JPH0972279A - Compressor - Google Patents
CompressorInfo
- Publication number
- JPH0972279A JPH0972279A JP22814095A JP22814095A JPH0972279A JP H0972279 A JPH0972279 A JP H0972279A JP 22814095 A JP22814095 A JP 22814095A JP 22814095 A JP22814095 A JP 22814095A JP H0972279 A JPH0972279 A JP H0972279A
- Authority
- JP
- Japan
- Prior art keywords
- muffler
- compressor
- discharge
- resonance
- discharge 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
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/0027—Pulsation and noise damping means
- F04B39/0055—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressor (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は、冷媒の凝縮、膨張によ
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
音化が強く望まれている。そこで、これらに用いられる
圧縮機についても高効率化と共に低騒音化が望まれてい
る。2. Description of the Related Art In recent years, noise reduction has been strongly desired in refrigerators, air conditioners and the like. Therefore, it is desired that the compressors used for them 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
こではスクロール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、
レシプロ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 scroll type compressor will be described, but basically, other types, such as a rotary piston type,
The same applies to a reciprocating compressor.
【０００４】従来圧縮機の吐出部は図４の（ａ）（ｂ）
に示すように、例えば略円筒状の圧縮機外殻ａとその内
部に設置された冷媒圧縮用の圧縮機械部ｂ、圧縮機械部
ｂで圧縮した冷媒を吐出する吐出口ｃ、吐出された冷媒
を密閉するための脈動を抑える効果も加味した圧縮部外
殻ｄ、脈動音をさらに抑えるために圧縮部外殻ｄと吐出
口ｃとの間に設けられたマフラーｅ、圧縮され吐出され
た冷媒をマフラーｅと圧縮部外殻ｄとの間からシステム
内に送り出す吐出管ｆ等から構成されている。The discharge part of the conventional compressor is shown in FIGS.
As shown in, for example, a substantially cylindrical compressor shell a, a compression machine part b for compressing the refrigerant installed inside the compressor shell b, a discharge port c for discharging the refrigerant compressed by the compression machine part b, a discharged refrigerant The outer shell d of the compression part, which also has the effect of suppressing the pulsation for sealing the air, the muffler e provided between the outer shell d of the compression part and the discharge port c to further suppress the pulsating sound, and the compressed and discharged refrigerant. Is composed of a discharge pipe f and the like that feeds into the system from between the muffler e and the compression part outer shell d.
【０００５】圧縮機械部ｂでの圧縮行程の繰り返し運転
が冷媒に脈動を生じさせ、この脈動が脈動音として吐出
口ｃから放出され、騒音源となっている。マフラーｅは
これを抑えるために設けられ、吐出口ｃからの吐出冷媒
を狭い空間に閉じ込めながら、限られた大きさの吐出穴
ｇから圧縮部外殻ｄとの間の空間に吐出させることによ
って、脈動音が外部に出るのを抑えている。Repetitive operation of the compression stroke in the compression machine section b causes pulsation in the refrigerant, and this pulsation is emitted as pulsating sound from the discharge port c, which is a noise source. The muffler e is provided to suppress this, and the refrigerant discharged from the discharge port c is confined in a narrow space and is discharged from the discharge hole g having a limited size to the space between the outer shell d of the compression part. , Suppressing the pulsating sound to the outside.
【０００６】[0006]
【発明が解決しようとする課題】しかし、従来のマフラ
ー構造では必ずしも消音効果が十分であるとは云えず、
さらなる改良が望まれている。これにつき本発明者等は
種々検討したところ、脈動音を抑えるために設けられて
いる上記マフラーｅの内部空間はその形状、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５〜図１０を用いて
説明する。説明の簡単のために空間形状は図５に示すよ
うな直方体とする。直方体の寸法は横の長さをＬ１ 、
縦の長さをＬ2 とする。However, it cannot be said that the conventional muffler structure has a sufficient silencing effect.
Further improvements are desired. As a result of various investigations by the present inventors, the internal space of the muffler e provided to suppress the pulsating sound has a spatial resonance frequency determined by conditions such as its shape, volume, and gas present inside. There is. This spatial resonance will be described with reference to FIGS. For simplicity of explanation, the space shape is a rectangular parallelepiped as shown in FIG. The dimension of the rectangular parallelepiped is the lateral length L 1 ,
The vertical length is L 2 .
【０００７】このような空間の場合、１次の空間共鳴は
図６に示すようなモードになる。ここで、横方向Ｌ1 ／
２の位置にある面１３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。In such a space, the first-order spatial resonance has a mode as shown in FIG. Where L 1 /
The surface 13 located at the position 2 is a portion corresponding to the 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.
【０００８】２次モードについては図７に示すとおり
で、縦方向Ｌ2 ／２の位置に空間共鳴モードの節の面１
４ができる。[0008] The second mode is as shown in FIG. 7, the longitudinal direction L 2/2 sections of surface space resonant modes in position 1
You can do 4.
【０００９】また、図８に３次モード、図９に４次モー
ド、図１０に５次モードを示す。３次モードについて
は、縦方向に２つの節の面１５が両端からＬ1 ／４の位
置にでき、４次モードは十字に節の面１６が中央に、５
次モードは横方向に２つの節の面１７が両端からＬ2 ／
４の位置にできる。FIG. 8 shows a third-order mode, FIG. 9 shows a fourth-order mode, and FIG. 10 shows a fifth-order mode. For third order mode, a surface 15 of the two sections in the longitudinal direction can be at the position of L 1/4 from either end, order mode to the face 16 is a central section in a cross 4, 5
In the next mode, the surface 17 of the two nodes in the lateral direction is L 2 /
It can be in position 4.
【００１０】この様な空間内に音源が存在する場合、そ
の音源の位置によって発生する音の増幅の度合が変化す
る。即ち、図６に示す１次のモードの場合、音源が節１
３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１３から離れるに従って騒音
の増幅が大きくなる。また、外部に音を放出する場合で
あれば、その放出の穴が節１３に近い場所にあれば共鳴
の周波数の音は放出されず、節１３から離れるに従って
放出される音は大きくなる。When a sound source exists in such a space, the degree of amplification of the generated sound changes depending on the position of the sound source. That is, in the case of the primary mode shown in FIG.
If the position is close to 3, 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 13. Further, in the case of emitting sound to the outside, if the emission hole is near the node 13, the sound of the resonance frequency is not emitted, and the sound emitted increases as the distance from the node 13 increases.
【００１１】このような視点にて従来のマフラーｅを再
検討すると、騒音源となる吐出口ｃの位置がマフラー内
部空間の空間共鳴と無関係に決められている。また、マ
フラーｅ内の吐出穴ｇの位置もマフラー内部空間と無関
係に決められている。これらのため吐出口ｃや吐出穴ｇ
は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、マフラーｅの消音効果が著しく低下し大きな騒音
となるという課題があった。When the conventional muffler e is reexamined from such a viewpoint, the position of the discharge port c, which is a noise source, is determined irrespective of the spatial resonance of the internal space of the muffler. The position of the discharge hole g in the muffler e is also determined independently of the muffler internal space. Because of these, discharge port c and discharge hole g
Is at a position outside the node of the spatial resonance of the internal space, and if pulsating sound is generated during operation, if the harmonic frequency of the pulsating frequency is close to the spatial resonance frequency, the pulsating sound is amplified by the spatial resonance, and the muffler's muffling There was a problem that the effect was significantly reduced and the noise was loud.
【００１２】以上の事情に鑑み、本発明は、運転時にマ
フラーの内部空間の共鳴による脈動音の増幅によりマフ
ラーの消音効果が低下し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 which does not cause a large noise due to the reduction of the muffler muffling effect due to the amplification of the pulsating sound due to the resonance of the internal space of the muffler. To do.
【００１３】[0013]
【課題を解決するための手段】上記課題を解決するため
に本発明圧縮機は、圧縮機械部の吐出口のマフラーを中
心軸まわりで縦横方向について軸対称な形状にし、吐出
口がマフラー中央になるようにマフラーを設置すること
を主たる特徴とするものである。この場合、マフラーを
縦横の長さの異なる形状にしてマフラーの吐出穴をマフ
ラー空間共鳴の節の位置に開けるのが好適である。In order to solve the above-mentioned problems, the compressor of the present invention has a muffler of the discharge port of the compression machine section which is axially symmetrical about the central axis in the vertical and horizontal directions, and the discharge port is located at the center of the muffler. The main feature is to install a muffler so that In this case, it is preferable that the muffler is formed in a shape having different vertical and horizontal lengths and the discharge holes of the muffler are formed at the nodes of the muffler spatial resonance.
【００１４】さらに、マフラーが直方体に近く、縦方向
について両端からほぼ４分の１の位置、横方向について
両端からほぼ４分の１の位置に吐出穴ほぼを４分の１開
けるのが好適である。Further, it is preferable that the muffler is close to a rectangular parallelepiped, and the discharge holes are formed at a position of about a quarter from both ends in the vertical direction and at a position of about a quarter from both ends in the horizontal direction. is there.
【００１５】[0015]
【作用】本発明の圧縮機の主たる特徴の上記構成では、
マフラー形状を中心軸まわりで縦横方向について軸対称
にすることで幾つかあるマフラー内空間共鳴モードのう
ち節がマフラー中心を通るモードの数が多くなる。そこ
に、音源となる圧縮機械部の吐出口がマフラーの中心に
なるようにマフラーを設置していることで節がマフラー
中心を通るモードの共鳴は励起されず、マフラー内空間
共鳴による消音効果の低下ならびに圧縮機の騒音を十分
に抑えることができる。In the above-mentioned constitution of the main features of the compressor of the present invention,
By making the muffler shape axially symmetrical about the central axis in the longitudinal and lateral directions, the number of modes in which a node passes through the center of the muffler among a number of spatial resonance modes in the muffler increases. By installing the muffler so that the discharge port of the compression machine part that is the sound source is at the center of the muffler, the resonance of the mode in which the node passes through the center of the muffler is not excited, and the muffling effect of the spatial resonance in the muffler The decrease and the noise of the compressor can be sufficiently suppressed.
【００１６】この場合、マフラーの縦横の長さが異なる
構成では、節がマフラー中心を通るモード以外のモード
の共鳴について共鳴モードの節の方向（軸）を定めて分
離することができ、それぞれの共鳴モードについての節
の位置にマフラーの吐出穴を開けていることで、マフラ
ー外には共鳴音は放出されず、結果としてマフラー内空
間共鳴による消音効果の低下ならびに圧縮機の騒音は抑
えることができる。In this case, in a configuration in which the muffler has different vertical and horizontal lengths, it is possible to determine the directions (axes) of the nodes of the resonance modes for the resonance of modes other than the mode in which the nodes pass through the center of the muffler, and to separate them. By opening the muffler discharge hole at the node position for the resonance mode, resonance noise is not emitted outside the muffler, and as a result, the muffling effect due to spatial resonance inside the muffler and compressor noise can be suppressed. it can.
【００１７】さらに、マフラーが直方体に近い構成で
は、吐出穴の位置をマフラーの縦方向について両端から
ほぼ４分の１の位置に、横方向について両端からほぼ４
分の１の位置に設定して上記特徴が簡易に得られる。Further, in the structure in which the muffler is close to a rectangular parallelepiped, the position of the discharge hole is approximately one-quarter position from both ends in the vertical direction of the muffler and approximately four positions from both ends in the horizontal direction.
The above feature can be easily obtained by setting the position to one-half.
【００１８】[0018]
【実施例】以下、本発明の実施例について図１を参照し
ながら説明する。図１の（ａ）に示すように、圧縮機外
殻１内に、圧縮機械部２、この圧縮機械部２からの冷媒
の吐出口３が設けられている。この吐出口３の吐出側部
分が吐出部外殻４によって前記圧縮機外殻１内で覆われ
ている。この吐出部外殻４内ではさらに、吐出口３を覆
うマフラー５が設けられマフラー５と吐出部外殻４との
間に外部への吐出管６が設けられ、圧縮機械部２で圧縮
された冷媒は、吐出口３からマフラー５内に吐出された
後、マフラー５の吐出穴７を通じて圧縮部外殻４内に
出、吐出管６からシステム内に送り出される。この際圧
縮機械部２の圧縮行程により冷媒の脈動が起こり、吐出
口３から脈動音が発生する。この脈動音は吐出口３のマ
フラー５によって低く抑えられている。Embodiments of the present invention will be described below with reference to FIG. As shown in FIG. 1 (a), a compression machine part 2 and a discharge port 3 for the refrigerant from the compression machine part 2 are provided in the compressor outer shell 1. The discharge side portion of the discharge port 3 is covered with the discharge portion outer shell 4 in the compressor outer shell 1. A muffler 5 that covers the discharge port 3 is further provided in the discharge part outer shell 4, and a discharge pipe 6 to the outside is provided between the muffler 5 and the discharge part outer shell 4 and is compressed by the compression machine part 2. After being discharged from the discharge port 3 into the muffler 5, the refrigerant is discharged into the outer shell 4 of the compression portion through the discharge hole 7 of the muffler 5 and is discharged from the discharge pipe 6 into the system. At this time, the pulsation of the refrigerant occurs due to the compression stroke of the compression mechanical section 2, and a pulsating sound is generated from the discharge port 3. This pulsating sound is suppressed low by the muffler 5 of the discharge port 3.
【００１９】ここで、マフラー５の形状は図１の（ｂ）
に示すように中心軸まわりで、縦横方向について軸対称
になっている。このためマフラー５の内部空間の空間共
鳴のうち図１の（ｂ）に示す１次モードの節８、図２の
（ａ）に示す２次モードの節９、図２の（ｂ）に示す４
次モードの節１１のそれぞれはマフラー５の中心を通
る。さらに脈動音源となる吐出口３の位置がマフラー５
の中心にあるため脈動の倍調周波数が空間共鳴の周波数
と近いか、あるいは一致した場合でも１次モード、２次
モード、４次モードの共鳴は励起されず、従ってマフラ
ー５の内部空間の空間共鳴による消音効果の低下は起こ
らず、圧縮機の騒音を十分に抑えることができる。The shape of the muffler 5 is shown in FIG. 1 (b).
As shown in Fig. 4, the axis is symmetrical about the central axis in the vertical and horizontal directions. Therefore, among the spatial resonances of the internal space of the muffler 5, the first-order mode section 8 shown in FIG. 1B, the second-order mode section 9 shown in FIG. 2A, and the second mode section 9 shown in FIG. Four
Each of the clauses 11 of the next mode passes through the center of the muffler 5. Further, the position of the discharge port 3 which is the pulsating sound source is the muffler 5
Since the center of the pulsation is close to or coincides with the frequency of spatial resonance, the resonances of the first-order mode, second-order mode, and fourth-order mode are not excited, and therefore the space of the internal space of the muffler 5 is The noise reduction of the compressor can be sufficiently suppressed without reducing the noise reduction effect due to the resonance.
【００２０】また、マフラー５の縦横の長さが図１の
（ｂ）に示すように異なっていることで３次モードと５
次モードの分離ができ、図３に示すようにそれぞれの３
次モードの節１０と５次モードの節１２の交わる位置に
マフラー５の吐出穴７が開けてあるので、脈動の倍調周
波数が空間共鳴の周波数と近いか、あるいは一致した場
合でもマフラー５から外部へは３次モードおよび５次モ
ードの音は放出されず、従ってマフラー５の内部空間の
空間共鳴による消音効果の低下は起こらず、圧縮機の騒
音を十分に抑えることができる。Further, since the muffler 5 has different vertical and horizontal lengths as shown in FIG.
The next mode can be separated, and each of the 3
Since the discharge hole 7 of the muffler 5 is formed at the position where the node 10 of the next mode and the node 12 of the fifth mode intersect, even if the double frequency of the pulsation is close to or coincides with the frequency of the spatial resonance, the muffler 5 The sounds of the third-order mode and the fifth-order mode are not emitted to the outside, and therefore the noise reduction effect due to the spatial resonance of the internal space of the muffler 5 does not occur and the noise of the compressor can be sufficiently suppressed.
【００２１】図３に示す３、５次各モードの節１０、１
２の位置は、マフラー５が直方体に近い形状の場合の特
徴を示しており、節は縦方向で見た両端からほぼ４分の
１の位置にあり、節１２は横方向で見た両端からほぼ４
分の１の位置にある。従って、マフラー５が直方体に近
い形状にした場合、これらの位置の重なり部に吐出穴７
を設けさえすれば良好な消音効果が簡易に得られること
になる。Sections 10 and 1 of the third and fifth modes shown in FIG.
The position 2 shows the characteristic when the muffler 5 has a shape close to a rectangular parallelepiped, the node is located at a position approximately 1/4 from both ends when viewed in the vertical direction, and the node 12 is viewed from both ends when viewed in the horizontal direction. Almost 4
It is in the position of one-half. Therefore, when the muffler 5 has a shape close to a rectangular parallelepiped, the discharge holes 7 are formed at the overlapping portions of these positions.
A good sound deadening effect can be easily obtained by only providing.
【００２２】本発明者等の実験では、本実施例におい
て、マフラー空間共鳴が発生する周波数において２０ｄ
Ｂ〜３０ｄＢの消音効果の向上が確認されている。ま
た、本実施例では、吐出口について示したが、圧縮機機
械部の吸入口についても消音の必要がある場合には吸入
口に同様のマフラーを設けると、同様な作用効果が得ら
れる。In the experiments conducted by the present inventors, in the present embodiment, at the frequency at which the muffler spatial resonance occurs, 20 d
It has been confirmed that the noise reduction effect of B to 30 dB is improved. In addition, although the discharge port is shown in the present embodiment, when the muffling of the suction port of the compressor mechanical section is also required, a similar muffler may be provided at the suction port to obtain the same effect.
【００２３】[0023]
【発明の効果】以上のように、本発明は、圧縮機械部の
吐出口または吸入口に、中心軸まわりで縦横方向につい
て軸対称な形状のマフラーを吐出口または吸入口がマフ
ラーの中心になるように設置することにより、また、マ
フラー吐出穴をマフラー内部空間共鳴モードの節の位置
に開けることで、マフラーの消音効果の低下を防ぎ圧縮
機の騒音の低減を図ることができ、特にマフラーが直方
体に近いとマフラーの縦方向で見た両端からほぼ４分の
１の位置、横方向で見た両端からほぼ４分の１の位置に
吐出穴を設けて消音条件を簡易に満足することができ
る。As described above, according to the present invention, the exhaust port or the intake port of the compression machine section is provided with a muffler which is axially symmetrical about the central axis in the longitudinal and lateral directions, and the exhaust port or the intake port is the center of the muffler. By installing the muffler discharge hole at the node position of the muffler internal space resonance mode, it is possible to prevent the muffler's noise reduction effect from decreasing and to reduce the noise of the compressor. When the muffler is close to a rectangular parallelepiped, it is possible to easily satisfy the muffling condition by providing discharge holes at positions approximately one-quarter from both ends when viewed in the vertical direction and at positions approximately one-fourth from both ends when viewed in the horizontal direction. it can.
【図１】本発明の１実施例における圧縮機の吐出機構部
を示す断面図、およびマフラーと１次共鳴モードの節位
置を示す平面図である。FIG. 1 is a cross-sectional view showing a discharge mechanism portion of a compressor in one embodiment of the present invention, and a plan view showing a muffler and a node position of a primary resonance mode.
【図２】２次、３次共鳴モードの節位置を示すマフラー
の平面図である。FIG. 2 is a plan view of a muffler showing node positions of secondary and tertiary resonance modes.
【図３】３次、５次の共鳴モードの節位置を示すマフラ
ーの平面図である。FIG. 3 is a plan view of a muffler showing node positions of third- and fifth-order resonance modes.
【図４】従来の圧縮機の吐出機構の断面図およびマフラ
ーの平面図である。FIG. 4 is a cross-sectional view of a discharge mechanism of a conventional compressor and a plan view of a muffler.
【図５】空間共鳴の説明用の直方体箱の斜視図である。FIG. 5 is a perspective view of a rectangular parallelepiped box for explaining spatial resonance.
【図６】直方体箱の１次の空間共鳴における音圧分布の
概略図である。FIG. 6 is a schematic diagram of sound pressure distribution in first-order spatial resonance of a rectangular parallelepiped box.
【図７】直方体箱の２次の空間共鳴における音圧分布の
概略図である。FIG. 7 is a schematic diagram of sound pressure distribution in the secondary spatial resonance of a rectangular parallelepiped box.
【図８】直方体箱の３次の空間共鳴における音圧分布の
概略図である。FIG. 8 is a schematic diagram of sound pressure distribution in third-order spatial resonance of a rectangular parallelepiped box.
【図９】直方体箱の４次の空間共鳴における音圧分布の
概略図である。FIG. 9 is a schematic diagram of sound pressure distribution in fourth-order spatial resonance of a rectangular parallelepiped box.
【図１０】直方体箱の５次の空間共鳴における音圧分布
の概略図である。FIG. 10 is a schematic diagram of sound pressure distribution in fifth-order spatial resonance of a rectangular parallelepiped box.
２ 圧縮機械部 ３ 吐出口 ４ 圧縮部外殻 ５ マフラー ７ 吐出穴 ８ 空間共鳴の１次のモードの節 ９ 空間共鳴の２次のモードの節 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 １２ 空間共鳴の５次のモードの節 2 Compressed mechanical part 3 Discharge port 4 Compressed part shell 5 Muffler 7 Discharge hole 8 Spatial resonance first-order mode node 9 Spatial resonance second-mode mode node 10 Spatial resonance third-mode mode node 11 Spatial resonance 4th-order mode section of 12 12th-order resonance 5th-order mode section
───────────────────────────────────────────────────── フロントページの続き (72)発明者 橋本 雄史 大阪府門真市大字門真1006番地 松下電器 産業株式会社内 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Yushi Hashimoto 1006 Kadoma, Kadoma City, Osaka Prefecture Matsushita Electric Industrial Co., Ltd.
Claims (3)
中心軸まわりで縦横方向について軸対称な形状をしたマ
フラーを吐出口または吸入口がマフラー中心になるよう
に設置したことを特徴とする圧縮機。1. A discharge port or a suction port in a compression machine section,
A compressor characterized in that a muffler having an axially symmetrical shape about the central axis in the longitudinal and lateral directions is installed so that the discharge port or the suction port is located at the center of the muffler.
フラーの空間共鳴モードの節の位置に吐出穴を開けた請
求項１に記載の圧縮機。2. The compressor according to claim 1, wherein the muffler is different in length and width, and a discharge hole is formed at a position of a node of the spatial resonance mode of the muffler.
て両端からほぼ４分の１の位置、横方向について両端か
らほぼ４分の１の位置に吐出穴を開けた請求項２に記載
の圧縮機。3. The compressor according to claim 2, wherein the muffler is close to a rectangular parallelepiped, and discharge holes are formed at positions approximately one-fourth from both ends in the vertical direction and approximately one-fourth from both ends in the horizontal direction. .
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP22814095A JPH0972279A (en) | 1995-09-05 | 1995-09-05 | Compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP22814095A JPH0972279A (en) | 1995-09-05 | 1995-09-05 | Compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH0972279A true JPH0972279A (en) | 1997-03-18 |
Family
ID=16871852
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP22814095A Pending JPH0972279A (en) | 1995-09-05 | 1995-09-05 | Compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0972279A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1998053204A1 (en) * | 1997-05-21 | 1998-11-26 | Matsushita Refrigeration Company | Enclosed compressor and cooling system |
| WO2012073365A1 (en) * | 2010-12-02 | 2012-06-07 | トヨタ自動車株式会社 | Apparatus for controlling internal combustion engine provided with turbocharger |
| JP2012522921A (en) * | 2009-04-06 | 2012-09-27 | ワールプール・エシ・ア | Structural arrangement of hermetic refrigeration compressors |
| CN105003416A (en) * | 2015-07-31 | 2015-10-28 | 广州万宝集团有限公司 | Air suction silencing structure of compressor |
-
1995
- 1995-09-05 JP JP22814095A patent/JPH0972279A/en active Pending
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1998053204A1 (en) * | 1997-05-21 | 1998-11-26 | Matsushita Refrigeration Company | Enclosed compressor and cooling system |
| JP2012522921A (en) * | 2009-04-06 | 2012-09-27 | ワールプール・エシ・ア | Structural arrangement of hermetic refrigeration compressors |
| WO2012073365A1 (en) * | 2010-12-02 | 2012-06-07 | トヨタ自動車株式会社 | Apparatus for controlling internal combustion engine provided with turbocharger |
| JP5136701B2 (en) * | 2010-12-02 | 2013-02-06 | トヨタ自動車株式会社 | Control device for an internal combustion engine with a supercharger |
| US8627660B2 (en) | 2010-12-02 | 2014-01-14 | Toyota Jidosha Kabushiki Kaisha | Control device for internal combustion engine with supercharger |
| CN105003416A (en) * | 2015-07-31 | 2015-10-28 | 广州万宝集团有限公司 | Air suction silencing structure of compressor |
| CN105003416B (en) * | 2015-07-31 | 2018-09-25 | 广州万宝集团有限公司 | A kind of compressor air suction noise-reducing structure |
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