JPS6336435B2 - - Google Patents
Info
- Publication number
- JPS6336435B2 JPS6336435B2 JP57004493A JP449382A JPS6336435B2 JP S6336435 B2 JPS6336435 B2 JP S6336435B2 JP 57004493 A JP57004493 A JP 57004493A JP 449382 A JP449382 A JP 449382A JP S6336435 B2 JPS6336435 B2 JP S6336435B2
- Authority
- JP
- Japan
- Prior art keywords
- pressure
- liquid
- discharge
- valve
- suction
- 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
- 239000007788 liquid Substances 0.000 claims description 30
- 238000002347 injection Methods 0.000 claims description 13
- 239000007924 injection Substances 0.000 claims description 13
- 230000007246 mechanism Effects 0.000 claims description 12
- 239000003507 refrigerant Substances 0.000 claims description 11
- 238000007906 compression Methods 0.000 claims description 8
- 239000010687 lubricating oil Substances 0.000 claims description 7
- 239000007789 gas Substances 0.000 description 13
- 239000003921 oil Substances 0.000 description 12
- 230000007423 decrease Effects 0.000 description 11
- 238000000034 method Methods 0.000 description 5
- 230000008859 change Effects 0.000 description 3
- 238000001816 cooling Methods 0.000 description 3
- 238000001514 detection method Methods 0.000 description 3
- 238000005057 refrigeration Methods 0.000 description 3
- 238000005461 lubrication Methods 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- 230000003247 decreasing effect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 230000004044 response Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/0007—Injection of a fluid in the working chamber for sealing, cooling and lubricating
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary-Type Compressors (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Description
【発明の詳細な説明】
本発明は冷媒や空気などの気体を圧縮するスク
リユー圧縮機、詳しくは、リキツドインジエクシ
ヨンチユーブを備え、圧縮工程中のスクリユー空
間に、潤滑油、液冷媒などのリキツドをインジエ
クシヨンするごとくしたスクリユー圧縮機に関す
る。Detailed Description of the Invention The present invention is a screw compressor that compresses gas such as refrigerant or air, and more specifically, it is equipped with a liquid-injection tube and compresses lubricating oil, liquid refrigerant, etc. into the screw space during the compression process. This invention relates to a screw compressor that is designed to inject liquid.
従来、此種圧縮機においては、圧縮工程中のス
クリユー空間に対し、潤滑油、液冷媒などのリキ
ツドをポンプにより強制的にインジエクシヨンさ
せるものと、圧縮工程における吐出側の高圧力と
前記スクリユー空間における中間圧力との差圧を
利用して、圧縮機における吐出側の高圧リキツド
をインジエクシヨンさせるものとが提案されてい
る。 Conventionally, in this type of compressor, liquid such as lubricating oil or liquid refrigerant is forcibly injected into the screw space during the compression process using a pump, and high pressure on the discharge side during the compression process and liquid in the screw space are used. It has been proposed that the high pressure liquid on the discharge side of the compressor is injected using the pressure difference between the compressor and the intermediate pressure.
所が、前者によれば、ポンプを必要とするため
高価となる問題があり、また、後者によれば運転
開始時及び冷凍装置に適用した場合の中間期にお
ける運転時のごとく高低圧間の差圧が低下する運
転時、前記スクリユー空間の中間圧力にくらべて
吐出側圧力が低下することが生じて、前記リキツ
ドをスクリユー空間にインジエクシヨンできなく
なる問題があつた。 However, according to the former method, there is a problem that it is expensive because a pump is required, and according to the latter method, the difference between high and low pressures is reduced at the start of operation and during the intermediate period when applied to a refrigeration system. During operation in which the pressure decreases, the discharge side pressure decreases compared to the intermediate pressure in the screw space, resulting in a problem that the liquid cannot be injected into the screw space.
しかして、本発明は以上の問題を解決すべく発
明したもので、目的とする所は、運転開始時及び
中間期における運転時のごとく、高低圧間の差圧
が低くなる運転時でも、圧縮工程中のスクリユー
空間に、ポンプを用いることなく、潤滑油、液冷
媒などのリキツドを確実にインジエクシヨンで
き、前記リキツドによるスクリユー空間のシー
ル、スクリユーの潤滑及び冷却を確実に行なえ、
信頼性を向上できるスクリユー圧縮機を提供する
点にある。 Therefore, the present invention was invented to solve the above problem, and the purpose is to compress even when the differential pressure between high and low pressures is low, such as at the start of operation and during the intermediate period of operation. Liquid such as lubricating oil and liquid refrigerant can be reliably injected into the screw space during the process without using a pump, and the liquid can reliably seal the screw space, lubricate and cool the screw,
The object of the present invention is to provide a screw compressor that can improve reliability.
即ち、リキツドインジエクシヨンチユーブを備
え、圧縮工程中のスクリユー空間に、潤滑油、液
冷媒などのリキツドを吐出圧力によりインジエク
シヨンするごとくしたスクリユー圧縮機であつ
て、前記インジエクシヨンチユーブに、吸入側に
連通するバイパス通路を設けて、該バイパス通路
に、開閉弁を介装すると共に、吐出側と吸入側と
の間に、吐出圧力と吸入圧力との圧力比が所定値
以下のとき動作する信号発生機構とこの信号発生
機構の動作で閉じる開閉器とをもつ圧力比検出器
を設け、前記開閉器の閉動作で前記開閉弁を開い
て、前記リキツドを前記吸入側にインジエクシヨ
ンするごとくしたことを特徴とするものである。 That is, the screw compressor is equipped with a liquid injection tube and injects liquid such as lubricating oil or liquid refrigerant into the screw space during the compression process by discharge pressure. A bypass passage communicating with the side is provided, and an on-off valve is interposed in the bypass passage, and the valve is operated between the discharge side and the suction side when the pressure ratio between the discharge pressure and the suction pressure is below a predetermined value. A pressure ratio detector having a signal generating mechanism and a switch closed by the operation of the signal generating mechanism is provided, and the opening/closing valve is opened by the closing operation of the switch, and the liquid is injected into the suction side. It is characterized by:
以下、本発明スクリユー圧縮機の実施例を図面
に基づいて説明する。 Embodiments of the screw compressor of the present invention will be described below with reference to the drawings.
即ち、第１図に示したものは、前記吸入管１６
ａと吐出管１６ｂとの間に、吐出、吸入圧力P2，
P1（Kg／cm2・abs）の圧力比P2／P1を検出する圧
力比検出器３１を設けて、該検出器３１の出力信
号により前記開閉弁Ｖを制御すべくしたものであ
る。 That is, what is shown in FIG.
between a and the discharge pipe 16b, the discharge and suction pressures P 2 ,
A pressure ratio detector 31 is provided to detect the pressure ratio P 2 /P 1 of P 1 (Kg/cm 2 ·abs), and the on-off valve V is controlled by the output signal of the detector 31. .
前記圧力比検出器３１は、低圧ガスの吸入管１
６ａと接続する接続部３２をもつた第１チヤンバ
ー３３と高圧ガスの吐出管１６ｂと接続する接続
部３４をもつた第２チヤンバー３５とを設け、こ
れら各チヤンバー３３，３５に臨む受圧面３６，
３７をもち、該受圧面３６，３７に作用する前記
低・高圧ガスの圧力P1，P2（Kg／cm2・abs）に応
動して作動する受圧作動体３８，３９を設ける。
また、これら作動体３８，３９の背面側空間４０
を前記各チヤンバー３３，３５に対し密閉すると
共に、前記各作動体３８，３９を連動体４１によ
り連結する一方、前記空間４０に前記連動体４１
の動作で作動する検出信号発生機構４２を設けた
ものである。そして、前記各接続部３２，３４を
吸入管１６ａ、吐出管１６ｂに接続するのであ
る。 The pressure ratio detector 31 is connected to the low pressure gas suction pipe 1.
A first chamber 33 having a connection part 32 connected to the high-pressure gas discharge pipe 16b and a second chamber 35 having a connection part 34 connected to the high-pressure gas discharge pipe 16b are provided.
37 and actuated in response to the pressures P 1 and P 2 (Kg/cm 2 ·abs) of the low and high pressure gases acting on the pressure receiving surfaces 36 and 37, respectively.
In addition, the rear side space 40 of these operating bodies 38 and 39
is sealed to each of the chambers 33, 35, and each of the operating bodies 38, 39 is connected by an interlocking body 41, while the interlocking body 41 is connected to the space 40.
A detection signal generating mechanism 42 is provided which is activated by the operation. The respective connecting portions 32 and 34 are then connected to the suction pipe 16a and the discharge pipe 16b.
前記空間４０は、前記各チヤンバー３３，３５
の各背面間に箱体４３を介装して、該箱体４３内
に形成するのであり、以下真空とした場合につい
て説明する。また、受圧作動体３８，３９はベロ
ーズを用い、その各後端部を箱体４３内に対向状
に開口させるのである。 The space 40 includes each of the chambers 33 and 35.
A box body 43 is interposed between each back surface of the box body 43 to form the inside of the box body 43, and the case where a vacuum is created will be described below. Further, the pressure receiving bodies 38 and 39 use bellows, and their respective rear ends are opened into the box body 43 in an opposing manner.
そして、前記受圧作動体３８，３９における受
圧面３６，３７の受圧面積S1，S2（cm2）の比S1／
S2は、前記定常運転時における吐出、吸入圧力
P2，P1（Kg／cm2・abs）の定常値の比に等しくし
て、受圧面３６，３７にそれぞれ定常圧力が作用
したとき、受圧面３６，３７に対向状に作用する
荷重（Kg）を等しくし、連動体４１を第１図のご
とく定常位置に位置させ、また、吐出、吸入圧力
P2，P1（Kg／cm2・abs）が変化して圧力比P2／P1
が増、減するに応じて連動体４１を右、左動させ
るごとく成すのである。 The ratio of the pressure receiving areas S 1 and S 2 (cm 2 ) of the pressure receiving surfaces 36 and 37 in the pressure receiving bodies 38 and 39 is S 1 /
S 2 is the discharge and suction pressure during steady operation.
When steady pressure is applied to the pressure-receiving surfaces 36 and 37, equal to the ratio of the steady values of P 2 and P 1 ( Kg/cm 2・abs), the load ( Kg) are made equal, the interlocking body 41 is positioned at a steady position as shown in Fig. 1, and the discharge and suction pressures are
As P 2 and P 1 (Kg/cm 2・abs) change, the pressure ratio P 2 /P 1
This is done by moving the interlocking body 41 to the right or left as the amount increases or decreases.
また、前記検出信号発生機構４２は、第１図の
ごとく連動体４１に操作片（４４）を固定する一
方、連動体４１の一側に、前記各作動体３８，３
９の動作に影響を与えることのない弱いリターン
用バネ４５をもつた揺動体４６を軸支すると共
に、揺動体４６の作動側にマイクロスイツチ４７
を設けて、吐出、吸入圧力比P2／P1が減少し前
記連動体４１が前記定常位置から左方に動作する
ことにより、前記揺動体４６を時計方向に回動さ
せ、前記圧力比P2／P1が所定値迄減少して連動
体４１が所定位置に達したとき、揺動体４６によ
りスイツチ４７を作動させ、オン信号を前記開閉
弁Ｖに出力させて開閉弁Ｖを開くのである。 Further, the detection signal generating mechanism 42 has an operating piece (44) fixed to the interlocking body 41 as shown in FIG.
A rocking body 46 having a weak return spring 45 that does not affect the operation of the rocking body 46 is pivotally supported, and a micro switch 47 is installed on the operating side of the rocking body 46.
is provided, the discharge/suction pressure ratio P 2 /P 1 decreases and the interlocking body 41 moves leftward from the steady position, thereby rotating the oscillating body 46 clockwise and increasing the pressure ratio P When 2 / P1 decreases to a predetermined value and the interlocking body 41 reaches a predetermined position, the oscillator 46 operates the switch 47 to output an on signal to the on-off valve V to open the on-off valve V. .
ところで、前記圧力比P2／P1の所定値は、運
転開始時及び中間期における運転時のごとく、例
えば吸入圧力P1（Kg／cm2・abs）が高く、吐出圧
力P2（Kg／cm2・abs）が低い場合で、前記スクリ
ユー空間１２の内部圧力P3（Kg／cm2・abs）が前
記吐出圧力P2（Kg／cm2・as）より高くなつて圧力
差（P2−P3）によりインジエクシヨンが行なえ
なくなるときの圧力比P2／P1の値とするのであ
る。 By the way, the predetermined value of the pressure ratio P 2 /P 1 is such that, for example, the suction pressure P 1 (Kg/cm 2 ·abs) is high and the discharge pressure P 2 (Kg/cm 2 ·abs) is high, such as at the start of operation and during the intermediate period of operation. cm 2・abs) is low, the internal pressure P 3 (Kg/cm 2・abs) of the screw space 12 becomes higher than the discharge pressure P 2 (Kg/cm 2・as), and the pressure difference (P 2 -P 3 ), the pressure ratio P 2 /P 1 is taken as the value when injection cannot be performed.
また、前記圧力比P2／P1の値が、前記所定値
から増加し、連動体４１が前記所定位置から右方
に戻り動作することにより、揺動体４６をバネ４
５の付勢力で反時計方向に戻り作動させ、スイツ
チ４７を復帰作動させて、オフ信号を前記開閉弁
Ｖに出力させて開閉弁Ｖを閉じるのである。 Further, the value of the pressure ratio P 2 /P 1 increases from the predetermined value, and the interlocking body 41 moves back to the right from the predetermined position, thereby causing the oscillating body 46 to move toward the spring 4.
The switch 47 is returned to the counterclockwise direction by the biasing force 5, and the switch 47 is returned to output an off signal to the on-off valve V, thereby closing the on-off valve V.
ところで、前記オン・オフ信号は、マイクロス
イツチ４７を用いて出力させるごとくしたが、マ
イクロスイツチ４７を用いる場合、その開閉操作
位置間にデイフアレンシヤルをもつているから、
前記連動体４１の戻り作動時、前記スイツチ４７
は、その作動位置に対し前記連動体４１のデイフ
アレンシヤル値以上の戻り作動で開くことにな
る。 By the way, the above-mentioned on/off signal was output using the micro switch 47, but when the micro switch 47 is used, there is a differential between its open and close operation positions.
When the interlocking body 41 returns, the switch 47
will open when the interlocking body 41 returns to its operating position by a value greater than or equal to the differential value.
また、以上の如く作動信号の出力とその停止と
の間にデイフアレンシヤルを設けることによりハ
ンチング動作を解消できることになるが、デイフ
アレンシヤルを設けることは特に必要でない。 Further, as described above, the hunting operation can be eliminated by providing a differential between the output of the actuation signal and its stop, but it is not particularly necessary to provide the differential.
又、デイフアレンシヤルを設ける場合、デイフ
アレンシヤルをもつたスイツチ４７を用いる以
外、受圧作動体３９の受圧面３７にバネ４８を対
設したり、揺動体４６の両腕の長さを調整するこ
とにより、さらにはこれらの組合わせにより必要
量得ることができる。 In addition, when providing a differential, in addition to using a switch 47 with a differential, a spring 48 may be provided opposite to the pressure receiving surface 37 of the pressure receiving actuating body 39, or the length of both arms of the oscillating body 46 may be The required amount can be obtained by adjusting or even by combining these.
又第１図において、４９は連動体４１の右動に
対するストツパ、５０は制御回路である。尚、５
１は前記空間４０を大気圧とした場合に、連動体
４１に生ずる面積差（S1−S2）に見合う偏荷重に
対設するバネである。 Further, in FIG. 1, 49 is a stopper for rightward movement of the interlocking body 41, and 50 is a control circuit. In addition, 5
Reference numeral 1 denotes a spring that is provided to counter an eccentric load commensurate with the area difference (S 1 -S 2 ) that occurs in the interlocking body 41 when the space 40 is at atmospheric pressure.
しかして、以上の構成において定常運転時、前
記吐出管１６ｂ及び吸入管１６ａを流れるガスの
吐出、吸入圧力P2，P1（Kg／cm2・abs）の比P2／
P1は定常時の圧力比に等しい状態にある。その
ため、連動体４１は第１図のごとく定常位置に位
置され、スイツチ４７からオン信号は出力され
ず、閉開弁Ｖは閉状態に保持される。従つて、油
分離器８内の高圧P2（Kg／cm2・abs）の油のリキ
ツドは油冷却器９により冷却されて中間圧力P3
（Kg／cm2・abs）のスクリユー空間１２内に圧力
差（P2−P3）によりインジエクシヨンされる。 Therefore, in the above configuration, during steady operation, the ratio of the discharge and suction pressures P 2 and P 1 (Kg/cm 2 ·abs) of the gas flowing through the discharge pipe 16b and the suction pipe 16a is P 2 /
P 1 is in a state equal to the pressure ratio at steady state. Therefore, the interlocking body 41 is located at a normal position as shown in FIG. 1, no on signal is output from the switch 47, and the close/open valve V is maintained in the closed state. Therefore, the oil liquid at high pressure P 2 (Kg/cm 2 ·abs) in oil separator 8 is cooled by oil cooler 9 to intermediate pressure P 3
(Kg/cm 2 ·abs) in the screw space 12 due to the pressure difference (P 2 −P 3 ).
また一方、運転開始時及び中間期における運転
時において、吸入圧力P1（Kg／cm2・abs）が定常
時より昇圧したり、高圧P2（Kg／cm2・abs）が定
常時よりも降圧したりして、吐出・吸入圧力比
P2／P1が前記所定値以下に減少すると、吸入ガ
ス及び吐出ガスは第１、第２チヤンバー３３，３
５内に連通するため、前記検出信号発生機構４２
のマイクロスイツチ４７からオン信号が出力し、
開閉弁Ｖが開動作する。その結果、油分離器８は
低圧の吸入管１６ａに連通され、油分離器８内の
油は、吸入管１６ａにインジエクシヨンされて低
圧ガス冷媒と共に吸入ポート５内に吸入され、ス
クリユーの潤滑、冷却及びスクリユー空間１２の
シールを確実に行なえるのである。 On the other hand, at the start of operation and during the intermediate period of operation, the suction pressure P 1 (Kg/cm 2・abs) increases from the steady state, and the high pressure P 2 (Kg/cm 2・abs) increases from the steady state. Pressure decreases and the discharge/suction pressure ratio
When P 2 /P 1 decreases below the predetermined value, the intake gas and the discharge gas are transferred to the first and second chambers 33, 3.
5, the detection signal generating mechanism 42
An on signal is output from the micro switch 47,
The on-off valve V operates to open. As a result, the oil separator 8 is communicated with the low-pressure suction pipe 16a, and the oil in the oil separator 8 is injected into the suction pipe 16a and sucked into the suction port 5 together with the low-pressure gas refrigerant, thereby lubricating and cooling the screw. And the screw space 12 can be reliably sealed.
そして、吸入ガスと吐出ガスとの圧力P1，P2
（Kg／cm2・abs）が逆に定常値方向に降、昇し、
圧力比P2／P1が高くなつて定常運転可能な状態
になると、連動体４１が定常位置方向に戻り動作
することにより、スイツチ４７からオフ信号が出
力され、開閉弁Ｖが閉状態に復帰して、何ら支障
なく定常状態に移行される。 And the pressures P 1 and P 2 of the suction gas and discharge gas
(Kg/cm 2・abs) decreases and increases in the direction of the steady value,
When the pressure ratio P 2 /P 1 becomes high and steady operation is possible, the interlocking body 41 returns to the normal position and an off signal is output from the switch 47, returning the on-off valve V to the closed state. The system is then transferred to a steady state without any problems.
斯くのごとく、前記圧力比検出器３１を用い、
高低圧力比を検出して、前記開閉弁Ｖを開閉制御
することにより、正確なインジエクシヨンの制御
が可能となり、潤滑不足、冷却不足やスクリユー
空間１２のシール不良による問題をなくし得るの
である。 In this way, using the pressure ratio detector 31,
By detecting the high/low pressure ratio and controlling the opening/closing of the on-off valve V, accurate injection control becomes possible, and problems caused by insufficient lubrication, insufficient cooling, and poor sealing of the screw space 12 can be eliminated.
なお、この場合、圧力比検出器３１の連動体４
１に弁体を固定することにより、開閉弁Ｖを構成
することもできる。 In this case, the interlocking body 4 of the pressure ratio detector 31
By fixing a valve body to 1, an on-off valve V can also be configured.
以上、本発明は冷凍装置に限らず空気圧縮機な
どのガス圧縮機に適用できることはもちろんであ
る。この場合、吐出圧力によりインジエクシヨン
するリキツドとしては潤滑油を用いるものであ
る。 As described above, the present invention is of course applicable not only to refrigeration equipment but also to gas compressors such as air compressors. In this case, lubricating oil is used as the liquid that is injected by the discharge pressure.
しかして、本発明は以上の如きスクリユー圧縮
機において、前記インジエクシヨンチユーブ１１
に、吸入側に連通するバイパス通路１７を設け
て、該バイパス通路１７に、開閉弁Ｖを介装する
と共に、吐出側と吸入側との間に、吐出圧力と吸
入圧力との圧力比が所定値以下のとき動作する信
号発生機構４２とこの信号発生機構４２の動作で
閉じる開閉器４７とをもつ圧力比検出器３１を設
け、前記開閉器４７の閉動作で前記開閉弁Ｖを開
いて、冷凍サイクルにおける吐出、吸入圧力の圧
力比が所定値以下の低圧力比運転時、油を前記吸
入側にインジエクシヨンすべく成すのである。 Therefore, the present invention provides a screw compressor as described above, in which the injection tube 11
A bypass passage 17 communicating with the suction side is provided, and an on-off valve V is interposed in the bypass passage 17, and a pressure ratio between the discharge pressure and the suction pressure is maintained between the discharge side and the suction side. A pressure ratio detector 31 is provided which has a signal generating mechanism 42 that operates when the pressure is below a value, and a switch 47 that is closed by the operation of the signal generating mechanism 42, and the opening/closing valve V is opened by the closing operation of the switch 47, The oil is injected into the suction side during low pressure ratio operation in which the pressure ratio of the discharge and suction pressures in the refrigeration cycle is below a predetermined value.
以上の如く本発明は、圧縮工程中のスクリユー
空間１２に、潤滑油、液冷媒などのリキツドを吐
出圧力によりインジエクシヨンするインジエクシ
ヨンチユーブ１１に、吸入側に連通するバイパス
通路１７を設けて該バイパス通路１７に、開閉弁
Ｖを介装すると共に、吐出側と吸入側との間に、
吐出圧力と吸入圧力との圧力比が所定値以下のと
き動作する信号発生機構４２とこの信号発生機構
４２の動作で閉じる開閉器４７とをもつ圧力比検
出器３１を設け、前記開閉器４７の閉動作で前記
開閉弁Ｖを開いて、前記リキツドを前記吸入側に
インジエクシヨンすべくしたのであるから、運転
開始時や中間期における運転時のごとく、圧力比
が低下し、スクリユー空間１２の内部圧力が吐出
圧力以上に高くなつて、吐出圧力とスクリユー空
間１２の内部圧力との圧力差によつて、前記リキ
ツドをスクリユー空間１２内にインジエクシヨン
できなくなる低圧力比運転時には、前記開閉弁Ｖ
が開かれ、吐出圧力をもつたリキツドは、該圧力
より低い吸入側に連通される。その結果、前記リ
キツドは吸入側に吸入ガスと共に確実に吸入さ
れ、前記低圧力比運転時においても、スクリユー
空間１２にインジエクシヨンするリキツドの量を
確実に確保でき、高価なポンプを用いることなく
スクリユーの潤滑、冷却及びスクリユー空間１２
のシールを確実に行なえ、信頼性を向上できるの
である。 As described above, the present invention provides a bypass passage 17 communicating with the suction side in the injection tube 11 that injects liquid such as lubricating oil or liquid refrigerant into the screw space 12 during the compression process by discharge pressure. An on-off valve V is interposed in the passage 17, and between the discharge side and the suction side,
A pressure ratio detector 31 is provided, which has a signal generating mechanism 42 that operates when the pressure ratio between the discharge pressure and the suction pressure is below a predetermined value, and a switch 47 that closes due to the operation of the signal generating mechanism 42. Since the opening/closing valve V is opened in the closing operation and the liquid is injected into the suction side, the pressure ratio decreases and the internal pressure of the screw space 12 decreases as at the start of operation or during the intermediate period of operation. During low pressure ratio operation, when the liquid becomes higher than the discharge pressure and the liquid cannot be injected into the screw space 12 due to the pressure difference between the discharge pressure and the internal pressure of the screw space 12, the on-off valve V
is opened, and the liquid having a discharge pressure is communicated with the suction side, which has a lower pressure. As a result, the liquid is reliably sucked into the suction side together with the suction gas, and even during the low pressure ratio operation, the amount of liquid to be injected into the screw space 12 can be ensured, and the screw can be pumped without using an expensive pump. Lubrication, cooling and screw space 12
This allows for reliable sealing and improved reliability.
即ち、圧力差で開閉弁Ｖの開閉を制御する場合
は、標準負荷のもとに前記開閉弁Ｖを開閉する差
圧を設定した場合、斯く設定した標準負荷の起動
時には、問題ないが、前記標準負荷より高い負荷
となり高低圧圧力が大きい状態で起動する場合、
冷媒循環量が大きくなり、インジエクシヨンすべ
き油量も多く必要となるにも拘わらず、定常運転
に至るまでに、前記した設定差圧になると前記開
閉弁Ｖが閉じて、圧縮工程中のスクリユー空間１
２にインジエクシヨンすることになつて、却つて
油量を減少してしまう問題があり、また、前記設
定差圧を前記した差圧より高く設定すると高低圧
圧力が大きい場合でも前記した問題はないが、逆
に低負荷で高圧圧力が小さい場合には定常運転に
なつても前記開閉弁Ｖが閉じないで吸入側にイン
ジエクシヨンし続けてしまい、効率低下の不都合
が生ずるのである。 That is, when controlling the opening and closing of the on-off valve V using a pressure difference, if the differential pressure for opening and closing the on-off valve V is set under a standard load, there will be no problem when starting the set standard load; When starting with a load higher than the standard load and high and low pressures,
Even though the amount of refrigerant circulation increases and the amount of oil to be injected is also required, the opening/closing valve V closes when the set differential pressure is reached before steady operation is reached, and the screw space during the compression process is closed. 1
2, there is a problem that the oil amount decreases on the contrary.Also, if the set differential pressure is set higher than the differential pressure described above, the above problem does not occur even if the high and low pressures are large. On the other hand, when the load is low and the high pressure is low, the on-off valve V does not close even in steady operation and continues to be injected to the suction side, resulting in a problem of reduced efficiency.
要するに、差圧式とした場合、負荷による高低
圧圧力の変化如何に拘わらず、設定差圧は変化せ
ず、設定した差圧においてのみ開閉弁Ｖの開閉が
行なわれることから、前記した不都合が生ずるの
である。 In short, when using a differential pressure type, the set differential pressure does not change regardless of changes in high and low pressures due to load, and the opening/closing valve V is opened and closed only at the set differential pressure, resulting in the above-mentioned inconvenience. It is.
之に対し今回限定した圧力比方式によると、標
準負荷をもとに前記開閉弁Ｖが開閉する圧力比を
設定した場合、標準負荷の起動時は勿論のこと、
標準負荷に対し高い負荷となつた場合でも、差圧
方式に比較して高圧圧力が高くなるまで、つまり
定常運転になるまで、前記開閉弁Ｖの閉動作をす
るための高圧圧力を拡げられるのであり、従つ
て、高低圧圧力が大きくなり冷媒循環量が増大す
る場合吸入側からのインジエクシヨンを補償で
き、冷媒循環量に対応して必要な油量を確保でき
るのである。 On the other hand, according to the pressure ratio method limited to this time, when the pressure ratio at which the on-off valve V opens and closes is set based on the standard load, of course when starting the standard load,
Even when the load is higher than the standard load, the high pressure required to close the on-off valve V can be expanded until the high pressure becomes higher compared to the differential pressure method, that is, until steady operation is reached. Therefore, when the high and low pressures increase and the refrigerant circulation amount increases, the injection from the suction side can be compensated for, and the necessary oil amount can be secured in accordance with the refrigerant circulation amount.
この結果、前記圧力比の設定は標準負荷に対応
して行なえるから、つまり標準負荷に対応する圧
力比より大きく設定する必要がないから、定常運
転になつても吸入側にインジエクシヨンし続ける
ことによる効率低下の問題もないのである。 As a result, the pressure ratio can be set in accordance with the standard load, that is, there is no need to set it higher than the pressure ratio corresponding to the standard load, so even during steady operation, injection continues to the suction side. There is no problem of decreased efficiency.
このように圧力比をもとに開閉弁Ｖを開閉する
ようにしたから、起動時や中間期における運転時
など、高圧圧力が低く圧縮工程中のスクリユー空
間にインジエクシヨンできない場合には吸入側か
らインジエクシヨンできながら、負荷条件が変化
し、高低圧圧力が高くなつても、定常運転に至る
まで吸入側にインジエクシヨンしてその油量を確
保できスクリユーの潤滑、冷却、シールを確実に
行なえ、信頼性を向上できながら、定常運転にな
ればスクリユー空間へのインジエクシヨンに切換
えられるので、効率低下を招くこともなくし得る
のである。 In this way, the on-off valve V is opened and closed based on the pressure ratio, so when the high pressure is low and injection cannot be performed into the screw space during the compression process, such as during start-up or intermediate operation, injection can be performed from the suction side. However, even when the load conditions change and the high and low pressures increase, the oil volume can be maintained by injecting oil into the suction side until steady operation is reached, and the screw can be reliably lubricated, cooled, and sealed, increasing reliability. While improving the efficiency, once steady operation is achieved, the injection can be switched to the screw space, so there is no reduction in efficiency.
第１図は本発明のスクリユー圧縮機を示す説明
図である。
１１……リキツドインジエクシヨンチユーブ、
１２……スクリユー空間、Ｖ……開閉弁、１７…
…バイパス通路。
FIG. 1 is an explanatory diagram showing a screw compressor of the present invention. 11...Liquid injector tube,
12...screw space, V...opening/closing valve, 17...
...bypass passage.
Claims (1)
え、圧縮工程中のスクリユー空間１２に、潤滑
油、液冷媒などのリキツドを吐出圧力によりイン
ジエクシヨンするごとくしたスクリユー圧縮機で
あつて、前記インジエクシヨンチユーブ１１に、
吸入側に連通するバイパス通路１７を設けて、該
バイパス通路１７に、開閉弁Ｖを介装すると共
に、吐出側と吸入側との間に、吐出圧力と吸入圧
力との圧力比が所定値以下のとき動作する信号発
生機構４２とこの信号発生機構４２の動作で閉じ
る開閉器４７とをもつ圧力比検出器３１を設け、
前記開閉器４７の閉動作で前記開閉弁Ｖを開い
て、前記リキツドを前記吸入側にインジエクシヨ
ンするごとくしたことを特徴とするスクリユー圧
縮機。1 A screw compressor equipped with a liquid injection tube 11 and configured to inject liquid such as lubricating oil or liquid refrigerant into a screw space 12 during a compression process by discharge pressure, the screw compressor having a liquid injection tube 11. ,
A bypass passage 17 communicating with the suction side is provided, and an on-off valve V is interposed in the bypass passage 17, and the pressure ratio between the discharge pressure and the suction pressure is below a predetermined value between the discharge side and the suction side. A pressure ratio detector 31 is provided which has a signal generating mechanism 42 that operates when the signal generating mechanism 42 operates and a switch 47 that closes by the operation of the signal generating mechanism 42
A screw compressor characterized in that the opening/closing valve V is opened by the closing operation of the opening/closing device 47, and the liquid is injected into the suction side.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP57004493A JPS58122390A (en) | 1982-01-14 | 1982-01-14 | Screw compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP57004493A JPS58122390A (en) | 1982-01-14 | 1982-01-14 | Screw compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS58122390A JPS58122390A (en) | 1983-07-21 |
| JPS6336435B2 true JPS6336435B2 (en) | 1988-07-20 |
Family
ID=11585599
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP57004493A Granted JPS58122390A (en) | 1982-01-14 | 1982-01-14 | Screw compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS58122390A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0211075U (en) * | 1988-07-01 | 1990-01-24 |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2603666B1 (en) * | 1986-09-10 | 1990-11-09 | Zimmern Bernard | INJECTED COMPRESSOR WITH LIQUID SWITCH |
| US4861246A (en) * | 1988-01-07 | 1989-08-29 | Bernard Zimmern | Injected compressor with liquid switch |
| JP2543463B2 (en) * | 1992-06-16 | 1996-10-16 | 株式会社二上鉄工所 | Paper feeder |
| JP3916511B2 (en) * | 2002-06-03 | 2007-05-16 | 株式会社神戸製鋼所 | Oil-cooled compressor |
| US7677051B2 (en) * | 2004-05-18 | 2010-03-16 | Carrier Corporation | Compressor lubrication |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS541041U (en) * | 1977-06-06 | 1979-01-06 |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS55104790U (en) * | 1979-01-17 | 1980-07-22 |
-
1982
- 1982-01-14 JP JP57004493A patent/JPS58122390A/en active Granted
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS541041U (en) * | 1977-06-06 | 1979-01-06 |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0211075U (en) * | 1988-07-01 | 1990-01-24 |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS58122390A (en) | 1983-07-21 |
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