JPH09268988A - Two stage screw compressor - Google Patents
Two stage screw compressorInfo
- Publication number
- JPH09268988A JPH09268988A JP14715596A JP14715596A JPH09268988A JP H09268988 A JPH09268988 A JP H09268988A JP 14715596 A JP14715596 A JP 14715596A JP 14715596 A JP14715596 A JP 14715596A JP H09268988 A JPH09268988 A JP H09268988A
- Authority
- JP
- Japan
- Prior art keywords
- stage
- pressure
- compressor
- oil
- stage compressor
- 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.)
- Granted
Links
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- Applications Or Details Of Rotary Compressors (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、例えば冷凍機、ヒ
ートポンプに適用される２段形スクリュ圧縮機に関する
ものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a two-stage screw compressor applied to, for example, refrigerators and heat pumps.
【０００２】[0002]
【従来の技術】従来、図８に示す冷凍機用の２段形スク
リュ圧縮機が公知である（特公平７−１８４２２号公
報）。この圧縮機は、単一のケーシング２１内におい
て、モータ２２を挟んで、その両側に互いに噛合う雌雄
一対の低圧段側、即ち第１段スクリュロータ２３および
同じく互いに噛合う雌雄一対の高圧段側、即ち第２段ス
クリュロータ２４をそれぞれ回転可能に設けて一体的に
形成された第１段圧縮機本体２５と第２段圧縮機本体２
６とを備えている。そして、この冷凍機の場合、図８に
おいて、第１段圧縮機本体２５の右側の箇所から図示し
ない蒸発器からの冷媒ガスを吸込み、第１段スクリュロ
ータ２３により圧縮し、第１段圧縮機本体２５の左側に
吐出する。続いて、この圧縮した冷媒ガスをモータ２２
内に通し、第２段圧縮機本体２６の右側から吸込み、さ
らに第２段スクリュロータ２４により圧縮し、第２段圧
縮機本体２６の左側から吐出するようになっている。こ
の吐出された冷媒ガスは、周知のように図示しない凝縮
器、膨張弁、さらに上記蒸発器を経て、再度第１段圧縮
機本体２５に吸込まれ、以後、上記同様に循環させられ
る。2. Description of the Related Art Conventionally, a two-stage screw compressor for a refrigerator shown in FIG. 8 is known (Japanese Patent Publication No. 7-18422). This compressor includes a pair of male and female low-pressure stages that engage with each other on both sides of a motor 22 in a single casing 21, that is, a first-stage screw rotor 23 and a pair of male and female high-pressure stages that also mesh with each other. That is, the first-stage compressor body 25 and the second-stage compressor body 2 integrally formed by rotatably providing the second-stage screw rotors 24, respectively.
6 is provided. Then, in the case of this refrigerator, in FIG. 8, the refrigerant gas from the evaporator (not shown) is sucked from the right side portion of the first-stage compressor body 25, and is compressed by the first-stage screw rotor 23 to obtain the first-stage compressor. Discharge to the left side of the main body 25. Then, the compressed refrigerant gas is supplied to the motor 22.
The second stage compressor body 26 is sucked in from the right side of the second stage compressor body 26, further compressed by the second stage screw rotor 24, and discharged from the left side of the second stage compressor body 26. As is well known, the discharged refrigerant gas is sucked into the first-stage compressor body 25 again through a condenser, an expansion valve, and the evaporator (not shown), and then circulated in the same manner as described above.
【０００３】さらに、この圧縮機の場合、第２段圧縮機
本体２６の吐出口と上記凝縮器との間に油分離回収器
（オイルセパレータ）２７が設けてあり、ここで圧縮さ
れた冷媒ガスと油とを分離し、冷媒ガスは図８中、Ｘで
示すように上記凝縮器に向かい、油は、油分離回収器２
７の下部の図示しない油溜まり部に一旦溜められる。こ
の油溜まり部の油は、さらに油冷却器（オイルクーラ）
２８、油フィルタ２９を経て、第１段、第２段圧縮機本
体２５、２６内の注油箇所に注入されるように形成され
ている。なお、図８中、Ｘは上述したように上記凝縮器
に向かうことを示し、Ｙは油圧源に通じていること、Ｚ
は上記蒸発器から続いていることを示している。Further, in the case of this compressor, an oil separator / collector (oil separator) 27 is provided between the discharge port of the second stage compressor body 26 and the condenser, and the refrigerant gas compressed therein is compressed. And oil are separated, the refrigerant gas is directed to the condenser as indicated by X in FIG.
It is temporarily stored in an oil sump (not shown) below 7. The oil in this oil reservoir is further cooled by an oil cooler (oil cooler).
It is formed so as to be injected into the oil-filling points in the first-stage and second-stage compressor bodies 25, 26 through the oil filter 28 and the oil filter 29. In FIG. 8, X indicates going to the condenser as described above, Y communicating with the hydraulic power source, and Z.
Indicates continuing from the evaporator.
【０００４】他方、図９に示す油冷式圧縮機が公知であ
る（特公平６−６８２７８号公報）。この圧縮機も上記
圧縮機の場合と同様に、圧縮機本体３１の吐出側に油分
離回収器３２、油冷却器３３、および油フィルタ３４を
備えている。さらに、この圧縮機は油フィルタ３４の二
次側に油ポンプ３５を備えている。そして、上記同様に
油分離回収器３２にて圧縮ガスと油とを分離し、圧縮ガ
スは油分離回収器３２の上方に続く吐出流路に送り出す
一方、油は一旦油分離回収器３２の下部の油溜まり部３
６に溜めるようになっている。油溜まり部３６の油は上
記同様に油冷却器３３、油フィルタ３４を経て、さらに
油ポンプ３５により加圧されて圧縮機本体３１内の注油
箇所に導かれ、その後圧縮機本体３１の吐出口から圧縮
ガスとともに油分離回収器３２に至り、上記同様に循環
するようになっている。On the other hand, the oil-cooled compressor shown in FIG. 9 is known (Japanese Patent Publication No. 6-68278). This compressor is also provided with an oil separation / recovery device 32, an oil cooler 33, and an oil filter 34 on the discharge side of the compressor body 31, as in the case of the compressor. Further, the compressor includes an oil pump 35 on the secondary side of the oil filter 34. Then, similarly to the above, the oil separation / recovery device 32 separates the compressed gas from the oil, and the compressed gas is sent to the discharge passage continuing above the oil separation / recovery device 32, while the oil is once in the lower part of the oil separation / recovery device 32. Oil sump part 3
It is designed to store in 6. Similarly to the above, the oil in the oil sump 36 passes through the oil cooler 33 and the oil filter 34, is further pressurized by the oil pump 35, and is guided to the lubricating point in the compressor body 31, and then the discharge port of the compressor body 31. The compressed gas and the oil separation / recovery device 32 are circulated and circulated in the same manner as described above.
【０００５】[0005]
【発明が解決しようとする課題】上記特公平７−１８４
２２号公報に開示の圧縮機の場合、第１段、第２段圧縮
機本体２５、２６内の注油箇所へは、第２段圧縮機本体
２６の吐出圧力とほぼ同じ圧力の油が油分離回収器２
７、油冷却器２８、油フィルタ２９を経て注入される。
一般に、高圧になるほど油へのガスの溶解度は大きくな
るが、例えば冷媒としてクロロジフルオロメタン（ＣＨ
ＣｌＦ2）を使用した場合、特に油に溶解し易いため、
問題となる。即ち、高圧下、クロロジフルオロメタンが
溶解した油が上記注油箇所に注入され、その箇所の圧力
まで減圧した場合、油中よりクロロジフルオロメタンガ
スがフラッシュし、フラッシュしたガスが第１段、第２
段圧縮機本体２５、２６の吸込ポートから吸込まれ、圧
縮機の吸込容量の低下を招来するという問題が生じる。
また、特公平６−６８２７８号公報に記載の圧縮機の場
合も、上記圧縮機と同様に、注油箇所各部に高圧の油を
そのまま注入するようになっているため、上記同様の問
題が生じる。本発明は、斯る従来の問題をなくすことを
を課題としてなされたもので、吸込容量の向上を可能と
した２段形スクリュ圧縮機を提供しようとするものであ
る。[Problems to be Solved by the Invention] Japanese Patent Publication No. 7-184
In the case of the compressor disclosed in Japanese Unexamined Patent Publication No. 22 No. 22, oil having a pressure substantially equal to the discharge pressure of the second-stage compressor body 26 is oil-separated into the oil-filling points in the first-stage and second-stage compressor bodies 25, 26. Collector 2
7, the oil cooler 28, and the oil filter 29 are injected.
Generally, the higher the pressure, the greater the solubility of gas in oil, but for example, chlorodifluoromethane (CH
When ClF 2 ) is used, it is particularly easy to dissolve in oil,
It becomes a problem. That is, when the oil in which chlorodifluoromethane is dissolved is injected into the above-mentioned lubrication location under high pressure and the pressure at that location is reduced, the chlorodifluoromethane gas is flushed from the oil, and the flushed gas is the first and second stages.
There is a problem in that the suction capacity is sucked from the suction ports of the stage compressor main bodies 25 and 26, and the suction capacity of the compressor is reduced.
Also, in the case of the compressor described in Japanese Patent Publication No. 6-68278, similar to the compressor, the high-pressure oil is directly injected into each part of the lubrication point, so that the same problem as described above occurs. The present invention has been made to eliminate the above-mentioned conventional problems, and an object of the present invention is to provide a two-stage screw compressor capable of improving the suction capacity.
【０００６】[0006]
【課題を解決するための手段】上記課題を解決するため
に、第１発明は、単一のケーシング内に、互いに噛合う
雌雄一対のスクリュロータの２組を、それぞれ回転可能
に収容して第１段、第２段圧縮機本体を形成し、各段の
一方の各ロータ軸を互いに一体回転可能に設け、かつ第
１段圧縮機本体の吐出口と第２段圧縮機本体の吸込口と
を連通させるとともに、第２段圧縮機本体の吐出口から
油分離回収器に至り、この油分離回収器の下部の油溜ま
り部から少なくとも第１段圧縮機本体のスクリュロータ
の吐出側の軸受、軸封部、および第２段圧縮機本体のス
クリュロータの軸受、軸封部、ロータ室を含む注油箇所
に通じる第１給油流路を設けた２段形スクリュ圧縮機に
おいて、第１段圧縮機本体と第２段圧縮機本体との間の
下部に生じる油溜まり部と第１段圧縮機本体のスクリュ
ロータの吸込側の軸受、軸封部とを連通させる第２給油
流路を設けて構成した。In order to solve the above-mentioned problems, a first aspect of the present invention is to provide a single casing in which two sets of a pair of male and female screw rotors meshing with each other are rotatably housed. First-stage and second-stage compressor bodies are formed, one rotor shaft of each stage is integrally rotatable with each other, and a first-stage compressor body discharge port and a second-stage compressor body suction port are provided. And the oil separation / recovery device from the discharge port of the second-stage compressor body, and at least the discharge-side bearing of the screw rotor of the first-stage compressor body from the oil sump part below the oil-separation / recovery device, A two-stage screw compressor provided with a shaft seal portion and a first oil supply passage leading to an oil-filling portion including a bearing of a screw rotor of the main body of the second stage compressor, a shaft seal portion, and a rotor chamber. Oil sump formed in the lower part between the main body and the second stage compressor main body Ri section and the suction side of the bearing of the screw rotor of the first stage compressor body, which is configured by providing a second oil supply passage for communicating the shaft seal unit.
【０００７】また、第２発明は、上記第１給油流路を第
１段圧縮機本体の吸込口および吐出口のいずれにも連通
することがないロータ室内におけるガス閉込み空間に連
通させる第３給油流路を設けて構成した。A second aspect of the present invention is a third aspect of the present invention, wherein the first oil supply passage is connected to a gas confining space in the rotor chamber that does not communicate with either the suction port or the discharge port of the first stage compressor body. It was configured by providing an oil supply channel.
【０００８】さらに、第３発明は、上記第３給油流路に
介在させた電磁式の第１開閉弁と、第１段圧縮機本体の
吸込側の圧力を検出可能に設けられ、検出圧力が予め定
めた値以上の場合にのみ上記第１開閉弁を開かせる圧力
スイッチ、或は第２段圧縮機本体の吐出側の圧力を検出
可能に設けられ、検出圧力が予め定めた値以下の場合に
のみ上記第１開閉弁を開かせる圧力スイッチ、或は第１
段、第２段圧縮機本体間の中間圧力と上記吐出側の圧力
との差圧を検出可能に設けられ、検出差圧が、予め定め
た値以下の場合にのみ上記第１開閉弁を開かせる圧力ス
イッチの内のいずれかの圧力スイッチとを設けて構成し
た。Further, according to the third aspect of the invention, the electromagnetic first opening / closing valve interposed in the third oil supply passage and the suction side pressure of the first stage compressor body are provided so as to detect the pressure. When the pressure switch that opens the first on-off valve only when the value is a predetermined value or more, or the discharge side pressure of the second stage compressor body is detected, and the detected pressure is less than or equal to the predetermined value Pressure switch that opens the first on-off valve only, or the first
The pressure difference between the pressure on the discharge side and the intermediate pressure between the main bodies of the second and second stage compressors is provided so as to be detected, and the first opening / closing valve is opened only when the detected pressure difference is equal to or less than a predetermined value. One of the pressure switches to be used is provided.
【０００９】さらに、第４発明は、上記第１給油流路の
内の上記注油箇所に直接連通する部分を電磁式の第２開
閉弁を介して上記第１段圧縮機本体のスクリュロータの
吸込側の軸受、軸封部に連通させる第４給油流路と、上
記第２給油流路に介在させた電磁式の第３開閉弁と、上
記第１段圧縮機本体の吸込側の圧力と第１段、第２段圧
縮機本体間の中間圧力との差圧を検出可能に設けられ、
検出差圧が、予め定めた値以上の場合には上記第２開閉
弁を閉じさせるとともに上記第３開閉弁を開かせ、上記
予め定めた値未満の場合には上記第２開閉弁を開かせる
とともに上記第３開閉弁を閉じさせる圧力スイッチとを
設けて構成した。Further, in a fourth aspect of the present invention, a portion of the first oil supply passage, which directly communicates with the lubrication point, is sucked into the screw rotor of the first stage compressor body via an electromagnetic second on-off valve. Side oil supply side, a fourth oil supply passage communicating with the shaft seal portion, an electromagnetic third on-off valve interposed in the second oil supply passage, a suction side pressure of the first stage compressor body, and It is provided to detect the pressure difference between the intermediate pressure between the main body of the first and second stage compressors.
When the detected differential pressure is a predetermined value or more, the second opening / closing valve is closed and the third opening / closing valve is opened, and when the detected differential pressure is less than the predetermined value, the second opening / closing valve is opened. A pressure switch for closing the third opening / closing valve is also provided.
【００１０】[0010]
【発明の実施の形態】次に、本発明の実施の一形態を図
面にしたがって説明する。図１は、何ら限定するもので
はないが、例えばフロンガスの一種であるクロロジフル
オロメタンを冷媒ガスとする冷凍機、或はヒートポンプ
に用いられる第１発明に係る２段形スクリュ圧縮機を示
している。図示する例の場合、単一のケーシング１内
に、互いに噛合う雌雄一対の第１段、第２段スクリュロ
ータ２，３の２組を、それぞれ回転可能に収容して低圧
側の第１段圧縮機本体Ｃ１および高圧側の第２段圧縮機
本体Ｃ２が形成してある。なお、第１段スクリュロータ
２は第１段圧縮機本体Ｃ１に対応し、第２段スクリュロ
ータ３は第２段圧縮機本体Ｃ２に対応する。図１におい
て第１段圧縮機本体Ｃ１の右側にはケーシング１を共有
するモータ４が設けてあり、このモータ４により第１段
圧縮機本体Ｃ１の一対のスクリュロータ２の一方のロー
タを駆動している。また、この駆動されるロータの軸と
第２段圧縮機本体Ｃ２の一対のスクリュロータ３の一方
のロータの軸とはカップリングを介して一体回転可能に
結合され、モータ４によりスクリュロータ２，３が回転
させられるようになっている。Next, an embodiment of the present invention will be described with reference to the drawings. FIG. 1 shows a two-stage screw compressor according to the first aspect of the present invention, which is used for, for example, a refrigerator that uses chlorodifluoromethane, which is a type of Freon gas, as a refrigerant gas, or a heat pump, although not limited thereto. . In the case of the illustrated example, two sets of a pair of first and second stage screw rotors 2 and 3 meshing with each other are rotatably housed in a single casing 1 to rotatably accommodate the first stage on the low pressure side. A compressor body C1 and a high pressure side second stage compressor body C2 are formed. The first-stage screw rotor 2 corresponds to the first-stage compressor body C1 and the second-stage screw rotor 3 corresponds to the second-stage compressor body C2. In FIG. 1, a motor 4 sharing the casing 1 is provided on the right side of the first-stage compressor body C1, and this motor 4 drives one rotor of a pair of screw rotors 2 of the first-stage compressor body C1. ing. The shaft of the driven rotor and the shaft of one rotor of the pair of screw rotors 3 of the second stage compressor body C2 are integrally rotatably coupled via a coupling, and the motor 4 drives the screw rotors 2, 2. 3 can be rotated.
【００１１】さらに、第１段圧縮機本体Ｃ１の右側の上
部に吸込口５が設けられ、第１段圧縮機本体Ｃ１の図示
しない吐出口と第２段圧縮機本体Ｃ２の吸込口６とは連
通している。なお、一部を除き図示していないが、例え
ば冷凍機或はヒートポンプの場合、周知のようにこの第
２段圧縮機本体Ｃ２の吐出口から出て、第１段圧縮機本
体Ｃ１の吸込口５に至る冷媒の閉じた循環流路が形成さ
れており、この循環流路には、典型的なものとしては、
第２段圧縮機本体Ｃ２の吐出口側から順番に、油分離回
収器７、凝縮器、膨張弁および蒸発器が介在させてあ
る。Further, a suction port 5 is provided on the upper right side of the first-stage compressor body C1, and a discharge port (not shown) of the first-stage compressor body C1 and a suction port 6 of the second-stage compressor body C2 are provided. It is in communication. Although not shown except for a part, in the case of, for example, a refrigerator or a heat pump, as is well known, it comes out from the discharge port of the second-stage compressor body C2 and the suction port of the first-stage compressor body C1. A closed circulation flow passage for the refrigerant up to 5 is formed, and this circulation flow passage typically includes:
The oil separation / recovery device 7, the condenser, the expansion valve, and the evaporator are provided in order from the discharge port side of the second-stage compressor body C2.
【００１２】この油分離回収器７の下部は油溜まり部８
になっており、ここからは、油冷却器９、油フィルタ１
０を経て、第１段スクリュロータ２の吐出側におけるロ
ータ軸の軸受、軸封部ｃ、第２段圧縮機本体Ｃ２内のロ
ータ室ｂ、および第２段スクリュロータ３の吐出側にお
けるロータ軸の軸受、軸封部ａ等の注油箇所に通じる第
１給油流路１１が延びている。さらに、第２段圧縮機本
体Ｃ２の吸込口６の箇所の下部に形成される油溜まり部
１２から第１段スクリュロータ２の吸込口５側における
ロータ軸の軸受、軸封部ｄに通じる第２給油流路１３が
設けてある。The lower part of the oil separating and collecting device 7 is an oil sump 8
From here, oil cooler 9 and oil filter 1
0, the bearing of the rotor shaft on the discharge side of the first-stage screw rotor 2, the shaft seal portion c, the rotor chamber b in the second-stage compressor body C2, and the rotor shaft on the discharge side of the second-stage screw rotor 3. The first oil supply passage 11 extending to the oil-filling points such as the bearing and the shaft seal portion a extends. Further, the oil reservoir 12 formed in the lower portion of the suction port 6 of the second-stage compressor body C2 communicates with the bearing of the rotor shaft on the suction port 5 side of the first-stage screw rotor 2 and the shaft sealing portion d. Two oil supply channels 13 are provided.
【００１３】そして、図１において矢印Ｉで示すように
上記蒸発器から流入してきた冷媒ガスを吸込口５から吸
込み、圧縮し、軸受、軸封部ｃ、ｄから流入してくる油
とともに第１段圧縮機本体Ｃ１の吐出口から吐出し、吸
込口６から吸込み、第２段圧縮機本体Ｃ２により圧縮
し、第２段圧縮機本体Ｃ２の吐出口から油分離回収器７
に向けて、吐出するようになっている。なお、この吐出
口から吐出された冷媒ガスは、第１段圧縮機本体Ｃ１か
ら流入してきた油、ロータ室ｂに供給された油、軸受、
軸封部ａから流入してきた油とともに油分離回収器７に
送られる。油分離回収器７では、気液分離し、高圧の冷
媒ガスは、矢印IIで示すように油分離回収器７の上部か
ら上記凝縮器に向けて送り出され、上記膨張弁、上記蒸
発器を経て循環流路内を循環するようになっている。一
方、気液分離され、油溜まり部８に溜められた油は、第
１給油流路１１により軸受、軸封部ａ、ロータ室ｂ、お
よび軸受、軸封部ｃに供給される。さらに、第２給油流
路１３からは第２段圧縮機本体Ｃ２の吐出口内に比して
圧力の低い油溜まり部１２の油が軸受、軸封部ｄに注入
されるようになっている。Then, as shown by an arrow I in FIG. 1, the refrigerant gas flowing from the evaporator is sucked from the suction port 5 and compressed, and together with the oil flowing from the bearing and the shaft sealing portions c and d, the first Discharge from the discharge port of the stage compressor body C1, suck from the suction port 6, compressed by the second stage compressor body C2, and from the discharge port of the second stage compressor body C2, the oil separation and recovery unit 7
It is designed to discharge toward. The refrigerant gas discharged from the discharge port is the oil flowing from the first-stage compressor body C1, the oil supplied to the rotor chamber b, the bearing,
It is sent to the oil separation / collector 7 together with the oil that has flowed in from the shaft sealing portion a. In the oil separation / recovery device 7, gas-liquid separated, high-pressure refrigerant gas is sent out from the upper part of the oil separation / recovery device 7 toward the condenser, and passes through the expansion valve and the evaporator. It circulates in the circulation channel. On the other hand, the oil separated into gas and liquid and stored in the oil sump 8 is supplied to the bearing, the shaft seal part a, the rotor chamber b, the bearing, and the shaft seal part c by the first oil supply passage 11. Further, the oil in the oil sump portion 12 having a lower pressure than that in the discharge port of the second-stage compressor body C2 is injected from the second oil supply passage 13 into the bearing and the shaft seal portion d.
【００１４】このように、この圧縮機では、第２段圧縮
機本体Ｃ２の吐出口の圧力とほぼ等しい圧力の油分離回
収器７からの油の供給箇所を、比較的高圧の状態にある
軸受、軸封部ａ、ロータ室ｂおよび軸受、軸封部ｃと
し、圧力の低い軸受、軸封部ｄには、第２段圧縮機本体
Ｃ２の吐出口内に比して圧力の低い油溜まり部１２の油
を注入するように形成してある。そして、例えば冷媒と
してクロロジフルオロメタンのように油に溶解し易い冷
媒を用いた場合でも、注油箇所で油が減圧され冷媒ガス
がフラッシュして、フラッシュしたガスが圧縮機に吸込
まれることによる吸込容量の低下が起こらないようにな
っている。As described above, in this compressor, the oil supply point from the oil separation / recovery device 7 having a pressure substantially equal to the pressure of the discharge port of the second stage compressor body C2 is in a relatively high pressure bearing. , A shaft seal portion a, a rotor chamber b and a bearing, and a shaft seal portion c, and a bearing having a low pressure and a shaft seal portion d have an oil sump portion having a pressure lower than that in the discharge port of the second stage compressor body C2. It is formed so as to inject 12 oils. Even when a refrigerant that is easily dissolved in oil, such as chlorodifluoromethane, is used as the refrigerant, the oil is depressurized at the lubrication point and the refrigerant gas is flushed, and the flushed gas is sucked into the compressor by suction. The capacity does not decrease.
【００１５】図２は、第２発明に係る２段形スクリュ圧
縮機を示し、図１に示す圧縮機とは、新たに第３給油流
路１４を設けた点を除き、実質的に同一であり、互いに
共通する部分については同一番号を付して説明を省略す
る。この第３給油流路１４は、第１給油流路１１を第１
段圧縮機本体Ｃ１の吸込口５および吐出口のいずれにも
連通することがないロータ室内におけるガス閉込み空間
に連通させたものである。この第３給油流路１４は第１
給油流路１１と同様に第２段圧縮機本体Ｃ２の吐出側の
圧力である吐出圧力にほぼ等しい状態にあり、かつ第１
段圧縮機本体Ｃ１内の上記ロータ室内の圧力が軸受、軸
封部ｃの箇所よりも低い故、図３を参照して以下に説明
するように、軸受、軸封部ｃ、ｄから第１段圧縮機本体
Ｃ１内のロータ室への油の流入が少ない場合でも、この
ロータ室への油の流入が促進されるようになっている。FIG. 2 shows a two-stage screw compressor according to the second invention, which is substantially the same as the compressor shown in FIG. 1 except that a third oil supply passage 14 is newly provided. Therefore, the common parts are given the same numbers and their explanations are omitted. The third refueling flow path 14 is formed by connecting the first refueling flow path 11 to the first refueling path 11.
It is connected to a gas confining space in the rotor chamber that does not communicate with either the suction port 5 or the discharge port of the stage compressor body C1. This third refueling passage 14 is the first
Similar to the oil supply passage 11, it is in a state substantially equal to the discharge pressure which is the pressure on the discharge side of the second stage compressor body C2, and
Since the pressure inside the rotor chamber in the main stage compressor body C1 is lower than that of the bearing and the shaft seal portion c, as will be described below with reference to FIG. Even if the oil flow into the rotor chamber in the stage compressor body C1 is small, the oil flow into the rotor chamber is promoted.
【００１６】図３は、図２に示す圧縮機の吸込圧力、吐
出圧力および第１段圧縮機本体Ｃ１の吐出口と第２段圧
縮機本体Ｃ２の吸込口６との間の圧力、即ち中間圧力と
の関係を示し、横軸は冷媒の吸込圧相当飽和温度（蒸発
温度）（℃）および対応する吸込圧力（ata）を示し、
縦軸は圧力（ata）を示している。図３に示されるよう
に、吸込圧相当飽和温度が低い場合には吐出圧力と中間
圧力との差圧は大きいが、吸込圧相当飽和温度が−２０
〜−３０℃と２段形スクリュ圧縮機としては高い状態の
場合、吐出圧力と中間圧力との差圧が小さくなり、第１
段圧縮機本体Ｃ１の吐出側の軸受、軸封部ｃに注入され
る油量は少なくなる、そして、結果的には軸受、軸封部
ｄに注入される油量も少なくなり、第１段圧縮機本体Ｃ
１のロータ室内に流入する油も少なくなる。FIG. 3 shows the suction pressure and discharge pressure of the compressor shown in FIG. 2 and the pressure between the discharge port of the first-stage compressor body C1 and the suction port 6 of the second-stage compressor body C2, that is, the intermediate pressure. The relationship with the pressure is shown. The horizontal axis shows the suction pressure equivalent saturation temperature (evaporation temperature) (° C) of the refrigerant and the corresponding suction pressure (ata).
The vertical axis represents pressure (ata). As shown in FIG. 3, when the suction pressure equivalent saturation temperature is low, the differential pressure between the discharge pressure and the intermediate pressure is large, but the suction pressure equivalent saturation temperature is -20.
When the temperature is up to -30 ° C and high as a two-stage screw compressor, the differential pressure between the discharge pressure and the intermediate pressure becomes small, and
The amount of oil injected into the bearing on the discharge side of the stage compressor body C1 and the shaft seal part c is reduced, and as a result, the amount of oil injected into the bearing and the shaft seal part d is also reduced. Compressor body C
The amount of oil flowing into the No. 1 rotor chamber is also reduced.
【００１７】そこで、図２に示す圧縮機では、軸受、軸
封部ｃよりも圧力の低いこのロータ室に高圧の第１給油
流路１１の油を第３給油流路１４により導き、給油量の
低下を回避するようにしてある。この圧縮機では、第３
給油流路１４を第１段圧縮機本体Ｃ１の吸込口５および
吐出口のいずれにも連通することがないロータ室内にお
けるガス閉込み空間に連通させることにより、注入した
油からフラッシュガスの影響を最小限にとどめ得るよう
になっている。なお、中間圧力は吸込圧力により一義的
に決まり、吐出圧力は上記凝縮器に通す冷却水の温度、
凝縮器の容量等により変動し、一般に冬場は低くなる。Therefore, in the compressor shown in FIG. 2, the high-pressure oil in the first oil supply passage 11 is guided to the rotor chamber whose pressure is lower than that of the bearing and the shaft seal portion c by the third oil supply passage 14 to supply oil. We are trying to avoid the decrease of. In this compressor,
By connecting the oil supply passage 14 to the gas confining space in the rotor chamber that does not communicate with either the suction port 5 or the discharge port of the first-stage compressor body C1, the effect of flash gas from the injected oil is reduced. It is designed to be kept to a minimum. The intermediate pressure is uniquely determined by the suction pressure, and the discharge pressure is the temperature of the cooling water passing through the condenser,
It varies depending on the capacity of the condenser, etc., and generally becomes low in winter.
【００１８】図４は、第３発明に係る２段形スクリュ圧
縮機を示し、図２に示す圧縮機とは、新たに第３給油流
路１４に電磁式の第１開閉弁１５を設けた点、および第
１段圧縮機本体Ｃ１の吸込流路の圧力を検出し、検出圧
力、即ち吸込圧力が予め定めた値以上の場合には、第１
開閉弁１５を開かせ、上記値よりも小さい場合には第１
開閉弁１５を閉じさせる圧力スイッチ１６を設けた点を
除き、実質的に同一であり、互いに共通する部分につい
ては同一番号を付して説明を省略する。なお、図４にお
いて※印同志は連続することを表している。圧縮機の吸
込圧相当飽和温度、即ち蒸発温度が低くなると吸込圧力
も低くなり、ロータ室への油の注入量に影響が出てくる
ため、図４に示す圧縮機では、吸込圧力を検出すること
により吸込圧力が予め定めた値以上の場合には、第１段
圧縮機本体Ｃ１のロータ室内の圧力と上記中間圧力との
差圧が小さくなるため、第１開閉弁１５を開くようにし
て上記ロータ室への油の注入量の低下を防止するように
してある。FIG. 4 shows a two-stage screw compressor according to the third aspect of the present invention, which is different from the compressor shown in FIG. 2 in that an electromagnetic first opening / closing valve 15 is newly provided in the third oil supply passage 14. Point, and the pressure in the suction passage of the first-stage compressor body C1 is detected. If the detected pressure, that is, the suction pressure is equal to or higher than a predetermined value, the first
Open the on-off valve 15 and if it is smaller than the above value, the first
Except that a pressure switch 16 for closing the on-off valve 15 is provided, the parts are substantially the same, and common parts are denoted by the same reference numerals and description thereof is omitted. In addition, in FIG. 4, * marks indicate that they are continuous. When the saturation temperature equivalent to the suction pressure of the compressor, that is, the evaporation temperature becomes low, the suction pressure also becomes low, and the amount of oil injected into the rotor chamber is affected. Therefore, the compressor shown in FIG. 4 detects the suction pressure. Therefore, when the suction pressure is equal to or higher than the predetermined value, the differential pressure between the pressure in the rotor chamber of the first-stage compressor body C1 and the intermediate pressure becomes small. Therefore, the first opening / closing valve 15 should be opened. The amount of oil injected into the rotor chamber is prevented from decreasing.
【００１９】なお、第３発明は、上述した例のものに限
定するものでなく、この他、圧力スイッチ１６に代え
て、例えば第２段圧縮機本体Ｃ２の吐出圧力を検出し、
検出圧力が予め定めた値以下の場合には第１開閉弁１５
を開き、この値よりも大きい場合には第１開閉弁１５を
閉じる圧力スイッチ、或は第２段圧縮機本体Ｃ２の吐出
圧力と中間圧力の差圧を検出し、この検出した値、即ち
圧力が予め定めた値以下の場合には、第１開閉弁１５を
開かせ、上記値よりも大きい場合には第１開閉弁１５を
閉じさせる圧力スイッチを設けた圧縮機も含むものであ
る。The third invention is not limited to the above-mentioned example, but instead of the pressure switch 16, for example, the discharge pressure of the second stage compressor body C2 is detected,
If the detected pressure is below a predetermined value, the first opening / closing valve 15
Open, and when it is larger than this value, the pressure switch that closes the first on-off valve 15 or the differential pressure between the discharge pressure and the intermediate pressure of the second-stage compressor body C2 is detected, and this detected value, that is, the pressure. The compressor includes a pressure switch that opens the first opening / closing valve 15 when is less than a predetermined value and closes the first opening / closing valve 15 when larger than the above value.
【００２０】図５は、第４発明に係る２段形スクリュ圧
縮機を示し、図１，２および図４に示す圧縮機と互いに
共通する部分については同一番号を付して説明を省略す
る。この圧縮機には、第１給油流路１１の内の上記注油
箇所に直接連通する部分を電磁式の第２開閉弁１７を介
して第１段圧縮機本体Ｃ１のスクリュロータ２の吸込側
の軸受、軸封部ｄに連通させる第４給油流路１８が設け
てある。また、第２給油流路１３には電磁式の第３開閉
弁１９が介在させてある。さらに、第１段圧縮機本体Ｃ
１の吸込側の圧力と第１段、第２段圧縮機本体Ｃ１，Ｃ
２間の中間圧力との間の差圧を検出し、検出差圧が、予
め定めた値、例えば２ata以上の場合には、第２開閉弁
１７を閉じさせるとともに第３開閉弁１９を開かせ、上
記予め定めた値未満の場合には、逆に第２開閉弁１７を
開かせるとともに第３開閉弁１９を閉じさせる圧力スイ
ッチ２０が設けてある。なお、図５において＊印同志は
連続することを表している。FIG. 5 shows a two-stage screw compressor according to the fourth aspect of the present invention. The parts common to those of the compressor shown in FIGS. 1, 2 and 4 are designated by the same reference numerals and their description is omitted. In this compressor, a portion of the first oil supply passage 11 that directly communicates with the above-mentioned lubrication point is connected to the suction side of the screw rotor 2 of the first-stage compressor body C1 via the electromagnetic second on-off valve 17. A fourth oil supply passage 18 is provided to communicate with the bearing and the shaft seal portion d. An electromagnetic third on-off valve 19 is interposed in the second oil supply passage 13. Furthermore, the first stage compressor body C
No. 1 suction side pressure and the first and second stage compressor bodies C1, C
The differential pressure between the intermediate pressure between the two is detected, and when the detected differential pressure is a predetermined value, for example, 2ata or more, the second opening / closing valve 17 is closed and the third opening / closing valve 19 is opened. A pressure switch 20 for opening the second opening / closing valve 17 and closing the third opening / closing valve 19 is provided if the value is less than the predetermined value. In addition, in FIG. 5, the asterisk marks indicate that they are continuous.
【００２１】ところで、この種の圧縮機では、例えば冷
媒ガスチャージ時や、蒸発温度が低い場合において無負
荷運転を行った場合のように、運転条件によっては上記
差圧が小さくなり、軸受、軸封部ｄに十分に油注入され
ない場合が生じる。これに対して、図５に示す圧縮機の
場合、上記差圧が大きい場合には、図１に示す圧縮機に
おけるのと同様に各注油箇所に油が導かれる一方、上記
差圧が小さくなった場合には、第２開閉弁１７が開き、
第４給油流路１８から軸受、軸封部ｄに第２段圧縮機本
体Ｃ２の吐出側の圧力にほぼ等しい圧力の油が導かれ、
軸受、軸封部ｄにも十分に油注入されるようになってい
る。By the way, in this type of compressor, the above-mentioned differential pressure becomes small depending on the operating conditions, for example, when the refrigerant gas is charged or when no load operation is performed when the evaporation temperature is low. In some cases, oil may not be sufficiently injected into the sealed portion d. On the other hand, in the case of the compressor shown in FIG. 5, when the differential pressure is large, the oil is guided to the respective lubrication points as in the compressor shown in FIG. 1, while the differential pressure becomes small. In the case of opening, the second on-off valve 17 opens,
Oil having a pressure substantially equal to the pressure on the discharge side of the second-stage compressor body C2 is guided from the fourth oil supply passage 18 to the bearing and the shaft sealing portion d,
Oil is sufficiently injected into the bearing and the shaft seal portion d.
【００２２】図６は、第４発明に係る別の形態の２段形
スクリュ圧縮機を示し、図５に示す圧縮機とは、図２に
示す圧縮機の場合と同様に第３給油流路１４を設けた点
を除き、他は実質的に同一であり、互いに共通する部分
については同一番号を付して説明を省略する。この圧縮
機の場合も、上記差圧が大きい場合には、図２に示す圧
縮機におけるのと同様に各注油箇所に油が導かれ、上記
差圧が小さくなった場合には、図５に示す圧縮機の場合
と同様に軸受、軸封部ｄにも十分に油注入されるように
なる。FIG. 6 shows another embodiment of a two-stage screw compressor according to the fourth aspect of the present invention. The compressor shown in FIG. 5 is similar to the compressor shown in FIG. Except for the point that 14 is provided, the other parts are substantially the same, and common parts are denoted by the same reference numerals and description thereof is omitted. Also in the case of this compressor, when the differential pressure is large, oil is introduced to the respective oiling points in the same manner as in the compressor shown in FIG. As in the case of the compressor shown, oil is sufficiently injected into the bearing and the shaft seal portion d.
【００２３】図７は、第４発明に係るさらに別の形態の
２段形スクリュ圧縮機を示し、図６に示す圧縮機とは、
図４の圧縮機の場合と同様に第３給油流路１４に第１開
閉弁１５を設けた点、および検出圧力に基づいて第１開
閉弁１５を上記同様に開閉させる圧力スイッチ１６を設
けた点を除き、他は実質的に同一であり、互いに共通す
る部分については同一番号を付して説明を省略する。こ
の圧縮機の場合も、上記差圧が大きい場合には、図４に
示す圧縮機におけるのと同様に各注油箇所に油が導か
れ、上記差圧が小さくなった場合には、図５に示す圧縮
機の場合と同様に軸受、軸封部ｄにも十分に油注入され
るようになる。FIG. 7 shows a two-stage screw compressor according to still another embodiment of the fourth invention, and the compressor shown in FIG.
As in the case of the compressor shown in FIG. 4, a point where the first opening / closing valve 15 is provided in the third oil supply passage 14 and a pressure switch 16 for opening / closing the first opening / closing valve 15 in the same manner as above based on the detected pressure are provided. Except for the points, the other parts are substantially the same, and the parts common to each other are denoted by the same reference numerals and the description thereof will be omitted. Also in the case of this compressor, when the differential pressure is large, oil is introduced to the respective lubrication points in the same manner as in the compressor shown in FIG. As in the case of the compressor shown, oil is sufficiently injected into the bearing and the shaft seal portion d.
【００２４】[0024]
【発明の効果】以上の説明より明らかなように、第１発
明によれば、単一のケーシング内に、互いに噛合う雌雄
一対のスクリュロータの２組を、それぞれ回転可能に収
容して第１段、第２段圧縮機本体を形成し、各段の一方
の各ロータ軸を互いに一体回転可能に設け、かつ第１段
圧縮機本体の吐出口と第２段圧縮機本体の吸込口とを連
通させるとともに、第２段圧縮機本体の吐出口から油分
離回収器に至り、この油分離回収器の下部の油溜まり部
から少なくとも第１段圧縮機本体のスクリュロータの吐
出側の軸受、軸封部、および第２段圧縮機本体のスクリ
ュロータの軸受、軸封部、ロータ室を含む注油箇所に通
じる第１給油流路を設けた２段形スクリュ圧縮機におい
て、第１段圧縮機本体と第２段圧縮機本体との間の下部
に生じる油溜まり部と第１段圧縮機本体のスクリュロー
タの吸込側の軸受、軸封部とを連通させる第２給油流路
を設けて構成してある。このため、例えばクロロジフル
オロメタンのような油に溶解し易い冷媒を用いた冷凍
機、ヒートポンプに本圧縮機を用いた場合でも、吸込容
量の低下は防止できるという効果を奏する。As is apparent from the above description, according to the first aspect of the present invention, two sets of a pair of male and female screw rotors meshing with each other are rotatably housed in a single casing. And a second stage compressor body are formed, one rotor shaft of each stage is integrally rotatable with each other, and a discharge port of the first stage compressor body and a suction port of the second stage compressor body are provided. While communicating with each other, the oil is separated from the discharge port of the main body of the second stage compressor to the oil separation / recovery device, and at least the discharge side bearing and shaft of the screw rotor of the first stage compressor main body is connected to the oil sump part under the oil separation / recovery device. A two-stage screw compressor provided with a first oil supply passage leading to an oil-filling portion including a sealing portion, a screw rotor bearing of the second-stage compressor body, a shaft sealing portion, and a rotor chamber, the first-stage compressor body Sump formed in the lower part between the main body of the second stage compressor and the When the suction side of the bearing of the screw rotor of the first stage compressor body, are configured by providing a second oil supply passage for communicating the shaft seal unit. Therefore, even if the present compressor is used in a refrigerator or heat pump that uses a refrigerant that is easily dissolved in oil, such as chlorodifluoromethane, it is possible to prevent a decrease in suction capacity.
【００２５】また、第２発明によれば、上記第１給油流
路を第１段圧縮機本体の吸込口および吐出口のいずれに
も連通することがないロータ室内におけるガス閉込み空
間に連通させる第３給油流路を設けて構成してある。こ
のため、第１発明による効果に加えて、上記同様に、冷
凍機、ヒートポンプに本圧縮機を用いた場合において、
蒸発温度が低下して、吐出圧力と中間圧力との差圧が小
さくなっても圧縮機内の各注油箇所への油の注入量の低
下を防止できるという効果を奏する。Further, according to the second aspect of the invention, the first oil supply passage is connected to the gas confining space in the rotor chamber that is not connected to either the suction port or the discharge port of the first stage compressor body. A third oil supply passage is provided and configured. Therefore, in addition to the effects of the first invention, in the same manner as above, when the present compressor is used for the refrigerator and the heat pump,
Even if the evaporation temperature decreases and the pressure difference between the discharge pressure and the intermediate pressure decreases, it is possible to prevent the decrease in the amount of oil injected into each oil injection point in the compressor.
【００２６】さらに、第３発明によれば、上記第３給油
流路に介在させた電磁式の第１開閉弁と、第１段圧縮機
本体の吸込側の圧力を検出可能に設けられ、検出圧力が
予め定めた値以上の場合にのみ上記第１開閉弁を開かせ
る圧力スイッチ、或は第２段圧縮機本体の吐出側の圧力
を検出可能に設けられ、検出圧力が予め定めた値以下の
場合にのみ上記第１開閉弁を開かせる圧力スイッチ、或
は第１段、第２段圧縮機本体間の中間圧力と上記吐出側
の圧力との差圧を検出可能に設けられ、検出差圧が、予
め定めた値以下の場合にのみ上記第１開閉弁を開かせる
圧力スイッチの内のいずれかの圧力スイッチとを設けて
構成してある。このため、第１、第２発明による効果に
加えて、圧縮機の吸込圧相当飽和温度の低下に伴い吸込
圧力が低下しても、上記各注油箇所への油の注入量に対
する影響を最小限にとどめ、必要な注入量を確保するこ
とが可能になるという効果を奏する。Further, according to the third aspect of the invention, the electromagnetic first opening / closing valve interposed in the third oil supply passage and the suction side pressure of the first stage compressor body are provided so as to be detectable, and detected. A pressure switch that opens the first on-off valve only when the pressure is a predetermined value or more, or a discharge side pressure of the second-stage compressor body is provided so that it can be detected, and the detected pressure is less than or equal to a predetermined value. In the case of the above, the pressure switch for opening the first opening / closing valve or the pressure difference between the discharge side pressure and the intermediate pressure between the main bodies of the first and second stage compressors is provided so as to be detected. Only one of the pressure switches that opens the first opening / closing valve only when the pressure is equal to or lower than a predetermined value is provided. For this reason, in addition to the effects of the first and second inventions, even if the suction pressure decreases as the saturation temperature equivalent to the suction pressure of the compressor decreases, the influence on the amount of oil injected into each of the above-mentioned lubrication points is minimized. This has the effect of making it possible to secure the required injection amount.
【００２７】さらに、第４発明によれば、上記第１給油
流路の内の上記注油箇所に直接連通する部分を電磁式の
第２開閉弁を介して上記第１段圧縮機本体のスクリュロ
ータの吸込側の軸受、軸封部に連通させる第４給油流路
と、上記第２給油流路に介在させた電磁式の第３開閉弁
と、上記第１段圧縮機本体の吸込側の圧力と第１段、第
２段圧縮機本体間の中間圧力との差圧を検出可能に設け
られ、検出差圧が、予め定めた値以上の場合には上記第
２開閉弁を閉じさせるとともに上記第３開閉弁を開か
せ、上記予め定めた値未満の場合には上記第２開閉弁を
開かせるとともに上記第３開閉弁を閉じさせる圧力スイ
ッチとを設けて構成してある。このため、第１、第２或
は第３発明による効果に加えて、運転条件によって第１
段圧縮機本体の吸込側の圧力と上記中間圧力との間の差
圧が小さくなっても、第１段圧縮機本体のスクリュロー
タの吸込側の軸受、軸封部に第２段圧縮機本体の吐出側
の圧力とほぼ等しい圧力の油が導かれ、この箇所にも十
分に油注入され、必要な注入量を確保することが可能に
なるという効果を奏する。Further, according to the fourth aspect of the invention, the screw rotor of the first-stage compressor body is provided through the electromagnetic second on-off valve in the portion of the first oil supply passage that directly communicates with the lubrication point. Bearing on the suction side, a fourth oil supply passage communicating with the shaft seal portion, an electromagnetic third on-off valve interposed in the second oil supply passage, and a suction side pressure of the first-stage compressor body. And a pressure difference between the intermediate pressure between the main body of the first and second stage compressors can be detected. When the detected pressure difference is equal to or more than a predetermined value, the second opening / closing valve is closed and A pressure switch for opening the third on-off valve and opening the second on-off valve and closing the third on-off valve when the value is less than the predetermined value is provided. Therefore, in addition to the effect of the first, second or third invention, the first
Even if the pressure difference between the suction side pressure of the main stage compressor body and the intermediate pressure becomes small, the second side compressor body is attached to the bearing and shaft seal portion of the screw rotor of the first stage compressor body. Oil having a pressure substantially equal to the pressure on the discharge side is introduced, and oil is sufficiently injected into this portion as well, and it is possible to secure the necessary injection amount.
【図１】 第１発明に係る２段形スクリュ圧縮機の要部
の構成を示す図である。FIG. 1 is a diagram showing a configuration of a main part of a two-stage screw compressor according to a first invention.
【図２】 第２発明に係る２段形スクリュ圧縮機の要部
の構成を示す図である。FIG. 2 is a diagram showing a configuration of a main part of a two-stage screw compressor according to a second invention.
【図３】 図２に示す２段形スクリュ圧縮機における吸
込圧力、中間圧力および吐出圧力の関係を示す図であ
る。3 is a diagram showing a relationship among a suction pressure, an intermediate pressure and a discharge pressure in the two-stage screw compressor shown in FIG.
【図４】 第３発明に係る２段形スクリュ圧縮機の要部
の構成を示す図である。FIG. 4 is a diagram showing a configuration of a main part of a two-stage screw compressor according to a third invention.
【図５】 第４発明に係る２段形スクリュ圧縮機の要部
の構成を示す図である。FIG. 5 is a diagram showing a configuration of a main part of a two-stage screw compressor according to a fourth invention.
【図６】 第４発明に係る別の形態の２段形スクリュ圧
縮機の要部の構成を示す図である。FIG. 6 is a diagram showing a configuration of a main part of a two-stage screw compressor of another form according to the fourth invention.
【図７】 第４発明に係るさらに別の形態の２段形スク
リュ圧縮機の要部の構成を示す図である。FIG. 7 is a diagram showing a configuration of a main part of a two-stage type screw compressor according to still another form of the fourth invention.
【図８】 従来の２段形スクリュ圧縮機の要部の構成を
示す図である。FIG. 8 is a diagram showing a configuration of a main part of a conventional two-stage screw compressor.
【図９】 従来の油冷式スクリュ圧縮機の全体構成を示
す図である。FIG. 9 is a diagram showing an overall configuration of a conventional oil-cooled screw compressor.
１ ケーシング ２ 第１段スクリュロータ ３ 第２段スクリュロータ ５、６ 吸込口 ７ 油分離回収器 ８ 油溜まり部 １１ 第１給油流路 １２ 油溜まり部 １３ 第２給油流路 １４ 第３給油流路 １５ 第１開閉弁 １６ 圧力スイッチ １７ 第２開閉弁 １８ 第４給油流路 １９ 第３開閉弁 ２０ 圧力スイッチ Ｃ１ 第１段圧縮機本体 Ｃ２ 第２段圧縮機本体 ａ、ｃ、ｄ 軸受、軸封部 ｂ ロータ室 DESCRIPTION OF SYMBOLS 1 Casing 2 1st stage screw rotor 3 2nd stage screw rotor 5 and 6 Suction port 7 Oil separation / collector 8 Oil sump portion 11 1st oil supply passage 12 Oil sump portion 13 2nd oil supply passage 14 3rd oil supply passage 15 First on-off valve 16 Pressure switch 17 Second on-off valve 18 Fourth oil supply passage 19 Third on-off valve 20 Pressure switch C1 First stage compressor body C2 Second stage compressor body a, c, d Bearing, shaft seal Part b rotor room
Claims (4)
雄一対のスクリュロータの２組を、それぞれ回転可能に
収容して第１段、第２段圧縮機本体を形成し、各段の一
方の各ロータ軸を互いに一体回転可能に設け、かつ第１
段圧縮機本体の吐出口と第２段圧縮機本体の吸込口とを
連通させるとともに、第２段圧縮機本体の吐出口から油
分離回収器に至り、この油分離回収器の下部の油溜まり
部から少なくとも第１段圧縮機本体のスクリュロータの
吐出側の軸受、軸封部、および第２段圧縮機本体のスク
リュロータの軸受、軸封部、ロータ室を含む注油箇所に
通じる第１給油流路を設けた２段形スクリュ圧縮機にお
いて、第１段圧縮機本体と第２段圧縮機本体との間の下
部に生じる油溜まり部と第１段圧縮機本体のスクリュロ
ータの吸込側の軸受、軸封部とを連通させる第２給油流
路を設けたことを特徴とする２段形スクリュ圧縮機。1. A first casing and a second stage compressor main body are formed by rotatably accommodating two sets of a pair of male and female screw rotors meshing with each other in a single casing. The respective rotor shafts are integrally rotatable with each other, and
The discharge port of the main body of the second-stage compressor and the suction port of the main body of the second-stage compressor are connected to each other, and the discharge port of the main body of the second-stage compressor reaches the oil separation / recovery device. First lubrication leading from at least part of the first stage compressor main body to the discharge side bearing of the screw rotor, the shaft sealing part, and the second stage compressor main body screw rotor bearing, shaft sealing part, and rotor chamber In a two-stage screw compressor provided with a flow path, an oil sump portion formed in a lower portion between a first-stage compressor body and a second-stage compressor body and a suction side of a screw rotor of the first-stage compressor body A two-stage screw compressor, characterized in that a second oil supply flow path is provided to connect the bearing and the shaft seal portion.
吸込口および吐出口のいずれにも連通することがないロ
ータ室内におけるガス閉込み空間に連通させる第３給油
流路を設けたことを特徴とする請求項１に記載の２段形
スクリュ圧縮機。2. A third oil supply passage is provided for connecting the first oil supply passage to a gas confining space in the rotor chamber that does not communicate with either the suction port or the discharge port of the first stage compressor body. The two-stage screw compressor according to claim 1, wherein the two-stage screw compressor is used.
第１開閉弁と、第１段圧縮機本体の吸込側の圧力を検出
可能に設けられ、検出圧力が予め定めた値以上の場合に
のみ上記第１開閉弁を開かせる圧力スイッチ、或は第２
段圧縮機本体の吐出側の圧力を検出可能に設けられ、検
出圧力が予め定めた値以下の場合にのみ上記第１開閉弁
を開かせる圧力スイッチ、或は第１段、第２段圧縮機本
体間の中間圧力と上記吐出側の圧力との差圧を検出可能
に設けられ、検出差圧が、予め定めた値以下の場合にの
み上記第１開閉弁を開かせる圧力スイッチの内のいずれ
かの圧力スイッチとを設けたことを特徴とする請求項２
に記載の２段形スクリュ圧縮機。3. An electromagnetic first opening / closing valve interposed in the third oil supply passage and a suction side pressure of the first stage compressor body are provided so as to be detectable, and the detected pressure is equal to or more than a predetermined value. Pressure switch that opens the first on-off valve only in the case of
A pressure switch which is provided so as to detect the pressure on the discharge side of the main stage compressor body and opens the first opening / closing valve only when the detected pressure is a predetermined value or less, or the first stage and second stage compressors. Any one of the pressure switches that is provided so as to be able to detect the differential pressure between the intermediate pressure between the main bodies and the discharge side pressure and that opens the first opening / closing valve only when the detected differential pressure is less than or equal to a predetermined value. 3. A pressure switch is provided.
The two-stage screw compressor described in.
直接連通する部分を電磁式の第２開閉弁を介して上記第
１段圧縮機本体のスクリュロータの吸込側の軸受、軸封
部に連通させる第４給油流路と、上記第２給油流路に介
在させた電磁式の第３開閉弁と、上記第１段圧縮機本体
の吸込側の圧力と第１段、第２段圧縮機本体間の中間圧
力との差圧を検出可能に設けられ、検出差圧が、予め定
めた値以上の場合には上記第２開閉弁を閉じさせるとと
もに上記第３開閉弁を開かせ、上記予め定めた値未満の
場合には上記第２開閉弁を開かせるとともに上記第３開
閉弁を閉じさせる圧力スイッチとを設けたことを特徴と
する請求項１から３のいずれかに記載の２段形スクリュ
圧縮機。4. A bearing and a shaft on the suction side of the screw rotor of the first-stage compressor main body through a second electromagnetic on-off valve at a portion of the first oil supply passage that directly communicates with the oil supply point. A fourth oil supply passage communicating with the sealing portion, an electromagnetic third on-off valve interposed in the second oil supply passage, pressure on the suction side of the first stage compressor body, first stage, second A differential pressure with respect to the intermediate pressure between the main body of the stage compressor is provided so that it can be detected. When the detected differential pressure is a predetermined value or more, the second on-off valve is closed and the third on-off valve is opened. 4. A pressure switch for opening the second on-off valve and closing the third on-off valve when the value is less than the predetermined value, provided in any one of claims 1 to 3. Two-stage screw compressor.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP14715596A JP3535938B2 (en) | 1996-02-02 | 1996-06-10 | Two-stage screw compressor |
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8-17522 | 1996-02-02 | ||
| JP1752296 | 1996-02-02 | ||
| JP14715596A JP3535938B2 (en) | 1996-02-02 | 1996-06-10 | Two-stage screw compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH09268988A true JPH09268988A (en) | 1997-10-14 |
| JP3535938B2 JP3535938B2 (en) | 2004-06-07 |
Family
ID=26354061
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP14715596A Expired - Fee Related JP3535938B2 (en) | 1996-02-02 | 1996-06-10 | Two-stage screw compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3535938B2 (en) |
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6755039B2 (en) * | 2002-09-17 | 2004-06-29 | Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) | Screw refrigerating apparatus |
| WO2007000815A1 (en) * | 2005-06-29 | 2007-01-04 | Mayekawa Mfg. Co., Ltd | Oil supply method and device for two-stage screw compressor, and method of operating refrigeration device |
| WO2010010925A1 (en) | 2008-07-25 | 2010-01-28 | 東京電力株式会社 | Compressor and freezer |
| WO2011114714A1 (en) | 2010-03-17 | 2011-09-22 | 東京電力株式会社 | Freezing machine |
| CN102635551A (en) * | 2011-02-15 | 2012-08-15 | 株式会社神户制钢所 | Two-stage screw compression type freezing device |
| CN102705238A (en) * | 2012-06-12 | 2012-10-03 | 浙江杰能压缩设备有限公司 | Shaft-seal-free series connection-type multi-stage screw compressor |
| CN108884834A (en) * | 2016-03-25 | 2018-11-23 | 株式会社神户制钢所 | Oil free screw compressor |
| TWI668373B (en) * | 2018-08-01 | 2019-08-11 | 復盛股份有限公司 | Two-stage compressor |
| JP2020041744A (en) * | 2018-09-11 | 2020-03-19 | 富士電機株式会社 | Heat pump type steam generating device |
| CN111963437A (en) * | 2019-07-31 | 2020-11-20 | 宁波鲍斯能源装备股份有限公司 | Integrated screw vortex two-stage compressor |
-
1996
- 1996-06-10 JP JP14715596A patent/JP3535938B2/en not_active Expired - Fee Related
Cited By (22)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6755039B2 (en) * | 2002-09-17 | 2004-06-29 | Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) | Screw refrigerating apparatus |
| WO2007000815A1 (en) * | 2005-06-29 | 2007-01-04 | Mayekawa Mfg. Co., Ltd | Oil supply method and device for two-stage screw compressor, and method of operating refrigeration device |
| JPWO2007000815A1 (en) * | 2005-06-29 | 2009-01-22 | 株式会社前川製作所 | Lubricating method for two-stage screw compressor, device and operating method for refrigerating device |
| US7722346B2 (en) | 2005-06-29 | 2010-05-25 | Mayekawa Mfg. Co., Ltd. | Oil supply method of two-stage screw compressor, two-stage screw compressor applying the method, and method of operating refrigerating machine having the compressor |
| US8277207B2 (en) | 2005-06-29 | 2012-10-02 | Mayekawa Mfg. Co., Ltd. | Oil supply method of two-stage screw compressor, two-stage screw compressor applying the method, and method of operating refrigerating machine having the compressor |
| WO2010010925A1 (en) | 2008-07-25 | 2010-01-28 | 東京電力株式会社 | Compressor and freezer |
| US8621882B2 (en) | 2008-07-25 | 2014-01-07 | Danish Technological Institute | Compressor and refrigerating machine |
| WO2011114714A1 (en) | 2010-03-17 | 2011-09-22 | 東京電力株式会社 | Freezing machine |
| US9494154B2 (en) | 2010-03-17 | 2016-11-15 | Tokyo Electric Power Company, Incorporated | Refrigerator |
| KR101330332B1 (en) * | 2011-02-15 | 2013-11-15 | 가부시키가이샤 고베 세이코쇼 | Two-stage screw compression type refrigerating device |
| JP2012167608A (en) * | 2011-02-15 | 2012-09-06 | Kobe Steel Ltd | Two-stage screw compression type refrigerating device |
| CN102635551A (en) * | 2011-02-15 | 2012-08-15 | 株式会社神户制钢所 | Two-stage screw compression type freezing device |
| CN102705238A (en) * | 2012-06-12 | 2012-10-03 | 浙江杰能压缩设备有限公司 | Shaft-seal-free series connection-type multi-stage screw compressor |
| CN108884834A (en) * | 2016-03-25 | 2018-11-23 | 株式会社神户制钢所 | Oil free screw compressor |
| CN108884834B (en) * | 2016-03-25 | 2020-03-03 | 株式会社神户制钢所 | Oil-free screw compressor |
| TWI668373B (en) * | 2018-08-01 | 2019-08-11 | 復盛股份有限公司 | Two-stage compressor |
| EP3604813A1 (en) * | 2018-08-01 | 2020-02-05 | Fu Sheng Industrial Co., Ltd. | Two-stage compressor |
| CN110792596A (en) * | 2018-08-01 | 2020-02-14 | 复盛股份有限公司 | Two-stage compressor |
| US10948220B2 (en) | 2018-08-01 | 2021-03-16 | Fu Sheng Industrial Co., Ltd. | Two-stage compressor |
| JP2020041744A (en) * | 2018-09-11 | 2020-03-19 | 富士電機株式会社 | Heat pump type steam generating device |
| CN111963437A (en) * | 2019-07-31 | 2020-11-20 | 宁波鲍斯能源装备股份有限公司 | Integrated screw vortex two-stage compressor |
| CN111963437B (en) * | 2019-07-31 | 2022-11-04 | 宁波鲍斯能源装备股份有限公司 | Integrated screw vortex two-stage compressor |
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