[go: up one dir, main page]

CN1957209A - Roof structure of high-altitude air conditioner - Google Patents

Roof structure of high-altitude air conditioner Download PDF

Info

Publication number
CN1957209A
CN1957209A CNA2005800170393A CN200580017039A CN1957209A CN 1957209 A CN1957209 A CN 1957209A CN A2005800170393 A CNA2005800170393 A CN A2005800170393A CN 200580017039 A CN200580017039 A CN 200580017039A CN 1957209 A CN1957209 A CN 1957209A
Authority
CN
China
Prior art keywords
top plate
fan
heat exchanger
air conditioner
fan motor
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.)
Granted
Application number
CNA2005800170393A
Other languages
Chinese (zh)
Other versions
CN100483034C (en
Inventor
刘继红
太田直之
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
Publication of CN1957209A publication Critical patent/CN1957209A/en
Application granted granted Critical
Publication of CN100483034C publication Critical patent/CN100483034C/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24HEATING; RANGES; VENTILATING
    • F24FAIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/20Casings or covers
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24HEATING; RANGES; VENTILATING
    • F24FAIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007Indoor units, e.g. fan coil units
    • F24F1/008Indoor units, e.g. fan coil units with perfuming or deodorising means
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24HEATING; RANGES; VENTILATING
    • F24FAIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007Indoor units, e.g. fan coil units
    • F24F1/0043Indoor units, e.g. fan coil units characterised by mounting arrangements
    • F24F1/0047Indoor units, e.g. fan coil units characterised by mounting arrangements mounted in the ceiling or at the ceiling
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24HEATING; RANGES; VENTILATING
    • F24FAIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/02Ducting arrangements
    • F24F13/06Outlets for directing or distributing air into rooms or spaces, e.g. ceiling air diffuser
    • F24F2013/0616Outlets 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

An air conditioner has a body casing for receiving a fan and a fan motor, heat exchanger, drain pump, switch box, etc. and has a top plate placed at a top surface of the body casing and hanging the fan and fan motor, heat exchanger, drain pump, switch box, etc. The top plate is thinned to a thickness not more than a predetermined value. Reinforcement ribs are formed to radially extend from the central portion of the top plate, which supports the fan and motor, to an outer peripheral portion, which supports the heat exchanger. A section between each reinforcement rib is formed flat. The number, cross-sectional shape (shape of drawing), depth, width, etc. of the reinforcement ribs are optimally adjusted. As a result, the construction eliminates the need of forming a large number of auxiliary reinforcement ribs etc. conventionally used. In addition, the rigidity, strength, deflection characteristics, vibration characteristics, etc. of the top plate can be improved to a required level.

Description

高处设置型空调机的顶板结构Roof structure of high-altitude air conditioner

技术领域technical field

本发明涉及一种设置在高处的空调机的顶板结构。The invention relates to a roof structure of an air conditioner arranged at a high place.

背景技术Background technique

已知有一种埋设或吊设在天花板等高处的空调机(室内机单元)。这种空调机例如在箱盒型的本体外壳的顶面部具有金属制的顶板。空调机在顶板上吊设热交换器、风扇及风扇电机、排水泵、开关箱等重物,且利用吊挂螺栓等吊挂本体外壳,从而空调机埋设在天花板部的内部、或吊设在天花板部的下表面上。There is known an air conditioner (indoor unit) that is buried or suspended at a height such as a ceiling. Such an air conditioner has, for example, a metal top plate on the top surface of a box-shaped main body case. The air conditioner hangs heavy objects such as heat exchangers, fans and fan motors, drain pumps, and switch boxes on the ceiling, and hangs the main body shell with hanging bolts, so that the air conditioner is buried inside the ceiling or hung on the ceiling. on the lower surface of the part.

图13~图15表示这种高处设置型空调机中的埋入天花板型空调机的一例。13 to 15 show an example of a ceiling-mounted air conditioner among such high-place-installed air conditioners.

在该空调机中,在天花板70上形成的开口部7的上方配置空调机本体1,在该空调机本体1上安装有覆盖开口部7的装饰面板2。在空调机本体1的箱盒型本体外壳3内配设有:大致环状的热交换器4;配置在该热交换器4的中心部、吸入侧朝向下方且空气吹出侧朝向热交换器4的内周面的风扇(叶轮)5及风扇电机9;以及配置在风扇5的吸入侧的合成树脂制的钟形口6。In this air conditioner, an air conditioner body 1 is disposed above an opening 7 formed in a ceiling 70 , and a decorative panel 2 covering the opening 7 is attached to the air conditioner body 1 . In the box-shaped main body casing 3 of the air conditioner main body 1, a substantially annular heat exchanger 4 is arranged; the heat exchanger 4 is arranged in the center of the heat exchanger 4 with the suction side facing downward and the air blowing side facing the heat exchanger 4. A fan (impeller) 5 and a fan motor 9 on the inner peripheral surface; and a bell mouth 6 made of synthetic resin disposed on the suction side of the fan 5 .

风扇5例如由在轮毂5a与套罩5c之间具有多片叶片5b的离心风扇构成。在热交换器4的下方配置有接水盘8,在热交换器4的外周形成有空气吹出通路10。箱盒型本体外壳3例如形成为大致六角形,包括:由绝热材料构成的侧壁31、以及覆盖该侧壁31上部的顶板32。The fan 5 is constituted by, for example, a centrifugal fan having a plurality of blades 5b between a hub 5a and a shroud 5c. A water receiving pan 8 is arranged below the heat exchanger 4 , and an air blowing passage 10 is formed on the outer periphery of the heat exchanger 4 . The box-type body casing 3 is formed in, for example, a substantially hexagonal shape, and includes side walls 31 made of a heat insulating material, and a top plate 32 covering the upper portion of the side walls 31 .

在热交换器4的两个开放端分别配置有管板11,各管板11之间通过规定的隔板12连接。本体外壳3的顶板32、管板11、隔板12及安装在钟形口6下表面的开关箱13都由板金件形成。并且,例如图14所示,在隔板12的上端及下端利用小螺钉分别固定有顶板32和开关箱13。Tube sheets 11 are arranged at both open ends of the heat exchanger 4 , and the tube sheets 11 are connected by predetermined partition plates 12 . The top plate 32 of the body shell 3, the tube plate 11, the partition plate 12 and the switch box 13 installed on the lower surface of the bell mouth 6 are all formed by sheet metal parts. And, for example, as shown in FIG. 14 , the top plate 32 and the switch box 13 are respectively fixed to the upper end and the lower end of the partition plate 12 with screws.

另一方面,在钟形口6上形成有用于收纳开关箱13的凹部14。另外,在隔板12的下端部形成有开关箱结合部15。在凹部14的顶面14a上形成有与隔板12的开关箱结合部15相对的开口16。On the other hand, a recess 14 for accommodating the switch box 13 is formed in the bell mouth 6 . In addition, a switch box coupling portion 15 is formed at a lower end portion of the partition plate 12 . An opening 16 is formed on the top surface 14 a of the concave portion 14 to face the switch case coupling portion 15 of the partition plate 12 .

在隔板12的上端隔开间隔地一体形成有作为与顶板32结合的结合部的一对上方安装片17。这些上方安装片17利用小螺钉18从下方安装在顶板32上。A pair of upper mounting pieces 17 serving as joints to the top plate 32 are integrally formed at intervals on the upper end of the partition plate 12 . These upper mounting pieces 17 are mounted on the top plate 32 from below with small screws 18 .

在隔板12的下端隔开间隔地一体形成有作为与各管板11的下端结合的结合部的一对下方安装片19。另外,在隔板12的下端、且在两个下方安装片19的中间部通过焊接固定有作为与开关箱13结合的结合部的中间安装片15。下方安装片19利用小螺钉20从下方固定在管板11上。中间安装片15具有作为与隔板12结合的结合部的L字状的基部15a,在该基部15a上一体形成有从其前端向下延伸的安装部15b。该中间安装片15在安装部15b从开口16面对凹部14内的状态下利用小螺钉21从下方固定在开关箱13的顶面13a上。A pair of lower attachment pieces 19 serving as joints to the lower ends of the tube plates 11 are integrally formed at a distance from each other at the lower end of the partition plate 12 . In addition, an intermediate mounting piece 15 serving as a coupling portion to the switch box 13 is fixed by welding to the lower end of the partition plate 12 and between the two lower mounting pieces 19 . The lower mounting piece 19 is fixed on the tube plate 11 from below by means of small screws 20 . The intermediate mounting piece 15 has an L-shaped base portion 15a as a coupling portion to the partition plate 12, and a mounting portion 15b extending downward from the front end thereof is integrally formed on the base portion 15a. The intermediate mounting piece 15 is fixed to the top surface 13 a of the switch box 13 from below with screws 21 in a state where the mounting portion 15 b faces the inside of the recessed portion 14 from the opening 16 .

排水泵22及浮动开关23配置在排水泵收容部24内,排水泵收容部24由隔板25分隔。开关箱13由盖体26覆盖。The drain pump 22 and the float switch 23 are disposed in the drain pump housing portion 24 , and the drain pump housing portion 24 is partitioned by a partition plate 25 . The switch box 13 is covered by a cover body 26 .

顶板32与空调机1的本体外壳3的形状对应地形成为大致六角形。在该顶板32的外周形成有供本体外壳3的上端部外周嵌入的截面呈钩状的缘部32c。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 . On the outer periphery of the top plate 32, an edge portion 32c having a hook-shaped cross section into which the outer periphery of the upper end portion of the main body case 3 fits is formed.

在顶板32上形成有用于支撑风扇5及风扇电机9的中央部33、以及用于支撑大致环状的热交换器4的外周部35,且形成有从该中央部33向外周部35放射状延伸的多根主补强肋32a。主补强肋32a从顶板32向下方凹陷,其宽度及深度设定为规定的值。并且,在位于这些主补强肋32a外侧的热交换器支撑部上形成有向下方凹陷的深度设定得较小的多个台阶部32b。A central portion 33 for supporting the fan 5 and the fan motor 9 and an outer peripheral portion 35 for supporting the substantially annular heat exchanger 4 are formed on the top plate 32 , and radially extending from the central portion 33 to the outer peripheral portion 35 is formed. A plurality of main reinforcing ribs 32a. The main reinforcing rib 32a is recessed downward from the top plate 32, and its width and depth are set to predetermined values. In addition, a plurality of step portions 32b are formed on the heat exchanger support portion located outside the main reinforcing ribs 32a, and the depth of the downward recess is set to be small.

并且,通过这些主补强肋32a将顶板32的基本刚性、强度、挠曲特性、振动特性设定在所需要的水平。And, the basic rigidity, strength, flexural characteristics, and vibration characteristics of the top plate 32 are set at required levels by these main reinforcing ribs 32a.

另一方面,在顶板32的外周侧,由于主补强肋32a相互间的间隔变宽,故相应地该顶板32的刚性、强度等不足。On the other hand, on the outer peripheral side of the top plate 32, since the intervals between the main reinforcing ribs 32a are widened, the rigidity, strength, etc. of the top plate 32 are insufficient accordingly.

因此,如图15所示,在多根主补强肋32a之间相邻形成有多个副补强肋34。副补强肋34根据推定的载荷大小等形成为期望的形状及大小。Therefore, as shown in FIG. 15 , a plurality of sub-reinforcement ribs 34 are adjacently formed between a plurality of main reinforcement ribs 32 a. The sub-reinforcing rib 34 is formed in a desired shape and size according to the magnitude of the estimated load and the like.

并且,通过主补强肋32a、台阶部32b、副补强肋34,在设计空调机时,使顶板32的静挠度在一定值以下,且为了避免风扇电机9的旋转引起的共振,使顶板32的一次固有频率维持在一定值以上。And, through the main reinforcing rib 32a, the stepped portion 32b, and the auxiliary reinforcing rib 34, when designing the air conditioner, the static deflection of the top plate 32 is kept below a certain value, and in order to avoid the resonance caused by the rotation of the fan motor 9, the top plate The primary natural frequency of 32 is maintained above a certain value.

另外,在位于顶板32的中央部33的风扇5及风扇电机9的支撑部的内侧也形成有补强肋33a。补强肋33a的平面形状形成为大致三角形。利用该补强肋33a来提高风扇5及风扇电机9的支撑部的刚性、强度、挠曲特性、振动特性。In addition, reinforcing ribs 33 a are also formed inside the supporting parts of the fan 5 and the fan motor 9 located in the central part 33 of the top plate 32 . The planar shape of the reinforcing rib 33a is substantially triangular. Rigidity, strength, flexural characteristics, and vibration characteristics of the support portion of the fan 5 and the fan motor 9 are improved by the reinforcing rib 33 a.

由这种补强肋33a补强的风扇5及风扇电机9的支撑部在其底边及顶点的各拐角部分别形成有圆形的凹槽。另外,在各凹槽的中央分别形成有风扇电机9的安装部a、b、c。并且,在风扇电机9的安装部a、b、c上通过具有吸振性的安装构件9m及安装架9b吊设有风扇电机9。由此,风扇5也通过电机轴9a可旋转地支撑在上述风扇电机9的安装部a、b、c上。The supporting parts of the fan 5 and the fan motor 9 reinforced by such reinforcing ribs 33a are formed with circular grooves at the corners of the bottom and top respectively. In addition, mounting portions a, b, and c of the fan motor 9 are respectively formed in the center of each groove. Further, the fan motor 9 is suspended from the mounting portions a, b, and c of the fan motor 9 via a vibration-absorbing mounting member 9m and a mounting frame 9b. Accordingly, the fan 5 is also rotatably supported on the mounting portions a, b, and c of the fan motor 9 via the motor shaft 9 a.

专利文献1:日本专利特开平11-201496号公报Patent Document 1: Japanese Patent Laid-Open No. 11-201496

发明公开invention disclosure

但是,最近在想尽各种方法来实现上述这种空调机的成本降低,顶板32也不例外。Recently, however, various methods have been devised to reduce the cost of the above-mentioned air conditioner, and the top plate 32 is no exception.

作为针对顶板32的降低成本的方法,例如想到将现有顶板的板厚(例如0.8mm)整体减薄(例如0.7~0.6mm左右)以减少材料费,且提高形成肋等时的加工性。As a cost reduction method for the top plate 32 , for example, it is conceivable to reduce the overall thickness (for example, 0.8 mm) of the conventional top plate (for example, about 0.7 to 0.6 mm) to reduce material costs and improve workability when forming ribs and the like.

但是,此时存在的问题是:顶板32的刚性和强度降低,且在驱动风扇5时如何应对顶板32的振动。However, there are problems in this case in that the rigidity and strength of the top plate 32 are reduced, and how to cope with the vibration of the top plate 32 when the fan 5 is driven.

若将顶板32的板厚形成为比现有的薄则可减少材料费。另外,板材容易变形,可减小冲压成形时所需施加的压力,故也可提高加工性。If the plate thickness of the top plate 32 is made thinner than conventional ones, material costs can be reduced. In addition, since the plate material is easily deformed, the pressure required for press forming can be reduced, so the processability can also be improved.

但是,实际上若减薄顶板32,则与现有的结构相比,静挠度量增大,随着风扇电机9的旋转,一次固有频率降低,因此,不能满足与现有结构相同水平的设计基准。However, in fact, if the top plate 32 is thinned, the amount of static deflection increases compared with the conventional structure, and the primary natural frequency decreases with the rotation of the fan motor 9. Therefore, the same level of design as the conventional structure cannot be satisfied. benchmark.

另外,现有的顶板32具有大量的补强肋,这些补强肋的形状也很复杂,因此,不仅进行顶板32的冲压加工时的金属模的成本上升,而且也容易产生褶皱、龟裂、翘曲等。In addition, the conventional top plate 32 has a large number of reinforcing ribs, and the shape of these reinforcing ribs is also very complicated. Therefore, not only the cost of the metal mold at the time of pressing the top plate 32 is increased, but also wrinkles, cracks, etc. are likely to occur. warping etc.

鉴于上述问题,本发明的目的在于提供一种包含驱动风扇时顶板的特性在内可实现薄型化、且可得到所需的刚性、强度、振动特性的高处设置型空调机的顶板结构。In view of the above problems, an object of the present invention is to provide a ceiling structure of an air conditioner installed at a height, which can be thinned including the characteristics of the ceiling when driving a fan, and can obtain desired rigidity, strength, and vibration characteristics.

为了实现上述目的,本发明的第一形态中,空调机包括:收纳风扇及风扇电机、热交换器、排水泵、开关箱的本体外壳;以及配置在该本体外壳的顶面、吊设风扇及风扇电机、热交换器、排水泵、开关箱的顶板,该空调机顶板结构的特征在于,从支撑所述风扇电机的所述顶板的中央部向支撑所述热交换器的该顶板的外周部放射状延伸形成有多根补强肋,且各补强肋之间形成为平面。In order to achieve the above object, in the first form of the present invention, the air conditioner includes: a body casing for accommodating a fan and a fan motor, a heat exchanger, a drain pump, and a switch box; The fan motor, the heat exchanger, the drain pump, and the top plate of the switch box. The top plate structure of the air conditioner is characterized in that, from the central portion of the top plate supporting the fan motor to the outer peripheral portion of the top plate supporting the heat exchanger There are a plurality of reinforcing ribs extending radially, and planes are formed between each reinforcing rib.

采用这种高处设置型空调机的顶板结构,即使顶板的板厚比现有技术薄,通过将多根补强肋的根数及截面形状(拉伸形状)、深度、宽度等调整到最佳,也可不需形成现有技术中的多根形状复杂的副补强肋。而且,也可改善顶板的刚性、强度、挠曲特性、振动特性等使其达到所需的水平。With the roof structure of this high-placed air conditioner, even if the thickness of the roof is thinner than in the prior art, by adjusting the number of reinforcing ribs, cross-sectional shape (stretched shape), depth, and width to the optimum It is better, and it is not necessary to form a plurality of secondary reinforcing ribs with complex shapes in the prior art. Furthermore, it is also possible to improve the rigidity, strength, flexural characteristics, vibration characteristics, etc. of the top plate to desired levels.

因此,与组合大量副补强肋的情况相比,加工性优异,冲压金属模的结构也简单,故也不会产生加工后的应变、不需要的变形、龟裂、翘曲等。Therefore, compared with the case where a large number of sub-reinforcing ribs are combined, the workability is excellent, and the structure of the stamping die is also simple, so strain after processing, unnecessary deformation, cracks, warpage, etc. do not occur.

并且,可减薄顶板的板厚、且可提高加工性,从而相应地可降低产品成本。In addition, the thickness of the top plate can be reduced, and the workability can be improved, so that the product cost can be reduced accordingly.

上述构成中,最好在位于补强肋外周侧的热交换器支撑部上形成有台阶部。此时,可实现用于将热交换器支撑在顶板上的正确定位。另外,热交换器被可靠地支撑在该定位后的位置上,从而其支撑状态更加稳定。结果是,也可改善顶板的振动特性。另外,由于该台阶部可提高补强肋的宽度方向的强度,故也可进一步改善顶板的挠曲特性。In the above configuration, it is preferable that a stepped portion is formed on the heat exchanger supporting portion located on the outer peripheral side of the reinforcing rib. At this point, the correct positioning for supporting the heat exchanger on the roof can be achieved. In addition, the heat exchanger is reliably supported at the positioned position, so that its support state is more stable. As a result, the vibration characteristics of the top plate can also be improved. In addition, since the stepped portion can increase the strength in the width direction of the reinforcing rib, the flexural characteristics of the top plate can be further improved.

在上述空调机中,最好在位于顶板中央部的风扇电机支撑部上设置有补强肋。此时,还可提高位于顶板中央部的风扇电机支撑部的刚性、强度、振动特性。In the above-mentioned air conditioner, it is preferable that a reinforcing rib is provided on the fan motor support portion located at the central portion of the top plate. In this case, the rigidity, strength, and vibration characteristics of the fan motor support portion located at the center of the top plate can also be improved.

在上述空调机中,顶板的板厚最好在0.6mm以上且不到0.8mm。此时,顶板的板厚越薄则材料成本越低,且冲压成形也越容易进行。In the above-mentioned air conditioner, the thickness of the top plate is preferably not less than 0.6 mm and not more than 0.8 mm. In this case, the thinner the thickness of the top plate, the lower the material cost, and the easier it is to perform press forming.

但是,顶板的强度、刚性会下降,挠曲特性、振动特性反而恶化。为了应对这种情况,虽然上述构成的补强肋很有效,但仅靠这种补强肋毕竟有限,需要使顶板的板厚大于规定厚度。However, the strength and rigidity of the top plate will decrease, and the flexural characteristics and vibration characteristics will deteriorate instead. In order to cope with such a situation, although the reinforcing ribs constituted as described above are effective, such reinforcing ribs alone are limited, and it is necessary to make the thickness of the top plate larger than a predetermined thickness.

考虑到现有产品的板厚与上述补强肋的效果的关系,可降低材料成本、提高加工性、确保所需的品质性能的适度的顶板的板厚最好为0.6mm以上且不到0.8mm。Considering the relationship between the plate thickness of existing products and the effect of the above-mentioned reinforcing ribs, it is preferable that the plate thickness of an appropriate top plate that can reduce material costs, improve workability, and ensure the required quality and performance is 0.6 mm or more and less than 0.8 mm. mm.

因此,采用本发明的高处设置型空调机的顶板结构,可实现顶板的薄型化、低成本化,且可实现其稳定的支撑刚性、支撑强度、低噪音性能。Therefore, by adopting the roof structure of the high-place air conditioner of the present invention, the thickness and cost of the roof can be reduced, and the stable support rigidity, support strength, and low noise performance can be realized.

附图说明Description of drawings

图1是表示本发明较佳实施例的空调机的顶板部的结构(设置有热交换器的状态)的仰视图。Fig. 1 is a bottom view showing the structure of a top plate portion (a state where a heat exchanger is installed) of an air conditioner according to a preferred embodiment of the present invention.

图2是表示空调机的顶板部的结构(没有设置热交换器的状态)的仰视图。Fig. 2 is a bottom view showing the structure of the top plate portion of the air conditioner (in a state where no heat exchanger is installed).

图3是顶板部的主视图。Fig. 3 is a front view of the top plate.

图4是沿图2的4-4线的放大剖视图。Fig. 4 is an enlarged sectional view taken along line 4-4 of Fig. 2 .

图5是表示作为顶板部主要部分的补强肋的构成的沿图2的5-5线的放大剖视图。Fig. 5 is an enlarged cross-sectional view taken along line 5-5 in Fig. 2 , showing the structure of a reinforcing rib as a main part of the top plate.

图6是表示以与图1的顶板部相同的规格结构制作的现有模型的结构的仰视图。Fig. 6 is a bottom view showing the structure of a conventional model produced with the same standard structure as that of the top plate in Fig. 1 .

图7是表示顶板的最大挠度与板厚和热交换器的安装方式的关系的图表。Fig. 7 is a graph showing the relationship between the maximum deflection of the top plate, the plate thickness, and the mounting method of the heat exchanger.

图8是表示顶板的共振转速与板厚和热交换器的安装方式的关系的图表。Fig. 8 is a graph showing the relationship between the resonance rotational speed of the top plate, the plate thickness, and the mounting method of the heat exchanger.

图9是表示顶板的最大挠度与副补强肋的深度的关系的图表。Fig. 9 is a graph showing the relationship between the maximum deflection of the top plate and the depth of the sub-reinforcing ribs.

图10是表示顶板的共振转速与副补强肋的深度的关系的图表。FIG. 10 is a graph showing the relationship between the resonance rotational speed of the top plate and the depth of the sub-reinforcing ribs.

图11是表示顶板的最大挠度与主补强肋的深度的关系的图表。Fig. 11 is a graph showing the relationship between the maximum deflection of the top plate and the depth of the main reinforcing rib.

图12是表示顶板的共振转速与主补强肋的深度的关系的图表。Fig. 12 is a graph showing the relationship between the resonance rotational speed of the top plate and the depth of the main reinforcing rib.

图13是表示现有空调机的整体构成的中央纵向剖视图,该图中的顶板部的截面相当于图15中的13-13线的截面。Fig. 13 is a central longitudinal cross-sectional view showing the overall configuration of a conventional air conditioner, and the cross-section of the top plate in this figure corresponds to the cross-section taken along line 13-13 in Fig. 15 .

图14是将图13所示的空调机的装饰面板及本体外壳卸下后从下侧观察到的仰视图。Fig. 14 is a bottom view of the air conditioner shown in Fig. 13 when the decorative panel and the main body case are removed from the lower side.

图15是表示图13所示的空调机的顶板部与钟形口及开关箱的安装关系的分解立体图。Fig. 15 is an exploded perspective view showing the mounting relationship of the top plate portion, the bell mouth, and the switch box of the air conditioner shown in Fig. 13 .

具体实施方式Detailed ways

图1~图5表示本发明较佳实施例的高处设置型空调机的顶板结构。1 to 5 show the top plate structure of the high place installation type air conditioner according to the preferred embodiment of the present invention.

本实施例的顶板32应用在与已经叙述的图13~图15所示的现有技术例基本相同的埋入天花板型空调机(室内机单元)的本体外壳3(参照图3)上。The top plate 32 of this embodiment is applied to the body casing 3 (see FIG. 3 ) of the ceiling-mounted air conditioner (indoor unit) basically the same as the prior art example shown in FIGS. 13 to 15 described above.

该顶板32的板厚D4比现有的0.8mm薄,形成为0.7mm左右,如图1及图2所示,顶板32的形状与该空调机的箱盒型本体外壳3的形状对应地形成为概略六角形。在顶板32的外周形成有用于嵌入本体外壳3的上端部外周的截面呈钩状的缘部32c。The plate thickness D4 of this top plate 32 is thinner than the existing 0.8mm, and is formed as about 0.7mm, as shown in Figure 1 and Figure 2, the shape of the top plate 32 corresponds to the shape of the box-type body shell 3 of this air conditioner. become a rough hexagon. On the outer periphery of the top plate 32, an edge portion 32c having a hook-shaped cross section for fitting into the outer periphery of the upper end portion of the main body case 3 is formed.

在顶板32上形成有:用于支撑图13~图15所示的风扇5及风扇电机9的中央部33、以及用于支撑大致环状的热交换器4的外周部35,且形成有从该中央部33向外周部35放射状延伸的多根补强肋32a。如图4及图5所示,各补强肋32a是通过使顶板32向下方凹陷来形成的,其截面形状形成为倒梯形。另外,各补强肋32a设定为底面宽度为W1、上端侧的宽度为W2、深度为D2、倾斜角为θ2,各补强肋32a之间形成为平面。并且,在各补强肋32a的外周端、且在热交换器4的支撑部形成有台阶部32b。各台阶部32b向下方凹陷的深度D3设定为比上述D2小规定尺寸。Formed on the top plate 32 are: a central portion 33 for supporting the fan 5 and the fan motor 9 shown in FIGS. The central portion 33 includes a plurality of reinforcing ribs 32a extending radially toward the outer peripheral portion 35 . As shown in FIGS. 4 and 5 , each reinforcing rib 32 a is formed by denting the top plate 32 downward, and its cross-sectional shape is formed into an inverted trapezoid. Each reinforcing rib 32a is set to have a bottom width W 1 , an upper end width W 2 , a depth D 2 , and an inclination angle θ 2 , and each reinforcing rib 32a is formed as a plane. Furthermore, a stepped portion 32 b is formed at the outer peripheral end of each reinforcing rib 32 a and at the supporting portion of the heat exchanger 4 . The downward recessed depth D3 of each step portion 32b is set to be smaller than the aforementioned D2 by a predetermined dimension.

另外,在位于顶板32的中央部33的风扇5及风扇电机9的支撑部上也形成有深度为D1的补强肋33a(D1=D2)。即,形成在该支撑部的补强肋33a的深度D1与上述补强肋32a的深度D2相等。该补强肋33a分别进入可进行三点支撑及四点支撑的五处风扇电机的支撑部a~e之间,并与风扇电机9的各支撑部a~e内接(参照图1及图2)。In addition, a reinforcing rib 33 a having a depth of D 1 is also formed on the supporting portion of the fan 5 and the fan motor 9 located in the central portion 33 of the top plate 32 (D 1 =D 2 ). That is, the depth D1 of the reinforcing rib 33a formed in the supporting portion is equal to the depth D2 of the reinforcing rib 32a. The reinforcement ribs 33a respectively enter between the support portions a to e of the five fan motors that can be supported at three points and four points, and are inscribed with each support portion a to e of the fan motor 9 (see FIG. 1 and FIG. 2).

并且,通过该补强肋33a可有效提高风扇5及风扇电机9的支撑部的刚性、强度、挠曲特性、振动特性。Moreover, the rigidity, strength, flexural characteristics, and vibration characteristics of the support portion of the fan 5 and the fan motor 9 can be effectively improved by the reinforcing rib 33a.

另外,如图1所示,与现有技术例相同,热交换器4、风扇5及风扇电机9、排水泵22、开关箱23等重物安装在本实施例的顶板32上。In addition, as shown in FIG. 1 , heavy objects such as heat exchanger 4 , fan 5 , fan motor 9 , drain pump 22 , and switch box 23 are mounted on the top plate 32 of this embodiment, as in the prior art example.

如上所述,本实施例中,从支撑风扇5及风扇电机9的顶板32的中央部33向支撑热交换器4的顶板32的外周部35放射状延伸形成有多根补强肋32a,且这些补强肋32a之间形成为平面。As mentioned above, in this embodiment, a plurality of reinforcing ribs 32a are formed extending radially from the central portion 33 of the top plate 32 supporting the fan 5 and the fan motor 9 to the outer peripheral portion 35 of the top plate 32 supporting the heat exchanger 4, and these Between the reinforcing ribs 32a, a flat surface is formed.

结果是,即使将顶板32的板厚形成为比现有的薄,但通过将多根补强肋32a的根数、截面形状(拉伸形状)、深度、宽度等调整到最佳,则不需要另外形成大量的副补强肋34等。另外,也可将顶板32的刚性、强度、挠曲特性、振动特性等提高到所需的水平。As a result, even if the plate thickness of the top plate 32 is formed thinner than conventional ones, by optimizing the number, cross-sectional shape (drawn shape), depth, and width of the plurality of reinforcing ribs 32a, etc., It is necessary to separately form a large number of sub-reinforcing ribs 34 and the like. In addition, the rigidity, strength, flexural characteristics, vibration characteristics, etc. of the top plate 32 can also be increased to desired levels.

因此,与组合大量副补强肋34等的情况相比,加工性优异,冲压模具的结构也简单,故不会产生加工后的应变、不需要的变形、龟裂、翘曲等。Therefore, compared with the case of combining a large number of sub-reinforcing ribs 34, etc., the workability is excellent, and the structure of the press die is also simple, so strain after processing, unnecessary deformation, cracks, warpage, etc. do not occur.

另外,由于可减薄顶板32的板厚、且可提高加工性,从而相应地可降低产品成本。In addition, since the plate thickness of the top plate 32 can be reduced and workability can be improved, the product cost can be reduced accordingly.

另外,在该构成中,在位于上述补强肋32a外周侧的热交换器4的支撑部上形成有台阶部32b。Moreover, in this structure, the step|step-difference part 32b is formed in the support part of the heat exchanger 4 located in the outer peripheral side of the said reinforcing rib 32a.

因此,在将热交换器4支撑在顶板32上时,可实现用于将热交换器4支撑在该顶板32上的正确定位。另外,热交换器4在卡合在台阶部32b上的状态下可靠地得到支撑,从而其支撑状态更加稳定。Therefore, when supporting the heat exchanger 4 on the top plate 32 , correct positioning for supporting the heat exchanger 4 on the top plate 32 can be achieved. In addition, since the heat exchanger 4 is reliably supported in a state engaged with the step portion 32b, the supported state is further stabilized.

结果是,也可进一步改善顶板32的振动特性。As a result, the vibration characteristics of the top plate 32 can also be further improved.

另外,由于台阶部32b可提高补强肋32a的宽度方向的强度,故可进一步改善顶板32的挠曲特性。In addition, since the stepped portion 32b can increase the strength in the width direction of the reinforcing rib 32a, the flexural characteristics of the top plate 32 can be further improved.

而且,在以上构成中,在位于顶板32的中央部33的风扇5及风扇电机9的支撑部a~e的周缘也形成有补强肋32a。因此,在顶板32的中央部33也可改善风扇5及风扇电机9的支撑部的刚性、强度、振动特性。Furthermore, in the above structure, the reinforcement rib 32a is formed also in the peripheral edge of the support part a-e of the fan 5 and the fan motor 9 located in the center part 33 of the top plate 32. As shown in FIG. Therefore, the rigidity, strength, and vibration characteristics of the supporting portion of the fan 5 and the fan motor 9 can also be improved in the central portion 33 of the top plate 32 .

另外,在本实施例中,例如顶板32的板厚最好在0.6mm以上且不到0.8mm。In addition, in this embodiment, for example, the plate thickness of the top plate 32 is preferably not less than 0.6 mm and less than 0.8 mm.

顶板32的板厚越薄则材料成本越低,且冲压成形也越容易进行。The thinner the top plate 32 is, the lower the material cost is, and the easier it is to perform press forming.

但是,顶板32的强度、刚性会下降,挠曲特性、振动特性反而恶化。为了应对这种情况,虽然上述构成的补强肋32a很有效,但仅靠补强肋32a毕竟有限,需要使顶板32的板厚大于规定厚度。However, the strength and rigidity of the top plate 32 are reduced, and the flexural characteristics and vibration characteristics are degraded on the contrary. In order to cope with such a situation, although the reinforcing rib 32a configured as above is effective, the reinforcing rib 32a alone is limited, and it is necessary to make the thickness of the top plate 32 larger than a predetermined thickness.

考虑到现有产品的板厚(0.8mm)与上述补强肋32a的效果的关系,可降低材料成本、提高加工性、确保所需的品质性能的适度的顶板32的板厚最好为0.6mm以上且不到0.8mm。Considering the relationship between the plate thickness (0.8mm) of the existing product and the effect of the above-mentioned reinforcing ribs 32a, it is preferable that the plate thickness of the moderate top plate 32 that can reduce the material cost, improve the workability, and ensure the required quality and performance is 0.6 mm. More than mm and less than 0.8mm.

因此,采用本实施例的高处设置型空调机的顶板结构,可实现顶板32的尽可能的薄型化、低成本化,且可实现其稳定的支撑刚性、支撑强度、低噪音性能。Therefore, by adopting the top plate structure of the high-place air conditioner of this embodiment, the top plate 32 can be made as thin as possible, and the cost can be reduced, and its stable support rigidity, support strength, and low noise performance can be realized.

(实施例)(Example)

为了实际确认以上的作用效果、即影响顶板32特性的补强肋32a的配置、深度、长度等,例如如图6所示,以与图2所示本实施例的顶板32相同的规格(板厚、形状、风扇5及风扇电机9的支撑部),制作与图13~图15所示现有技术例相同结构(具有主补强肋32a、副补强肋34)的顶板32,对各自的强度及振动进行分析。在本分析中,采用了作为分析结构物的变形和应力用的近似分析方法之一的有限元法分析(EFM分析)。另外,在本分析中,使用有限元分析软件(EDF公司生产,I-DEAS MS9m2 Model Solution)。In order to actually confirm the above effects, that is, the configuration, depth, length, etc. of the reinforcing ribs 32a that affect the characteristics of the top plate 32, for example, as shown in FIG. Thickness, shape, support portion of fan 5 and fan motor 9), make the top plate 32 with the same structure (with main reinforcing rib 32a, secondary reinforcing rib 34) shown in Fig. 13-Fig. Strength and vibration analysis. In this analysis, finite element method analysis (EFM analysis), which is one of approximate analysis methods for analyzing deformation and stress of structures, is used. In addition, in this analysis, finite element analysis software (manufactured by EDF Corporation, I-DEAS MS9m2 Model Solution) was used.

(1)分析模型(1) Analysis model

在图2所示实施例的空调机及图6所示现有技术例的空调机中,都将顶板32作为四节点的壳体要素模型化,将安装在顶板32上的热交换器4、风扇5及风扇电机9、排水泵22、开关箱13等各重物作为集中质量要素模型化,且将顶板32和重物的结合作为刚体要素模型化。In the air conditioner of the embodiment shown in FIG. 2 and the air conditioner of the prior art example shown in FIG. 6, the top plate 32 is modeled as a four-node housing element, and the heat exchanger 4, Each heavy object such as the fan 5 , the fan motor 9 , the drain pump 22 , and the switch box 13 is modeled as a lumped mass element, and the combination of the top plate 32 and the heavy objects is modeled as a rigid body element.

图2、图6中,点A~E表示热交换器4的安装位置,支撑部a~e表示风扇5及风扇电机9的安装位置。In FIGS. 2 and 6 , points A to E indicate the installation positions of the heat exchanger 4 , and support portions a to e indicate the installation positions of the fan 5 and the fan motor 9 .

排水泵22固定在热交换器4上,通过热交换器4的安装位置、即点A~E作为载荷作用在顶板32上。The drain pump 22 is fixed to the heat exchanger 4, and acts on the top plate 32 as a load through the installation position of the heat exchanger 4, that is, points A to E.

开关箱13也固定在钟形口6上,因此通过其安装位置作用在顶板32上的载荷不明。The switch box 13 is also fixed to the bell mouth 6, so that the load acting on the top plate 32 through its mounting position is unknown.

另一方面,作为热交换器4及风扇电机9向顶板32上安装的安装方法有下述的两种方式,对热交换器4及风扇电机9的各方法进行研究。On the other hand, there are the following two methods of mounting the heat exchanger 4 and the fan motor 9 on the top plate 32, and each method of the heat exchanger 4 and the fan motor 9 will be examined.

<热交换器4的场合><In the case of heat exchanger 4>

(第一方式)(first way)

在图2、图6中的点A、B、C这三处安装。Install at points A, B, and C in Figure 2 and Figure 6.

(第二方式)(second method)

在图2、图6中的点A、B、D、E这四处安装。Install these four places at points A, B, D, and E in Fig. 2 and Fig. 6 .

<风扇电机9的场合><In the case of fan motor 9>

(第一方式)(first way)

在图2、图6中的支撑部a、b、c这三处安装。It is installed at the three supporting parts a, b, and c in Fig. 2 and Fig. 6 .

(第二方式)(second method)

在图2、图6中的点a、b、d、e这四处安装。It is installed at points a, b, d, and e in Fig. 2 and Fig. 6 .

(2)分析试样(2) Analysis sample

2-1)图2所示的本实施例的空调机2-1) The air conditioner of the present embodiment shown in Fig. 2

板厚D4为0.7mm,补强肋32a的深度D2为8.8~12.8mmThe plate thickness D4 is 0.7mm, and the depth D2 of the reinforcing rib 32a is 8.8-12.8mm

2-2)图6所示的现有技术例的空调机2-2) The air conditioner of the prior art example shown in FIG. 6

<试样1><Sample 1>

板厚D4为0.8mm、主补强肋32a的深度D2为8.8mm、副补强肋34的深度D5为8.8mm的顶板32Top plate 32 with plate thickness D4 of 0.8mm, depth D2 of main reinforcing rib 32a of 8.8mm, and depth D5 of sub-reinforcing rib 34 of 8.8mm

<试样2><Sample 2>

板厚D4为0.7mm、主补强肋32a的深度D2为8.8mm、副补强肋34的深度D5为8.8mm的顶板32Top plate 32 with a plate thickness D4 of 0.7mm, a depth D2 of the main rib 32a of 8.8mm, and a depth D5 of the sub-rib 34 of 8.8mm

<试样3><Sample 3>

板厚D4为0.6mm、主补强肋32a的深度D2为8.8mm、副补强肋34的深度D5为8.8mm的顶板32Top plate 32 with plate thickness D4 of 0.6 mm, depth D2 of main reinforcing rib 32a of 8.8 mm, and depth D5 of sub-reinforcing rib 34 of 8.8 mm

(3)分析方法(3) Analysis method

在将安装有上述各重物的各顶板32的外周完全固定的状态下,进行各顶板32的动态分析和静态分析。The dynamic analysis and the static analysis of each top plate 32 were performed in the state which completely fixed the outer periphery of each top plate 32 to which each said weight was attached.

在静态分析中仅考虑顶板32和各重物的自重,在动态分析中不考虑各重物的惯性矩。另外,由于作用在顶板32上的开关箱13的重量比例Wα不明,故使各重物的质量及重心位置(作用在顶板32上的开关箱13的重量比例)Wα在25.0%~100%之间变化。各重物的质量和重心位置如表1所示。In the static analysis, only the self-weight of the top plate 32 and each weight is considered, and the moment of inertia of each weight is not considered in the dynamic analysis. In addition, since the weight ratio W α of the switch box 13 acting on the top plate 32 is unknown, the mass and center of gravity position of each weight (the weight ratio of the switch box 13 acting on the top plate 32 ) W α is between 25.0% and 100%. % varies between. The mass and center of gravity of each weight are shown in Table 1.

<各重物的质量及重心位置><Mass and center of gravity of each weight>

表1: 重物 电动机 风扇 热交换器 排水泵   作用在顶板上的开关箱的重量比例Wα   100.0%   75.0%   50.0%   25.0%   质量(×10-4kgfs2/mm)   2.396   2.417   7.373   0.8158   1.529   1.148   0.7645   0.3822   重心(mm)   0.0,0.0,56.7   0.0,0.0,126.5   0.0,0.0,126.7   326.0,276.0,150.0           150.0,-296.5,300.0 Table 1: heavy object electric motor fan heat exchanger drain pump The weight ratio W α of the switch box acting on the top plate 100.0% 75.0% 50.0% 25.0% Mass (×10 -4 kgfs 2 /mm) 2.396 2.417 7.373 0.8158 1.529 1.148 0.7645 0.3822 Center of gravity (mm) 0.0, 0.0, 56.7 0.0, 0.0, 126.5 0.0, 0.0, 126.7 326.0, 276.0, 150.0 150.0, -296.5, 300.0

另外,作为各顶板32的材料使用表2所示的材料。In addition, the materials shown in Table 2 were used as the material of each top plate 32 .

<材料物性值><Material property value>

表2:   品名   材质   杨氏模量(kgf/mm2)   泊松比   密度(kgfs2/mm4)   钢   SECD-DKA   21078.7   0.29   7.97×10-10 Table 2: product name material Young's modulus (kgf/mm 2 ) Poisson's ratio Density (kgfs 2 /mm 4 ) steel SECD-DKA 21078.7 0.29 7.97×10 -10

                                      (SECD-DKA:JISG 3313规定的电镀锌钢板)(SECD-DKA: Electro-galvanized steel sheet specified in JISG 3313)

结果评价是以图6所示的现有顶板32(板厚D4=0.8mm)的结果为基准进行的。作为评价项目使用顶板32的最大挠度(mm)和共振转速(rpm)。最大Mises应力不作为评价项目使用,仅用于参考。这是因为最大Mises应力是在作为应力奇异点的安装部(或其附近)产生的缘故。另外,所谓Mises应力是指将三轴应力场中的值与单轴应力值(例如通过材料实验得到的数据值)进行比较时使用的典型的等效应力。Evaluation of the results was performed based on the results of the conventional top plate 32 (thickness D 4 =0.8 mm) shown in FIG. 6 . The maximum deflection (mm) and the resonance rotational speed (rpm) of the top plate 32 were used as evaluation items. The maximum Mises stress is not used as an evaluation item, but for reference only. This is because the maximum Mises stress occurs at the mounting portion (or its vicinity) which is a singular point of stress. In addition, the Mises stress refers to a typical equivalent stress used when comparing a value in a triaxial stress field with a uniaxial stress value (for example, a data value obtained by a material experiment).

(4)分析结果(4) Analysis results

如上所述地进行分析后得到下述的分析结果。Analysis was performed as described above, and the following analysis results were obtained.

另外,下述的结果评价是以表3所示的图6的现有技术例为基准进行的。In addition, the following result evaluation was performed based on the prior art example shown in Table 3 in FIG. 6 .

<图6的现有技术例(现有的顶板32)的分析结果><Analysis result of the prior art example (conventional top plate 32) of FIG. 6>

表3:   板厚(mm)   最大挠度(mm)   最大Mises应力(kgf/mm2)  共振转速(rpm)   0.8   1.30   8.70  742.0 table 3: Plate thickness (mm) Maximum deflection (mm) Maximum Mises stress (kgf/mm 2 ) Resonant speed(rpm) 0.8 1.30 8.70 742.0

因热交换器4的安装方式、板厚D4、作用在顶板32上的开关箱13的重量比例Wα的不同而引起的顶板32的最大挠度、最大Mises应力及共振转速的变化如表4及表5所示。另外,表5中所示的次数表示固有频率的次数。另外,板厚D4及开关箱13的重量比例Wα对最大挠度和共振转速的影响如图7及图8所示。由此,得出下面的结论。The changes in the maximum deflection, maximum Mises stress and resonance speed of the top plate 32 caused by the installation method of the heat exchanger 4, the plate thickness D 4 , and the weight ratio W α of the switch box 13 acting on the top plate 32 are shown in Table 4 And shown in Table 5. In addition, the orders shown in Table 5 represent the orders of the natural frequencies. In addition, the effects of the plate thickness D4 and the weight ratio of the switch box 13 on the maximum deflection and the resonance rotational speed are shown in Fig. 7 and Fig. 8 . From this, the following conclusions are drawn.

4-1)在热交换器4的第二方式中,顶板32的最大挠度与第一方式时相比几乎没有变化,但共振转速明显比第一方式时高。从该结果可以明显看出第二方式较佳。因此,在下面的分析中使用第二方式。4-1) In the second mode of the heat exchanger 4, the maximum deflection of the top plate 32 hardly changes from that of the first mode, but the resonance rotational speed is significantly higher than that of the first mode. From this result, it is clear that the second mode is preferable. Therefore, the second approach is used in the analysis below.

4-2)在使开关箱13的重量比例Wα在25.0%~100.0%之间变化的场合,采用第一方式时,顶板32的最大挠度约增大4.0%,其结果是,该顶板32的刚性下降。另外,共振转速约下降14.0%,其结果是,该顶板32的特性上升。另一方面,在第二方式中,最大挠度约增大3.0%,其增大幅度比上述第一方式小。另外,共振转速也仅下降约2.0%。无论哪种场合,Wα对顶板32特性的影响都限,在下面的分析中将Wα设为50.0%。4-2) When the weight ratio of the switch box 13 is changed between 25.0% and 100.0%, when the first method is adopted, the maximum deflection of the top plate 32 increases by about 4.0%. As a result, the top plate 32 rigidity decreased. In addition, the resonance rotational speed is reduced by about 14.0%, and as a result, the characteristics of the top plate 32 are improved. On the other hand, in the second form, the maximum deflection increases by about 3.0%, and the increase range is smaller than that of the above-mentioned first form. In addition, the resonance rotational speed also drops by only about 2.0%. In any case, W α has a limited influence on the characteristics of the top plate 32, and W α is set to 50.0% in the following analysis.

4-3)其结果是,若板厚D4变薄,则顶板32的最大挠度显著上升,共振转速大幅下降。为了确保与上述现有的顶板32相同的特性(参照表3),推测顶板32的板厚D4必须在0.8mm以上。4-3) As a result, when the plate thickness D4 becomes thinner, the maximum deflection of the top plate 32 increases remarkably, and the resonance rotational speed decreases significantly. In order to ensure the same characteristics as the above-mentioned conventional top plate 32 (see Table 3), it is estimated that the plate thickness D4 of the top plate 32 must be 0.8 mm or more.

<因作用在顶板32上的开关箱13的重量比例Wα和板厚D4的不同而引起的顶板32的最大挠度及最大Mises应力的变化><Changes in maximum deflection and maximum Mises stress of top plate 32 due to difference in weight ratio W α of switch box 13 acting on top plate 32 and thickness D 4 >

表4:   板厚   热交换器安装(第一方式)   热交换器安装(第二方式)   最大挠度(mm)   最大Mises应力(kgf/mm2)   最大挠度(mm)   最大Mises应力(kgf/mm2) Wα Wα Wα Wα   100.0%   75.0%   50.0%   25.0%   100.0%   75.0%   50.0%   25.0%   100.0%   75.0%   50.0%   25.0%   100.0%   75.0%   50.0%   25.0%   0.8   1.23   1.21   1.19   1.18   11.37   11.32   11.27   11.22   1.23   1.21   1.20   1.19   8.25   7.91   7.57   7.23   0.7   1.57   1.54   1.51   1.49   13.47   13.42   13.38   13.34   1.55   1.53   1.52   1.51   9.50   9.10   8.70   8.30   0.6   2.09   2.05   2.01   1.97   16.54   16.51   16.48   16.45   2.04   2.02   2.00   1.99   12.14   11.31   10.49   9.95 Table 4: plate thickness Heat exchanger installation (first method) Heat Exchanger Installation (Second Method) Maximum deflection (mm) Maximum Mises stress (kgf/mm 2 ) Maximum deflection (mm) Maximum Mises stress (kgf/mm 2 ) W α W α W α W α 100.0% 75.0% 50.0% 25.0% 100.0% 75.0% 50.0% 25.0% 100.0% 75.0% 50.0% 25.0% 100.0% 75.0% 50.0% 25.0% 0.8 1.23 1.21 1.19 1.18 11.37 11.32 11.27 11.22 1.23 1.21 1.20 1.19 8.25 7.91 7.57 7.23 0.7 1.57 1.54 1.51 1.49 13.47 13.42 13.38 13.34 1.55 1.53 1.52 1.51 9.50 9.10 8.70 8.30 0.6 2.09 2.05 2.01 1.97 16.54 16.51 16.48 16.45 2.04 2.02 2.00 1.99 12.14 11.31 10.49 9.95

<因作用在顶板32上的开关箱13的重量比例Wα和板厚D4的不同而引起的共振转速的变化><Changes in the resonance rotation speed due to the difference in the weight ratio of the switch box 13 acting on the top plate 32 and the plate thickness D4 >

表5:   板厚   次数   热交换器安装(第一方式)   热交换器安装(第二方式) Wα Wα   100.0%   75.0%   50.0%   25.0%   100.0%   75.0%   50.0%   25.0%   0.8   1   728.5   759.4   793.4   830.5   985.6   991.2   996.4   1001.2   2   978.6   989.9   1002.2   1016.6   1173.9   1183.1   1191.0   1197.7   3   1181.4   1184.6   1186.5   1188.0   1214.9   1224.4   1233.6   1242.2   4   1189.7   1193.4   1198.7   1205.2   1755.4   1812.0   1868.8   1925.7   0.7   1   622.3   648.6   677.6   709.5   870.8   876.6   881.9   886.7   2   860.4   871.6   883.5   897.1   1021.9   1029.7   1036.2   1041.7   3   1027.3   1028.6   1029.5   1030.4   1052.9   1061.1   1069.2   1077.0   4   1030.1   1034.1   1039.0   1044.4   1515.9   1563.1   1610.7   1658.8 0.6   1   518.3   540.0   564.1   590.7   751.5   757.4   762.7   767.5   2   738.1   749.0   760.4   773.0   868.9   875.3   880.3   884.5   3   869.7   870.2   870.7   871.5   891.1   898.0   905.1   911.9   4   873.6   877.2   881.0   885.0   1277.3   1315.4   1354.1   1393.6 table 5: plate thickness frequency Heat exchanger installation (first method) Heat Exchanger Installation (Second Method) W α W α 100.0% 75.0% 50.0% 25.0% 100.0% 75.0% 50.0% 25.0% 0.8 1 728.5 759.4 793.4 830.5 985.6 991.2 996.4 1001.2 2 978.6 989.9 1002.2 1016.6 1173.9 1183.1 1191.0 1197.7 3 1181.4 1184.6 1186.5 1188.0 1214.9 1224.4 1233.6 1242.2 4 1189.7 1193.4 1198.7 1205.2 1755.4 1812.0 1868.8 1925.7 0.7 1 622.3 648.6 677.6 709.5 870.8 876.6 881.9 886.7 2 860.4 871.6 883.5 897.1 1021.9 1029.7 1036.2 1041.7 3 1027.3 1028.6 1029.5 1030.4 1052.9 1061.1 1069.2 1077.0 4 1030.1 1034.1 1039.0 1044.4 1515.9 1563.1 1610.7 1658.8 0.6 1 518.3 540.0 564.1 590.7 751.5 757.4 762.7 767.5 2 738.1 749.0 760.4 773.0 868.9 875.3 880.3 884.5 3 869.7 870.2 870.7 871.5 891.1 898.0 905.1 911.9 4 873.6 877.2 881.0 885.0 1277.3 1315.4 1354.1 1393.6

(5)风扇5的重量和风扇电机9的安装方式的影响(热交换器4的安装方式为第二方式时)(5) Influence of the weight of the fan 5 and the installation method of the fan motor 9 (when the installation method of the heat exchanger 4 is the second method)

在下面的分析中,假定作为热交换器4的安装方式采用第二方式,作用在顶板32上的开关箱13的重量比例Wα为50.0%。In the following analysis, assuming that the second installation method is adopted as the heat exchanger 4, the weight ratio of the switch box 13 acting on the top plate 32 is 50.0%.

风扇5的重量从2.370kgf减轻到1.960kgf的场合,风扇电机9的安装方式从第一方式变更为第二方式时顶板32的最大挠度和共振转速分别如表6及表7所示。由此,得出下面的结论。When the weight of the fan 5 is reduced from 2.370kgf to 1.960kgf, the maximum deflection and resonance speed of the top plate 32 when the installation method of the fan motor 9 is changed from the first method to the second method are shown in Table 6 and Table 7, respectively. From this, the following conclusions are drawn.

5-1)在减轻风扇5时,顶板32的最大挠度降低,且共振转速上升,故该顶板32的特性得到改善。5-1) When the fan 5 is lightened, the maximum deflection of the top plate 32 decreases and the resonance rotational speed increases, so the characteristics of the top plate 32 are improved.

5-2)在作为风扇电机9的安装方式采用第二方式时,与第一方式相比,顶板32的最大挠度降低,且共振转速也上升,故顶板32的特性提高,但其效果有限。5-2) When the second method is used as the installation method of the fan motor 9, compared with the first method, the maximum deflection of the top plate 32 is reduced, and the resonance speed is also increased, so the characteristics of the top plate 32 are improved, but the effect is limited.

<因风扇5的重量不同而引起的顶板32的最大挠度、最大Mises应力及共振转速的变化(热交换器4的安装方式为第二方式,Wα=50.0%,风扇电机9的安装方式为第二方式)><The variation of the maximum deflection, the maximum Mises stress and the resonance speed of the top plate 32 caused by the different weights of the fan 5 (the installation method of the heat exchanger 4 is the second method, W α =50.0%, and the installation method of the fan motor 9 is Second way)>

表6:   板厚   2.370kgf   1.960kgf 最大挠度 最大Mises应力 共振转速 最大挠度 最大Mises应力 共振转速   0.8   1.20   7.57   996.4   1.15  7.42   1024.0   0.7   1.52   8.70   881.9   1.45  8.53   907.0   0.6   2.00   10.49   762.7   1.91  10.34   784.0 Table 6: plate thickness 2.370kgf 1.960kgf Maximum deflection Maximum Mises stress Resonance speed Maximum deflection Maximum Mises stress Resonance speed 0.8 1.20 7.57 996.4 1.15 7.42 1024.0 0.7 1.52 8.70 881.9 1.45 8.53 907.0 0.6 2.00 10.49 762.7 1.91 10.34 784.0

<因风扇电机9的安装部位不同而引起的顶板32的最大挠度、最大Mises应力及共振转速的变化(热交换器4的安装方式为第二方式,Wα=50.0%,风扇重量为2.370kgf)><The maximum deflection of the top plate 32, the maximum Mises stress and the change of the resonance speed due to the different installation positions of the fan motor 9 (the installation method of the heat exchanger 4 is the second method, W α =50.0%, and the weight of the fan is 2.370kgf )>

表7:   板厚   电动机安装(第一方式)   电动机安装(第二方式) 最大挠度 最大Mises应力 共振转速 最大挠度 最大Mises应力 共振转速   0.8   1.20  7.57   996.4   1.17   7.56   1010.0   0.7   1.52  8.70   881.9   1.48   8.69   893.0   0.6   2.00  10.49   762.7   1.95   10.46   772.0 Table 7: plate thickness Motor installation (first method) Motor installation (second method) Maximum deflection Maximum Mises stress Resonance speed Maximum deflection Maximum Mises stress Resonance speed 0.8 1.20 7.57 996.4 1.17 7.56 1010.0 0.7 1.52 8.70 881.9 1.48 8.69 893.0 0.6 2.00 10.49 762.7 1.95 10.46 772.0

5-3)板厚D4减薄为0.7mm的顶板32为了维持与现有的顶板32基本相同的特性,需要使配置在顶板32上的补强肋32a的形状达到最佳(参照表6)。5-3) The top plate 32 whose plate thickness D4 is reduced to 0.7mm maintains basically the same characteristics as the conventional top plate 32, and it is necessary to optimize the shape of the reinforcing rib 32a arranged on the top plate 32 (see Table 6 ).

在本分析中,将图6所示的放射状的肋称为主补强肋32a,将夹在该主补强肋32a之间的肋称为副补强肋34。在此,对各肋32a、34对顶板32的特性的影响进行研究。另外,本分析中使用了下述条件。In this analysis, the radial ribs shown in FIG. 6 are referred to as main reinforcing ribs 32 a, and the ribs sandwiched between the main reinforcing ribs 32 a are referred to as sub-reinforcing ribs 34 . Here, the influence of each rib 32a, 34 on the characteristic of the top plate 32 is examined. In addition, the following conditions were used in this analysis.

·作用在顶板32上的开关箱13的重量比例Wα为50.0%,风扇5的重量为现有的2.370kgf。- The weight ratio W α of the switch box 13 acting on the top plate 32 is 50.0%, and the weight of the fan 5 is 2.370kgf conventionally.

·风扇电机9的安装方式为第一方式,热交换器4的安装方式为第二方式。·The installation method of the fan motor 9 is the first method, and the installation method of the heat exchanger 4 is the second method.

·板厚D4为0.7mm。· Plate thickness D4 is 0.7mm.

主补强肋32a的深度为现有的8.8mm而副补强肋34的深度在0.0~8.8mm(现有深度)之间变化时的分析结果如表8和图9、图10所示。The analysis results when the depth of the main reinforcing rib 32a is the conventional 8.8 mm and the depth of the secondary reinforcing rib 34 varies between 0.0 and 8.8 mm (the existing depth) are shown in Table 8 and FIGS. 9 and 10 .

表8:   副补强肋的深度(mm)   0.0   0.8   1.8   2.8   3.8   4.8   5.8   6.8   7.8   8.8   最大挠度   1.38   1.43   1.46   1.49   1.52   1.54   1.55   1.55   1.54   1.52   最大Mises应力   13.41   13.55   12.69   13.08   13.50   13.87   14.11   14.16   14.00   13.66   共振转速   902.0   893.0   892.0   887.0   882.0   878.0   877.0   878.0   882.0   887.0 Table 8: Depth of secondary reinforcing rib (mm) 0.0 0.8 1.8 2.8 3.8 4.8 5.8 6.8 7.8 8.8 Maximum deflection 1.38 1.43 1.46 1.49 1.52 1.54 1.55 1.55 1.54 1.52 Maximum Mises stress 13.41 13.55 12.69 13.08 13.50 13.87 14.11 14.16 14.00 13.66 Resonance speed 902.0 893.0 892.0 887.0 882.0 878.0 877.0 878.0 882.0 887.0

由此,得出下面的结论。From this, the following conclusions are drawn.

1.顶板32的特性(最大挠度和共振转速)显然因副补强肋34的深度不同而有所不同。副补强肋34的深度在0.0~5.8mm的范围内时,随着该深度增大则顶板32的特性下降,但在该深度比5.8mm深时,则顶板32的特性的降低变小。另外,当副补强肋34的深度为0.0mm、即没有副补强肋34而主补强肋32a之间形成为平面时,顶板32的最大挠度达到最小,共振转速达到最大。1. The characteristics of the top plate 32 (maximum deflection and resonant rotational speed) obviously vary depending on the depth of the sub-reinforcing ribs 34 . When the depth of the sub-reinforcing ribs 34 is in the range of 0.0 to 5.8 mm, the properties of the top plate 32 deteriorate as the depth increases, but when the depth is deeper than 5.8 mm, the degradation of the properties of the top plate 32 becomes smaller. In addition, when the depth of the sub-reinforcing ribs 34 is 0.0 mm, that is, when there is no sub-reinforcing ribs 34 and the main reinforcing ribs 32a are flat, the maximum deflection of the top plate 32 is minimized and the resonance rotational speed is maximized.

2.虽然可以认为使副补强肋34的深度增大到比现有的8.8mm大时,顶板32的特性与没有副补强肋34的情况相比会有所提高,但由于热交换器4的设置及板金加工方面的限制,不希望形成深的副补强肋34。在0.0~8.8mm的范围内,表现出最优异的特性的没有副补强肋34的顶板(板厚D4=0.7mm)32与图6所示的现有的顶板(D4=0.8mm)32相比,具有基本相同的最大挠度(1.30mm→1.38mm)和较高的共振转速(742.0rpm→902.0rpm)。2. Although it can be considered that when the depth of the sub-reinforcement rib 34 is increased to be greater than the existing 8.8mm, the characteristics of the top plate 32 will be improved compared with the case without the sub-reinforcement rib 34, but due to the heat exchanger 4 and restrictions on sheet metal processing, it is not desirable to form deep sub-reinforcing ribs 34 . In the range of 0.0 to 8.8 mm, the top plate (thickness D 4 =0.7 mm) 32 without sub-rib 34 exhibiting the most excellent characteristics is different from the conventional top plate (D 4 =0.8 mm) shown in FIG. 6 . )32, it has basically the same maximum deflection (1.30mm→1.38mm) and higher resonance speed (742.0rpm→902.0rpm).

3.因此,没有副补强肋34而将各主补强肋32a之间形成为平面的顶板32不仅表现出优异的特性,而且成形加工也容易,可实现材料减少带来的成本降低和产品加工品质的提高。3. Therefore, the top plate 32 formed flat between the main reinforcing ribs 32a without the sub-reinforcing ribs 34 not only exhibits excellent characteristics, but also is easy to form and process, and can realize cost reduction and product quality due to material reduction. Improvement of processing quality.

5-4)在没有副补强肋34的情况下使主补强肋32a的深度D2变化时的分析结果如表9和图11、图12所示。得到的结论如下所述。5-4) The analysis results when the depth D2 of the main reinforcing rib 32a was changed without the sub reinforcing rib 34 are shown in Table 9 and FIGS. 11 and 12 . The conclusions obtained are as follows.

1.随着主补强肋32a的加深,顶板32的特性显著提高,但提高率逐渐降低。1. With the deepening of the main reinforcing rib 32a, the characteristics of the top plate 32 are significantly improved, but the rate of improvement is gradually reduced.

2.主补强肋32a对顶板32的特性的影响极大。2. The main reinforcing rib 32 a greatly affects the characteristics of the top plate 32 .

<因主补强肋32a的深度不同而引起的顶板32的最大挠度、最大Mises应力及共振转速的变化(没有副补强肋34)><Changes in maximum deflection, maximum Mises stress, and resonance rotational speed of top plate 32 due to difference in depth of main rib 32a (without sub-rib 34)>

表9:   主补强肋的深度(mm)   8.8   9.0   9.2   9.4   9.6   9.8   10.0   10.4   10.8   11.2   11.6   12.0   12.4   最大挠度   1.38   1.36   1.33   1.30   1.28   1.26   1.24   1.20   1.17   1.14   1.11   1.09   1.06   最大Mises应力   13.41   13.26   13.12   12.99   12.87   12.77   12.68   12.51   12.36   12.22   12.09   11.97   11.87   共振转速   902.0   909.0   916.0   922.0   927.0   933.0   938.0   947.6   956.0   964.0   971.0   978.0   984.0 Table 9: Depth of main reinforcing rib (mm) 8.8 9.0 9.2 9.4 9.6 9.8 10.0 10.4 10.8 11.2 11.6 12.0 12.4 Maximum deflection 1.38 1.36 1.33 1.30 1.28 1.26 1.24 1.20 1.17 1.14 1.11 1.09 1.06 Maximum Mises stress 13.41 13.26 13.12 12.99 12.87 12.77 12.68 12.51 12.36 12.22 12.09 11.97 11.87 Resonance speed 902.0 909.0 916.0 922.0 927.0 933.0 938.0 947.6 956.0 964.0 971.0 978.0 984.0

Claims (4)

1, a kind of top board structure of air conditioner installed at high place, this air conditioner comprises: the body housing of taking in fan and fan electromotor, heat exchanger, draining pump, switch-box; And be configured in this body housing end face, hang the top board of establishing described fan and fan electromotor, heat exchanger, draining pump, switch-box,
It is characterized in that, on described top board, be formed with central portion that is used for the supports fan motor and the peripheral part that is used to support described heat exchanger, and be formed with from the many piece reinforced ribs of this central portion, form the plane between each reinforced ribs to the radial extension of described peripheral part.
2, the top board structure of air conditioner installed at high place as claimed in claim 1 is characterized in that, is formed with stage portion on the support portion of the described heat exchanger that is positioned at described reinforced ribs periphery.
3, the top board structure of air conditioner installed at high place as claimed in claim 1 or 2 is characterized in that, the support portion that is positioned at the described fan electromotor of described top board central portion is provided with described reinforced ribs.
As the top board structure of each described air conditioner installed at high place in the claim 1 to 3, it is characterized in that 4, the thickness of slab of described top board is more than 0.6mm and less than 0.8mm.
CNB2005800170393A 2004-06-17 2005-06-15 Top plate structure for air conditioner installed at high place Active CN100483034C (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP179871/2004 2004-06-17
JP2004179871A JP2006003011A (en) 2004-06-17 2004-06-17 Top plate structure of a high-altitude air conditioner

Publications (2)

Publication Number Publication Date
CN1957209A true CN1957209A (en) 2007-05-02
CN100483034C CN100483034C (en) 2009-04-29

Family

ID=35509777

Family Applications (1)

Application Number Title Priority Date Filing Date
CNB2005800170393A Active CN100483034C (en) 2004-06-17 2005-06-15 Top plate structure for air conditioner installed at high place

Country Status (4)

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

Cited By (2)

* 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 Fan and grille assembly
CN106152439A (en) * 2014-12-31 2016-11-23 Lg电子株式会社 Air-supply arrangement and there is the air conditioner of this air-supply arrangement

Families Citing this family (6)

* 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
JP4884781B2 (en) * 2006-01-17 2012-02-29 三菱重工業株式会社 Cabinet for air conditioner and air conditioner using the same
JP4582818B2 (en) * 2006-04-28 2010-11-17 東芝キヤリア株式会社 Indoor unit of air conditioner
JP6323143B2 (en) * 2014-04-22 2018-05-16 新日鐵住金株式会社 Indoor unit top plate
KR102396941B1 (en) * 2015-08-13 2022-05-13 엘지전자 주식회사 Indoor unit for air conditoiner
KR102201289B1 (en) * 2018-11-06 2021-01-08 엘지전자 주식회사 Indoor Unit for Air Conditioner

Family Cites Families (2)

* 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
JP3367607B2 (en) 2000-11-10 2003-01-14 株式会社日立製作所 Air conditioner indoor unit

Cited By (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 Fan and grille assembly
CN106152439A (en) * 2014-12-31 2016-11-23 Lg电子株式会社 Air-supply arrangement and there is the air conditioner of this air-supply arrangement
CN106152439B (en) * 2014-12-31 2019-05-28 Lg电子株式会社 Air supply device and air regulator with the air supply device

Also Published As

Publication number Publication date
CN100483034C (en) 2009-04-29
EP1775518A1 (en) 2007-04-18
JP2006003011A (en) 2006-01-05
EP1775518B1 (en) 2018-06-06
WO2005124238A1 (en) 2005-12-29

Similar Documents

Publication Publication Date Title
US20080159848A1 (en) Top Plate Structure for High Location Installation Type Air Conditioner
CN1131970C (en) Air regulator
CN1782568A (en) Outdoor unit of air conditioner
CN1676947A (en) Air supply device
US7805957B2 (en) Top plate structure for air conditioner installed at high location
CN1847735A (en) Indoor unit of air conditioner
CN1957209A (en) Roof structure of high-altitude air conditioner
CN1143988C (en) Split type air conditioner and method for assembling indoor unit
CN1089346A (en) Portable dehumidifier
CN1243231A (en) Air conditioner, mounting structural member, and mounting method for air conditioner
CN100335849C (en) Indoor unit for air conditioner
CN1143996C (en) Air conditioner motor installation structure
CN2807095Y (en) Scroll casing of centrifugal blower, centrifugal blower and indoor unit of air conditioner
CN1097197C (en) Air-conditioner
CN101061354A (en) Air-conditioner
CN1299069C (en) Outdoor unit of refrigerator, and electrical equipment box of outdoor unit
JP4884781B2 (en) Cabinet for air conditioner and air conditioner using the same
CN2536950Y (en) Air conditioner
CN101078540A (en) Indoor unit of air conditioner
CN1303325C (en) Packaged Compressor
CN100344909C (en) Electric motor installing structure of unitary air conditioner
CN1755241A (en) Integrated air conditioner
CN1553094A (en) Indoor air flow guiding structure of unitary air conditioner
CN101078536A (en) Indoor unit of air conditioner
CN1553087A (en) Shielding assembly installing structure of unitary air conditioner

Legal Events

Date Code Title Description
C06 Publication
PB01 Publication
C10 Entry into substantive examination
SE01 Entry into force of request for substantive examination
C14 Grant of patent or utility model
GR01 Patent grant