JPH0462359A - Oil separator for air conditioner - Google Patents
Oil separator for air conditionerInfo
- Publication number
- JPH0462359A JPH0462359A JP17315190A JP17315190A JPH0462359A JP H0462359 A JPH0462359 A JP H0462359A JP 17315190 A JP17315190 A JP 17315190A JP 17315190 A JP17315190 A JP 17315190A JP H0462359 A JPH0462359 A JP H0462359A
- Authority
- JP
- Japan
- Prior art keywords
- refrigerant
- oil
- chamber
- expansion chamber
- refrigerant gas
- 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
- 239000003507 refrigerant Substances 0.000 claims abstract description 78
- 239000003921 oil Substances 0.000 claims abstract description 44
- 238000005057 refrigeration Methods 0.000 claims abstract description 27
- 239000010721 machine oil Substances 0.000 claims description 27
- 239000010726 refrigerant oil Substances 0.000 abstract description 3
- 238000000926 separation method Methods 0.000 description 7
- 230000006835 compression Effects 0.000 description 4
- 238000007906 compression Methods 0.000 description 4
- 238000003780 insertion Methods 0.000 description 4
- 230000037431 insertion Effects 0.000 description 4
- 239000002699 waste material Substances 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000005461 lubrication Methods 0.000 description 2
- 239000002184 metal Substances 0.000 description 2
- 238000000465 moulding Methods 0.000 description 2
- 230000002411 adverse Effects 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 238000002474 experimental method Methods 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 210000002784 stomach Anatomy 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
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/02—Centrifugal separation of gas, liquid or oil
Landscapes
- Compressor (AREA)
Abstract
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、圧ａｌｌから吐出される冷凍機油を冷媒から
分離して冷凍サイクル吸込側配管路へ導く空気調和機用
油分離器に係り、特に、分離器を通過する際の圧力損失
を低減した空気調和機用油分離器に関する６
（従来の技術）
近年、冷凍サイクルを用いたセパレート型空気調和機は
、設置の自由度を高めるため、室内ユニットと室外ユニ
ットとを接続する冷媒配管か長くなってきている。この
ような空気調和機においては、室外ユニット内の圧縮機
から冷媒ガスと共に吐出される冷凍機油か上記冷媒配管
に流出すると、長くなった冷媒配管内壁に冷凍機油が付
着して、圧縮機内の冷凍機油が相対的に不足し、潤滑不
良となる。また、流出した冷凍機油は、蒸発器や凝縮器
内部に付着し、それらの熱交換効率を低下させる。Detailed Description of the Invention [Object of the Invention] (Industrial Application Field) The present invention is directed to an air conditioner oil that separates refrigeration oil discharged from a pressure all from a refrigerant and guides it to a refrigeration cycle suction side piping path. 6. Related to separators, especially oil separators for air conditioners that reduce pressure loss when passing through the separator (Prior art) In recent years, separate air conditioners using a refrigeration cycle have been installed freely. To increase the temperature, refrigerant piping connecting indoor units and outdoor units is becoming longer. In such an air conditioner, when the refrigerating machine oil discharged from the compressor in the outdoor unit along with the refrigerant gas flows into the refrigerant pipe, the refrigerating machine oil adheres to the inner wall of the long refrigerant pipe, causing the refrigeration inside the compressor to There is a relative shortage of machine oil, resulting in poor lubrication. Furthermore, the leaked refrigerating machine oil adheres to the inside of the evaporator and condenser, reducing their heat exchange efficiency.
この対策として本出願人は先に第４図に示すような空気
調和機用油分離器ａを開発した。図示するように、冷凍
サイクル吐出側配管！？８ｂ（圧縮ｉｃの吐出ｒｒｓ＞
に油分離室ｄが介設されている。As a countermeasure to this problem, the present applicant has previously developed an oil separator a for air conditioners as shown in FIG. As shown, the refrigeration cycle discharge side piping! ? 8b (compression IC discharge rrs>
An oil separation chamber d is interposed between the two.
この油分離室ｄ内には、金属製のモールからなるデミス
タｅが設けられている。このデミスタｅは、冷媒流入口
ｆから油分離室ｄ内に流入する冷媒ガスに抵抗を与え、
その流速を落とすことによって冷媒カス中の冷凍機油を
分離させるものである。A demister e made of a metal molding is provided in the oil separation chamber d. This demister e provides resistance to the refrigerant gas flowing into the oil separation chamber d from the refrigerant inlet f,
By reducing the flow rate, the refrigerating machine oil in the refrigerant scum is separated.
分離された冷凍機油は、油分離室ｄ底部に流下し、底部
に接続された油戻用キャピラリチューブｇを通って冷凍
サイクル吸込側配管路ｈ（圧縮＠ｃの吸込側）に導かれ
るようになっている。一方、冷凍機油が分離された冷媒
カスは、冷媒流出口ｉを通って凝縮器や蒸発器側へ導か
れる。The separated refrigeration oil flows down to the bottom of the oil separation chamber d, passes through the oil return capillary tube g connected to the bottom, and is guided to the refrigeration cycle suction side piping h (suction side of compression@c). It has become. On the other hand, the refrigerant residue from which the refrigerating machine oil has been separated is guided to the condenser or evaporator side through the refrigerant outlet i.
この空気調和機用油分離器ａによれば、圧縮機Ｃから吐
出される冷凍機油は、デミスタｅによって冷媒ガスから
分離され、油戻用キャピラリチューブｇを通って、長く
なった冷媒配管および蒸発器や凝縮器などをバイパスし
て、冷凍サイクル吸込側配管ｈｌｌｌｌに導かれる。よ
って、圧ｍｍｃの潤滑不良や蒸発器や凝縮器などの熱交
換効率の低下が未然に防止される。According to this air conditioner oil separator a, the refrigerating machine oil discharged from the compressor C is separated from the refrigerant gas by the demister e, passes through the oil return capillary tube g, and is passed through the elongated refrigerant pipe and evaporated. It bypasses the container, condenser, etc., and is led to the refrigeration cycle suction side piping hllll. Therefore, poor lubrication of the pressure mmc and a decrease in heat exchange efficiency of the evaporator, condenser, etc. can be prevented.
（発明が解決しようとする課題）
しかしながら、上記空気調和機用油分離器ａにあっては
、金属モールからなるデミスタｅか冷媒カスに抵抗を与
えることによって、冷媒ガス中から冷凍機油を分離して
いるので、そこでの圧力損失か大きくなってしまう、こ
の圧力損失は、空気調和機の冷凍能力、効率などに悪影
響を与え、性能向上の妨げとなる。(Problem to be Solved by the Invention) However, in the oil separator a for air conditioners, refrigerating machine oil is separated from the refrigerant gas by applying resistance to the refrigerant residue using the demister e made of a metal molding. This pressure loss increases the pressure loss there. This pressure loss adversely affects the refrigerating capacity and efficiency of the air conditioner, and hinders performance improvement.
以上の事情を考慮して創案された本発明の目的は、圧力
損失を大きくすることなく冷媒ガス中から冷凍機油を分
離することができる空気調和機用油分離器を提供するも
のである。An object of the present invention, which was created in consideration of the above circumstances, is to provide an oil separator for air conditioners that can separate refrigerating machine oil from refrigerant gas without increasing pressure loss.
［発明の構成１
（課題を解決するための手段）
上記目的を達成するため本発明に係る空気調和機用油分
離器は、冷凍サイクルの吐出側配管路に、該配管路より
大きな断面積を有する膨張室を介設し、該膨張室内壁に
臨ませて上記配管路の冷媒流入口を設けると共に、上記
配管路の冷媒流出口を上記冷媒流入口の口径より大きく
設定し、且つ上記膨張室内底部に、これに捕集される冷
凍機油を冷凍サイクルの吸込側配管路へ導くための油戻
用キャピラリチューブを接続したことから構成されてい
る。[Structure 1 of the Invention (Means for Solving the Problems) In order to achieve the above object, the oil separator for an air conditioner according to the present invention has a pipe line on the discharge side of a refrigeration cycle that has a larger cross-sectional area than that of the pipe line. A refrigerant inlet of the piping is provided so as to face the wall of the expansion chamber, and a refrigerant outlet of the piping is set to be larger than the diameter of the refrigerant inlet. It is constructed by connecting an oil return capillary tube to the bottom for guiding the refrigerating machine oil collected thereto to the suction side piping path of the refrigeration cycle.
（作 用）
上記構成によれば、冷媒流入１］から！＃張室内に流入
する冷媒ガスは、その流入口か膨張室内壁に臨まされて
いることから、膨張室内壁に流れ当たる。この際、上記
Ｗ６張室は、冷媒流入口より大きな断面積になっている
ので、そのガス流速が減速され、冷媒ガス中から冷凍機
油か分離される６分離された冷凍機油は、膨張室内壁を
伝って膨張室内底部に流下しそこに捕集され、油戻用キ
ャピラリチューブを通って冷凍サイクル吸込側配管路に
導かれる。(Function) According to the above configuration, from refrigerant inflow 1]! #The refrigerant gas flowing into the expansion chamber flows against the expansion chamber wall because its inlet port faces the expansion chamber wall. At this time, since the above-mentioned W6 expansion chamber has a larger cross-sectional area than the refrigerant inlet, the gas flow rate is decelerated and the refrigerating machine oil is separated from the refrigerant gas. The oil flows down to the bottom of the expansion chamber, where it is collected, and is led to the refrigeration cycle suction side piping through the oil return capillary tube.
また、上記膨張室の冷媒流出口は冷媒流入口より大きな
口径になっているので、膨張室から流出する冷媒ガス流
は膨張室に流入する冷媒ガス流より低速となり、上記冷
凍機油の分離が一層促進される。Furthermore, since the refrigerant outlet of the expansion chamber has a larger diameter than the refrigerant inlet, the refrigerant gas flow flowing out of the expansion chamber has a lower speed than the refrigerant gas flow flowing into the expansion chamber, and the separation of the refrigerating machine oil is further facilitated. promoted.
（実線例）
以下に本発明の好適実施例を添付図面に基づいて説明す
る。(Example of solid line) Preferred embodiments of the present invention will be described below based on the accompanying drawings.
第２図は、冷凍サイクルを用いた空気調和機の概略図を
表すものである０図示すように、圧縮Ｉｆｉｌ凝縮器２
、絞り器３、蒸発器４が冷媒配管で接続されて、冷凍サ
イクルが構成されている。FIG. 2 is a schematic diagram of an air conditioner using a refrigeration cycle. As shown in FIG.
, a restrictor 3, and an evaporator 4 are connected through refrigerant piping to form a refrigeration cycle.
この冷凍サイクル上には、冷房時と暖房時とで冷媒の流
れを逆に切り替える四方弁５か備えられており、所謂ヒ
ートポンプ式の空気調和機となっている。上記冷凍サイ
クルの吐出側配管路６（圧縮１１！１の吐出側）には、
冷媒ガス中から冷凍機油を分離して、分離した冷凍機油
を冷凍サイクルの吸込側配管路７（圧ｔａ機１の吸込ｆ
Ｆｌ）へ導くための空気調和機用油分離器８が介設され
ている。This refrigeration cycle is equipped with a four-way valve 5 that reverses the flow of refrigerant between cooling and heating, making it a so-called heat pump type air conditioner. In the discharge side piping line 6 (discharge side of compression 11!1) of the refrigeration cycle,
The refrigerating machine oil is separated from the refrigerant gas, and the separated refrigerating machine oil is transferred to the suction side pipe line 7 of the refrigerating cycle (the suction f of the pressure ta machine 1).
An air conditioner oil separator 8 is provided to guide the oil to Fl).
第１図に示すようにこの空気調和機用油分離器８は、そ
の外郭が、冷凍サイクルの吐出側配管路６に介設された
円筒状の膨張室９から形成されている。この膨張室９は
、その断面積Ｓ２が上記配管路６の断面積Ｓ１より大き
な断面積に形成されており、膨張室９内に流入した冷媒
カスの流速が減速されるようになっている。具体的には
、上記冷媒ガスの流速が１１５以下に減速されるように
断面積Ｓ、、Ｓ２が設定されている。As shown in FIG. 1, the outer shell of this oil separator 8 for an air conditioner is formed from a cylindrical expansion chamber 9 interposed in the discharge side piping path 6 of the refrigeration cycle. The expansion chamber 9 is formed to have a cross-sectional area S2 larger than the cross-sectional area S1 of the piping path 6, so that the flow velocity of the refrigerant scum flowing into the expansion chamber 9 is reduced. Specifically, the cross-sectional areas S and S2 are set so that the flow velocity of the refrigerant gas is reduced to 115 or less.
また、上記膨張室９は、その上部に上記配管路６の入口
側配管６ａが挿入接続されて冷媒流入口１０か形成され
ていると共に、下部に上記配管路６の出口側配管６ｂが
挿入接続されて冷媒流出口１１か形成されている。上記
冷媒流出口１１の口径（断面積）３３は、冷媒流入口１
ｏの口径（断面積）Ｓｌより大きく設定されており、冷
媒流入口１０を通って膨張室９内に流入する冷媒ガス流
よりも、冷媒流出口１１を通って流出する冷媒ガス流の
方か低速となるように構成されている。Further, the expansion chamber 9 has an inlet side pipe 6a of the piping path 6 inserted and connected to the upper part thereof to form a refrigerant inlet 10, and an outlet side piping 6b of the piping path 6 to the lower part thereof is inserted and connected. A refrigerant outlet 11 is formed. The diameter (cross-sectional area) 33 of the refrigerant outlet 11 is the same as that of the refrigerant inlet 1.
o is set larger than the diameter (cross-sectional area) Sl, and the refrigerant gas flow flows out through the refrigerant outlet 11 rather than the refrigerant gas flow flowing into the expansion chamber 9 through the refrigerant inlet 10. It is configured to be slow.
上記入口側配管６ａの冷媒流入口１ｏは、第１図に示す
ように、斜めにカットされて膨張室９内壁に臨むように
なっている。上記カット角度θは、実験によると４０″
〜８０″程度が望ましいことが解った。The refrigerant inlet 1o of the inlet side pipe 6a is cut diagonally so as to face the inner wall of the expansion chamber 9, as shown in FIG. According to the experiment, the above cut angle θ is 40″
It was found that approximately 80″ is desirable.
また、上記膨張室９内底部には、これに捕集される冷凍
機油を、第２図に示す冷凍サイクルの吸込側配管路７（
圧！ａ機１の吸込側）へ導くための油戻用キャピラリチ
ューブ１２が挿入接続されている。この油戻用キャピラ
リチューブ１２の挿入長さは、上記出口側配管６ｂの挿
入長さより短くなっている。すなわち、油戻用キャピラ
リチューブ１２の挿入先端部が出口側配管６ｂの挿入先
端部よりも水平方向からみて低く位置されている。In addition, the refrigerating machine oil collected therein is stored in the inner bottom of the expansion chamber 9 in the suction side piping path 7 (see FIG. 2) of the refrigeration cycle.
Pressure! An oil return capillary tube 12 for guiding the oil to the suction side of the machine 1 is inserted and connected. The insertion length of this oil return capillary tube 12 is shorter than the insertion length of the outlet side piping 6b. That is, the insertion tip of the oil return capillary tube 12 is positioned lower than the insertion tip of the outlet pipe 6b when viewed from the horizontal direction.
よって、膨張室９内底部に捕集された冷凍機油は、出口
側配管６ｂから流出することなく必ず油戻用キャピラリ
チューブ１２から流出することになる。Therefore, the refrigerating machine oil collected at the inner bottom of the expansion chamber 9 always flows out from the oil return capillary tube 12 without flowing out from the outlet side pipe 6b.
なお、図中１は、膨張室９内底部に捕集される冷凍機油
が５０ｃｃ以上となる寸法になっている。In addition, 1 in the figure is a dimension in which the amount of refrigerating machine oil collected at the inner bottom of the expansion chamber 9 is 50 cc or more.
以上の構成からなる本実緒例の作用について述べる。The operation of this practical example with the above configuration will be described.
第１図に示すように、冷媒流入口１０から膨張室９内に
流入する冷媒ガスは、その流入口１０が斜めにカットさ
れて膨張室９内壁に臨まされていることから、図中矢印
１３で示すように膨張室９内壁に流れ当たる。この際、
上記膨張室９の断面積Ｓ２が冷媒流入口１０の断面積Ｓ
１より大きいことから、膨張室９内に流入する冷媒ガス
は、そのカス流速が減速されて略１１５以下のガス流速
となる。よって、冷媒ガスが膨張室９内壁に流れ当った
ときに冷媒ガス中から冷凍機油が分離される。As shown in FIG. 1, the refrigerant gas flows into the expansion chamber 9 from the refrigerant inlet 10 because the inlet 10 is cut diagonally and faces the inner wall of the expansion chamber 9. The liquid flows against the inner wall of the expansion chamber 9 as shown in . On this occasion,
The cross-sectional area S2 of the expansion chamber 9 is the cross-sectional area S of the refrigerant inlet 10.
1, the refrigerant gas flowing into the expansion chamber 9 has its gas flow velocity reduced to a gas flow velocity of about 115 or less. Therefore, when the refrigerant gas flows against the inner wall of the expansion chamber 9, the refrigerating machine oil is separated from the refrigerant gas.
また、上記膨張室９の冷媒流出口１１の口径（Ｉｌｆｒ
而１）面ｌが冷媒流入口１０の口径（断面積）Ｓｌより
大きくなっているので、膨張室９がら流出する冷媒カス
流は膨張室９に流入する冷媒ガス流より低速となり、上
記冷凍機油の分離が一層促進される。Also, the diameter of the refrigerant outlet 11 of the expansion chamber 9 (Ilfr
1) Since the surface l is larger than the diameter (cross-sectional area) Sl of the refrigerant inlet 10, the refrigerant waste flow flowing out of the expansion chamber 9 has a lower speed than the refrigerant gas flow flowing into the expansion chamber 9, and the refrigerating machine oil separation is further promoted.
このように、本実施例の油分離器８は、冷媒ガス通路を
拡大することによって冷媒ガス流速を減速させ冷凍機油
の分離をおこなっているので、圧力損失が殆ど生じない
。よって、この圧力損失に起因する空気調和機の冷凍能
力の低下、効率の低下などが生じないことになる。また
、本実施例の油分離器８は、第４図に示す油分離器ａの
如くデミスタｅを内蔵する必要がなことがら、低コスト
で製造できる。In this way, the oil separator 8 of the present embodiment reduces the refrigerant gas flow velocity and separates the refrigerating machine oil by enlarging the refrigerant gas passage, so almost no pressure loss occurs. Therefore, there will be no reduction in the refrigerating capacity or efficiency of the air conditioner due to this pressure loss. Furthermore, the oil separator 8 of this embodiment can be manufactured at low cost because it does not require a built-in demister e like the oil separator a shown in FIG.
分離された冷凍機油は、膨張室９内壁を伝って膨張室内
底部に流下しそこに捕集される。捕集された冷凍機油１
４は、油戻用キャピラリチューブ１２を通って、第２図
に示す冷凍サイクル吸込側配管路７に導かれる。一方、
冷凍機油１ ＝１か分離された冷媒ガスは、冷媒流出口
１１を通って、第２図に示す四方弁５に導かれる。The separated refrigerating machine oil flows down the inner wall of the expansion chamber 9 to the bottom of the expansion chamber and is collected there. Collected refrigeration oil 1
4 passes through the oil return capillary tube 12 and is led to the refrigeration cycle suction side piping path 7 shown in FIG. on the other hand,
The separated refrigerant gas passes through the refrigerant outlet 11 and is guided to the four-way valve 5 shown in FIG.
以上説明したように、第２図に示す圧縮機１から冷媒ガ
スと共に吐出される冷凍機油１４は、上記空気調和機用
油分離器８によって冷媒ガスから分離され、四方弁５．
凝縮器２．絞り器３．蒸発器４などを接続する冷媒配管
をバイパスして、冷凍サイクル吸込側配管路７に短絡さ
れて導かれる。この結果、冷凍機油１４による圧縮１１
９１１の潤滑が常に良好に維持されると共に、冷凍機油
１４が凝縮器２や蒸発器４内部に付着することによって
生じる熱交換率の低下が未然に防止される。As explained above, the refrigerating machine oil 14 discharged together with the refrigerant gas from the compressor 1 shown in FIG. 2 is separated from the refrigerant gas by the air conditioner oil separator 8, and the four-way valve 5.
Condenser 2. Squeezer 3. It bypasses the refrigerant piping connecting the evaporator 4 and the like, and is short-circuited and guided to the refrigeration cycle suction side piping path 7. As a result, compression 11 by the refrigerating machine oil 14
911 is always kept well lubricated, and a decrease in heat exchange efficiency caused by adhesion of refrigerating machine oil 14 inside condenser 2 or evaporator 4 is prevented.
また、上記膨張室９は、圧縮機１から吐出された冷媒カ
ス流を減速させるものなので、圧１ａ機１の膨張形マフ
ラーとしても機能する。Further, since the expansion chamber 9 decelerates the refrigerant waste flow discharged from the compressor 1, it also functions as an expansion type muffler of the pressure 1a machine 1.
本発明の変形実施例を第３図ｆａ）（ｂ）に示す。A modified embodiment of the present invention is shown in FIGS. 3fa and 3b.
図示するように、この変形実施例は、膨張室９への入口
側配管６ａか曲げられて、冷媒流入口１０が膨張室９内
壁に臨まされている点か第１図に示す前実施例と胃なり
、その他は全く同様の構成となっている。詳しくは、上
記入口側配管６ａは、第３図（ａ）に示すように、冷媒
流入口１０から吐出される冷媒ガスか円筒状の膨張室９
内壁に沿って旋回するように曲げられている。なお、膨
張室９内壁に沿って、冷媒カス流の旋回を案内する螺旋
状のガイドフィン（図示せず）を設けてもよい。As shown in the figure, this modified embodiment differs from the previous embodiment shown in FIG. The stomach and other features are exactly the same. Specifically, as shown in FIG. 3(a), the inlet side pipe 6a is connected to the refrigerant gas discharged from the refrigerant inlet 10 to the cylindrical expansion chamber 9.
It is curved to pivot along the inner wall. Note that a spiral guide fin (not shown) may be provided along the inner wall of the expansion chamber 9 to guide the swirling of the refrigerant waste flow.
この変形実施例にあっては、冷媒流入口１０からの冷媒
ガスが膨張室９内壁に沿って旋回することから、冷媒ガ
ス中の冷凍機油は遠心作用を受け、冷媒ガス中からの冷
凍機油の分離が一層促進されることになる。In this modified embodiment, since the refrigerant gas from the refrigerant inlet 10 swirls along the inner wall of the expansion chamber 9, the refrigerating machine oil in the refrigerant gas is subjected to centrifugal action, and the refrigerating machine oil from the refrigerant gas is Separation will be further promoted.
［発明の効果］
以上説明したように本発明によれば、圧力損失を大きく
することなく冷媒カス中から冷凍機油を分離することが
できるという優れた効果を発揮することができる。[Effects of the Invention] As explained above, according to the present invention, it is possible to exhibit the excellent effect of being able to separate refrigerant oil from refrigerant scum without increasing pressure loss.
第１図は本発明の一実施例を表す空気調和機用油分離器
の一１断面図、第２図は上記空気調和機用油分離器を備
えた空気調和機の冷凍サイクル図、第３図ｆｔ＋）は本
発明の変形実施例を表す空気調和機用油分離器の側断面
図、第３図（ａ）は第３図（ｂ）の上面図、第４図は本
出顯人か先に開発した空気調和機用油分離器の側断面図
である。
図中、６は冷凍サイクルの吐出側配管路、７は冷凍サイ
クルの吸込側配管路、８は空気調和機用油分離器、９は
膨張室、１０は冷！ａ流入口、１１は冷媒流出口、１２
は油戻用キャピラリチューブ、１４は冷凍機油である。FIG. 1 is a sectional view of an oil separator for an air conditioner representing an embodiment of the present invention, FIG. 2 is a refrigeration cycle diagram of an air conditioner equipped with the oil separator for an air conditioner, and FIG. Figure ft+) is a side sectional view of an oil separator for an air conditioner representing a modified embodiment of the present invention, Figure 3(a) is a top view of Figure 3(b), and Figure 4 is the author of this publication. FIG. 2 is a side sectional view of the previously developed oil separator for air conditioners. In the figure, 6 is a piping path on the discharge side of the refrigeration cycle, 7 is a piping path on the suction side of the refrigeration cycle, 8 is an oil separator for an air conditioner, 9 is an expansion chamber, and 10 is a cold! a inlet, 11 refrigerant outlet, 12
14 is a capillary tube for oil return, and refrigeration oil.
Claims (1)
な断面積を有する膨張室を介設し、該膨張室内壁に臨ま
せて上記配管路の冷媒流入口を設けると共に、上記配管
路の冷媒流出口を上記冷媒流入口の口径より大きく設定
し、且つ上記膨張室内底部に、これに捕集される冷凍機
油を冷凍サイクルの吸込側配管路へ導くための油戻用キ
ャピラリチューブを接続したことを特徴とする空気調和
機用油分離器。1. An expansion chamber having a larger cross-sectional area than that of the piping is provided in the discharge side piping of the refrigeration cycle, and a refrigerant inlet of the piping is provided facing the wall of the expansion chamber. The refrigerant outlet is set larger than the diameter of the refrigerant inlet, and an oil return capillary tube is connected to the bottom of the expansion chamber to guide the refrigerating machine oil collected thereto to the suction side piping of the refrigeration cycle. An oil separator for air conditioners characterized by:
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP17315190A JPH0462359A (en) | 1990-06-29 | 1990-06-29 | Oil separator for air conditioner |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP17315190A JPH0462359A (en) | 1990-06-29 | 1990-06-29 | Oil separator for air conditioner |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH0462359A true JPH0462359A (en) | 1992-02-27 |
Family
ID=15955050
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP17315190A Pending JPH0462359A (en) | 1990-06-29 | 1990-06-29 | Oil separator for air conditioner |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0462359A (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5915367A (en) * | 1996-09-03 | 1999-06-29 | Hitachi, Ltd. | Igniter for internal combustion engine having outer packing case equipped with coil and igniter unit |
| EP1248057A3 (en) * | 2001-03-26 | 2004-01-14 | Visteon Global Technologies, Inc. | Oil separator |
| EP1975370A1 (en) * | 2007-03-28 | 2008-10-01 | Fujitsu General Limited | Rotary compressor with accumulator and heat pump system |
| JP4699758B2 (en) * | 2002-10-25 | 2011-06-15 | ハネウェル・インターナショナル・インコーポレーテッド | Compositions containing fluorine-substituted olefins |
| WO2014083674A1 (en) * | 2012-11-30 | 2014-06-05 | 三菱電機株式会社 | Compressor, refrigeration cycle device, and heat pump hot-water supply device |
| JP5892261B2 (en) * | 2012-11-30 | 2016-03-23 | 三菱電機株式会社 | Refrigeration cycle apparatus and heat pump water heater |
| WO2016181558A1 (en) * | 2015-05-14 | 2016-11-17 | 三菱電機株式会社 | Compressor muffler |
-
1990
- 1990-06-29 JP JP17315190A patent/JPH0462359A/en active Pending
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5915367A (en) * | 1996-09-03 | 1999-06-29 | Hitachi, Ltd. | Igniter for internal combustion engine having outer packing case equipped with coil and igniter unit |
| US6055969A (en) * | 1996-09-03 | 2000-05-02 | Hitachi, Ltd. | Igniter for internal combustion engine having outer packing case equipped with coil and igniter unit |
| EP1248057A3 (en) * | 2001-03-26 | 2004-01-14 | Visteon Global Technologies, Inc. | Oil separator |
| JP4699758B2 (en) * | 2002-10-25 | 2011-06-15 | ハネウェル・インターナショナル・インコーポレーテッド | Compositions containing fluorine-substituted olefins |
| EP1975370A1 (en) * | 2007-03-28 | 2008-10-01 | Fujitsu General Limited | Rotary compressor with accumulator and heat pump system |
| WO2014083674A1 (en) * | 2012-11-30 | 2014-06-05 | 三菱電機株式会社 | Compressor, refrigeration cycle device, and heat pump hot-water supply device |
| WO2014083901A1 (en) * | 2012-11-30 | 2014-06-05 | 三菱電機株式会社 | Compressor, refrigeration cycle device, and heat pump hot-water supply device |
| JP5892261B2 (en) * | 2012-11-30 | 2016-03-23 | 三菱電機株式会社 | Refrigeration cycle apparatus and heat pump water heater |
| JPWO2014083901A1 (en) * | 2012-11-30 | 2017-01-05 | 三菱電機株式会社 | Refrigeration cycle apparatus and heat pump water heater |
| WO2016181558A1 (en) * | 2015-05-14 | 2016-11-17 | 三菱電機株式会社 | Compressor muffler |
| JPWO2016181558A1 (en) * | 2015-05-14 | 2018-01-11 | 三菱電機株式会社 | Compressor muffler |
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