JPH062688A - Refrigerant compressor - Google Patents
Refrigerant compressorInfo
- Publication number
- JPH062688A JPH062688A JP4160673A JP16067392A JPH062688A JP H062688 A JPH062688 A JP H062688A JP 4160673 A JP4160673 A JP 4160673A JP 16067392 A JP16067392 A JP 16067392A JP H062688 A JPH062688 A JP H062688A
- Authority
- JP
- Japan
- Prior art keywords
- pipe
- compressor
- gas
- refrigerant
- chamber
- 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.)
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Links
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- Applications Or Details Of Rotary Compressors (AREA)
- Pipe Accessories (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明はロータリ圧縮機の圧縮中
のガスを冷却するために圧縮室に凝縮した液体冷媒を供
給することに関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to the supply of condensed liquid refrigerant to a compression chamber to cool the gas being compressed in a rotary compressor.
【０００２】[0002]
【従来の技術】最近、ロータリ圧縮機（以下圧縮機とい
う）は、フロンガス対応による冷媒の変更に伴い、従来
同等の寿命をもたせるためには、圧縮機の運転中の温度
を低減させる技術が重要となっている。2. Description of the Related Art Recently, a rotary compressor (hereinafter referred to as "compressor") is required to have a technique for reducing the temperature during operation of the compressor in order to have a life equivalent to that of a conventional compressor due to the change of refrigerant due to the use of CFC gas. Has become.
【０００３】以下、図面を参照しながら従来の圧縮機温
度を低減させる技術について説明する。図２〜６は、特
公昭３９−２４２６０号公報に示されている圧縮機であ
る。図において、図２は気密外匣２を有する気密圧縮機
１を示し、外匣２内にはシリンダー即ち外匣５内に作っ
た環状の室即ち圧縮室４を有する冷媒圧縮機３を設け
る。室４内には電動機９から下方へ延びる駆動軸８と一
体に構成した偏心部７で駆動する回転子６を回転し得る
如く設ける。支持主枠１２と共動して、シリンダーの環
状圧縮室４の上方端壁を構成する軸受１１で偏心部７の
上方で軸８を支持し電動機で回転するようにする。A conventional technique for reducing the compressor temperature will be described below with reference to the drawings. 2 to 6 show a compressor disclosed in Japanese Patent Publication No. 39-24260. In FIG. 2, FIG. 2 shows an airtight compressor 1 having an airtight outer casing 2, in which a refrigerant compressor 3 having an annular chamber or compression chamber 4 formed in a cylinder or outer casing 5 is provided. In the chamber 4, a rotor 6 driven by an eccentric portion 7 formed integrally with a drive shaft 8 extending downward from the electric motor 9 is provided so as to be rotatable. A shaft 11 is supported above the eccentric portion 7 by a bearing 11 which constitutes the upper end wall of the annular compression chamber 4 of the cylinder in cooperation with the support main frame 12 so that the shaft 8 is rotated by an electric motor.
【０００４】主枠１２は又圧縮機３を外匣内に支持す
る。室３の反対側即ち下方の端壁は同様に軸８の下端を
軸受１０ａ内に支持する軸受板１０で構成する。The main frame 12 also supports the compressor 3 in an outer casing. The opposite or lower end wall of the chamber 3 likewise comprises a bearing plate 10 which supports the lower end of the shaft 8 in a bearing 10a.
【０００５】図３に示すように、シリンダー５には半径
方向の溝１３を設け、その中に翼板１４を摺動自在に設
けて、これを回転子６の周面６ａに圧接し、室４を低圧
側４ａと高圧側４ｂとに分割する。図示の実施例では翼
板１４の端部は、半径方向の溝１３の後部を形成する拡
大した開口１３ａ内に設けたバネ１６で回転子の周面に
圧接する。運転中回転子６は、偏心部７によって、室内
を偏心的に回転せしめられるから回転子の周面６ａは環
状室の次々の部分と、逐次密封関係に動き、かくして周
知の如く回転方向において、それより前方にあるガスを
押すからガスは室の端部、回転子の周面６ａおよび回転
子の高圧側で囲まれる漸次減少する空所内で圧縮され
る。As shown in FIG. 3, the cylinder 5 is provided with a radial groove 13 in which a vane 14 is slidably provided, which is pressed against the peripheral surface 6a of the rotor 6 to form a chamber. 4 is divided into a low pressure side 4a and a high pressure side 4b. In the illustrated embodiment, the ends of the vanes 14 are pressed against the peripheral surface of the rotor by a spring 16 provided in an enlarged opening 13a forming the rear of the radial groove 13. During operation, the rotator 6 is eccentrically rotated in the chamber by the eccentric portion 7, so that the peripheral surface 6a of the rotor moves in successive sealing relation with the successive portions of the annular chamber, thus, as is well known, in the rotational direction. Since the gas in front of it is pushed, the gas is compressed in a gradually decreasing cavity surrounded by the end of the chamber, the peripheral surface 6a of the rotor and the high pressure side of the rotor.
【０００６】図４に示す如く、密封圧縮機１は、吸込管
２０を通じて、蒸発器１５から吸込ガスを受けるように
冷凍方式内に接続するものである。吸込ガスを吸込管２
０から環状室４の低圧側４ａへ供給する装置を設ける。
即ち、図３に示す如くこの装置はシリンダー５に設けら
れ、環状室４と連通する吸込口１７を含んでいる。吸込
口１７は低圧ガスを圧縮室４の低圧側４ａへ供給し、そ
こでガスは回転子６が室内で回転する際回転子６の周面
と、環状室の両側面と翼板１４の高圧側１４ａとの間で
圧縮される。As shown in FIG. 4, the hermetic compressor 1 is connected to the inside of the refrigeration system so as to receive the suction gas from the evaporator 15 through the suction pipe 20. Suction gas suction pipe 2
A device for supplying 0 to the low pressure side 4a of the annular chamber 4 is provided.
That is, as shown in FIG. 3, this device is provided in the cylinder 5 and includes a suction port 17 communicating with the annular chamber 4. The suction port 17 supplies the low-pressure gas to the low-pressure side 4a of the compression chamber 4, where the gas is in contact with the peripheral surface of the rotor 6 when the rotor 6 rotates in the chamber, both side surfaces of the annular chamber and the high-pressure side of the vane 14. 14a and compressed.
【０００７】高圧ガスを環状室４の高圧側から気密外匣
２内へ導くために吐出口１８と吐出室１９とからなる装
置を設ける。吐出室１９内には吐出口１８から出るガス
を適当に圧縮しかつ圧縮室４へのガスの逆流を防止する
適当な弁２１を設ける。図２に示す如く、高圧ガス吐出
室１９から圧縮機の上方端壁を構成する主枠１２内の通
路２５を経て気密外匣２内へ流入する。高圧ガスは電動
機９の周りを上方へ流れた後、外匣上端の図示しない適
当な吐出装置を経て、気密外匣２外へ出、吐出管２１
（図４に示す）を経て、凝縮器２２内へ流入し、冷凍方
式の他の部分で冷媒が吸収した熱を放出する。凝縮器２
２内のガスは冷却すると凝縮するから凝縮器の後段内の
冷媒は大部分液状である。冷凍方式の作動中に液体冷媒
を凝縮器圧力から蒸発器圧力へ膨脹させるために凝縮器
および蒸発器間に適当な膨脹装置を設ける。図示した実
施例では膨脹装置は凝縮器と蒸発器との間に設けた毛細
管２３である。A device including a discharge port 18 and a discharge chamber 19 is provided to guide the high-pressure gas from the high-pressure side of the annular chamber 4 into the airtight casing 2. Provided in the discharge chamber 19 is a suitable valve 21 for appropriately compressing the gas discharged from the discharge port 18 and preventing backflow of the gas into the compression chamber 4. As shown in FIG. 2, it flows from the high-pressure gas discharge chamber 19 into the airtight outer casing 2 through the passage 25 in the main frame 12 which constitutes the upper end wall of the compressor. After the high-pressure gas flows upward around the electric motor 9, it goes out of the airtight outer casing 2 through an appropriate discharge device (not shown) at the upper end of the outer casing, and the discharge pipe 21
After passing through (as shown in FIG. 4), the heat flows into the condenser 22 and releases the heat absorbed by the refrigerant in the other part of the refrigeration system. Condenser 2
Since the gas in 2 is condensed when cooled, the refrigerant in the latter stage of the condenser is mostly liquid. A suitable expansion device is provided between the condenser and the evaporator to expand the liquid refrigerant from the condenser pressure to the evaporator pressure during operation of the refrigeration system. In the illustrated embodiment, the expansion device is a capillary tube 23 located between the condenser and the evaporator.
【０００８】図２は潤滑油を装置の種々の軸受表面およ
び他の運動部分に供給する配置を示す。即ち、密封外匣
の下部には潤滑剤２４の溜がある。油の量は軸８の下端
および圧縮機の下方端壁１０の一部が油内にほぼ漬かる
ような量にする。潤滑剤を圧縮機の種々の運動物分へ送
る装置を設ける。即ち、軸８内には比較的大きな軸方向
の通路を設け、これを溜２４と連通させてあるから軸が
回転すると、軸方向の通路２６に入る潤滑剤は直ちに軸
８と同一回転速度になる。しかる時速は遠心力により潤
滑剤を軸方向通路２６の内面に向かって外方へ流し、次
いで通路２６に沿って上方へ流す、軸の周辺に設けた油
の吐出口から油を圧縮機の種々の軸受へ供給する。夫々
底板１０および主枠１２に設けた油戻し通路２７，２８
は過剰の油を外匣下部の油溜２４へ戻す。外匣内の油は
圧縮機および電動機上を絶えず流れているから、溜２４
内の油は比較的高温である。FIG. 2 shows an arrangement for supplying lubricating oil to various bearing surfaces and other moving parts of the device. That is, there is a reservoir of the lubricant 24 in the lower part of the sealed case. The amount of oil is such that the lower end of the shaft 8 and part of the lower end wall 10 of the compressor are substantially submerged in the oil. A device is provided for delivering the lubricant to the various moving parts of the compressor. That is, since a relatively large axial passage is provided in the shaft 8 and communicates with the reservoir 24, when the shaft rotates, the lubricant entering the axial passage 26 immediately reaches the same rotational speed as the shaft 8. Become. At a certain speed, centrifugal force causes the lubricant to flow outward toward the inner surface of the axial passage 26 and then upward along the passage 26. The oil is discharged from the compressor through various oil discharge ports provided in the periphery of the shaft. Supply to bearings. Oil return passages 27 and 28 provided in the bottom plate 10 and the main frame 12, respectively
Returns excess oil to the oil sump 24 in the lower part of the outer casing. Since the oil in the outer casing is constantly flowing over the compressor and electric motor,
The oil inside is relatively hot.
【０００９】前述の型の圧縮機を約２１℃の空気を蒸発
器１５に吹きつけ、そして、２８℃の空気を凝縮器２２
に吹きつける冷凍方式内で試験すると、密封外匣内の冷
凍ガスの圧力は約２１kg／cm2であった。そして、環状
室の高圧側４ｂ内の圧力は約２３kg／cm2で最高値に達
した。かかる冷凍方式の吸込圧力は約１５．７５kg／cm
2であって吐出圧力より約５．２５kg／cm2丈け少なく吸
込ガスの温度は約１５．５〜２１℃である。もちろん、
前記圧縮機の種々の用途および冷凍方式の特定の設計特
徴が外匣内のガスの圧力に影響を及ぼす。併し乍ら、前
述の代表的数字から解るように密封外匣２内の圧力は吸
込圧力より相当高い。吸込ガスを室４内で約５．２５kg
／cm2から約２３kg／cm2に圧縮するときはこのガスの温
度は圧縮中に相当増加する。例えば、前述の冷凍方式で
はガスの温度は約２４℃から１２０℃に増加する。この
温度は大抵の作動条件下で電動機の作動温度を適当に保
つように計算した割合で、電動機から熱を取り去るには
高すぎる。従って、ガスをこの高温で吐出するときは電
動機９の冷却が不充分となり、電動機の絶縁又は巻線を
損傷することがしばしばある。A compressor of the type described above blows air at about 21 ° C. into the evaporator 15 and 28 ° C. air at the condenser 22.
The pressure of the frozen gas in the sealed outer casing was about 21 kg / cm 2 when tested in a refrigerating method in which it was sprayed on the. The pressure inside the high pressure side 4b of the annular chamber reached a maximum value of about 23 kg / cm 2 . The suction pressure of this refrigeration system is about 15.75 kg / cm
2 , which is about 5.25 kg / cm 2 less than the discharge pressure, and the temperature of the suction gas is about 15.5 to 21 ° C. of course,
The various uses of the compressor and the particular design features of the refrigeration system influence the pressure of the gas in the casing. However, as can be seen from the above-mentioned typical numbers, the pressure inside the sealed casing 2 is considerably higher than the suction pressure. About 5.25kg of suction gas in chamber 4
When compressing from / cm 2 to about 23 kg / cm 2 , the temperature of this gas increases considerably during compression. For example, in the refrigeration system described above, the temperature of the gas increases from about 24 ° C to 120 ° C. This temperature is too high to remove heat from the motor at a rate calculated to keep the motor operating temperature adequate under most operating conditions. Therefore, when the gas is discharged at this high temperature, the electric motor 9 is insufficiently cooled, and the insulation or winding of the electric motor is often damaged.
【００１０】ガスが電動機上を通る際、電動機を適当に
冷却するように吐出ガスの温度を充分低い温度に保つた
めに本発明によれば、回転子の各圧縮サイクル中に少量
の液体冷媒を圧縮室４内に注入して吐出ガスの最終温度
を減少する装置を設ける。即ち、圧縮室４の高圧側４ｂ
に注入口３１を設ける。本発明の好ましい実施例では圧
縮室４の高圧側４ｂのガス圧が吐出圧力の５０〜９５％
である各サイクルの短い時間中は吐出口３１は開き、そ
の他の時間中は回転子６の端部３２が吐出口３１を完全
に覆うように、吐出口３１を圧縮室４の高圧側４ｂに設
ける。According to the present invention, a small amount of liquid refrigerant is added during each compression cycle of the rotor in order to keep the temperature of the discharge gas sufficiently low to adequately cool the motor as it passes over the motor. A device for injecting into the compression chamber 4 to reduce the final temperature of the discharge gas is provided. That is, the high pressure side 4b of the compression chamber 4
An injection port 31 is provided in. In the preferred embodiment of the present invention, the gas pressure on the high pressure side 4b of the compression chamber 4 is 50 to 95% of the discharge pressure.
The discharge port 31 is opened during the short time of each cycle, and the discharge port 31 is opened to the high pressure side 4b of the compression chamber 4 so that the end portion 32 of the rotor 6 completely covers the discharge port 31 during the other time. Set up.
【００１１】図２および図４に示すように、冷凍方式の
凝縮した冷媒源から液体冷媒を注入口３１へ供給する装
置を設ける。即ち、方式中の凝縮器２２の後段と接続し
て凝縮器から液即ち凝縮した冷媒を注入口３１へ導く液
体冷媒供給通路を設ける。図２に示す如く、この通路は
管３３と太い管３４とからなり、この管３４は外匣２内
に入って油溜２４内を上方へ至り、そこで注入口３１と
一致して設けた連結短管３５により底板１０に接続す
る。細い毛細管３６を連結短管３５の中心を通し管３４
内の液体冷媒中に常に浸漬して注入口３１へ至る液体冷
媒供給通路を形成する。管３３と３６との間の開口は液
体冷媒が大きい管３４内へ流入することを可能にする。
この配置は管３６の端部を覆う。液体冷媒溜を作り大き
い管３６内に冷媒ガスのトラップ即ち膨脹室３６ａを作
る。後で詳細に説明するように、膨脹室３６ａは回転子
の回転中、注入口３１の間歇的開閉に基いて発生される
振動即ち液体の衝撃を緩和する。As shown in FIGS. 2 and 4, a device for supplying a liquid refrigerant to the inlet 31 from a condensed refrigerant source of a refrigeration system is provided. That is, a liquid refrigerant supply passage is provided which is connected to the subsequent stage of the condenser 22 in the system and guides the liquid, that is, the condensed refrigerant from the condenser to the inlet 31. As shown in FIG. 2, this passage is composed of a pipe 33 and a thick pipe 34. The pipe 34 enters the outer casing 2 and reaches the inside of the oil reservoir 24 upward, where it is provided so as to coincide with the inlet 31. It is connected to the bottom plate 10 by a short pipe 35. A thin capillary tube 36 is inserted through the center of the connecting short tube 35
It is constantly immersed in the liquid refrigerant inside to form a liquid refrigerant supply passage leading to the inlet 31. The opening between tubes 33 and 36 allows liquid refrigerant to flow into large tube 34.
This arrangement covers the end of tube 36. A liquid refrigerant reservoir is created to create a refrigerant gas trap or expansion chamber 36a in a large tube 36. As will be described later in detail, the expansion chamber 36a absorbs vibrations, that is, liquid shocks, which are generated due to the intermittent opening and closing of the inlet 31 during the rotation of the rotor.
【００１２】図４の線図で示す如く、注入口３１は回転
子の接触即ち周面６ａが環状室の点Ａから点Ｃまで動く
期間以外の回転子６のサイクル中のすべての時間中閉じ
られている。図５から解るように図示した圧縮機の注入
口３１の位置は室の中心を通過し、そして、翼板１４の
中心線に対して約１２度の角度を有する直線上で翼板１
４の高圧側１４ａに隣接している。点Ａでは回転子の端
部３２は液体注入口３１をちょうど開き始め、そして点
Ｃでは再び注入口を閉じる。As shown in the diagram of FIG. 4, the inlet 31 is closed for all the time during the cycle of the rotor 6 except during the rotor contact or the circumferential surface 6a moving from point A to point C of the annular chamber. Has been. As can be seen in FIG. 5, the position of the inlet 31 of the compressor shown passes through the center of the chamber and on a straight line having an angle of about 12 degrees with the centerline of the vane 14.
4 is adjacent to the high pressure side 14a. At point A the end 32 of the rotor just begins to open the liquid inlet 31 and at point C closes the inlet again.
【００１３】図示した実施例では点Ａの位置は圧縮衝程
の終了より約２４５度進んでいる。即ち、翼板１４の中
心線より前方にある。図面に示した寸法を有する試験し
た圧縮機では回転子表面６ａが点Ａにあるときの室４の
高圧側４ｂ内のガスは約１１．２kg／cm2即ち、外匣内
のガス圧の約５０％である。点Ｃは圧縮衝程の終了より
約１４０度前方にあり、即ち、翼板１４の中心線より前
方にある。試験した圧縮機の回転子が点Ｃで示す位置に
あるときは室の高圧側４ｂ内の圧力は約２０．３kg／cm
2であって、これは外匣２内の圧力の約９３％である。
ガス注入口３１を経て、逆流するのを防ぐには室内の圧
力が外匣内の圧力を超過するとき、又は外匣内の圧力よ
りわずか低い凝縮器内の圧力を超過するとき回転子６の
端部３２によって完全に塞がれる位置に注入口を設けな
ければならない。液体注入口３１が開かれるサイクルの
部分では試験した圧縮機の室４の高圧側４ｂの平均ガス
圧力は約１５．７５kg／cm2である。これは吐出圧力よ
り平均して５．２５kg／cm2丈け低く膨脹室内へ注入さ
れる液体冷媒を若干膨脹して室内で圧縮されるガスを冷
却するが、圧縮機の能率に著しい影響を与えない。図３
および図５から解るように冷媒が圧縮機中へ注入される
間吸込口１７は閉じている。即ち、環状室４と接触する
周面６ａは吸込口１７の縁１７ａを通過し、注入口３１
が開かれる前に吸入口を完全に塞ぐ。このようにして室
の高圧側４ｂ内に閉じ込められている吸込ガスは全部液
体冷媒を冷却のために前記室内に注入するときに室内に
ある。In the illustrated embodiment, the position of point A is about 245 degrees ahead of the end of the compression stroke. That is, it is in front of the center line of the blade 14. In the tested compressor having the dimensions shown in the drawing, the gas in the high pressure side 4b of the chamber 4 when the rotor surface 6a is at point A is about 11.2 kg / cm 2, that is, about the gas pressure in the outer casing. 50%. Point C is approximately 140 degrees forward of the end of the compression stroke, ie, forward of the vane 14 centerline. When the rotor of the tested compressor is in the position indicated by point C, the pressure in the high pressure side 4b of the chamber is about 20.3 kg / cm.
2 , which is about 93% of the pressure in the outer casing 2.
In order to prevent reverse flow through the gas inlet 31, when the pressure in the chamber exceeds the pressure in the outer casing, or when the pressure in the condenser slightly lower than the pressure in the outer casing exceeds the pressure in the rotor 6, The inlet must be located where it is completely blocked by the end 32. In the part of the cycle in which the liquid inlet 31 is opened, the average gas pressure on the high-pressure side 4b of the compressor chamber 4 tested is about 15.75 kg / cm 2 . This is lower than the discharge pressure by 5.25 kg / cm 2 on average and slightly expands the liquid refrigerant injected into the expansion chamber to cool the gas compressed in the chamber, but it has a significant effect on the efficiency of the compressor. Absent. Figure 3
And as can be seen from FIG. 5, the suction port 17 is closed while the refrigerant is injected into the compressor. That is, the peripheral surface 6a that contacts the annular chamber 4 passes through the edge 17a of the suction port 17 and
Fully block inlet before opening. The suction gas thus confined in the high pressure side 4b of the chamber is all inside the chamber when the liquid refrigerant is injected into it for cooling.
【００１４】各圧縮サイクル中室４内に注入される冷い
液体冷媒が、室４ｂ内の比較的熱い半ば圧縮したガスと
遭遇するとき蒸発してガス状になる。液体冷媒が蒸発し
てガス状になるとき半ば圧縮したガスから奪われる熱は
室４ｂ内のガスの温度を著しく低下するから吐出口１８
および通路２５から出るガスは注入された液体を加えな
い場合よりも一様な低温になる。During each compression cycle, the cold liquid refrigerant injected into chamber 4 evaporates into a gas when it encounters the relatively hot, semi-compressed gas in chamber 4b. When the liquid refrigerant evaporates into a gas state, the heat removed from the partially compressed gas significantly lowers the temperature of the gas in the chamber 4b, so the discharge port 18
And the gas exiting passage 25 will be at a substantially lower temperature than if no injected liquid was added.
【００１５】本発明の試験した実施例ではガスの温度は
約８２℃に低下したが、室内に液体冷媒を注入しないと
きの吐出温度は１１０℃である。８２℃のこの大きい密
度のガスは充分な冷却能力を有し、電動機の周りを通す
ときその熱を全部除去し電動機を安全な作動温度に保
つ。さらに、圧縮室４内のガスの温度が減少するためガ
スは一層容易に圧縮され圧縮機の能率を著しく阻害する
ことがない。In the tested examples of the present invention, the temperature of the gas dropped to about 82 ° C., but the discharge temperature when the liquid refrigerant was not injected into the chamber was 110 ° C. This high density gas at 82 ° C has sufficient cooling capacity to remove all of its heat when passing around the motor, keeping it at a safe operating temperature. Furthermore, since the temperature of the gas in the compression chamber 4 is reduced, the gas is more easily compressed and does not significantly impair the efficiency of the compressor.
【００１６】前に述べたように回転子６の端部３２にす
る注入口３１の連続開閉作動は適当に緩衝しない限り噪
音の原因となる脈動又は振動を生ずる。この脈動が冷凍
方式の他の部分へ伝わることを防止するために図示した
実施例では液体冷媒を注入口３１へ導く通路内に膨脹室
を設ける。前述の如く管３４は管３３から液体冷媒を供
給される膨脹室３６ａを構成する。膨脹室即ち、溜３６
ａは外匣の底部内の熱い潤滑油を貫通して外匣の上部へ
突出する。比較的熱い潤滑油が管３４を包囲して膨脹室
３６ａ内の液体冷媒を温めるから膨脹室内で少量の冷媒
が膨脹してガスになる。もちろんガスは管状膨脹室３６
ａの上部へ昇り、注入口３１から管３６を経て伝わる脈
動を緩衝する緩衝帯、即ち、ガスポケットを作る。換言
すれば膨脹室３６ａの上部にあるガス状冷媒のポケット
は室内である程度圧縮されて、管３６から伝えられる脈
動を吸収し、それが方式の他の部分へ伝わることを防
ぐ。管３６の下端は外匣２外で管３４の一部分の中に延
入し、熱い潤滑剤２４と接触していないから常時液体冷
媒は管３６の端部へ供給される。As described above, the continuous opening and closing operation of the injection port 31 which is the end portion 32 of the rotor 6 causes pulsation or vibration which causes noises unless properly buffered. In order to prevent this pulsation from being transmitted to other parts of the refrigeration system, an expansion chamber is provided in the passage for guiding the liquid refrigerant to the inlet 31 in the illustrated embodiment. As described above, the pipe 34 constitutes the expansion chamber 36a to which the liquid refrigerant is supplied from the pipe 33. Expansion chamber or reservoir 36
The a penetrates the hot lubricating oil in the bottom of the outer casing and projects to the upper portion of the outer casing. The relatively hot lubricating oil surrounds the tube 34 and warms the liquid refrigerant in the expansion chamber 36a so that a small amount of the refrigerant expands into gas in the expansion chamber. Of course, the gas is tubular expansion chamber 36
A buffer zone, that is, a gas pocket, which rises to the upper part of a and buffers the pulsation transmitted from the inlet 31 through the pipe 36, is formed. In other words, the pocket of gaseous refrigerant at the top of expansion chamber 36a is compressed to some extent in the chamber to absorb the pulsations transmitted from tube 36 and prevent it from being transmitted to other parts of the system. The lower end of the tube 36 extends into the part of the tube 34 outside the casing 2 and is not in contact with the hot lubricant 24 so that the liquid refrigerant is always supplied to the end of the tube 36.
【００１７】本発明の好ましい実施例では、液体冷媒供
給通路を流れる冷媒の量を制限するために、該通路内に
毛細管３７を設ける。これはこの装置の蒸発器の短絡を
防止し、凝縮器２２内の冷媒が液化するに充分冷却され
ないとき該通路を通して、ガスが流れることを有効に防
止する。注入される液体冷媒は吐出ガスとともに室から
出る前に圧縮されるガスと有効に混合するように吐出口
１８から遠ざかる方向に向けることが望ましい。このよ
うにして液体冷媒は半ば圧縮されたガスが、翼板の高圧
側１４ａに向かって室を巡るように押される際、該半ば
圧縮したガス中に注入される。即ち、図５の変形では注
入口３１の中心線４０は室の端壁１０の表面１０ｂに対
して鋭角をなしている。この鋭角の開放端は翼板１４か
ら遠ざかる方向に向いているから液体冷媒は翼板に向か
って環状室の周りを押される乱流ガスの方へ、即ち、回
転子の回転方向と反対方向へ吐出される。各圧縮サイク
ル中冷い液体冷媒は室４ｂ内に入ってくる比較的熱い半
ば圧縮されたガス内に吐出されると、蒸発してガス状と
なり、圧縮されたガスと混合する。液体冷媒が蒸発する
際半ば圧縮されたガスから熱を奪うため、室４ｂ内のガ
スの温度を著しく減少するから吐出口１８および通路２
５から出るガスは、液体冷媒を加えない場合よりもはる
かに一様な低温度となる。In the preferred embodiment of the present invention, a capillary tube 37 is provided in the liquid coolant supply passage to limit the amount of coolant flowing therein. This prevents short circuiting of the evaporator of the device and effectively prevents gas from flowing through the passage when the refrigerant in the condenser 22 is not cooled sufficiently to liquefy. It is desirable to direct the injected liquid refrigerant away from the discharge port 18 so as to effectively mix with the discharge gas and the gas that is compressed before it exits the chamber. Thus, the liquid refrigerant is injected into the semi-compressed gas as the semi-compressed gas is pushed around the chamber towards the high pressure side 14a of the vane. That is, in the modification of FIG. 5, the center line 40 of the inlet 31 forms an acute angle with the surface 10b of the end wall 10 of the chamber. Since the open end of this acute angle is directed away from the vane 14, the liquid refrigerant is directed toward the turbulent gas that is pushed around the annular chamber toward the vane, that is, in the direction opposite to the direction of rotation of the rotor. Is ejected. During each compression cycle, the cold liquid refrigerant is evaporated into a gaseous state as it is discharged into the relatively hot, semi-compressed gas entering chamber 4b and mixes with the compressed gas. When the liquid refrigerant evaporates, heat is taken from the semi-compressed gas, which significantly reduces the temperature of the gas in the chamber 4b.
The gas exiting 5 is at a much more uniform low temperature than if no liquid refrigerant was added.
【００１８】図示の実施例では中心線４０の角度は室の
端壁の表面１０ｂに対して４５度である。注入口３１か
ら吐出される液体冷媒を室の端壁１０に対して、ある角
度をもたせ、かつ、室内で圧縮されるガスに向かって、
回転子即ち、軸８の回転方向と反対方向に向けることに
より、吐出されるガスは吐出口１８から遠ざかる方向に
向けられ、注入される液体を室から吐出される前に半ば
圧縮されたガスと完全に混合させる。液体冷媒は室の端
壁１０ｂと直角に注入されるとき吐出ガスを冷却する
が、試験した圧縮機では液体冷媒を半ば圧縮されたガス
中に、それが室の周りに回転子で圧縮される際吐出する
ことにより温度が約５℃又は以上下がることを認めた。
この追加の冷却はガスがなお室内にある際に、液体冷媒
が半ば圧縮されたガスと一層完全に混合されるために起
こるものと思われる。吐出口１８から押し出される混合
しない液体冷媒は最後には蒸発してガスの温度を低下す
るが、室４内で液体冷媒を充分に混合するとき一層一様
な冷却が行われるものと信ぜられる。In the illustrated embodiment, the angle of the centerline 40 is 45 degrees with respect to the surface 10b of the chamber end wall. The liquid refrigerant discharged from the inlet 31 is inclined at an angle with respect to the end wall 10 of the chamber, and toward the gas compressed in the chamber,
By directing the rotor, that is, the direction opposite to the direction of rotation of the shaft 8, the discharged gas is directed in a direction away from the discharge port 18, and the injected liquid is partially compressed before being discharged from the chamber. Mix thoroughly. The liquid refrigerant cools the discharge gas when injected perpendicularly to the chamber end wall 10b, but in the compressor tested the liquid refrigerant is compressed in the semi-compressed gas by the rotor around the chamber. It was confirmed that the temperature was lowered by about 5 ° C. or more by discharging at the time.
This additional cooling is believed to occur because the liquid refrigerant is more thoroughly mixed with the semi-compressed gas while the gas is still in the chamber. The unmixed liquid refrigerant extruded from the discharge port 18 finally evaporates to lower the temperature of the gas, but it is believed that more uniform cooling is performed when the liquid refrigerant is sufficiently mixed in the chamber 4.
【００１９】圧縮機の端壁１０の表面１０ｂに対して４
５度の角度が望ましいが、注入口３１の中心線４０が環
状圧縮室４の端壁１０の表面１０ｂとなす鋭角が６０度
に増加しても、端壁１０ｂに対して直角に吐出する場合
よりも冷却効果が増大することを認めた。中心線３７と
直角な圧縮機の断面を示す図６に示すように注入口３１
は翼板１４と約１２度の角度をもって配置した中心線３
７を直角に通過する平面内に設けられている。従って、
注入口３１は室の中心および注入口の出口を通過する中
心線３７と直角な平面内に作られている。この平面は回
転子が注入口３１を完全に開くとき即ち、回転子の周面
が図５の文字Ｄで示す位置にあるとき、回転子の周面６
ａに対してほぼ切線をなしている。4 for the surface 10b of the end wall 10 of the compressor
Although an angle of 5 degrees is desirable, when the center line 40 of the injection port 31 forms an acute angle with the surface 10b of the end wall 10 of the annular compression chamber 4 to 60 degrees, the discharge is perpendicular to the end wall 10b. It was found that the cooling effect is increased more than that. As shown in FIG. 6, which shows a cross section of the compressor perpendicular to the center line 37, the inlet 31
Is the center line 3 arranged at an angle of about 12 degrees with the vanes 14.
It is provided in a plane passing through 7 at a right angle. Therefore,
The inlet 31 is made in a plane perpendicular to the centerline 37 passing through the center of the chamber and the outlet of the inlet. When the rotor completely opens the inlet 31, that is, when the peripheral surface of the rotor is at the position indicated by the letter D in FIG.
It is almost cut with respect to a.
【００２０】本発明の試験した実施例では液体が上流部
分に注入される圧縮室から吐出されるガスの温度は約７
１℃であり、これに対し液体を注入しない圧縮機の吐出
温度は１００〜１１０℃である。この７１℃の高い密度
のガスは充分な冷却能力を有し、電動機の周りを通過す
るときそれから充分の熱を奪って電動機を実用的な運転
温度に保つ。さらに、圧縮室４ｂ内の半ば圧縮されたガ
スの温度が減少するためガスを一層容易に圧縮すること
ができ、圧縮機の能率にほとんど影響を与えない。In the tested embodiment of the invention, the temperature of the gas discharged from the compression chamber in which the liquid is injected in the upstream portion is about 7
The discharge temperature of the compressor which does not inject the liquid is 100 to 110 ° C. This high density gas of 71 ° C. has sufficient cooling capacity to remove sufficient heat from it as it passes around it, keeping it at a practical operating temperature. Furthermore, since the temperature of the partially compressed gas in the compression chamber 4b decreases, the gas can be compressed more easily, and the efficiency of the compressor is hardly affected.
【００２１】[0021]
【発明が解決しようとする課題】しかしながら上記のよ
うな構成では、バイパス管出口付近（図２のＥ付近）が
折れて冷凍機不良となるトラブルが多かった。これは圧
縮機が振動の伝わりやすいロータリ型で圧縮機の振動が
伝わり、比較的細いチューブであり太いチューブとの接
ぎ部分であるバイパス管出口付近に振動による応力が集
中して折れるものである。本発明は上記課題に鑑みバイ
パス管の折れを防止してトラブルを起こさない圧縮機の
バイパス管接続装置を提供するものである。However, in the above structure, there are many problems that the vicinity of the bypass pipe outlet (near E in FIG. 2) is broken and the refrigerator is defective. This is because the compressor is a rotary type in which vibration is easily transmitted, and the vibration of the compressor is transmitted, and the stress due to the vibration is concentrated near the outlet of the bypass pipe, which is a relatively thin tube and a connecting portion with the thick tube, and breaks. In view of the above problems, the present invention provides a bypass pipe connecting device for a compressor, which prevents breakage of the bypass pipe and causes no trouble.
【００２２】[0022]
【課題を解決するための手段】以上のような課題を解決
するために本発明の冷媒圧縮機のバイパス管接続装置
は、凝縮器と、凝縮した液体冷媒をシリンダーの環状室
の高圧側に前記凝縮器に連結して直接注入するバイパス
管と、前記バイパス管の出口と冷媒圧縮機に設けられた
管との間に可撓性の金属ジャバラを配設し、バイパス管
出口部をキャビネット部材に固着した、金属ジャバラの
端面を前記の管と銀ろう又ははんだのろう付けによって
接続したという構成を備えたものである。In order to solve the above problems, a bypass connecting device for a refrigerant compressor according to the present invention comprises a condenser and a condensed liquid refrigerant on the high pressure side of an annular chamber of a cylinder. A bypass pipe connected to the condenser and directly injected, and a flexible metal bellows is arranged between the outlet of the bypass pipe and the pipe provided in the refrigerant compressor, and the bypass pipe outlet is used as a cabinet member. The end face of the metal bellows, which is fixed, is connected to the above-mentioned tube by silver brazing or solder brazing.
【００２３】[0023]
【作用】本発明は上記した構成のバイパス管出口付近に
振動による応力が発生しないように、可撓性の金属ジャ
バラを配設することにり、バイパス管に振動による応力
が発生しないからバイパス管の折れはなくなる。According to the present invention, a flexible metal bellows is provided so that the stress due to vibration is not generated near the outlet of the bypass pipe having the above-mentioned structure, and the stress due to vibration is not generated in the bypass pipe. No breakage
【００２４】[0024]
【実施例】以下、本発明の一実施例の冷媒圧縮機のバイ
パス管接続装置について、図面を参照しながら説明す
る。なお、従来例と同一部品は同一符号を用いて説明
し、構成，動作の同じところは省略する。図１におい
て、５０はバイパス管で図４の３３と同機能である。５
１は冷媒圧縮機に連結された管で一端は図３の注入口３
１に繋がっている。５２はバイパス管５０と管５１との
可撓性の特性をもって入っている金属ジャバラで、図の
如く凹凸があり自由に伸びちぢみする蛇腹状で管５１か
ら伝わる振動を蛇腹が吸収してバイパス管５０にはほと
んど振動が伝わらない。５４はキャビネット部材で、バ
イパス管５０を弾性帯５６とクランプ５７を介してネジ
５８でキャビネット部材５４に固定している。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A bypass connecting device for a refrigerant compressor according to an embodiment of the present invention will be described below with reference to the drawings. The same parts as those of the conventional example will be described using the same reference numerals, and the same parts of the configuration and the operation will be omitted. In FIG. 1, a bypass pipe 50 has the same function as 33 in FIG. 5
Reference numeral 1 denotes a pipe connected to the refrigerant compressor, and one end thereof has an injection port 3 shown in FIG.
It is connected to 1. Reference numeral 52 is a metal bellows having the flexibility characteristics of the bypass pipe 50 and the pipe 51. The bellows absorbs the vibration transmitted from the pipe 51 in a bellows shape having irregularities and extending freely as shown in the figure. Almost no vibration is transmitted to 50. Reference numeral 54 is a cabinet member, and the bypass pipe 50 is fixed to the cabinet member 54 with a screw 58 via an elastic band 56 and a clamp 57.
【００２５】５５は金属ジャバラ５２の外周５２ａと管
５１の端部拡管部５１ａの両面を気密的に接合している
ろう付けで、管５１とバイパス管５０の材質が銅又は鋼
であり、金属ジャバラの材質が銅又はしんちゅうである
ことから、ろう付けはすゞと鉛系合金ではんだ付け、又
は硬ろう付と呼ばれる銀ろう溶接されている。以上のよ
うに構成された部分がバイパス管接続装置５３である。Reference numeral 55 is a brazing for airtightly joining both surfaces of the outer periphery 52a of the metal bellows 52 and the end expanded portion 51a of the pipe 51. The material of the pipe 51 and the bypass pipe 50 is copper or steel. Since the material of the bellows is copper or brass, the brazing is performed by soldering with a lead-based alloy such as isuzu or silver brazing, which is called hard brazing. The portion configured as described above is the bypass pipe connecting device 53.
【００２６】以上のような構成において、ロータリ型の
圧縮機１が運転すると、その振動は管５１を伝わって金
属ジャバラを振動させるがほとんどの振動は蛇腹で吸収
される。バイパス管５０をキャビネット部材５４に固着
することにより前記の振動はすべて蛇腹で吸収されてし
まってバイパス管５０には振動しなくなり、振動による
応力が発生しないからバイパス管の折れは確実に防止で
きる。なお、図１は縦型となっているが、横型ロータリ
の冷媒圧縮機にも適用できるものである。When the rotary type compressor 1 is operated in the above-mentioned structure, its vibration is transmitted through the pipe 51 and vibrates the metal bellows, but most of the vibration is absorbed by the bellows. By fixing the bypass pipe 50 to the cabinet member 54, all the above-mentioned vibrations are absorbed by the bellows so that the bypass pipe 50 does not vibrate, and the stress due to the vibration is not generated, so that the bypass pipe can be surely prevented from being broken. Although FIG. 1 is a vertical type, it is also applicable to a horizontal rotary refrigerant compressor.
【００２７】[0027]
【発明の効果】以上のように本発明は、凝縮器と、凝縮
した液体冷媒をシリンダーの環状室の高圧側に前記凝縮
器に連結して直接注入するバイパス管と、前記バイパス
管の出口と冷媒圧縮機に設けられた管との間に可撓性の
金属ジャバラを配設し、バイパス管出口部をキャビネッ
ト部材に固着した金属ジャバラの端面を前記の管と銀ろ
う又は、はんだのろう付けによって接続したという構成
を備えたものであり、圧縮機から管を伝わった振動は金
属ジャバラの蛇腹で吸収されてしまうので、バイパス管
には振動による応力が発生しない。従って、バイパス管
の折れは確実に防止でき、管やチューブの折れによる冷
凍機不良を撲滅することができる。又、金属ジャバラ５
２は圧縮機の回転中、注入口（図３の３１）の間歇的開
閉に基いて発生される振動即ち液体の衝撃を蛇腹の伸縮
によって緩和することができる。As described above, according to the present invention, the condenser, the bypass pipe for directly injecting the condensed liquid refrigerant into the high pressure side of the annular chamber of the cylinder by connecting to the condenser, and the outlet of the bypass pipe are provided. A flexible metal bellows is arranged between the pipe provided in the refrigerant compressor and the end face of the metal bellows, in which the outlet of the bypass pipe is fixed to the cabinet member, is brazed to the pipe by silver brazing or soldering. Since the vibration transmitted from the compressor through the pipe is absorbed by the bellows of the metal bellows, no stress is generated in the bypass pipe due to the vibration. Therefore, breakage of the bypass pipe can be surely prevented, and failure of the refrigerator due to breakage of the pipe or tube can be eliminated. Also, metal bellows 5
When the compressor 2 is rotating, the vibration, that is, the liquid shock generated by the intermittent opening and closing of the inlet (31 in FIG. 3) while the compressor is rotating can be alleviated by the expansion and contraction of the bellows.
【図１】本発明の一実施例における冷媒圧縮機のバイパ
ス管接続装置の断面図FIG. 1 is a sectional view of a bypass pipe connecting device for a refrigerant compressor according to an embodiment of the present invention.
【図２】従来の冷媒圧縮機の一部の縦断面図FIG. 2 is a vertical sectional view of a part of a conventional refrigerant compressor.
【図３】図２の２−２線に沿う一部の平面図FIG. 3 is a partial plan view taken along line 2-2 of FIG.
【図４】図２の冷媒圧縮機を使用する冷凍方式の線図4 is a diagram of a refrigeration system using the refrigerant compressor of FIG.
【図５】図２の冷媒圧縮機の液体冷媒注入口を回転子端
部で開閉するときの回転子の角位置を示す線図5 is a diagram showing the angular position of the rotor when the liquid refrigerant inlet of the refrigerant compressor of FIG. 2 is opened and closed at the rotor end.
【図６】図２の他の実施例の一部の断面図6 is a partial cross-sectional view of another embodiment of FIG.
５０ バイパス管 ５１ 冷媒圧縮機に凍結された管 ５２ 金属ジャバラ ５３ バイパス管接続装置 ５４ キャビネット部材 ５５ ろう付け 50 Bypass Pipe 51 Pipe Frozen in Refrigerant Compressor 52 Metal Bellows 53 Bypass Pipe Connection Device 54 Cabinet Member 55 Brazing
Claims (3)
ーの環状室の高圧側にもどすバイパス管と、前記バイパ
ス管の出口と冷媒圧縮機に連結された管との間に可撓性
の金属ジャバラとからなる冷媒圧縮機。1. A flexible metal between a condenser, a bypass pipe for returning condensed liquid refrigerant to a high pressure side of an annular chamber of a cylinder, and an outlet of the bypass pipe and a pipe connected to a refrigerant compressor. Refrigerant compressor consisting of bellows.
ーの環状室の高圧側に前記凝縮器に連結して直接注入す
るバイパス管と、前記バイパス管の出口と冷媒圧縮機に
設けられた管との間に可撓性の金属ジャバラとを配設
し、バイパス管出口部をキャビネットに固着したことを
特徴とする冷媒圧縮機。2. A condenser, a bypass pipe for injecting condensed liquid refrigerant directly into the high pressure side of an annular chamber of a cylinder by connecting to the condenser, an outlet of the bypass pipe and a pipe provided in the refrigerant compressor. A flexible metal bellows is provided between the compressor and the bypass pipe, and the bypass pipe outlet is fixed to the cabinet.
ーの環状室の高圧側に前記凝縮器に連結した直接注入す
るバイパス管と、前記バイパス管の出口と冷媒圧縮器に
設けられた管との間に可撓性の金属ジャバラとを配設
し、前記金属ジャバラの端面を前記の管と、ろう付けに
よって接続したことを特徴とする冷媒圧縮機。3. A condenser, a bypass pipe for directly injecting condensed liquid refrigerant into a high pressure side of an annular chamber of a cylinder, the bypass pipe being connected to the condenser, an outlet of the bypass pipe, and a pipe provided in the refrigerant compressor. A refrigerant compressor, wherein a flexible metal bellows is arranged between the pipes, and an end surface of the metal bellows is connected to the pipe by brazing.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4160673A JPH062688A (en) | 1992-06-19 | 1992-06-19 | Refrigerant compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4160673A JPH062688A (en) | 1992-06-19 | 1992-06-19 | Refrigerant compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH062688A true JPH062688A (en) | 1994-01-11 |
Family
ID=15720009
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP4160673A Pending JPH062688A (en) | 1992-06-19 | 1992-06-19 | Refrigerant compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH062688A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2008123171A1 (en) * | 2007-03-28 | 2008-10-16 | Daikin Industries, Ltd. | Mechanism for controlling and operating compressor capacity and air conditioner having the same |
-
1992
- 1992-06-19 JP JP4160673A patent/JPH062688A/en active Pending
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2008123171A1 (en) * | 2007-03-28 | 2008-10-16 | Daikin Industries, Ltd. | Mechanism for controlling and operating compressor capacity and air conditioner having the same |
| AU2008236150B2 (en) * | 2007-03-28 | 2011-04-28 | Daikin Industries, Ltd. | Compressor capacity control operation mechanism and air conditioner provided with same |
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