidity and strength, deflection characteristics, and vibration characteristics of the fan 5 and fan motor 9 support portions are effectively improved and improved.

また、同構成において、図１に示す如く、従来のものと同様にして、熱交換器４、ファン５およびファンモータ９、ドレインポンプ、スイッチボックス等の重量物が取り付けられる。   Further, in the same configuration, as shown in FIG. 1, heavy objects such as a heat exchanger 4, a fan 5 and a fan motor 9, a drain pump, a switch box and the like are attached in the same manner as the conventional one.

以上のように、本実施の形態の構成では、天板３２のファン５およびファンモータ９が支持される略中央部３３から熱交換器４が支持される半径方向外周部にかけて、複数本の補強リブ３２ａ，３２ａ・・・を放射状に延設するとともに、それら各補強リブ３２ａ，３２ａ・・・の間をフラットに形成したことを特徴としている。   As described above, in the configuration of the present embodiment, a plurality of reinforcements are provided from the substantially central portion 33 where the fan 5 and the fan motor 9 of the top plate 32 are supported to the radially outer peripheral portion where the heat exchanger 4 is supported. The ribs 32a, 32a,... Extend radially, and the space between these reinforcing ribs 32a, 32a,.

その結果、同構成では、仮に従来よりも天板の板厚を薄くしたとしても、複数本の補強リブ３２ａ，３２ａ・・・の本数および断面形状（絞り形状）、深さ、幅などを最適に調整、設定することにより、他に多数の副補強リブ等を設けることなく、剛性、強度、たわみ特性、振動特性等を必要なレベルに改善することができる。   As a result, even if the thickness of the top plate is made thinner than the conventional structure, the number of the plurality of reinforcing ribs 32a, 32a... And the cross-sectional shape (drawing shape), depth, width, etc. are optimal. By adjusting and setting, the rigidity, strength, deflection characteristics, vibration characteristics, etc. can be improved to the required level without providing a number of other auxiliary reinforcing ribs.

したがって、多くの副補強リブ等を組み合わせる場合に比べて、加工性が良く、プレス型の構造も簡単になり、加工後の歪みや不要な変形、亀裂、反り等を伴わなくて済む。   Therefore, compared with the case where many sub-reinforcing ribs are combined, the workability is good, the structure of the press die is simplified, and there is no need for distortion, unnecessary deformation, cracks, warpage, and the like after processing.

また、板厚を薄くでき、かつ加工性が向上する分、製品コストの削減が可能となる。   Further, the product cost can be reduced by reducing the plate thickness and improving the workability.

また、同構成では、上記補強リブ３２ａ，３２ａ・・・外周側の熱交換器４の支持部には、段差部３２ｂ，３２ｂ・・・が形成されている。   In the same configuration, step portions 32b, 32b,... Are formed on the support portions of the heat exchanger 4 on the outer peripheral side of the reinforcing ribs 32a, 32a,.

したがって、天板３２に対して熱交換器４を支持する際に適正な位置決めを図ることができ、また熱交換器４を同段差部３２ｂ，３２ｂ・・・に係合した状態で確実に支持することができるので、より支持状態が安定する。   Therefore, proper positioning can be achieved when the heat exchanger 4 is supported with respect to the top plate 32, and the heat exchanger 4 is reliably supported in a state where the heat exchanger 4 is engaged with the step portions 32b, 32b. As a result, the supporting state is more stable.

その結果、振動特性も一層改善される。   As a result, vibration characteristics are further improved.

また、同段差部３２ｂ，３２ｂ・・・が補強リブ３２ａ，３２ａ・・・の幅方向の強度を向上させるので、より天板３２のたわみ特性も改善される。   Further, since the step portions 32b, 32b,... Improve the strength in the width direction of the reinforcing ribs 32a, 32a,.

さらに、以上の構成では、略中央部３３のファン５およびファンモータ９支持部ａ〜ｅの周縁にも、補強リブ３２ａが設けられていることから、天板中央部のファン５およびファンモータ９支持部の剛性、強度、振動特性も改善向上される。   Furthermore, in the above configuration, since the reinforcing ribs 32a are also provided on the peripheral edges of the fan 5 and fan motor 9 support portions a to e in the substantially central portion 33, the fan 5 and the fan motor 9 in the central portion of the top plate. The rigidity, strength and vibration characteristics of the support part are also improved and improved.

また、以上の構成において、例えば上記天板３２の板厚は、０．６ｍｍ以上０．８ｍｍ未満の厚さであることが好ましい。   Further, in the above configuration, for example, the thickness of the top plate 32 is preferably 0.6 mm or more and less than 0.8 mm.

天板３２の板厚は、薄いほど材料コストは低下し、プレス成形も容易になる。   The thinner the top plate 32, the lower the material cost and the easier the press molding.

しかし、逆に強度、剛性は低下し、たわみ特性、振動特性は悪化する。これを補うのに、上記構成の補強リブ３２ａ，３２ａ・・・は有効であるが、しかし補強リブ３２ａ，３２ａ・・・のみでは限界があり、やはり一定の板厚は必要である。   However, on the contrary, the strength and rigidity are lowered, and the deflection characteristics and the vibration characteristics are deteriorated. In order to compensate for this, the reinforcing ribs 32a, 32a... Configured as described above are effective, but the reinforcing ribs 32a, 32a.

従来の製品の板厚（０．８ｍｍ）および上述の補強リブ３２ａ，３２ａ・・・の効果との関係を考慮して、材料コストの低減、加工性の向上、必要な品質性能の確保を図ることができる適度な板厚は、０．６ｍｍ以上０．８ｍｍ未満が好ましい。   Considering the relationship between the plate thickness (0.8 mm) of the conventional product and the effects of the above-mentioned reinforcing ribs 32a, 32a, ..., the material cost is reduced, the workability is improved, and the necessary quality performance is ensured. An appropriate plate thickness that can be used is preferably 0.6 mm or more and less than 0.8 mm.

以上の結果、本実施の形態の高所設置型空気調和機の天板構造によると、天板３２の可及的な薄肉化、低コスト化を図りながら、その安定した支持剛性、支持強度、低騒音性能を実現することができるようになる。   As a result of the above, according to the top plate structure of the height-installation type air conditioner of the present embodiment, the stable support rigidity, the support strength, while reducing the thickness of the top plate 32 as much as possible and reducing the cost. Low noise performance can be realized.

（実験例）
以上の作用効果（天板３２の挙動に及ぼす補強リブ３２ａ，３２ａ・・・の配置、深さ、長さ等）を実際に確認するために、例えば図６に示すように、上記図２の本実施の形態の天板３２と同様の仕様（板厚、形状、ファン５およびファンモータ９支持部）で、図１３〜図１５の従来例と同様の構造（主補強リブ３２ａ，３２ａ・・・、副補強リブ３４，３４・・・を具備）の天板３２を製作し、それら各々の強度および振動を解析（ＦＥＭ解析）した。 (Experimental example)
In order to actually confirm the above-described effects (arrangement, depth, length, etc. of the reinforcing ribs 32a, 32a... Affecting the behavior of the top plate 32), for example, as shown in FIG. The same structure (main reinforcing ribs 32a, 32a,...) With the same specifications (plate thickness, shape, fan 5 and fan motor 9 support) as the top plate 32 of the present embodiment, and the conventional example of FIGS. The top plate 32 having sub-reinforcing ribs 34, 34... Was manufactured, and the strength and vibration of each of them were analyzed (FEM analysis).

この解析には、Ｉ−ＤＥＡＳ ＭＳ９ｍ２ Ｍｏｄｅｌ Ｓｏｌｕｔｉｏｎを使用した。   For this analysis, I-DEAS MS9m2 Model Solution was used.

（１） 解析モデル
上述した図２の最良の実施の形態のものおよび図６の従来例（現行）のものの何れにおいても、天板３２を四節点のシェル要素で、天板３２に取り付けられる熱交換器４、ファン５およびファンモータ９、ドレインポンプ、スイッチボックスなどの各重量物を集中質量要素で、また天板３２と重量物の結合を剛体要素で各々モデリングした。 (1) Analytical model In any of the above-described best embodiment of FIG. 2 and the conventional example of FIG. 6 (current), the top plate 32 is a four-node shell element and the heat attached to the top plate 32 Each heavy object such as the exchanger 4, the fan 5 and the fan motor 9, the drain pump, and the switch box was modeled with a concentrated mass element, and the connection between the top plate 32 and the heavy object was modeled with a rigid element.

今例えば、図２、図６中において、Ａ〜Ｅは熱交換器４の取り付けられる位置、ａ〜ｅはファン５およびファンモータ９の取付位置を示す。   Now, for example, in FIGS. 2 and 6, A to E indicate positions where the heat exchanger 4 is mounted, and a to e indicate positions where the fan 5 and the fan motor 9 are mounted.

ドレインポンプは、熱交換器４に固定され、上記熱交換器４の取付位置Ａ〜Ｅを介して天板３２に荷重として作用する。   The drain pump is fixed to the heat exchanger 4 and acts as a load on the top plate 32 via the attachment positions A to E of the heat exchanger 4.

スイッチボックス１３はベルマウス６にも固定されるため、その取付位置を通じて天板３２に作用する荷重は、不明である。   Since the switch box 13 is also fixed to the bell mouth 6, the load acting on the top plate 32 through its mounting position is unknown.

一方、熱交換器４およびファンモータ９の天板３２に対する取付方法には、それぞれ次に示す２つの方式があり、それぞれについて検討した
＜熱交換器４の場合＞
（第１方式）
図２、図６中のＡ，Ｂ，Ｃの３ケ所で取り付ける。 On the other hand, there are the following two methods for attaching the heat exchanger 4 and the fan motor 9 to the top plate 32, and each of them has been studied <In the case of the heat exchanger 4>
(First method)
It is attached at three locations A, B, and C in FIGS.

（第２方式）
図２、図６中のＡ，Ｂ，Ｄ，Ｅの４ケ所で取り付ける。 (Second method)
Attached at four locations A, B, D, and E in FIGS.

＜ファンモータ９の場合＞
（第１方式）
図２、図６中のａ，ｂ，ｃの３ケ所で取り付ける。 <Fan motor 9>
(First method)
It is attached at three points a, b, and c in FIGS.

（第２方式）
図２、図６中のａ，ｂ，ｄ，ｅの４ケ所で取り付ける。 (Second method)
It is attached at four points a, b, d, and e in FIGS.

（２） 解析サンプル
２−１） 図２の本実施の形態のもの
板厚Ｄ4（Ｄ）が０．７ｍｍで、補強リブ３２ａ，３２ａの深さＤ2が８．８〜１２．８ｍｍのもの
２−２） 図６の従来例のもの
＜サンプル１＞
板厚Ｄ4（Ｄ）が、０．８ｍｍで、主補強リブ３２ａ，３２ａ・・・の深さＤ2が８．８ｍｍ、副補強リブ３４，３４・・・の深さＤ5が８．８ｍｍのもの
＜サンプル２＞
板厚Ｄ4（Ｄ）が、０．７ｍｍで、主補強リブ３２ａ，３２ａ・・・の深さＤ2が８．８ｍｍ、副補強リブ３４，３４・・・の深さＤ5が８．８ｍｍのもの
＜サンプル３＞
板厚Ｄ4（Ｄ）が、０．６ｍｍで、主補強リブ３２ａ，３２ａ・・・の深さＤ2が８．８ｍｍ、副補強リブ３４，３４・・・の深さＤ5が８．８ｍｍのもの
（３） 解析方法
上述した各重量物を取り付けた各天板３２，３２の外周を完全に固定した状態において、その動解析と静解析を行った。 (2) Analytical sample 2-1) According to the embodiment of FIG. 2 The plate thickness D 4 (D) is 0.7 mm, and the depth D 2 of the reinforcing ribs 32a and 32a is 8.8 to 12.8 mm. Material 2-2) Conventional example of FIG. 6 <Sample 1>
The plate thickness D 4 (D) is 0.8 mm, the depth D 2 of the main reinforcing ribs 32a, 32a... Is 8.8 mm, and the depth D 5 of the auxiliary reinforcing ribs 34, 34. 8mm <Sample 2>
The plate thickness D 4 (D) is 0.7 mm, the depth D 2 of the main reinforcing ribs 32a, 32a... Is 8.8 mm, and the depth D 5 of the auxiliary reinforcing ribs 34, 34. 8mm <Sample 3>
The plate thickness D 4 (D) is 0.6 mm, the depth D 2 of the main reinforcing ribs 32 a, 32 a... Is 8.8 mm, and the depth D 5 of the auxiliary reinforcing ribs 34, 34. 8 mm (3) Analysis method The dynamic analysis and the static analysis were performed in the state which fixed the outer periphery of each top plate 32 and 32 which attached each heavy article mentioned above completely.

静解析では天板３２と各重量物の自重のみを考慮し、動解析では各重量物の慣性モーメントを考慮しないものとした。なお、天板３２にかかるＳＢ重量の割合Ｗαが不明であるため、各重量物の質量および重心位置（天板にかかるＳＢ重量の割合）Ｗαを２５．０％〜１００．０％に変化させる。各重量物の質量と重心位置を次表１に示す。   In the static analysis, only the weight of the top plate 32 and each heavy object is considered, and in the dynamic analysis, the moment of inertia of each heavy object is not considered. In addition, since the ratio Wα of the SB weight applied to the top plate 32 is unknown, the mass and the gravity center position (the ratio of the SB weight applied to the top plate) Wα of each heavy object are changed to 25.0% to 100.0%. . The mass of each heavy object and the position of the center of gravity are shown in Table 1 below.

＜各重量物の質量および重心位置＞   <Mass and center of gravity of each heavy object>

Figure 2006003011
Figure 2006003011

さらに、各天板３２，３２の材料として、次の表２のものを用いた。   Further, the materials of the following Table 2 were used as materials for the top plates 32 and 32.

＜材料物性値＞   <Material properties>

Figure 2006003011
Figure 2006003011

結果評価は、図６の従来の天板３２（板厚Ｄ4（Ｄ）＝０．８ｍｍ）の結果を基準に行った。評価項目として天板３２の最大たわみと共振回転数を用いる。最大Ｍｉｓｅｓ応力は、評価項目としては使わない。これは最大Ｍｉｓｅｓ応力が、応力の特異点である取付け部（または、その近傍）において発生するからである。 The result evaluation was performed based on the result of the conventional top plate 32 (plate thickness D 4 (D) = 0.8 mm) of FIG. The maximum deflection of the top plate 32 and the resonance rotational speed are used as evaluation items. The maximum Mises stress is not used as an evaluation item. This is because the maximum Mises stress occurs at the attachment portion (or the vicinity thereof) that is a singular point of the stress.

（４） 解析結果
以上のようにして解析を行った結果、次のような解析結果が得られた。 (4) Analysis results As a result of the analysis as described above, the following analysis results were obtained.

なお、以下の結果評価は、次表３に示す図６の従来例（現行）のものを基準として行う。   In addition, the following result evaluation is performed on the basis of the conventional example (current) of FIG.

＜図６の従来例（現行の天板）の解析結果＞   <Analysis result of conventional example (current top plate) of FIG. 6>

Figure 2006003011
Figure 2006003011

熱交換器４の取付方式と板厚Ｄ4（Ｄ）および天板３２にかかるＳＢ重量の割合Ｗαの違いによる天板３２の最大たわみと最大Ｍｉｓｅｓ応力ならびに共振回転数の変化を次表の４と５に示す。また最大たわみと共振回転数に及ぼす板厚Ｄ4（Ｄ）とＷαの影響を図７、図８に示す。これらによれば、次の知見が得られる。 The following table shows changes in the maximum deflection, maximum Mises stress and resonance rotational speed of the top plate 32 due to differences in the mounting method of the heat exchanger 4 and the thickness D 4 (D) and the SB weight ratio Wα applied to the top plate 32. And 5 7 and 8 show the influence of the plate thickness D 4 (D) and Wα on the maximum deflection and the resonance rotational speed. According to these, the following knowledge is obtained.

４−１） 熱交換器４の第１の取付方式と比べれば、第２の取付方式では、天板３２の最大たわみがほとんど変わらないのに対し、共振回転数が顕著に上昇することが読み取れる。この結果から、第２の取付方式が優れていることが明らかである。したがって、以下の解析では、第２の取付方式を用いる。   4-1) Compared with the first mounting method of the heat exchanger 4, it can be read that the maximum deflection of the top plate 32 is hardly changed in the second mounting method, whereas the resonance rotational speed is remarkably increased. . From this result, it is clear that the second mounting method is excellent. Therefore, the second analysis method is used in the following analysis.

４−２） Ｗαを２５．０％〜１００．０％に変化させた場合、第１の取付方式では、天板３２の最大たわみが約４．０％低下し共振回転数が約１４．０％上昇するが、第２の取付方式では、最大たわみが約３．０％小さく共振回転数が約２．０％しか高くならないことがわかる。いずれの場合においても、天板３２の挙動に及ぼすＷαの影響が限定的であるので、以下の解析では、Ｗαを５０．０％とする。   4-2) When Wα is changed from 25.0% to 100.0%, in the first mounting method, the maximum deflection of the top plate 32 is reduced by about 4.0% and the resonance rotational speed is about 14.0. However, in the second mounting method, it can be seen that the maximum deflection is about 3.0% smaller and the resonance rotational speed is only about 2.0% higher. In any case, since the influence of Wα on the behavior of the top board 32 is limited, Wα is set to 50.0% in the following analysis.

４−３） この結果、板厚Ｄ4（Ｄ）が薄くなると、天板３２の最大たわみが顕著に上昇し共振回転数が大きく低下することが読み取れる。上記従来の天板３２と同等の挙動を確保するには、天板３２の板厚Ｄ4（Ｄ）が０．８ｍｍ以上必要であると推測される。 4-3) As a result, it can be seen that when the plate thickness D 4 (D) is reduced, the maximum deflection of the top plate 32 is remarkably increased and the resonance rotational speed is greatly decreased. In order to ensure the same behavior as the conventional top plate 32, it is estimated that the plate thickness D 4 (D) of the top plate 32 needs to be 0.8 mm or more.

＜天板にかかるＳＢ重量の割合Ｗαと板厚Ｄ4（Ｄ）の違いによる天板の最大たわみおよび最大Ｍｉｓｅｓ応力の変化＞ <Change in the maximum deflection and maximum Mises stress of the top plate due to the difference in the ratio Wα of the SB weight on the top plate and the thickness D 4 (D)>

Figure 2006003011
Figure 2006003011

＜天板にかかるＳＢ重量の割合Ｗαと板厚Ｄ4（Ｄ）の違いによる共振回転数（ｒｐｍ）の変化＞ <Change in Resonance Rotation Speed (rpm) due to Difference in SB Weight Ratio Wα and Plate Thickness D 4 (D) on Top Plate>

Figure 2006003011
Figure 2006003011

（５） ファン５の重量とファンモータ９の取付方式の影響（熱交換器４の取付方式が第２の取付方式の場合）
以下の解析では、熱交換器４の取付方式は第２の取付方式で、天板３２にかかるＳＢ重量の割合Ｗαは５０．０％であるとする。 (5) Influence of the weight of the fan 5 and the mounting method of the fan motor 9 (when the mounting method of the heat exchanger 4 is the second mounting method)
In the following analysis, it is assumed that the mounting method of the heat exchanger 4 is the second mounting method, and the SB weight ratio Wα applied to the top plate 32 is 50.0%.

ファン５の重量が２．３７０ｋｇｆから１．９６０ｋｇｆに軽量化された場合と、ファンモータ９の取付方式を第１の取付方式から第２の取付方式に変更した場合の天板３２における最大たわみと天板３２の共振回転数とを、それぞれ以下の表６と表７に示す。これらによれば、次の知見が得られる。   The maximum deflection of the top plate 32 when the weight of the fan 5 is reduced from 2.370 kgf to 1.960 kgf and when the mounting method of the fan motor 9 is changed from the first mounting method to the second mounting method. The resonance rotational speeds of the top plate 32 are shown in the following Tables 6 and 7, respectively. According to these, the following knowledge is obtained.

５−１） ファン５が軽量化された場合、天板３２の挙動が改善されることが読み取れる。   5-1) It can be read that the behavior of the top board 32 is improved when the fan 5 is lightened.

５−２） 第１のファンモータ取付方式と比べ、第２の取付方式を用いる方が天板３２の挙動の向上に寄与するが、効果が限定的であることがわかる。   5-2) Compared with the first fan motor mounting method, the use of the second mounting method contributes to the improvement of the behavior of the top plate 32, but it is understood that the effect is limited.

＜ファン重量の違いによる天板の最大たわみ（ｍｍ）と最大Ｍｉｓｅｓ応力（ｋｇｆ／ｍｍ2）および共振回転数（ｒｐｍ）の変化（第２の熱交換器取付方式：Ｗα＝５０．０％；第２のモータ取付方式）＞ <Maximum deflection (mm) and maximum Mises stress (kgf / mm 2 ) and resonance rotation speed (rpm) due to difference in fan weight (second heat exchanger mounting method: Wα = 50.0%; Second motor mounting method)>

Figure 2006003011
Figure 2006003011

＜ファンモータ取付け箇所の違いによる天板３２の天板の最大たわみ（ｍｍ）と最大Ｍｉｓｅｓ応力（ｋｇｆ／ｍｍ2）および共振回転数（ｒｐｍ）の変化（第２の熱交換器取付方式；Ｗα＝５０．０％；ファン重量２．３７０ｋｇｆ）＞ <Maximum deflection (mm), maximum Mises stress (kgf / mm 2 ) and resonance rotational speed (rpm) of top plate 32 due to difference in fan motor mounting location (second heat exchanger mounting method; Wα = 50.0%; fan weight 2.370 kgf)>

Figure 2006003011
Figure 2006003011

５−３） 板厚Ｄ4（Ｄ）が０．７ｍｍに薄肉化された天板３２が、上記従来の天板３２とほぼ同等な挙動を維持するには、天板３２に配置された補強リブ３２ａ，３２ａ・・・の形状の最適化が必要である。 5-3) In order for the top plate 32 having the thickness D 4 (D) thinned to 0.7 mm to maintain substantially the same behavior as that of the conventional top plate 32, reinforcement disposed on the top plate 32 is used. It is necessary to optimize the shape of the ribs 32a, 32a.

本解析では、図６に示した放射状リブ３２ａ，３２ａ・・・を主補強リブと呼び主補強リブの間に挟まれたリブ３４，３４・・・を副補強リブと呼ぶ。ここでは、天板３２の挙動に及ぼす各リブの影響について検討する。なお、解析には次の条件を用いる。   In this analysis, the radial ribs 32a, 32a,... Shown in FIG. 6 are called main reinforcing ribs, and the ribs 34, 34,. Here, the influence of each rib on the behavior of the top plate 32 will be examined. The following conditions are used for the analysis.

・天板３２にかかるＳＢ重量の割合Ｗαは５０．０％で、ファン５の重量は現行の２．３７０ｋｇｆである。   The ratio Wα of the SB weight applied to the top board 32 is 50.0%, and the weight of the fan 5 is the current 2.370 kgf.

・ファンモータ９の取付方式は第１の取付方式で、熱交換器４の取付方式は第２の取付方式である。   The attachment method of the fan motor 9 is the first attachment method, and the attachment method of the heat exchanger 4 is the second attachment method.

・板厚Ｄ4（Ｄ）は０．７ｍｍである。 And plate thickness D 4 (D) is 0.7mm.

主補強リブの深さが現行（８ｍｍ）のままで、副補強リブの深さを０．０〜８．８ｍｍ（現行深さ）に変化させた場合の解析結果を次の表８と図９，１０に示す。   Table 8 and FIG. 9 show the analysis results when the depth of the sub-reinforcing rib is changed from 0.0 to 8.8 mm (current depth) while the depth of the main reinforcing rib remains as it is (8 mm). , 10.

Figure 2006003011
Figure 2006003011

これらによれば、次の知見が得られる。   According to these, the following knowledge is obtained.

１． 天板３２の挙動（最大たわみと共振回転数）は副補強リブ３４，３４・・・の深さによって異なることが明らかである。０．０〜５．８ｍｍの範囲内において、同副補強リブ３４，３４・・・の深さが増すにしたがい、天板３２の挙動の低下が大きくなるが、副補強リブ３４，３４・・・の深さが５．８ｍｍを過ぎたところから、天板３２の挙動の低下が小さくなることがわかる。また、副補強リブ３４，３４・・・の深さが０．０ｍｍ、すなわち、副補強リブ３４，３４・・・を無くし、主補強リブ３２ａ，３２ａ・・・の間をフラットに形成した場合においては、天板３２の最大たわみが最小となり、共振回転数が最大になることが読み取れる。   1. It is clear that the behavior (maximum deflection and resonance rotational speed) of the top plate 32 varies depending on the depth of the auxiliary reinforcing ribs 34, 34. In the range of 0.0 to 5.8 mm, as the depth of the auxiliary reinforcing ribs 34, 34... Increases, the behavior of the top plate 32 decreases greatly, but the auxiliary reinforcing ribs 34, 34. From the point where the depth of 5.8 passed 5.8 mm, it can be seen that the decrease in the behavior of the top plate 32 becomes small. Further, when the depth of the auxiliary reinforcing ribs 34, 34... Is 0.0 mm, that is, the auxiliary reinforcing ribs 34, 34... Are eliminated and the space between the main reinforcing ribs 32a, 32a. It can be seen that the maximum deflection of the top plate 32 is minimum and the resonance rotational speed is maximum.

２． 副補強リブ３４，３４・・・の深さを現行の８．８ｍｍより大きく増やした場合、天板３２の挙動が副補強リブ３４，３４・・・のない場合と比べて向上すると思われるが、熱交設置および板金加工上の制限から、あまり深い副補強リブ３４，３４・・・は望ましくないと思われる。０．０〜８．８ｍｍの範囲内において、もっとも優れた挙動を示す副補強リブ３４，３４・・・のない天板（板厚Ｄ4（Ｄ）＝０．７ｍｍ）３２は、図６の現行天板（Ｄ4（Ｄ）＝０．８ｍｍ）３２と比べても、ほぼ同等な最大たわみ（１．３０ｍｍ→１．３８ｍｍ）と高い共振回転数（７４２．０ｒｐｍ→９０２．０ｒｐｍ）をもつことが読み取れる。 2. When the depth of the auxiliary reinforcing ribs 34, 34... Is increased more than the current 8.8 mm, the behavior of the top plate 32 seems to be improved as compared with the case without the auxiliary reinforcing ribs 34, 34. Due to heat exchange installation and sheet metal working limitations, the too deep secondary reinforcing ribs 34, 34. In the range of 0.0 to 8.8 mm, the top plate (thickness D 4 (D) = 0.7 mm) 32 without the auxiliary reinforcing ribs 34, 34. Compared with the current top plate (D 4 (D) = 0.8 mm) 32, it has a substantially equal maximum deflection (1.30 mm → 1.38 mm) and a high resonance speed (742.0 rpm → 902.0 rpm). I can read.

３． したがって、副補強リブ３４，３４・・・を無くし各主補強リブ３２ａ，３２ａ・・・間をフラットにした天板３２は優れた挙動を示すだけでなく、成形加工もしやすくなり、材料削減によるコストダウンと製品加工品質の向上にも繋がる。   3. Therefore, the top plate 32 in which the auxiliary reinforcing ribs 34, 34,... Are eliminated and the main reinforcing ribs 32a, 32a,... Are flattened not only exhibits excellent behavior, but is also easy to be molded, thereby reducing material. It leads to cost reduction and product processing quality improvement.

５−４） 副補強リブ３４，３４・・・を無くして主補強リブ３２ａ，３２ａ・・・の深さＤ2を変化させた場合の解析結果を、以下の表９と図１１，図１２に示す。得られた知見は次の通りである。 5-4) sub reinforcement ribs 34, 34 to eliminate the ... main reinforcing ribs 32a, the analysis result in the case of changing the depth D 2 of 32a ..., the following Table 9 and Figure 11, Figure 12 Shown in The obtained knowledge is as follows.

１． 主補強リブ３２ａ，３２ａ・・・が深くなるにしたがい、天板３２の挙動の顕著な向上が見られるが、向上率は次第に低下することが明らかになった。   1. As the main reinforcing ribs 32a, 32a,... Become deeper, the behavior of the top plate 32 is remarkably improved, but the improvement rate gradually decreases.

２． 天板３２の挙動に与える主補強リブ３２ａ，３２ａ・・・の影響は、極めて大きいことが明らかになった。   2. It has been clarified that the influence of the main reinforcing ribs 32a, 32a... On the behavior of the top board 32 is extremely large.

＜主補強リブ３２ａ，３２ａ・・・の深さの違いによる天板３２の最大たわみと最大Ｍｉｓｅｓ応力および共振回転数の変化（副補強リブ無し）＞   <Changes in Maximum Deflection, Maximum Mises Stress and Resonance Rotation Speed of Top Plate 32 Due to Difference in Depth of Main Reinforcement Ribs 32a, 32a.

Figure 2006003011
Figure 2006003011

本願発明の最良の実施の形態に係る高所設置型空気調和機の天板部の構造（熱交換器設置状態での）を示す下面図である。It is a bottom view which shows the structure (in the heat exchanger installation state) of the top-plate part of the high place installation type air conditioner which concerns on the best embodiment of this invention. 同高所設置型空気調和機の天板部の構造（熱交換器非設置状態での）を示す下面図である。It is a bottom view which shows the structure (in the heat exchanger non-installation state) of the top-plate part of the same height installation type air conditioner. 同天板部の正面図である。It is a front view of the same top plate part. 同天板部の中央縦断面図（図２のＡ−Ａ）である。It is a center longitudinal cross-sectional view (AA of FIG. 2) of the same top plate part. 同天板部の要部である補強リブ部分の構成を示す横断面図（図２のＢ−Ｂ）である。It is a cross-sectional view (BB of FIG. 2) which shows the structure of the reinforcement rib part which is the principal part of the top plate part. 同天板部と同様の仕様構造の下において、製作した従来モデルの構造を示す下面図である。It is a bottom view which shows the structure of the manufactured conventional model under the specification structure similar to the top plate part. 同天板の最大たわみに及ぼす板厚と熱交取付方式との関係を示すグラフである。It is a graph which shows the relationship between the board thickness which affects the maximum deflection of the same top board, and a heat exchanger mounting system. 同天板の共振回転数に及ぼす板厚と熱交取付方式との関係を示すグラフである。It is a graph which shows the relationship between plate | board thickness and the heat exchanger attachment system which influence on the resonant rotation speed of the same top plate. 同天板の最大たわみ量と副補強リブの深さとの関係を示すグラフである。It is a graph which shows the relationship between the maximum deflection amount of the same top plate, and the depth of a sub reinforcement rib. 同天板の共振回転数と副補強リブの深さとの関係を示すグラフである。It is a graph which shows the relationship between the resonant rotation speed of the same top plate, and the depth of a sub reinforcement rib. 同天板の最大たわみ量と主補強リブの深さとの関係を示すグラフである。It is a graph which shows the relationship between the maximum deflection amount of the same top plate, and the depth of the main reinforcement rib. 同天板の共振回転数と主補強リブの深さとの関係を示すグラフである。It is a graph which shows the relationship between the resonance rotational speed of the same top plate, and the depth of the main reinforcement rib. 従来の高所設置型空気調和機の全体構成を示す中央縦断面図（この図における天板部の断面は、図１５のＣ−Ｃ断面に相当する）である。It is a center longitudinal cross-sectional view (The cross section of the top-plate part in this figure is equivalent to CC cross section of FIG. 15) which shows the whole structure of the conventional high place installation type air conditioner. 同空気調和機の化粧パネルおよび本体ケーシングを除去して下方側から見た下面図である。It is the bottom view which removed the decorative panel and main body casing of the air conditioner, and was seen from the lower side. 同空気調和機の天板部とベルマウスおよびスイッチボックス等の取付関係を示す分解斜視図である。It is a disassembled perspective view which shows attachment relations, such as a top plate part of the same air conditioner, a bell mouth, and a switch box.

符号の説明Explanation of symbols

１は空気調和機、３は本体ケーシング、４は熱交換器、５はファン（羽根車）、６はベルマウス、９はファンモータ、９ａはモータ軸、９ｂは取付ブラケット、１１はマウント部材、３２は天板、３２ａは補強リブ、３２ｂは段差部、３３は中央部、３３ａは補強リブ、４１は熱交換器支持部材である。   1 is an air conditioner, 3 is a main body casing, 4 is a heat exchanger, 5 is a fan (impeller), 6 is a bell mouth, 9 is a fan motor, 9a is a motor shaft, 9b is a mounting bracket, 11 is a mounting member, 32 is a top plate, 32a is a reinforcing rib, 32b is a stepped portion, 33 is a central portion, 33a is a reinforcing rib, and 41 is a heat exchanger support member.

Claims (4)

ファンおよびファンモータ、熱交換器、ドレインポンプ、スイッチボックス等を収納する本体ケーシングと、該本体ケーシングの天面にあって、上記ファンおよびファンモータ、熱交換器、ドレインポンプ、スイッチボックス等を吊設支持する天板とを備えてなる空気調和機において、上記天板の上記ファンモータが支持される略中央部から上記熱交換器が支持される半径方向外周部にかけて、複数本の補強リブを放射状に延設するとともに、それら各補強リブの間をフラットに形成したことを特徴とする高所設置型空気調和機の天板構造。   A main casing that houses a fan, fan motor, heat exchanger, drain pump, switch box, and the like, and a fan casing, the fan motor, a heat exchanger, a drain pump, a switch box, etc. In the air conditioner comprising a top plate to be installed and supported, a plurality of reinforcing ribs are provided from a substantially central portion where the fan motor of the top plate is supported to a radially outer peripheral portion where the heat exchanger is supported. A top plate structure for an air conditioner installed at a high location, characterized by extending radially and between the reinforcing ribs being flat. 補強リブ外周側の熱交換器支持部には、段差部が形成されていることを特徴とする請求項１記載の高所設置型空気調和機の天板構造。   The top plate structure for an altitude installation type air conditioner according to claim 1, wherein a step portion is formed in the heat exchanger support portion on the outer peripheral side of the reinforcing rib. 天板略中央部のファンモータ支持部には、補強リブが設けられていることを特徴とする請求項１又は２記載の高所設置型空気調和機の天板構造。   The top plate structure for an altitude installation type air conditioner according to claim 1 or 2, wherein a reinforcing rib is provided on a fan motor support portion at a substantially central portion of the top plate. 天板の板厚は、０．６ｍｍ以上０．８ｍｍ未満の厚さであることを特徴とする請求項１，２又は３記載の高所設置型空気調和機の天板構造。
The top plate structure of an air conditioner with a high location according to claim 1, 2 or 3, wherein the top plate has a thickness of 0.6 mm or more and less than 0.8 mm.
JP2004179871A 2004-06-17 2004-06-17 Top plate structure of a high-altitude air conditioner Pending JP2006003011A (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
JP2004179871A JP2006003011A (en) 2004-06-17 2004-06-17 Top plate structure of a high-altitude air conditioner
CNB2005800170393A CN100483034C (en) 2004-06-17 2005-06-15 Top plate structure for air conditioner installed at high place
EP05751179.2A EP1775518B1 (en) 2004-06-17 2005-06-15 Top plate structure for air conditioner installed at high place
PCT/JP2005/010961 WO2005124238A1 (en) 2004-06-17 2005-06-15 Top plate structure for air conditioner installed at high place

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2004179871A JP2006003011A (en) 2004-06-17 2004-06-17 Top plate structure of a high-altitude air conditioner

Publications (1)

Publication Number Publication Date
JP2006003011A true JP2006003011A (en) 2006-01-05

Family

ID=35509777

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2004179871A Pending JP2006003011A (en) 2004-06-17 2004-06-17 Top plate structure of a high-altitude air conditioner

Country Status (4)

Country Link
EP (1) EP1775518B1 (en)
JP (1) JP2006003011A (en)
CN (1) CN100483034C (en)
WO (1) WO2005124238A1 (en)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007192415A (en) * 2006-01-17 2007-08-02 Mitsubishi Heavy Ind Ltd Cabinet for air conditioner and air conditioner using the same
WO2007126072A1 (en) * 2006-04-28 2007-11-08 Toshiba Carrier Corporation Indoor unit of air conditioning system
KR100867467B1 (en) * 2006-01-13 2008-11-10 엘지전자 주식회사 Anti-vibration Structure of Air Conditioner
JP2015206556A (en) * 2014-04-22 2015-11-19 新日鐵住金株式会社 Top plate for indoor unit
KR20200051944A (en) * 2018-11-06 2020-05-14 엘지전자 주식회사 Indoor Unit for Air Conditioner

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101743446B (en) * 2007-06-20 2013-08-07 澳大利亚奇胜有限公司 A fan and grille window assembly
KR101529223B1 (en) * 2014-12-31 2015-06-16 엘지전자 주식회사 Air conditioner and Control method of the same
KR102396941B1 (en) 2015-08-13 2022-05-13 엘지전자 주식회사 Indoor unit for air conditoiner

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2956675B2 (en) 1998-01-16 1999-10-04 ダイキン工業株式会社 Air conditioner
CN2418409Y (en) * 2000-04-26 2001-02-07 大金工业株式会社 Air-conditioning apparatus
JP3367607B2 (en) 2000-11-10 2003-01-14 株式会社日立製作所 Air conditioner indoor unit

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR100867467B1 (en) * 2006-01-13 2008-11-10 엘지전자 주식회사 Anti-vibration Structure of Air Conditioner
JP2007192415A (en) * 2006-01-17 2007-08-02 Mitsubishi Heavy Ind Ltd Cabinet for air conditioner and air conditioner using the same
WO2007126072A1 (en) * 2006-04-28 2007-11-08 Toshiba Carrier Corporation Indoor unit of air conditioning system
JPWO2007126072A1 (en) * 2006-04-28 2009-09-10 東芝キヤリア株式会社 Indoor unit of air conditioner
JP4582818B2 (en) * 2006-04-28 2010-11-17 東芝キヤリア株式会社 Indoor unit of air conditioner
AU2007244221B2 (en) * 2006-04-28 2011-02-03 Toshiba Carrier Corporation Indoor unit of air conditioning system
EP2017544A4 (en) * 2006-04-28 2012-04-11 Toshiba Carrier Corp INDOOR UNIT OF AIR CONDITIONING SYSTEM
JP2015206556A (en) * 2014-04-22 2015-11-19 新日鐵住金株式会社 Top plate for indoor unit
KR20200051944A (en) * 2018-11-06 2020-05-14 엘지전자 주식회사 Indoor Unit for Air Conditioner
KR102201289B1 (en) * 2018-11-06 2021-01-08 엘지전자 주식회사 Indoor Unit for Air Conditioner

Also Published As

Publication number Publication date
CN1957209A (en) 2007-05-02
EP1775518A1 (en) 2007-04-18
WO2005124238A1 (en) 2005-12-29
EP1775518B1 (en) 2018-06-06
CN100483034C (en) 2009-04-29

Similar Documents

Publication Publication Date Title
JP3807436B2 (en) Top plate structure of a high-altitude air conditioner
JP2006003011A (en) Top plate structure of a high-altitude air conditioner
JP2006292312A (en) Top plate structure of a high-altitude air conditioner
CN207132450U (en) Indoor apparatus of air conditioner
JP4693842B2 (en) Centrifugal blower and air conditioner using the same
KR20090115278A (en) Duct type air conditioner
EP0922911A2 (en) An outdoor unit of an air-conditioning system
JP2010127594A (en) Outdoor unit of air conditioner
JP2017048979A (en) Ceiling embedded type air conditioner
KR102203437B1 (en) Indoor Unit for Air Conditioner
JP5849795B2 (en) Air conditioner
JPH07158902A (en) Outdoor unit of air conditioner and assembling method thereof
JP6575754B2 (en) Embedded ceiling air conditioner
CN103673247A (en) Air conditioning unit
JP4821515B2 (en) Air conditioner
KR20090080749A (en) Ceiling air conditioners
KR100452374B1 (en) The motor mounting of an air-conditioner
JPH10184591A (en) Turbo fan
KR101419943B1 (en) Air conditioner and Fan assembly thereof
EP1657450A1 (en) A plate for a fan
JP2001173998A (en) Outdoor unit of air conditioner
KR20090074869A (en) Fan assembly of air conditioner and air conditioner
JPH0468230A (en) Blower device of air conditioner
JP2017048799A (en) Centrifugal blower
JP2011027323A (en) Outdoor unit for air conditioner

Legal Events

Date Code Title Description
A521 Request for written amendment filed

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20051115

A02 Decision of refusal

Free format text: JAPANESE INTERMEDIATE CODE: A02

Effective date: 20060214