JPH0126469B2 - - Google Patents
Info
- Publication number
- JPH0126469B2 JPH0126469B2 JP55183804A JP18380480A JPH0126469B2 JP H0126469 B2 JPH0126469 B2 JP H0126469B2 JP 55183804 A JP55183804 A JP 55183804A JP 18380480 A JP18380480 A JP 18380480A JP H0126469 B2 JPH0126469 B2 JP H0126469B2
- Authority
- JP
- Japan
- Prior art keywords
- refrigerant
- orifice tube
- outlet
- porous body
- expansion section
- 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.)
- Expired
Links
- 239000003507 refrigerant Substances 0.000 claims description 57
- 239000002184 metal Substances 0.000 claims description 13
- 229910052751 metal Inorganic materials 0.000 claims description 13
- 238000005057 refrigeration Methods 0.000 claims description 10
- 230000000694 effects Effects 0.000 description 8
- 230000001105 regulatory effect Effects 0.000 description 5
- 239000007788 liquid Substances 0.000 description 4
- 239000011148 porous material Substances 0.000 description 4
- 238000013016 damping Methods 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 238000002474 experimental method Methods 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 238000011144 upstream manufacturing Methods 0.000 description 2
- 238000003915 air pollution Methods 0.000 description 1
- 230000002238 attenuated effect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 150000002739 metals Chemical class 0.000 description 1
- 239000003595 mist Substances 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000000644 propagated effect Effects 0.000 description 1
- 230000001902 propagating effect Effects 0.000 description 1
- 230000001743 silencing effect Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
Description
【発明の詳細な説明】
［発明の目的］
（産業上の利用分野）
本発明は、自動車等に搭載される空気調和装置
に関し、冷媒膨張部から発生する騒音を防止する
ようにしたもである。[Detailed Description of the Invention] [Object of the Invention] (Industrial Application Field) The present invention relates to an air conditioner installed in an automobile, etc., and is designed to prevent noise generated from a refrigerant expansion section. .
（従来の技術）
一般的な自動車用空気調和装置の冷凍サイクル
は第１図に示すように、図示しないエンジンによ
りクラツチを介して駆動するコンプレツサＡと、
ラジエータの前面に取付けられて前記コンプレツ
サから送られてきた冷媒を凝縮するコンデンサＢ
と、高圧の液冷媒を急激に膨張させることにより
等該冷媒を低温、低圧、霧状の冷媒にする冷媒膨
張部Ｃと、車室内に取付けられ室内の空気から熱
を奪うことにより車室内に冷風を供給するエバポ
レータＤとから構成されている。(Prior Art) As shown in FIG. 1, the refrigeration cycle of a typical automobile air conditioner includes a compressor A driven by an engine (not shown) via a clutch;
A condenser B is attached to the front of the radiator and condenses the refrigerant sent from the compressor.
, a refrigerant expansion part C that rapidly expands high-pressure liquid refrigerant to turn the refrigerant into a low-temperature, low-pressure, atomized refrigerant; It is composed of an evaporator D that supplies cold air.
（発明が解決しようとする課題）
近年の自動車性能の向上は特に凄まじく、その
中でも車室内における静寂性の向上は著しい。従
つてこのような情況にあつては、自動車用空気調
和装置から発生する騒音が更に顕著化してしま
い、乗員に不快感を与えるだけでなく、前記自動
車技術の開発が徒労に終わる結果となる。そこ
で、この自動車用空気調和装置にあつても、車室
内の居住性の向上、特に静寂性が希求されてい
る。(Problems to be Solved by the Invention) In recent years, improvements in automobile performance have been particularly remarkable, and among these improvements, the quietness inside the vehicle interior has been significantly improved. Therefore, in such a situation, the noise generated from the automobile air conditioner becomes even more noticeable, which not only causes discomfort to the occupants, but also results in the development of the above-mentioned automobile technology ending up in vain. Therefore, even in the case of this air conditioner for automobiles, there is a demand for improved comfort in the vehicle interior, especially quietness.
この自動車用空気調和装置の冷凍サイクルにあ
つて騒音源として挙げられるのは、冷媒が圧縮さ
れる前記コンプレツサＡと、冷媒が急激に膨張さ
れる前記冷媒膨張部Ｃとであるが、前者のコンプ
レツサＡはエンジンルーム内に取付けられ、エン
ジン室がその性質上防音構造となつているため、
車室内への音の影響は特に問題とならない。これ
に対して後者の冷媒膨張部Ｃは、その機能上エバ
ポレータＤの直近に取付けられ、当該エバポレー
タＤは車室内に設置されるのが常であるから、冷
媒膨張部Ｃにおける騒音は車室内に直接伝播され
ることになる。 In the refrigeration cycle of this automotive air conditioner, noise sources include the compressor A where the refrigerant is compressed and the refrigerant expansion section C where the refrigerant is rapidly expanded. A is installed in the engine room, and the engine room has a soundproof structure due to its nature.
The influence of sound inside the vehicle interior is not a particular problem. On the other hand, the latter refrigerant expansion section C is functionally installed close to the evaporator D, and the evaporator D is usually installed inside the vehicle interior, so the noise from the refrigerant expansion section C is inside the vehicle interior. It will be propagated directly.
そこで、上記冷媒膨張部Ｃの騒音問題を解消す
るものとして、例えば実開昭54−19356号公報に
開示された冷凍装置がある。この装置は、冷凍回
路の冷媒膨脹部の出口と冷媒管とを連結する管状
のジヨイント内に多孔質体を介設したものである
が、当該冷凍装置にあつても、機種によつては、
まだ尚発生騒音が高いものがあり、前記自動車室
内の静寂化を図る上で満足すべき装置ではなかつ
た。 Therefore, as a solution to the noise problem of the refrigerant expansion section C, there is a refrigeration system disclosed in, for example, Japanese Utility Model Application Publication No. 19356/1983. This device has a porous body interposed in a tubular joint that connects the outlet of the refrigerant expansion section of the refrigeration circuit and the refrigerant pipe, but depending on the model of the refrigeration device,
There are still some devices that generate high noise, and the device is not satisfactory for making the interior of the vehicle quieter.
本発明は、上述した従来技術に伴う問題点に鑑
みてなされたもので、冷媒膨張部における騒音の
発生要因を解明して騒音減衰効果を奏する技術的
手段を講じることにより、車室内の騒音を低減
し、居住性の向上を図り得る自動車用空気調和装
置を提供することを目的とする。 The present invention has been made in view of the problems associated with the above-mentioned conventional technology, and it reduces noise inside the vehicle interior by elucidating the cause of noise generation in the refrigerant expansion section and taking technical measures to achieve a noise attenuation effect. The purpose of the present invention is to provide an air conditioner for an automobile that can reduce air pollution and improve livability.
［発明の構成］
（課題を解決するための手段）
上記目的を達成するための本発明は、冷媒膨脹
部を備えた冷凍サイクルにおいて、前記冷媒膨張
部の下流側に、当該冷媒膨張部の出口の口径に対
し0.5〜5.0倍の間隔をおいて発泡金属から成る多
孔質体を設けたことを特徴とする空気調和装置で
ある。[Structure of the Invention] (Means for Solving the Problems) The present invention for achieving the above object provides, in a refrigeration cycle equipped with a refrigerant expansion section, an outlet of the refrigerant expansion section on the downstream side of the refrigerant expansion section. This is an air conditioner characterized in that porous bodies made of foamed metal are provided at intervals of 0.5 to 5.0 times the diameter of the air conditioner.
（作用）
このように構成した本発明にあつては、冷媒膨
張部に流入した液体冷媒は、当該冷媒膨張部によ
つて絞られ、その出口から噴出する際に断熱膨張
し、この断熱膨張によつて前記冷媒は、低温、低
圧の霧状冷媒となり、同時に膨張音を発すること
になる。(Function) In the present invention configured as described above, the liquid refrigerant that has flowed into the refrigerant expansion section is throttled by the refrigerant expansion section, expands adiabatically when jetting out from the outlet, and due to this adiabatic expansion. Therefore, the refrigerant becomes a low-temperature, low-pressure atomized refrigerant, and at the same time generates an expansion sound.
しかし、この膨張音は、冷媒膨張部出口から流
出した噴流の乱れが、前記冷媒膨張部の出口近傍
に設けた多孔質体の小孔を通過する際に、最も好
適に整流、整圧化される冷媒の流速と流量との関
係があることから、多孔率がほぼ100％である発
泡金属から成る多孔質体の設置位置を、冷媒膨張
部出口から、当該冷媒膨張部出口の口径の0.5〜
5.0倍の間隔を隔てた位置に設置することによつ
て、冷媒の背圧が増加することなく好適に整流、
整圧化させることができ、前記発生した騒音を減
衰させることができる。 However, this expansion noise is most preferably rectified and pressure-regulated when the turbulence of the jet flowing out from the outlet of the refrigerant expansion section passes through small holes in the porous body provided near the outlet of the refrigerant expansion section. Since there is a relationship between the flow rate and the flow rate of the refrigerant, the porous body made of foamed metal with a porosity of approximately 100% is installed at a position from the outlet of the refrigerant expansion section to 0.5 to 0.5 of the diameter of the outlet of the refrigerant expansion section.
By installing them at 5.0 times the distance, the refrigerant can be properly rectified without increasing its back pressure.
The pressure can be regulated and the generated noise can be attenuated.
（実施例）
以下、図面を参照して本発明の一実施例を説明
する。(Example) Hereinafter, an example of the present invention will be described with reference to the drawings.
第２図は、本発明の一実施例に係る自動車用空
気調和装置を示すものであり、その冷媒膨張部Ｃ
における縦断面図である。 FIG. 2 shows an air conditioner for an automobile according to an embodiment of the present invention, in which the refrigerant expansion section C
FIG.
第２図において、この冷媒膨張部Ｃは、膨張手
段としてオリフイスチユーブ１と、発泡金属から
成る多孔質体２と、オリフイスチユーブホルダ３
と、内部に冷媒を流通する上流側及び下流側冷媒
流通管４Ａ，４Ｂと、プラグ５Ａ及びソケツト５
Ｂから成る連結部５とから構成されている。 In FIG. 2, this refrigerant expansion section C includes an orifice tube 1 as an expansion means, a porous body 2 made of foamed metal, and an orifice tube holder 3.
, upstream and downstream refrigerant flow pipes 4A and 4B through which refrigerant flows, a plug 5A and a socket 5.
A connecting portion 5 consisting of B.
前記オリフイスチユーブ１は、液体冷媒を急激
に断熱膨張させて低温、低圧の霧状冷媒にするも
のであり、所定の内径ｄと長さとに形成されてい
る。また、前記オリフイスチユーブホルダ３は、
流通管４Ａの内径に略等しい外径を有する薄肉内
筒形状の筒形状部３Ａと、この筒形状部３Ａの下
流側の端部外周上にその外形が算盤玉形状に膨出
形成された大径部３Ｂとから成り、前記一対の流
通管４Ａ，４Ｂを互いに突合わせにし、この部分
に前記大径部３Ｂを挟み込んだ状態で前記連結部
５を緊締することにより、前記オリフイスチユー
ブホルダ３を流通管４の途中に固定するようにな
つている。 The orifice tube 1 rapidly adiabatically expands liquid refrigerant to form a low-temperature, low-pressure mist refrigerant, and is formed to have a predetermined inner diameter d and length. Further, the orifice tube holder 3 is
A cylindrical portion 3A having a thin inner cylinder shape having an outer diameter approximately equal to the inner diameter of the flow pipe 4A, and a large cylindrical portion 3A having an abacus-shaped outer shape on the outer periphery of the downstream end of the cylindrical portion 3A. The orifice tube holder 3 is constructed by abutting the pair of flow tubes 4A and 4B against each other and tightening the connecting portion 5 with the large diameter portion 3B sandwiched between these portions. It is designed to be fixed in the middle of the flow pipe 4.
前記多孔質体２は、発泡金属から成り、多数の
連続した小孔を有し通気性及び耐久性に優れた材
料であつて、多孔率は80〜100％、孔径は約100μ
ｍ〜10mmである。ちなみに、従来冷媒膨張部に使
用されていた多孔質体である焼結金属の多孔率
は、約20〜50％、孔径は約0.1〜10μｍである。従
つて、従来使用していた焼結金属等と比較して、
小孔を通過する際の冷媒の流れを均一化し、整
流、整圧化する機能は、格段に優れた材料であ
る。この多孔質体２は、前記ホルダ３の大径部３
Ｂの内周に保持されており、オリフイスチユーブ
１の出口から所定の間隔Ｌを隔てた下流側に位置
した設けられている。本実施例においては、この
間隔Ｌを、前記オリフイスチユーブ１出口の口径
ｄの0.5〜5.0倍の値としている。 The porous body 2 is made of foamed metal and has a large number of continuous small pores, and is a material with excellent breathability and durability, and has a porosity of 80 to 100% and a pore diameter of approximately 100μ.
m to 10 mm. Incidentally, the porosity of the sintered metal, which is a porous body conventionally used in the refrigerant expansion section, is about 20 to 50%, and the pore diameter is about 0.1 to 10 μm. Therefore, compared to conventionally used sintered metals,
It is a material that is extremely superior in its ability to equalize, rectify, and pressure the refrigerant flow as it passes through the small holes. This porous body 2 is a large diameter portion 3 of the holder 3.
It is held on the inner periphery of the orifice tube 1 and is located downstream from the outlet of the orifice tube 1 by a predetermined distance L. In this embodiment, this distance L is set to a value of 0.5 to 5.0 times the diameter d of the outlet of the orifice tube 1.
ここで、第６図は、オリフイスチユーブ出口の
口径ｄに対する多孔質体２の間隔Ｌと発生騒音と
の関係に関する実験結果を示すデータであり、縦
軸には相対的な消音の程度を表わしており、横軸
には多孔質体２の間隔Ｌを口径ｄの倍率で表わし
ている。また、図上実線にて示すデータは、当該
冷媒膨張部Ｃから発生する騒音の内、その周波数
が7KHzの低周波数音を、点線にて示すデータは
同じく20KHzの高周波数音を表わしており、更に
図上一点鎖線にて示す騒音の程度は、実用上殆ん
ど不快感を感じない許容騒音レベルの境界線を表
わしている。尚、本実験にて使用したオリフイス
チユーブの口径ｄは、1.6mmである。 Here, FIG. 6 shows the data showing the experimental results regarding the relationship between the distance L of the porous body 2 and the generated noise with respect to the diameter d of the orifice tube outlet, and the vertical axis represents the relative degree of noise reduction. The horizontal axis represents the distance L between the porous bodies 2 as a magnification of the diameter d. In addition, the data shown by the solid line in the figure represents the low frequency sound with a frequency of 7KHz among the noise generated from the refrigerant expansion part C, and the data shown by the dotted line represents the high frequency sound of 20KHz. Further, the level of noise indicated by the dashed line in the figure represents the boundary line of the allowable noise level at which practically no discomfort is felt. Note that the diameter d of the orifice tube used in this experiment was 1.6 mm.
この実験結果からも明らかなように、多孔質体
２とオリフイスチユーブ１の出口との間隔Ｌが口
径ｄの約２倍の値2dの場合に、高周波数音域及
び低周波数音域ともに、最も発生騒音が小さく消
音効果が顕著となる。また、前記間隔Ｌが口径ｄ
の0.5〜5.0倍の範囲内においては、実用上車室内
に与える影響を無視することができる。 As is clear from this experimental result, when the distance L between the porous body 2 and the outlet of the orifice tube 1 is 2d, which is approximately twice the diameter d, the noise generated is the highest in both the high frequency sound range and the low frequency sound range. is small and the silencing effect is significant. Also, the distance L is the diameter d
Within the range of 0.5 to 5.0 times, the effect on the interior of the vehicle can be practically ignored.
つまり、本実験結果から言えることは、オリフ
イスチユーブ１出口から流出した冷媒が発する膨
張音は、その噴流の乱れにより生じることになる
が、この噴流の乱れを多孔質体２によつて整流、
整圧化する際に、多孔質体２の小孔を通過する冷
媒の流速や流量等により最も整流、整圧化し得る
範囲が存在して、これは多孔質体２の設置位置を
オリフイスチユーブ１出口の口径ｄとの関係によ
つて決定すれば良いということである。例えば、
オリフイスチユーブ１出口の直近に多孔質体２を
設けた場合には、冷媒の噴流が最も乱れた状態と
なつており、このような冷媒が多孔質体２を通過
しても、冷媒自身が備えている流速の方向が一定
とならず、好適に整流、整圧化されない。また、
オリフイスチユーブ１出口と多孔質体２との間隔
Ｌを長くした場合にあつては、出口から流出した
際に発生する膨張音が、多孔質体２を通過するま
でに外部に伝播することになり、多孔質体２を通
過する際には、既に車室内等に大きな騒音を与え
てしまつていることになる。従つて、闇雲に多孔
質体２を設置するのではなく、オリフイスチユー
ブ１出口の口径ｄとの関係によつて決定しなけれ
ば減衰効果は得られないのである。 In other words, what can be said from the results of this experiment is that the expansion noise generated by the refrigerant flowing out from the outlet of the orifice tube 1 is caused by the turbulence of the jet flow, but the turbulence of the jet flow is rectified by the porous body 2.
When regulating the pressure, there is a range in which the flow rate and pressure of the refrigerant passing through the small holes of the porous body 2 is the most possible. This means that it may be determined based on the relationship with the outlet diameter d. for example,
When the porous body 2 is provided close to the outlet of the orifice tube 1, the refrigerant jet flow is in the most turbulent state, and even if such a refrigerant passes through the porous body 2, the refrigerant itself is The direction of the flow velocity is not constant, and the flow is not properly rectified and the pressure is not regulated. Also,
If the distance L between the orifice tube 1 outlet and the porous body 2 is increased, the expansion noise generated when it flows out from the outlet will propagate to the outside before passing through the porous body 2. , when passing through the porous body 2, it has already caused a large amount of noise inside the vehicle interior. Therefore, the damping effect cannot be obtained unless the porous body 2 is installed blindly, but determined based on the relationship with the diameter d of the outlet of the orifice tube 1.
次に、本実施例の作用を説明する。 Next, the operation of this embodiment will be explained.
上流側流通管４Ａからオリフイスチユーブ１に
流入した液体冷媒は、当該オリフイスチユーブ１
によつて絞られその出口から噴出する際に断熱膨
張する。この断熱膨張によつて前記冷媒は、低
温、低圧の霧状冷媒となり、同時に膨張音を発し
ようとするが、前記オリフイスチユーブ１の出口
近傍に発泡金属から成る多孔質体２が設けられて
いるため、出口から流出した噴流の乱れは発泡金
属の連続した、しかも多孔率の高い小孔を通過す
る際に整流、整圧化されて前記発生した騒音を減
衰させることになる。そして、この減衰の程度
は、多孔質体２の取付け位置がオリフイスチユー
ブ１出口から、当該オリフイスチユーブ１出口の
口径ｄの0.5〜5.0倍の間隔Ｌを隔てた位置が好適
となる。 The liquid refrigerant flowing into the orifice tube 1 from the upstream flow pipe 4A flows through the orifice tube 1.
It expands adiabatically when it is squeezed by the gas and ejected from its outlet. Due to this adiabatic expansion, the refrigerant becomes a low-temperature, low-pressure atomized refrigerant, and at the same time it tries to emit an expansion sound.A porous body 2 made of foamed metal is provided near the outlet of the orifice tube 1. Therefore, the turbulence of the jet flowing out from the outlet is rectified and pressure-regulated when it passes through the continuous and highly porous pores of the foamed metal, thereby attenuating the generated noise. The degree of this attenuation is preferably determined by mounting the porous body 2 at a distance L from the outlet of the orifice tube 1 at a distance L that is 0.5 to 5.0 times the diameter d of the outlet of the orifice tube 1.
第３〜５図は、本発明の他の実施例を示すもの
であり、それぞれオリフイスチユーブ１及び多孔
質体２の保持構造が異なるだけで、その作用効果
は前記第１実施例と同様である。尚、第３〜５図
において連結部５の図示を省略している。 3 to 5 show other embodiments of the present invention, and the only difference is the holding structure of the orifice tube 1 and the porous body 2, and the operation and effect are the same as those of the first embodiment. . In addition, illustration of the connecting portion 5 is omitted in FIGS. 3 to 5.
すなわち、第３図に示す実施例に場合は、オリ
フイスチユーブ１が、円筒形状部が省略されたオ
リフイスチユーブホルダ３の大径部３Ｂの下流側
に一体的に連設されて保持されたものであり、発
泡金属から成る多孔質体２は、下流側流通管４Ｂ
の管壁を褶曲加工することにより保持されるよう
になつている。この場合の多孔質体２の取付け位
置も、オリフイスチユーブ１出口から当該オリフ
イスチユーブ１出口の口径ｄの0.5〜5.0倍の間隔
Ｌを隔てた位置である。 That is, in the case of the embodiment shown in FIG. 3, the orifice tube 1 is integrally connected and held on the downstream side of the large diameter portion 3B of the orifice tube holder 3, in which the cylindrical portion is omitted. Yes, the porous body 2 made of foamed metal is connected to the downstream flow pipe 4B.
It is held in place by folding the tube wall. The mounting position of the porous body 2 in this case is also a position separated from the orifice tube 1 outlet by a distance L that is 0.5 to 5.0 times the diameter d of the orifice tube 1 outlet.
第４図に示すものは、オリフイスチユーブ１を
オリフイスチユーブホルダ３の大径部３Ｂがその
中間部を保持するように形成したもので、発泡金
属から成る多孔質体２はオリフイスチユーブホル
ダ３の筒形状部３Ａの下流側の一端部内周に保持
するようになつている。この場合の多孔質体２の
取付け位置も、オリフイスチユーブ１出口から当
該オリフイスチユーブ１出口の口径ｄの0.5〜5.0
倍の間隔Ｌを隔てた位置である。 In the configuration shown in FIG. 4, the orifice tube 1 is formed so that the large-diameter portion 3B of the orifice tube holder 3 holds its middle portion, and the porous body 2 made of foamed metal is attached to the tube of the orifice tube holder 3. It is adapted to be held on the inner periphery of one downstream end of the shaped portion 3A. In this case, the mounting position of the porous body 2 is also 0.5 to 5.0 of the diameter d of the orifice tube 1 outlet from the orifice tube 1 outlet.
This is a position separated by twice the distance L.
更に、第５図に示す実施例の場合は、オリフイ
スチユーブ１をオリフイスチユーブホルダ３の大
径部３Ｂがその中間部を保持するように形成した
もので、前記第３実施例（第４図に図示）との相
違点は、多孔質体２をオリフイスチユーブ１に一
体的に連設した筒形状ホルダ部１Ａの下流側の一
端部内周に保持している点である。この場合の多
孔質体２の取付け位置も、オリフイスチユーブ１
出口から当該オリフイスチユーブ１出口の口経ｄ
の0.5〜5.0倍の間隔Ｌを隔てた位置である。 Furthermore, in the case of the embodiment shown in FIG. 5, the orifice tube 1 is formed so that the large-diameter portion 3B of the orifice tube holder 3 holds the intermediate portion thereof, and the 2) is that the porous body 2 is held on the inner periphery of one downstream end of a cylindrical holder portion 1A that is integrally connected to the orifice tube 1. In this case, the mounting position of the porous body 2 is also the orifice tube 1.
From the exit to the orifice tube 1 exit d
These positions are separated by an interval L of 0.5 to 5.0 times.
このような変形例においても、本発明の要旨で
ある冷媒膨張部における騒音の減衰効果は、冷媒
膨張部出口の口径との関係における多孔質体の設
置位置により決定されることから、冷媒膨張部の
下流側に所定の間隔をおいて、発泡金属から成る
多孔質体を設けるように構成している点で全て共
通しており、前記第１実施例と同様の作用効果を
奏することは明らかであるから、詳細な説明は省
略する。 Even in such a modification, the noise damping effect in the refrigerant expansion section, which is the gist of the present invention, is determined by the installation position of the porous body in relation to the diameter of the outlet of the refrigerant expansion section. All of them have the same structure in that a porous body made of foamed metal is provided at a predetermined interval on the downstream side of the structure, and it is clear that they have the same effect as the first embodiment. Therefore, detailed explanation will be omitted.
［発明の効果］
以上述べたように、本発明によれば、冷凍サイ
クルにおける冷媒膨張部の下流側に、当該冷媒膨
張部の出口の口径に対して0.5〜5.0倍の間隔を隔
てた位置に、発泡金属から成る多孔質体を設けた
ため、冷媒膨張部において発生する騒音を減衰さ
せることができ、これによつて車室内に伝播する
当該騒音を防止し、車室内の居住性を向上させ得
る自動車用空気調和装置を提供することができる
という極めて優れた効果を奏する。[Effects of the Invention] As described above, according to the present invention, there is provided a refrigerant expansion section downstream of the refrigerant expansion section in the refrigeration cycle, at a position spaced apart from 0.5 to 5.0 times the diameter of the outlet of the refrigerant expansion section. Since the porous body made of foamed metal is provided, it is possible to attenuate the noise generated in the refrigerant expansion section, thereby preventing the noise from propagating into the vehicle interior and improving the comfort inside the vehicle interior. This has an extremely excellent effect of being able to provide an air conditioner for automobiles.
第１図は一般的な自動車用空気調和装置の冷凍
回路図、第２図は本発明の一実施例を示す縦断面
図、第３〜５図は本発明の他の実施例を示す一部
省略縦断面図、第６図は多孔質体のオリフイスチ
ユーブ出口までの距離と発生騒音との関係を示す
グラフである。
１……オリフイスチユーブ、２……多孔質体、
３……オリフイスチユーブホルダ、４……冷媒流
通管、５……連結手段、１０……冷凍サイクル、
Ｃ……冷媒膨張部、ｄ……膨張部出口の口径、Ｌ
……間隔。
Fig. 1 is a refrigeration circuit diagram of a general automobile air conditioner, Fig. 2 is a longitudinal sectional view showing one embodiment of the present invention, and Figs. 3 to 5 are parts showing other embodiments of the present invention. The abbreviated vertical cross-sectional view, FIG. 6, is a graph showing the relationship between the distance of the porous body to the orifice tube outlet and the generated noise. 1... Orifice tube, 2... Porous body,
3... Orifice tube holder, 4... Refrigerant flow pipe, 5... Connection means, 10... Refrigeration cycle,
C... Refrigerant expansion section, d... Diameter of expansion section outlet, L
……interval.
Claims (1)
いて、前記冷媒膨張部Ｃの下流側に、当該冷媒膨
張部Ｃの出口の口径ｄに対し0.5〜5.0倍の間隔Ｌ
をおいて、発泡金属から成る多孔質体２を設けた
ことを特徴とする空気調和装置。1 In a refrigeration cycle 10 equipped with a refrigerant expansion section C, an interval L that is 0.5 to 5.0 times the diameter d of the outlet of the refrigerant expansion section C is provided on the downstream side of the refrigerant expansion section C.
An air conditioner characterized in that a porous body 2 made of foamed metal is provided.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP55183804A JPS57108568A (en) | 1980-12-26 | 1980-12-26 | Air conditioning equipment |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP55183804A JPS57108568A (en) | 1980-12-26 | 1980-12-26 | Air conditioning equipment |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS57108568A JPS57108568A (en) | 1982-07-06 |
| JPH0126469B2 true JPH0126469B2 (en) | 1989-05-24 |
Family
ID=16142182
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP55183804A Granted JPS57108568A (en) | 1980-12-26 | 1980-12-26 | Air conditioning equipment |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS57108568A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2002061350A1 (en) * | 2001-01-31 | 2002-08-08 | Mitsubishi Denki Kabushiki Kaisha | Refrigerating cycle device, air conditioner, choke, and flow rate controller |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3417351B2 (en) * | 1999-08-06 | 2003-06-16 | 三菱電機株式会社 | Aperture device |
| JP3395761B2 (en) * | 2000-04-27 | 2003-04-14 | 三菱電機株式会社 | Throttling device, refrigeration cycle device. |
| JP2002061879A (en) * | 2000-08-21 | 2002-02-28 | Mitsubishi Electric Corp | Indoor unit of air conditioner |
| JP3712355B2 (en) * | 2000-09-25 | 2005-11-02 | 三菱電機株式会社 | Refrigeration cycle equipment |
| JP2002195696A (en) * | 2000-12-21 | 2002-07-10 | Matsushita Electric Ind Co Ltd | Air conditioner |
| DE10258453B4 (en) * | 2002-12-13 | 2007-11-15 | Otto Egelhof Gmbh & Co. Kg | Circulation for the production of cold or heat |
| DE102004063486B4 (en) * | 2004-12-23 | 2019-07-11 | OET GmbH | Expansion valve, in particular for a refrigeration cycle operated with CO2 |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5111740U (en) * | 1974-07-13 | 1976-01-28 | ||
| JPS5419356B2 (en) * | 1976-02-16 | 1979-07-14 |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5419356U (en) * | 1977-07-11 | 1979-02-07 |
-
1980
- 1980-12-26 JP JP55183804A patent/JPS57108568A/en active Granted
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5111740U (en) * | 1974-07-13 | 1976-01-28 | ||
| JPS5419356B2 (en) * | 1976-02-16 | 1979-07-14 |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2002061350A1 (en) * | 2001-01-31 | 2002-08-08 | Mitsubishi Denki Kabushiki Kaisha | Refrigerating cycle device, air conditioner, choke, and flow rate controller |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS57108568A (en) | 1982-07-06 |
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