JPH0693968A - Compressor - Google Patents

Compressor

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Publication number
JPH0693968A
JPH0693968A JP24054692A JP24054692A JPH0693968A JP H0693968 A JPH0693968 A JP H0693968A JP 24054692 A JP24054692 A JP 24054692A JP 24054692 A JP24054692 A JP 24054692A JP H0693968 A JPH0693968 A JP H0693968A
Authority
JP
Japan
Prior art keywords
compressor
resonance
refrigerant
mode
spatial resonance
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
JP24054692A
Other languages
Japanese (ja)
Other versions
JP3098870B2 (en
Inventor
Noriyuki Fujiwara
憲之 藤原
Masaru Nagaike
勝 長池
Kazuaki Iwao
和章 巌
Takao Yoshimura
多佳雄 吉村
Takashi Koyama
隆 小山
Hironari Akashi
浩業 明石
Ko Inagaki
耕 稲垣
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.)
Panasonic Holdings Corp
Original Assignee
Matsushita Refrigeration Co
Matsushita Electric Industrial Co 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 Matsushita Refrigeration Co, Matsushita Electric Industrial Co Ltd filed Critical Matsushita Refrigeration Co
Priority to JP04240546A priority Critical patent/JP3098870B2/en
Publication of JPH0693968A publication Critical patent/JPH0693968A/en
Application granted granted Critical
Publication of JP3098870B2 publication Critical patent/JP3098870B2/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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  • Compressor (AREA)

Abstract

PURPOSE:To provide a compressor which is prevented from the generation of high noise by amplifying pulsation noise of a refrigerant during operation through resonance of a space in a compressor. CONSTITUTION:Both or one of a suction port 3 and a delivery port 4 for a refrigerant is set to a plural number and arranged on the nodes 5 and 6 of a mode where space resonance of the space of an outer sell 1 occurs and in relation to the node of other mode 7, the suction ports are formed in positions symmetrical to each other.

Description

【発明の詳細な説明】Detailed Description of the Invention

【0001】[0001]

【産業上の利用分野】本発明は、冷媒の凝縮,膨脹によ
る冷凍サイクルにより冷凍効果を実現する際に冷媒を圧
縮する圧縮機に関するものである。
BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a compressor for compressing a refrigerant when realizing a refrigerating effect by a refrigerating cycle by condensing and expanding the refrigerant.

【0002】[0002]

【従来の技術】近年、冷蔵庫,空調機器等において低騒
音化が望まれている。そこで、圧縮機についても高効率
化と共に低騒音化が強く望まれている。
2. Description of the Related Art In recent years, noise reduction has been desired in refrigerators, air conditioners and the like. Therefore, it is strongly demanded that the compressor also have high efficiency and low noise.

【0003】以下に従来の圧縮機について説明する。こ
こではレシプロ方式の圧縮機について説明するが、基本
的には他の方式、例えば、ロータリーピストン方式や、
スクロール方式の圧縮機についても同様である。
A conventional compressor will be described below. Here, a reciprocating type compressor will be described, but basically, another type, for example, a rotary piston type or
The same applies to the scroll type compressor.

【0004】従来の圧縮機は図2aの側面断面図および
図2bの上面断面図に示すように、例えば略円筒状の外
殻1とその内部に設置された冷媒圧縮用の機械部2、冷
媒を機械部に吸い込む吸込口3、冷媒を外殻1の内部空
間に開放する吐出口4等から構成されていた。
As shown in the side sectional view of FIG. 2a and the top sectional view of FIG. 2b, a conventional compressor has, for example, a substantially cylindrical outer shell 1 and a mechanical portion 2 for compressing a refrigerant installed in the outer shell 1 and a refrigerant. And a discharge port 4 for opening the refrigerant into the inner space of the outer shell 1.

【0005】以上のように構成された圧縮機において、
運転時、吸込口3から機械部2に取り込まれた冷媒は機
械部2内部で圧縮され、冷凍サイクルの次の工程へ送ら
れていた。また、冷凍サイクルを終え圧縮工程まで戻っ
てきた冷媒は吐出口4から外殻1の内部空間に開放さ
れ、ふたたび圧縮工程に移っていた。
In the compressor configured as described above,
During operation, the refrigerant taken into the mechanical section 2 from the suction port 3 was compressed inside the mechanical section 2 and sent to the next step of the refrigeration cycle. Further, the refrigerant that has finished the refrigeration cycle and returned to the compression step is released from the discharge port 4 into the internal space of the outer shell 1 and again moves to the compression step.

【0006】このような従来の構成においては、運転時
の機械部2での冷媒の圧縮工程における繰り返し運動が
冷媒の脈動となり、それが脈動音として吸込口3あるい
は吐出口4から放出され、騒音源となっていた。
[0006] In such a conventional structure, the repetitive motion in the compression process of the refrigerant in the mechanical section 2 during operation becomes the pulsation of the refrigerant, which is emitted as pulsating sound from the suction port 3 or the discharge port 4 to cause noise. Was the source.

【0007】また、外殻1の内部空間のような空間はそ
の形状,容積,内部に存在する気体等の条件から決まる
空間共鳴周波数を持っている。この空間共鳴について図
3〜図7を用いて説明する。簡単のために空間形状は図
3に示すような直方体とする。このような空間の場合、
1次の空間共鳴は図4に示すようなモードになる。ここ
で中央付近にある面8はモードの節に当たる部分であ
り、空間共鳴状態においてこの部分の音圧は理論上0と
なる。また、この節の両側では節から遠ざかるにつれて
音圧が高くなり節から最も遠い位置で最も音圧が高くな
る。なお、節の両側で音圧の絶対値は等しく変化してい
くが位相については逆になる。2次,3次の空間共鳴モ
ードは図5,図6に示す通りで基本的な現象は1次のモ
ードと同じである。4次以上では例えば図7に示す4次
のモードのように節11が複数個存在するような複雑な
モードになっていく。
A space such as the inner space of the outer shell 1 has a spatial resonance frequency determined by conditions such as its shape, volume and gas existing inside. This spatial resonance will be described with reference to FIGS. For simplicity, the space shape is a rectangular parallelepiped as shown in FIG. In such a space,
The first-order spatial resonance has a mode as shown in FIG. Here, the surface 8 near the center is a portion corresponding to a mode node, and the sound pressure in this portion is theoretically zero in the spatial resonance state. Further, on both sides of this node, the sound pressure becomes higher as the distance from the node increases, and the sound pressure becomes highest at the position farthest from the node. The absolute value of sound pressure changes equally on both sides of the node, but the phases are opposite. The secondary and tertiary spatial resonance modes are as shown in FIGS. 5 and 6, and the basic phenomenon is the same as the primary mode. In the fourth and higher modes, for example, the fourth mode shown in FIG. 7 becomes a complicated mode in which a plurality of nodes 11 exist.

【0008】このような空間内に音源が存在する場合、
その音源の位置により騒音の増幅の度合いが変化する。
即ち、図4に示す1次のモードの場合、音源が節8に近
い場所にあればこの周波数の騒音は増幅されることはな
いが、音源位置が節8から離れるに従って騒音の増幅が
大きくなる。
When a sound source exists in such a space,
The degree of amplification of noise changes depending on the position of the sound source.
That is, in the case of the first-order mode shown in FIG. 4, if the sound source is located near the node 8, the noise of this frequency will not be amplified, but the amplification of the noise will increase as the sound source position moves away from the node 8. .

【0009】[0009]

【発明が解決しようとする課題】しかしながらこのよう
な従来の構成においては、騒音源となる吸込口あるいは
吐出口の位置が内部空間の空間共鳴と無関係に決められ
ていたため、内部空間の空間共鳴の節からはずれた位置
にあり、運転時に脈動音が発生した場合、脈動周波数の
倍調周波数と空間共鳴周波数が近いと空間共鳴により脈
動音が増幅され、大きな騒音となるという課題があっ
た。
However, in such a conventional structure, since the position of the suction port or the discharge port, which is a noise source, is determined independently of the spatial resonance of the internal space, the spatial resonance of the internal space is suppressed. When a pulsating sound is generated at a position deviating from the node during driving, if the harmonic frequency of the pulsating frequency is close to the spatial resonance frequency, the pulsating sound is amplified due to the spatial resonance, which causes a problem of large noise.

【0010】以上の事情に鑑み、本発明は、運転時に外
殻の内部空間の共鳴により脈動音が増幅され大きな騒音
となることのない圧縮機を提供することを課題とする。
In view of the above circumstances, it is an object of the present invention to provide a compressor in which the pulsating sound is not amplified by the resonance of the inner space of the outer shell to cause a large noise during operation.

【0011】[0011]

【課題を解決するための手段】上記課題を解決するため
の、本発明の技術的手段は、圧縮機内部の冷媒の吸込口
および吐出口の両方あるいはどちらか一方を複数にし、
圧縮機内部空間の空間共鳴による脈動音の増幅を防止す
る位置に設置することを特徴とする。
Means for Solving the Problems The technical means of the present invention for solving the above-mentioned problems is to provide a plurality of refrigerant suction ports and / or discharge ports inside a compressor,
The compressor is characterized in that it is installed at a position that prevents amplification of pulsating sound due to spatial resonance in the internal space of the compressor.

【0012】[0012]

【作用】この技術的手段による作用は以下のようにな
る。運転時に音源となる吸込口あるいは吐出口の両方あ
るいは一方を複数にし、問題となる空間共鳴モードのう
ちのあるモードの節の位置でありかつ他のモードの節に
関して対称な位置になるように設置する。これにより、
音源を節上に設置したモードについては共鳴による増幅
が起こらず、節に関して対称な位置に音源を設置したモ
ードについてはちょうど逆位相の位置に音源があるた
め、共鳴による増幅が起こってもお互いに逆位相の音に
より打ち消し合うことになり結果として騒音の増幅は防
止できる。
The operation of this technical means is as follows. Install both or one of the suction ports and / or the discharge ports that are the sound source during operation so that they are located at the node of one mode of the spatial resonance modes in question and symmetrically with respect to the nodes of other modes. To do. This allows
Amplification due to resonance does not occur in the mode where the sound source is installed on the node, and there is a sound source at the opposite phase position for the mode where the sound source is installed in a symmetrical position with respect to the node. Noises of opposite phases cancel each other out, and as a result, amplification of noise can be prevented.

【0013】[0013]

【実施例】以下、本発明の実施例について図を参照しな
がら説明する。図1aは本発明の実施例における圧縮機
の側面断面図、図1bは上面断面図である。図1におい
て1は圧縮機の外殻、2は機械部、3は冷媒の吸込口、
4は冷媒の吐出口である。また、5,6,7はそれぞれ
外殻1の内部空間の空間共鳴の1次,2次,3次のモー
ドの節である。
Embodiments of the present invention will be described below with reference to the drawings. 1a is a side sectional view of a compressor in an embodiment of the present invention, and FIG. 1b is a top sectional view. In FIG. 1, 1 is an outer shell of a compressor, 2 is a mechanical part, 3 is a suction port of a refrigerant,
Reference numeral 4 is a refrigerant discharge port. Reference numerals 5, 6 and 7 are nodes of the first, second and third modes of spatial resonance in the inner space of the outer shell 1, respectively.

【0014】以上のように構成された圧縮機において、
運転時の圧縮工程により冷媒の脈動が起こり、吸込口3
から脈動音が発生する。このとき、吸込口3が内部空間
の空間共鳴に1次のモードの節5および2次のモードの
節6上に設置されているため、脈動の倍調周波数が空間
共鳴の周波数と近いあるいは一致した場合でもこれらの
空間共鳴は励起されず、従って空間共鳴により脈動音が
増幅され騒音が大きくなることはない。また、空間共鳴
の3次のモードについては、吸込口3が内部空間の空間
共鳴の3次モードの節7からずれた位置にあるため、空
間共鳴により脈動音が増幅される可能性がある。しか
し、吸込口3が3次のモードの節7に関して対称な位置
に設置されているため、空間共鳴により位相が逆で大き
さが同じである2つのモードが励起され、それらがお互
いに打ち消し合い結果として脈動による騒音の発生を防
止することができる。本実施例においては吸込口3につ
いてのみ複数にし、空間共鳴による脈動音の増幅を防止
する位置に設置したが、吐出口4からの脈動音のレベル
が吸込口3からの脈動音のレベルと同等あるいは大きい
ような場合については吐出口4についても同様にすれば
よい。また、本実施例においては吸込口3について示し
たが、同様の効果が得られるのであれば、吐出口4のみ
あるいは吸込口3,吐出口4の両方についての場合であ
ってもよいことは言うまでもない。
In the compressor configured as described above,
The pulsation of the refrigerant occurs due to the compression process during operation, and the suction port 3
Pulsating sound is generated from. At this time, since the suction port 3 is installed on the node 5 of the first-order mode and the node 6 of the second-order mode for the spatial resonance of the internal space, the double-frequency of the pulsation is close to or equal to the frequency of the spatial resonance. Even in this case, these spatial resonances are not excited, so that the pulsating sound is not amplified by the spatial resonance and the noise is not increased. Regarding the third-order mode of spatial resonance, since the suction port 3 is located at a position displaced from the node 7 of the third-order mode of spatial resonance in the internal space, the pulsating sound may be amplified by the spatial resonance. However, since the suction port 3 is installed symmetrically with respect to the node 7 of the third-order mode, two modes having opposite phases and the same magnitude are excited by spatial resonance, and they cancel each other out. As a result, generation of noise due to pulsation can be prevented. In the present embodiment, only a plurality of suction ports 3 are provided and installed at a position where amplification of pulsating sound due to spatial resonance is prevented. However, the level of pulsating sound from the discharge port 4 is equal to the level of pulsating sound from the suction port 3. Alternatively, in the case of a large size, the same applies to the discharge port 4. Further, although the suction port 3 is shown in the present embodiment, it is needless to say that only the discharge port 4 or both the suction port 3 and the discharge port 4 may be provided as long as the same effect can be obtained. Yes.

【0015】以上のように、本実施例によれば空間共鳴
による脈動音の増幅が防止でき、運転時の騒音の増大を
防止することができる。
As described above, according to this embodiment, the amplification of the pulsating sound due to the spatial resonance can be prevented, and the increase of the noise during operation can be prevented.

【0016】[0016]

【発明の効果】以上のように、本発明は、圧縮機内部の
冷媒の吸込口および吐出口の両方あるいはどちらか一方
を複数にし、圧縮機内部空間の空間共鳴による脈動音の
増幅を防止する位置に設置することにより、運転時の脈
動音の増大を防止し騒音の低減を図ることができる。
As described above, according to the present invention, a plurality of suction ports and / or discharge ports of the refrigerant inside the compressor are provided in plural, and the amplification of the pulsating sound due to the spatial resonance of the internal space of the compressor is prevented. By installing in a position, it is possible to prevent an increase in pulsating sound during operation and reduce noise.

【図面の簡単な説明】[Brief description of drawings]

【図1】(a)本発明の実施例における圧縮機の側面断
面図 (b)本発明の実施例における圧縮機の上面断面図
1A is a side sectional view of a compressor according to an embodiment of the present invention, and FIG. 1B is a top sectional view of a compressor according to an embodiment of the present invention.

【図2】(a)従来の圧縮機の側面断面図 (b)従来の圧縮機の上面断面図2A is a side sectional view of a conventional compressor, and FIG. 2B is a top sectional view of a conventional compressor.

【図3】空間共鳴の説明用の直方体箱の斜視図FIG. 3 is a perspective view of a rectangular parallelepiped box for explaining spatial resonance.

【図4】直方体箱の1次の空間共鳴における音圧分布の
概略図
FIG. 4 is a schematic diagram of sound pressure distribution in the first-order spatial resonance of a rectangular parallelepiped box.

【図5】直方体箱の2次の空間共鳴における音圧分布の
概略図
FIG. 5 is a schematic diagram of sound pressure distribution in the secondary spatial resonance of a rectangular parallelepiped box.

【図6】直方体箱の3次の空間共鳴における音圧分布の
概略図
FIG. 6 is a schematic diagram of sound pressure distribution in third-order spatial resonance of a rectangular parallelepiped box.

【図7】直方体箱の4次の空間共鳴における音圧分布の
概略図
FIG. 7 is a schematic diagram of sound pressure distribution in fourth-order spatial resonance of a rectangular parallelepiped box.

【符号の説明】[Explanation of symbols]

1 圧縮機の外殻 2 機械部 3 吸込口 4 吐出口 5,8 空間共鳴の1次のモードの節 6,9 空間共鳴の2次のモードの節 7,10 空間共鳴の3次のモードの節 11 空間共鳴の4次のモードの節 1 Outer shell of compressor 2 Mechanical part 3 Suction port 4 Discharge port 5,8 Spatial resonance first mode section 6,9 Spatial resonance second mode section 7,10 Spatial resonance third mode mode Clause 11 Clause of the fourth mode of spatial resonance

───────────────────────────────────────────────────── フロントページの続き (72)発明者 巌 和章 大阪府門真市大字門真1006番地 松下電器 産業株式会社内 (72)発明者 吉村 多佳雄 大阪府東大阪市高井田本通3丁目22番地 松下冷機株式会社内 (72)発明者 小山 隆 大阪府東大阪市高井田本通3丁目22番地 松下冷機株式会社内 (72)発明者 明石 浩業 大阪府東大阪市高井田本通3丁目22番地 松下冷機株式会社内 (72)発明者 稲垣 耕 大阪府東大阪市高井田本通3丁目22番地 松下冷機株式会社内 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Kazuaki Iwao 1006 Kadoma, Kadoma City, Osaka Prefecture Matsushita Electric Industrial Co., Ltd. (72) Inventor Takao Yoshimura 3-22, Takaidahondori, Higashiosaka, Osaka Matsushita Chiller Co., Ltd. (72) Inventor Takashi Oyama 3-22 Takaida Hondori, Higashi-Osaka City, Osaka Prefecture Matsushita Chiller Co., Ltd. (72) Kou Akashi 3-22, Takaida Hon-dori, Higashi Osaka City, Osaka Matsushita Chiller Co., Ltd. (72) Inventor Ko Inagaki 3-22 Takaidahondori, Higashi-Osaka City, Osaka Prefecture Matsushita Cold Machinery Co., Ltd.

Claims (1)

【特許請求の範囲】[Claims] 【請求項1】 圧縮機内部の冷媒の吸込口および吐出口
の両方あるいはどちらか一方を複数にし、圧縮機内部空
間の空間共鳴による脈動音の増幅を防止する位置に設置
することを特徴とする圧縮機。
1. A plurality of suction inlets and / or discharge outlets for the refrigerant inside the compressor are provided in plurality, and the refrigerant is installed at a position where amplification of pulsating sound due to spatial resonance in the internal space of the compressor is prevented. Compressor.
JP04240546A 1992-09-09 1992-09-09 Compressor Expired - Fee Related JP3098870B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP04240546A JP3098870B2 (en) 1992-09-09 1992-09-09 Compressor

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP04240546A JP3098870B2 (en) 1992-09-09 1992-09-09 Compressor

Publications (2)

Publication Number Publication Date
JPH0693968A true JPH0693968A (en) 1994-04-05
JP3098870B2 JP3098870B2 (en) 2000-10-16

Family

ID=17061139

Family Applications (1)

Application Number Title Priority Date Filing Date
JP04240546A Expired - Fee Related JP3098870B2 (en) 1992-09-09 1992-09-09 Compressor

Country Status (1)

Country Link
JP (1) JP3098870B2 (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1294357C (en) * 2002-10-30 2007-01-10 日立家用电器公司 Closed compressor and refrigerator using the same
WO2017163646A1 (en) * 2016-03-24 2017-09-28 株式会社神戸製鋼所 Package-type compressor

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1294357C (en) * 2002-10-30 2007-01-10 日立家用电器公司 Closed compressor and refrigerator using the same
WO2017163646A1 (en) * 2016-03-24 2017-09-28 株式会社神戸製鋼所 Package-type compressor

Also Published As

Publication number Publication date
JP3098870B2 (en) 2000-10-16

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