JPS6316179A - Noise damping device for compressor - Google Patents
Noise damping device for compressorInfo
- Publication number
- JPS6316179A JPS6316179A JP15903586A JP15903586A JPS6316179A JP S6316179 A JPS6316179 A JP S6316179A JP 15903586 A JP15903586 A JP 15903586A JP 15903586 A JP15903586 A JP 15903586A JP S6316179 A JPS6316179 A JP S6316179A
- Authority
- JP
- Japan
- Prior art keywords
- accumulator
- compression element
- compressor
- straight pipe
- suction port
- 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
Links
- 238000013016 damping Methods 0.000 title claims description 6
- 230000006835 compression Effects 0.000 claims abstract description 26
- 238000007906 compression Methods 0.000 claims abstract description 26
- 239000000463 material Substances 0.000 claims abstract description 11
- 230000000694 effects Effects 0.000 description 3
- 229910000831 Steel Inorganic materials 0.000 description 2
- 230000002159 abnormal effect Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000005284 excitation Effects 0.000 description 2
- 239000002184 metal Substances 0.000 description 2
- 239000010959 steel Substances 0.000 description 2
- 235000000139 Musa basjoo Nutrition 0.000 description 1
- 240000000569 Musa basjoo Species 0.000 description 1
- 230000001133 acceleration Effects 0.000 description 1
- 230000002238 attenuated effect Effects 0.000 description 1
- 230000000052 comparative effect Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000004804 winding Methods 0.000 description 1
Landscapes
- Compressor (AREA)
Abstract
Description
【発明の詳細な説明】
産業上の利用分野
本発明は、空気調和機等に用いられるアキュムレータを
具備した圧縮機の騒音減衰装置に関する。DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The present invention relates to a noise damping device for a compressor equipped with an accumulator used in an air conditioner or the like.
従来の技術
従来、この種の密閉型回転圧縮機は第4図に示すように
、圧縮要素1と電動要素2を内蔵した密閉容器3に、前
記圧縮要素1の吸入ポート部4に曲管5等を介してアキ
ュムレータ6を連結し、前記アキュムレータ6の取り付
は用金具7を用いて・このアキュムレータ6を前記密閉
容器3のアキュムレータ取付台8に連結する構造であっ
た。2. Description of the Related Art Conventionally, as shown in FIG. 4, this type of hermetic rotary compressor has a hermetic container 3 containing a compression element 1 and an electric element 2, and a bent pipe 5 connected to the suction port 4 of the compression element 1. The accumulator 6 was connected to the accumulator mounting base 8 of the closed container 3 using a metal fitting 7 to attach the accumulator 6.
発明が解決しようとする問題点
このような従来の圧縮機においては、前記圧縮要素1お
よび前記電動要素2から発生する振動成分により前記圧
縮要素1および前記電動要素2を内蔵した密閉容器3、
前記圧縮要素1の吸入ポート部4に連なる曲管部5、前
記アキュムレータ6およびアキュムレータ6の内部へ延
出した直管部9からなる振動系が、前記直管部9におい
て軸に対して直角な方向に共振を起こし、特定の周波数
で異常騒、音を発生させる問題があった。Problems to be Solved by the Invention In such a conventional compressor, vibration components generated from the compression element 1 and the electric element 2 cause damage to the airtight container 3 containing the compression element 1 and the electric element 2,
A vibration system consisting of a bent pipe section 5 connected to the suction port section 4 of the compression element 1, the accumulator 6, and a straight pipe section 9 extending into the inside of the accumulator 6 is configured to vibrate at right angles to the axis in the straight pipe section 9. There was a problem in that it caused resonance in the direction and generated abnormal noise and sound at specific frequencies.
これを防止するため、従来は、この直管部9の材質、お
よび設計寸法を変更することにより、また前記アキュム
レータ6の側壁部1oにダンピング材11等を貼付ける
ことにより、前記振動系の剛性等を調節したり、また前
記振動系にて異常騒音が放射しにくいようにして、前記
振動系が特定周波数域で共振の生じることのないよう(
こ設計が行われているが、圧縮機の性能上、製造上、あ
るいはコスト上の問題により、簡単にこれらを調節する
ことができないという問題点があった。In order to prevent this, conventionally, the rigidity of the vibration system has been improved by changing the material and design dimensions of the straight pipe section 9 and by pasting damping material 11 or the like on the side wall section 1o of the accumulator 6. etc., or to make it difficult for the vibration system to radiate abnormal noise so that the vibration system does not resonate in a specific frequency range (
Although this design has been implemented, there is a problem in that these cannot be easily adjusted due to problems in the performance, manufacturing, or cost of the compressor.
本発明は前記従来の欠点に鑑みてなされたもので、きわ
めて簡単な手段によってアキュムレータから発生する騒
音、振動を低減することを目的とする。The present invention has been made in view of the above-mentioned drawbacks of the conventional art, and it is an object of the present invention to reduce noise and vibration generated from an accumulator by extremely simple means.
問題点を解決するための手段
この目的を達成するための構成として、本発明は密閉容
器の内部に圧縮要素と電動要素を内蔵し、一端を前記圧
縮要素の吸入口に接続し、他端を前記密閉容器の外方に
設けられたアキュムレータ内部に直管部として延出した
曲管を設け、前記アキュムレータ外周部にコイル状のバ
ネ材を巻きつけ固定したものである。Means for Solving the Problems To achieve this object, the present invention incorporates a compression element and an electric element inside a closed container, one end of which is connected to the suction port of the compression element, and the other end of which is connected to the inlet of the compression element. A curved pipe extending as a straight pipe is provided inside the accumulator provided outside the airtight container, and a coiled spring material is wound and fixed around the outer periphery of the accumulator.
作 用
上記構成により、密閉容器と圧縮要素の吸入口からアキ
ュムレータ内に延出した直管と、アキュムレータとから
なる振動系の軸に直角方向の振動応答特性の向上がはか
れる。Operation With the above configuration, it is possible to improve the vibration response characteristics in the direction perpendicular to the axis of the vibration system consisting of the accumulator and the straight pipe extending from the airtight container and the inlet of the compression element into the accumulator.
実施例
以下、本発明をその一実施例を示す添付図面の第1図を
参考に説明する。EXAMPLE Hereinafter, the present invention will be explained with reference to FIG. 1 of the accompanying drawings showing one example thereof.
第1図において、3は密閉容器で、周知の構造からなる
圧縮要素1および電動要素2を内蔵している。5は前記
圧縮要素1に連なる曲管、6は周知の構成からなるアキ
ュムレータであり、前記アキュムレータ6の内部は、前
記曲管5を介して前記圧縮要素1の吸入口4と連結され
、また前記密閉容器3の外周部に溶接されているアキュ
ムレータ取付用の台8ヘアキュムレータ取付用金具7を
介して固定されている。9は一端が前記曲管5と連結さ
れ、他端が前記アキュムレータ6の内部へ延出した直管
部、12はコイル状のバネ材で前記アキュムレータ6の
外周部に巻きつけ固定している。In FIG. 1, reference numeral 3 denotes a closed container, which houses a compression element 1 and an electric element 2 having a well-known structure. 5 is a bent pipe connected to the compression element 1; 6 is an accumulator having a well-known configuration; the inside of the accumulator 6 is connected to the suction port 4 of the compression element 1 via the bent pipe 5; An accumulator mounting stand 8 welded to the outer periphery of the airtight container 3 is fixed via a hair accumulator mounting metal fitting 7. Reference numeral 9 is a straight pipe portion whose one end is connected to the bent pipe 5 and the other end extends into the inside of the accumulator 6. Reference numeral 12 is a coiled spring material that is wound around the outer periphery of the accumulator 6 and fixed thereto.
上記構成において、公称出力が500ワツトから150
0ワツトの密閉形回転圧縮機を使用し、外径が約50ミ
リメートル、板厚が約0.8ミリメートル程度で材質が
鋼材からなるアキュムレータ5を使用し、また直管部8
を外径が約14ミリメートル、板厚が約1ミリメートル
程度で材質を鋼管とし、さらに前記アキュムレータ6の
外周部に線径が約1ミリメートル程度のコイル状のバネ
材12を巻きつけ固定した場合の前記振動系の振動応答
特性の実験を行った結果、第2図の実線で示す特性が得
られた。これは、圧縮要素1と電動要素2を内蔵する密
閉容器3にて、圧縮要素1の吸入口4近傍を密閉容器3
の軸に対して、直角な半径方向に加振した場合の、加振
方向と同一方向のアキュムレータ側壁の振動応答特性で
ある。ここで破線は従来例を示し、縦軸に振動応答レベ
ル(加速度/力)を、横軸に周波数をとっている。In the above configuration, the nominal output is from 500 watts to 150 watts.
A 0 watt hermetic rotary compressor is used, and an accumulator 5 made of steel with an outer diameter of about 50 mm and a plate thickness of about 0.8 mm is used, and a straight pipe section 8 is used.
is made of a steel pipe with an outer diameter of about 14 mm, a plate thickness of about 1 mm, and a coiled spring material 12 with a wire diameter of about 1 mm is wound around the outer periphery of the accumulator 6 and fixed. As a result of conducting an experiment on the vibration response characteristics of the vibration system, the characteristics shown by the solid line in FIG. 2 were obtained. This is done by connecting the vicinity of the suction port 4 of the compression element 1 to the airtight container 3 that contains the compression element 1 and the electric element 2.
This is the vibration response characteristic of the accumulator side wall in the same direction as the excitation direction when the vibration is applied in the radial direction perpendicular to the axis of . Here, the broken line indicates the conventional example, with the vertical axis representing the vibration response level (acceleration/force) and the horizontal axis representing the frequency.
この振動応答特性において、800Hzから1800H
z程度までの周波数域および2200Hzから3500
Hz程度までの周波数域は密閉形回転圧縮機を50Hz
および60Hz、電動周波数で運転した場合において発
生する密閉形回転圧縮機の加振力の500Hz以上の高
周波成分で特に大きい周波数域であり、騒音特性として
重要視されている周波数域である。In this vibration response characteristic, from 800Hz to 1800H
Frequency range up to about z and from 2200Hz to 3500Hz
For the frequency range up to about Hz, the hermetic rotary compressor can be used at 50Hz.
and 60 Hz, which is a particularly large frequency range of high frequency components of 500 Hz or more of the excitation force of the hermetic rotary compressor that is generated when operating at an electric frequency, and is a frequency range that is considered important as a noise characteristic.
しかしながら、第2図から明らかなように、本実施例に
おいては、上記周波数帯域で総体的に振動応答レベルが
下がり、しかも前記振動系の共振が他の周波数域へ大き
く移動している。また第4図に示す密閉形圧縮機の騒音
周波数特性においても従来例を示す破線特性に比較して
2500Hzの周波数成分が大きく減衰している。However, as is clear from FIG. 2, in this embodiment, the vibration response level is generally lowered in the above frequency band, and moreover, the resonance of the vibration system has largely moved to other frequency ranges. Also, in the noise frequency characteristic of the hermetic compressor shown in FIG. 4, the frequency component of 2500 Hz is greatly attenuated compared to the broken line characteristic showing the conventional example.
すなわち、実施例のごとく、圧縮要素1および電動要素
2を内蔵した密閉容器3、圧縮要素1の吸入口4に連な
る曲管5、アキュムレータ側壁、およびアキュムレータ
6の内部へ延出した直管部8からなる振動系において、
前記アキュムレータ6の外周部にコイル状のバネ材12
を巻きつけ固定することにより、上記振動系で軸に直角
な方向の共振を特定の周波数域において調節することが
できる。That is, as in the embodiment, the airtight container 3 containing the compression element 1 and the electric element 2, the bent pipe 5 connected to the suction port 4 of the compression element 1, the accumulator side wall, and the straight pipe part 8 extending into the inside of the accumulator 6. In a vibration system consisting of
A coiled spring material 12 is provided on the outer periphery of the accumulator 6.
By winding and fixing the vibration system, resonance in a direction perpendicular to the axis can be adjusted in a specific frequency range.
発明の効果
本発明における圧縮機の騒音減衰装置は、密閉容器の内
部に圧縮要素と電動要素を内蔵し、一端を前記圧縮要素
の吸入口に接続し、他端を前記密閉容器の外方に設けら
れたアキュムレータ内部に直管部として延出した曲管を
設け、前記アキュムレータ外周部にコイル状のバネ材を
巻きつけ固定したもので、前記圧縮要素および電動要素
を内蔵した密閉容器と、前記圧縮要素の吸入口からアキ
ュムレータ内に延出した直管と、アキュムレータとから
なる振動系の軸に直角方向の振動応答特性の向上がはか
られ、より静かな圧縮効果が得られ、しかもアキュムレ
ータ外周部にコイル状のバネ材を巻きつけているため、
アキュムレータ部が大形化することもなく、さらに構造
もきわめて簡素であるなど、優れた効果を奏するもので
ある。Effects of the Invention The compressor noise attenuation device according to the present invention has a compression element and an electric element built into a sealed container, one end of which is connected to the suction port of the compression element, and the other end of which is connected to the outside of the sealed container. A bent pipe extending as a straight pipe part is provided inside the provided accumulator, and a coiled spring material is wound and fixed around the outer periphery of the accumulator, and the airtight container contains the compression element and the electric element; The vibration response characteristics in the direction perpendicular to the axis of the vibration system consisting of the accumulator and the straight pipe extending from the suction port of the compression element into the accumulator have been improved, resulting in quieter compression effects and even lower Because a coiled spring material is wrapped around the
The accumulator part does not become large in size, and the structure is extremely simple, resulting in excellent effects.
第1図は本発明の一実施例における圧縮機の騒音減衰装
置を示す縦断面図、第2図は本実施例と従来例における
振動応答レベルの比較特性図、第3図は本実施例と従来
例における圧縮機の騒音比較特性図、第4図は従来の圧
縮機の騒音減衰装置を示す縦断面図である。
1・−・・圧縮要素、2・・・・・・電動要素、3・・
・・密閉容器、5・・・・曲管、6 ・・アキュムレー
タ、9・・・直管部、12・・・・・コイル状のバネ材
。
代理人の氏名 弁理士 中 尾 敏 男 ほか1名1−
−一疋粗婆欺
5−−一典 管
6−−−アヤユムレータ
ノ2−−−コイル:医のバネ主オ
第2図
(d8)
黒洩奴(KHz)
第3図
扇選a(Hy−)Fig. 1 is a longitudinal cross-sectional view showing a noise damping device for a compressor according to an embodiment of the present invention, Fig. 2 is a comparative characteristic diagram of vibration response levels between this embodiment and a conventional example, and Fig. 3 is a comparison characteristic diagram of the vibration response level of this embodiment and a conventional example. FIG. 4 is a longitudinal sectional view showing a noise damping device for a conventional compressor. 1... Compression element, 2... Electric element, 3...
... airtight container, 5 ... bent pipe, 6 ... accumulator, 9 ... straight pipe section, 12 ... coiled spring material. Name of agent: Patent attorney Toshio Nakao and 1 other person1-
-Ichihiki Basho Deception 5--Ikunori Tube 6--Ayayumuratano 2--Coil: Medical Spring Main O Figure 2 (d8) Kurokoro (KHz) Figure 3 Fan Selection a (Hy-)
Claims (1)
を前記圧縮要素の吸入口に接続し、他端を前記密閉容器
の外方に設けられたアキュムレータ内部に直管部として
延出した曲管を設け、前記アキュムレータ外周部にコイ
ル状のバネ材を巻きつけ固定した圧縮機の騒音減衰装置
。A compression element and an electric element are built into the airtight container, one end of which is connected to the inlet of the compression element, and the other end of which extends as a straight pipe into an accumulator provided outside of the airtight container. A noise damping device for a compressor, in which a pipe is provided, and a coiled spring material is wound and fixed around the outer periphery of the accumulator.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP15903586A JPS6316179A (en) | 1986-07-07 | 1986-07-07 | Noise damping device for compressor |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP15903586A JPS6316179A (en) | 1986-07-07 | 1986-07-07 | Noise damping device for compressor |
Publications (1)
Publication Number | Publication Date |
---|---|
JPS6316179A true JPS6316179A (en) | 1988-01-23 |
Family
ID=15684826
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP15903586A Pending JPS6316179A (en) | 1986-07-07 | 1986-07-07 | Noise damping device for compressor |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS6316179A (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR100504908B1 (en) * | 2002-09-10 | 2005-07-29 | 엘지전자 주식회사 | Vibration reducing structure for compressor by accumulator |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5898677A (en) * | 1981-12-09 | 1983-06-11 | Matsushita Electric Ind Co Ltd | Noise attenuating device for enclosed type rotary compressor |
-
1986
- 1986-07-07 JP JP15903586A patent/JPS6316179A/en active Pending
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5898677A (en) * | 1981-12-09 | 1983-06-11 | Matsushita Electric Ind Co Ltd | Noise attenuating device for enclosed type rotary compressor |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR100504908B1 (en) * | 2002-09-10 | 2005-07-29 | 엘지전자 주식회사 | Vibration reducing structure for compressor by accumulator |
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