JPS6135754Y2 - - Google Patents
Info
- Publication number
- JPS6135754Y2 JPS6135754Y2 JP1981007009U JP700981U JPS6135754Y2 JP S6135754 Y2 JPS6135754 Y2 JP S6135754Y2 JP 1981007009 U JP1981007009 U JP 1981007009U JP 700981 U JP700981 U JP 700981U JP S6135754 Y2 JPS6135754 Y2 JP S6135754Y2
- Authority
- JP
- Japan
- Prior art keywords
- gas
- refrigeration cycle
- liquid
- oil
- 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.)
- Expired
Links
- 239000007788 liquid Substances 0.000 claims description 48
- 238000005057 refrigeration Methods 0.000 claims description 44
- 230000006835 compression Effects 0.000 claims description 16
- 238000007906 compression Methods 0.000 claims description 16
- 238000002347 injection Methods 0.000 claims description 14
- 239000007924 injection Substances 0.000 claims description 14
- 239000007789 gas Substances 0.000 description 51
- ATUOYWHBWRKTHZ-UHFFFAOYSA-N Propane Chemical compound CCC ATUOYWHBWRKTHZ-UHFFFAOYSA-N 0.000 description 16
- 239000003921 oil Substances 0.000 description 16
- 238000001816 cooling Methods 0.000 description 10
- 239000001294 propane Substances 0.000 description 8
- 230000000694 effects Effects 0.000 description 7
- 238000007789 sealing Methods 0.000 description 5
- 239000003507 refrigerant Substances 0.000 description 4
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 4
- 239000001273 butane Substances 0.000 description 2
- 239000010687 lubricating oil Substances 0.000 description 2
- 238000005461 lubrication Methods 0.000 description 2
- IJDNQMDRQITEOD-UHFFFAOYSA-N n-butane Chemical compound CCCC IJDNQMDRQITEOD-UHFFFAOYSA-N 0.000 description 2
- OFBQJSOFQDEBGM-UHFFFAOYSA-N n-pentane Natural products CCCCC OFBQJSOFQDEBGM-UHFFFAOYSA-N 0.000 description 2
- 230000001105 regulatory effect Effects 0.000 description 2
- QGZKDVFQNNGYKY-UHFFFAOYSA-N Ammonia Chemical compound N QGZKDVFQNNGYKY-UHFFFAOYSA-N 0.000 description 1
- UFHFLCQGNIYNRP-UHFFFAOYSA-N Hydrogen Chemical compound [H][H] UFHFLCQGNIYNRP-UHFFFAOYSA-N 0.000 description 1
- QVGXLLKOCUKJST-UHFFFAOYSA-N atomic oxygen Chemical compound [O] QVGXLLKOCUKJST-UHFFFAOYSA-N 0.000 description 1
- 230000005494 condensation Effects 0.000 description 1
- 238000009833 condensation Methods 0.000 description 1
- 238000011109 contamination Methods 0.000 description 1
- 239000000498 cooling water Substances 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 239000001257 hydrogen Substances 0.000 description 1
- 229910052739 hydrogen Inorganic materials 0.000 description 1
- 239000000314 lubricant Substances 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 238000013021 overheating Methods 0.000 description 1
- 239000001301 oxygen Substances 0.000 description 1
- 229910052760 oxygen Inorganic materials 0.000 description 1
- 230000002265 prevention Effects 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 239000000126 substance Substances 0.000 description 1
- 230000001360 synchronised effect Effects 0.000 description 1
Description
【考案の詳細な説明】
〔考案の目的〕
（産業上の利用分野）
本考案は、無接触式スクリユー圧縮機を用いて
ガスを圧縮するに際し圧縮機内に油を噴射しない
ガス圧縮装置に関するものである。[Detailed description of the invention] [Purpose of the invention] (Field of industrial application) The present invention relates to a gas compression device that does not inject oil into the compressor when compressing gas using a non-contact screw compressor. be.
（従来の技術）
従来例えばプロパンガス、ブタン等は、油に溶
解し易いため又油を嫌う水素、酸素の圧縮機とし
ては無給油式のガス圧縮機が用いられた。例えば
横型対向ピストン圧縮機を無給油で用いた場合
は、大型となりリング摩耗、過熱の間題があり、
又回転圧縮機で完全無給油のものはターボ式が使
われるが大型大容量のものは10000r／ｍ以上の高
速回転となり、高圧縮比が出ないこと、騒音、耐
久性、コストの点で問題がある。又小型のものは
無給油式スクリユー圧縮機が用いられるが、無給
油、無接触式であるため8000r／ｍ〜14000r／ｍ
の回転数を出しても1.5Kg／cm2〜2.0Kg／cm2の昇圧
がせいぜいであつて圧力が上らず、断熱圧縮温度
やメタルの昇温防止には本体に水冷ジヤケツトを
設け又ロータを中空として内部に冷却水や冷却油
を通する必要があり、更にガス洩れ防止のために
機械的精度を高め回転数を上げるための増速機や
クリアランスを微少にする必要があつた。したが
つて構造が複雑となりコスト高になるという欠点
があつた。(Prior Art) Conventionally, oil-free gas compressors have been used for compressing hydrogen and oxygen, which do not like oil, since propane gas, butane, etc., are easily dissolved in oil. For example, when a horizontal opposed piston compressor is used without oil, it becomes large and has problems such as ring wear and overheating.
In addition, turbo type rotary compressors are used for completely oil-free rotary compressors, but large and large-capacity ones rotate at high speeds of over 10,000 r/m, which causes problems in terms of high compression ratios, noise, durability, and cost. There is. In addition, small-sized compressors use oil-free screw compressors, but since they are oil-free and contactless, they can run from 8000r/m to 14000r/m.
Even if the rotation speed is increased to 1.5Kg/cm 2 to 2.0Kg/cm 2 , the pressure will not rise.In order to prevent the adiabatic compression temperature and the temperature of the metal from rising, a water cooling jacket is installed on the main body, and the rotor is It was necessary to make it hollow so that cooling water and oil could pass through it, and to prevent gas leaks, it was necessary to increase mechanical precision and increase the number of revolutions by increasing the speed and making the clearance very small. Therefore, the structure is complicated and the cost is high.
（考案が解決しようとする問題点）
上述のように無給油式スクリユー圧縮機を用い
て油を噴射しないでガスを圧縮しようとする場合
は、圧力を上げることが困難であり、昇温防止手
段を設ける必要があり、ガス洩れ防止のための機
械的精度を高め、別に増速機を必要とする等の問
題があつた。(Problems to be solved by the invention) As mentioned above, when trying to compress gas without injecting oil using an oilless screw compressor, it is difficult to increase the pressure, and temperature rise prevention measures are required. There were problems such as the need to provide a separate speed increaser and the need to increase mechanical precision to prevent gas leaks.
本考案は無給油式スクリユー圧縮機を用いて増
速機を用いることなく回転数を高めて高圧縮し特
に昇温防止の手段を必要とせず、かつ機械的精度
を高める必要もなく簡単な構造で高圧縮のガスを
得られるようにしようとするものである。 This invention uses an oil-free screw compressor to increase the rotational speed and high compression without using a speed increaser, and has a simple structure that does not require any means to prevent temperature rise or increase mechanical precision. The aim is to make it possible to obtain highly compressed gas.
（問題点を解決するための手段）
本考案は第１、第２の冷凍サイクルを備え、第
１の冷凍サイクルに挿入された無接触、無給油式
スクリユー圧縮機のガス圧縮路程のガス閉じ込み
後の位置に、前記第２の冷凍サイクルで冷却、凝
縮させた第１の冷凍サイクルの凝縮液の一部が噴
射される液噴射孔を設け、第１、第２の冷凍サイ
クルよりなる二元冷凍サイクルにおいて、第１の
冷凍サイクルの圧縮機を無給油、無接触式スクリ
ユー圧縮機とし、このスクリユー圧縮機のガス閉
じ込み時の位置に油の代りに自己の凝縮液の一部
を噴射して潤滑、シール、冷却をさせるとき、こ
の凝縮液を第２の冷凍サイクルで冷却させること
により凝縮液の粘度を増して潤滑、シール効果を
向上させるとともに冷却効果をあげかつ一部の液
の蒸発潜熱によつてさらに冷却効果を向上させス
クリユー圧縮機を簡単な構造にして高圧縮のガス
を得ようとするものである。
(Means for Solving the Problems) The present invention includes first and second refrigeration cycles, and gas confinement in the gas compression path of a non-contact, oil-free screw compressor inserted into the first refrigeration cycle. A liquid injection hole through which a part of the condensed liquid of the first refrigeration cycle cooled and condensed in the second refrigeration cycle is injected is provided at the rear position, and In the refrigeration cycle, the compressor of the first refrigeration cycle is an oil-free, non-contact type screw compressor, and a part of its own condensate is injected instead of oil into the position of the screw compressor when gas is trapped. When performing lubrication, sealing, and cooling, this condensate is cooled in the second refrigeration cycle to increase the viscosity of the condensate, improving the lubrication and sealing effects, increasing the cooling effect, and preventing some of the liquid from evaporating. The aim is to further improve the cooling effect using latent heat, simplify the structure of the screw compressor, and obtain highly compressed gas.
（作用）
本考案は、第１、第２の冷凍サイクルを用いた
二元冷凍サイクルにおいて、第１の冷凍サイクル
に挿入した無給油、無接触式スクリユー圧縮機の
ガス圧縮路程に、第２の冷凍サイクルで冷却した
凝縮液の一部を噴射することにより、無給油、無
接触のガス圧縮路程において冷却された粘度の高
い凝縮液がガスのシールと冷却及び潤滑作用をす
るものである。(Function) In a binary refrigeration cycle using a first and second refrigeration cycle, the present invention provides a second By injecting a portion of the condensate cooled in the refrigeration cycle, the highly viscous condensate cooled in the oil-free, non-contact gas compression path acts as a gas seal, cooling, and lubricant.
（実施例） 次に本考案の実施例を説明する。(Example) Next, embodiments of the present invention will be described.
実施例 １
第１図に示すものは一般的なプロパンガス液化
装置を示し、１は無接触式スクリユー圧縮機で、
ロータは互に無接触でありタイミングギヤ（同調
ギヤ）を用いて連動させヒーター直結か必要に応
じて増速ギヤを附帯していることもある。そして
この圧縮機１と、吐出ガス管２、凝縮器３、液管
４、膨張弁５、防熱ジヤケツト６を有する液体プ
ロパン貯蔵タンク７、吸入ガス管８より第１の冷
凍サイクルＡが構成されている。又液管４の途中
より分岐液管９を分岐し、この分岐液管９を途中
に前記圧縮機１の発停に伴つて開閉する電磁弁１
０と流量調整弁１１を介して圧縮機１ロータのガ
ス閉じ込み後の位置に開口した液噴射孔１２に連
通させる。又凝縮器３は第２の冷凍サイクルＢの
蒸発器１３が挿入された熱交換器１４に挿入され
ている。又第２の冷凍サイクルＢは冷媒としてフ
レオンＲ２２などを用いて圧縮機１５としてはタ
イミングギヤ増速機を用いない一般的油噴射式ス
クリユー圧縮機（又はレシプロ、ターボ式でもよ
い。）を用い圧縮機１５、吐出ガス管１６、凝縮
器１７、液管１８、膨脹弁１９、前記熱交換器１
４に挿入された蒸発器１３、吸入ガス管２０より
構成され、前記吐出ガス管１６の途中に挿入され
た油分離器２１の油管２２を途中に油ポンプ２３
を介し圧縮機１５のロータのガス閉じ込み後の位
置に設けた液噴射孔２４に連通させる。又凝縮器
１７は水冷又は空気の冷却器２５が導入された熱
交換器２６に挿入されている。Example 1 The one shown in Fig. 1 shows a general propane gas liquefaction device, and 1 is a non-contact type screw compressor.
The rotors are not in contact with each other and are interlocked using a timing gear (synchronized gear), and may be directly connected to the heater or may be equipped with a speed increasing gear if necessary. A first refrigeration cycle A is comprised of the compressor 1, a discharge gas pipe 2, a condenser 3, a liquid pipe 4, an expansion valve 5, a liquid propane storage tank 7 having a heat-insulating jacket 6, and an intake gas pipe 8. There is. Further, a branch liquid pipe 9 is branched from the middle of the liquid pipe 4, and a solenoid valve 1 is installed in the middle of the branch liquid pipe 9 to open and close as the compressor 1 starts and stops.
0 and a flow rate regulating valve 11 to communicate with a liquid injection hole 12 opened at a position after the gas is trapped in the rotor of the compressor 1. Further, the condenser 3 is inserted into a heat exchanger 14 into which the evaporator 13 of the second refrigeration cycle B is inserted. The second refrigeration cycle B uses Freon R22 or the like as the refrigerant, and the compressor 15 is a general oil injection screw compressor (or a reciprocating or turbo type) that does not use a timing gear speed increaser. machine 15, discharge gas pipe 16, condenser 17, liquid pipe 18, expansion valve 19, and the heat exchanger 1
An oil pump 23 is connected to an oil pipe 22 of an oil separator 21 inserted in the middle of the discharge gas pipe 16.
The liquid injection hole 24 is connected to the liquid injection hole 24 provided in the rotor of the compressor 15 at a position after the gas is trapped. The condenser 17 is also inserted into a heat exchanger 26 into which a water or air cooler 25 is introduced.
次にこの実施例の作用を説明する。 Next, the operation of this embodiment will be explained.
第１の冷凍サイクルＡにおいてプロパンガス貯
蔵タンク７中には−40℃、0.104Kg／cm2の液体プ
ロパンガスが収納されており、防熱ジヤケツト６
を介存させるにもかかわらず外部からの熱によつ
て液体プロパンガスがガス化する。この蒸発ガス
は吸入ガス管８によつて圧縮機１に導入されて圧
縮され圧縮されたガスは吐出ガス管２に−５℃〜
＋２℃前後1.93Kg／cm2で吐出され、熱交換器１４
に導入されここで−20℃のフレオンガスと熱交換
し凝縮器３より−15℃、1.913Kg／cm2の凝縮液が
液管４に導出され、この液は膨脹弁５に減圧され
て−40℃、0.104Kg／cm2の液となつての液体プロ
パン貯蔵タンク７中に導入される。又液管４の途
中から−15℃の液の一部は分岐液管９に分岐され
圧縮機１の液噴射孔１２からロータに噴射され無
接触ロータの間隙を液シールすると共に圧縮機１
内を冷却する。又フレオンＲ２２を冷媒とした第
２の冷凍サイクルＢにおいては、圧縮機１５で油
噴射されながら圧縮されたガスは、凝縮器１７で
水冷又は空冷により液化し＋35℃、12.9Kg／cm2の
液が膨脹弁１９で減圧され、蒸発器１３では−20
℃、1.48Kg／cm2のガスとなつて第１の冷凍サイク
ルＡの凝縮器３を冷却する。 In the first refrigeration cycle A, the propane gas storage tank 7 stores liquid propane gas at -40°C and 0.104 kg/ cm2 , and the heat insulating jacket 6
Liquid propane gas is gasified by external heat despite the presence of heat. This evaporated gas is introduced into the compressor 1 through the suction gas pipe 8 and compressed, and the compressed gas is sent to the discharge gas pipe 2 from -5°C to
It is discharged at around +2℃ at 1.93Kg/ cm2 , and the heat exchanger 14
Here, the condensed liquid at -15°C and 1.913 kg/cm 2 is led out from the condenser 3 to the liquid pipe 4, and this liquid is depressurized by the expansion valve 5 to -40° C. ℃, 0.104 Kg/cm 2 liquid is introduced into the liquid propane storage tank 7. A part of the -15°C liquid from the middle of the liquid pipe 4 is branched to a branch liquid pipe 9 and injected to the rotor from the liquid injection hole 12 of the compressor 1, sealing the gap between the non-contact rotors and the compressor 1.
Cool the inside. In the second refrigeration cycle B using Freon R22 as a refrigerant, the gas compressed while being injected with oil in the compressor 15 is liquefied by water cooling or air cooling in the condenser 17, and becomes a liquid at +35°C and 12.9 kg/cm 2. is reduced in pressure by the expansion valve 19, and -20 in the evaporator 13.
℃ and 1.48 Kg/cm 2 to cool the condenser 3 of the first refrigeration cycle A.
実施例 ２ 次に第２図について説明する。Example 2 Next, FIG. 2 will be explained.
これは負荷側となる第１の冷凍サイクルＡに油
が全く混入しない冷凍方式である場合の冷凍装置
の一例である。 This is an example of a refrigeration system in which the first refrigeration cycle A on the load side is of a refrigeration type in which no oil is mixed in at all.
１は第１図の実施例で説明したものと同様な無
接触式スクリユー圧縮機で、この圧縮機１、吐出
ガス管２、凝縮器３、液管４、膨脹弁５、低圧受
液器２７、低圧液管２８、液ポンプ２９、流量調
整弁３０、熱発器３１、蒸発ガス管３２、吸入ガ
ス管８より第１の冷凍サイクルＡを構成し、前記
液管４の途中より分岐した分岐液管９を、途中に
流量調整弁１１を介して前記圧縮機１のロータの
ガス閉じ込み後の位置に設けた液噴射孔１２に連
通させる。又蒸発器３１には負荷側熱交換器３３
を臨ませる。第２の冷凍サイクルＢは実施例１と
同様である。 Reference numeral 1 designates a non-contact type screw compressor similar to that explained in the embodiment shown in FIG. , a low pressure liquid pipe 28, a liquid pump 29, a flow rate adjustment valve 30, a heat generator 31, an evaporative gas pipe 32, and an intake gas pipe 8 constitute a first refrigeration cycle A, and a branch liquid branched from the middle of the liquid pipe 4. The pipe 9 is communicated with a liquid injection hole 12 provided at a position after the gas is trapped in the rotor of the compressor 1 via a flow rate regulating valve 11 in the middle. In addition, the evaporator 31 is equipped with a load side heat exchanger 33.
to appear. The second refrigeration cycle B is similar to the first embodiment.
次にこの実施例２の作用を説明する。 Next, the operation of this second embodiment will be explained.
第１の冷凍サイクルＡは冷媒としてフレオンＲ
１２、アンモニアガスなどを用い第２の冷凍サイ
クルＢには冷媒としてフレオンＲ２２等を用い
る。第１の冷凍サイクルＡは圧縮機１で圧縮され
たフレオンＲ１２ガスが凝縮器３で−20℃のフレ
オンＲ２２と熱交換し膨脹弁５を経て減圧されて
低圧受液器２７内に−40℃、1.654Kg／cm2の低圧
液となつて貯溜され、負荷側の必要に応じて流量
を調整されて液ポンプ２９によつて蒸発器３１に
供給されガスは低圧受液器２７の気相部を介して
圧縮機１に吸入される。又圧縮機１内は−20℃の
凝縮液の一部が噴射されガスのシールと冷却がな
される。第１の冷凍サイクルＡには全く油が混入
せず、蒸発器３１の伝熱効果は抜群である。第２
の冷凍サイクルＢの作用は実施例１と同様であ
る。 The first refrigeration cycle A uses Freon R as the refrigerant.
12. Freon R22 or the like is used as a refrigerant in the second refrigeration cycle B using ammonia gas or the like. In the first refrigeration cycle A, Freon R12 gas compressed by the compressor 1 exchanges heat with Freon R22 at -20°C in the condenser 3, is depressurized through the expansion valve 5, and is stored at -40°C in the low-pressure liquid receiver 27. The gas is stored as a low-pressure liquid of 1.654 Kg/cm 2 and is supplied to the evaporator 31 by the liquid pump 29 with the flow rate adjusted according to the needs of the load side. It is sucked into the compressor 1 via. A portion of the -20°C condensate is injected into the compressor 1 for gas sealing and cooling. No oil is mixed into the first refrigeration cycle A, and the heat transfer effect of the evaporator 31 is excellent. Second
The operation of the refrigeration cycle B is the same as in the first embodiment.
実施例 ３
第３図に示すものは実施例２の一部を変更した
もので第１の冷凍サイクルＡにおいて低圧液管２
８より低圧分岐液管３４を分岐させてこれを液噴
射孔１２に連通され液ポンプ２９の圧力により液
を噴射するようにしたものでこの場合は低圧受液
器２７からの液が噴射されるから噴射液の温度を
更に低く（−40℃）することが出来る。Embodiment 3 The one shown in FIG. 3 is a partially modified version of Embodiment 2, in which the low pressure liquid pipe 2 is
A low-pressure branch liquid pipe 34 is branched from 8 and communicated with the liquid injection hole 12, and liquid is injected by the pressure of the liquid pump 29. In this case, liquid from the low-pressure liquid receiver 27 is injected. The temperature of the injection liquid can be further lowered (-40℃).
本考案によれば、第１、第２の冷凍サイクルを
備え、第１の冷凍サイクルに挿入された無接触、
無給油式スクリユー圧縮機のガス圧縮路程のガス
閉じ込み後の位置に、前記第２の冷凍サイクルで
冷却、圧縮させ第１の冷凍サイクルの凝縮液の一
部が噴射される液噴射孔を設けたため、第１の冷
凍サイクルに挿されたスクリユー圧縮機が無給
油、無接触式であるから、ガス圧縮路程に給油け
ずに運転することができ第１の冷凍サイクルにお
いては被圧縮ガスがプロパン、ブタン、フレオン
のように潤滑油に溶解し易く潤滑油と分離し難い
もの、或いは油の混入を全く避けたいガスの圧縮
に好都合である。又スクリユー圧縮機は、ロータ
とロータケース及びロータ相互が無接触であるた
めガス圧縮路程は無給油で運転することが可能に
なるが高圧縮ができず吐出ガスは比較的低圧とな
る。しかしこの低圧吐出ガスを圧縮機が何ら制約
されない第２の冷凍サイクルを用いて冷却するこ
とにより冷却することができるから第１の冷凍サ
イクルの凝縮効果を挙げることができる。更に第
１の冷凍サイクルのスクリユー圧縮機の無給油の
ガス圧縮路程のガス閉じ込み後の位置に第２の冷
凍サイクルで冷却した凝縮液の一部を噴射する液
噴射孔を設けたから、低温の凝縮液を液噴射孔よ
り噴射することにより、低温で粘度の高い凝縮液
によりガス圧縮路程における無接触のロータの隙
間が液密閉されロータが無接触式かつ3000r／ｍ
〜4000r／ｍ程度の比較的低い回転数であるにも
かかわらず２Kg／cm2〜３Kg／cm2程度の圧力を得る
ことができる。これは従来増速機を付けて
10000r／ｍ以上にした無給油、無接触のスクリユ
ー圧縮機の能力に匹敵する。そして２Kg／cm2〜３
Kg／cm2に圧縮されたガスを第２の冷凍サイクルで
冷却凝縮することにより無給油、無接触のスクリ
ユー圧縮機を用いて40℃以下の超低温を得ること
ができる。又第１の冷凍サイクルのスクリユー圧
縮機のガス圧縮路程に噴射される凝縮液は第２の
冷凍サイクルを用いて低温で凝縮させることがで
きるから液の温度が低く、粘度が高いから潤滑効
果とガスのシール効果を一層向上させることがで
きると共にガス圧縮路程で圧縮される圧縮ガスの
冷却効果を挙げることができる。従つて従来の無
給油、無接触式スクリユー圧縮機では機体に水冷
ジヤケツトを設けたり、ロータを中空にして内部
に冷水を通して冷却していたが、このような複雑
な構造を必要とせず、回転数も高速回転は必要と
せず、２極モーター直結で増速装置は不要であ
り、圧縮機を簡単な構造にして小型化することが
でき、駆動力も少なくてすみ経済上有利となるも
のでる。
According to the present invention, the non-contact device includes first and second refrigeration cycles, and is inserted into the first refrigeration cycle.
A liquid injection hole is provided at a position after gas confinement in the gas compression path of the oil-free screw compressor, through which a part of the condensate of the first refrigeration cycle cooled and compressed in the second refrigeration cycle is injected. Therefore, since the screw compressor inserted in the first refrigeration cycle is an oil-free, non-contact type, it can be operated without refueling the gas compression path.In the first refrigeration cycle, the compressed gas is propane, It is convenient for compressing substances such as butane and freon that are easily dissolved in lubricating oil and difficult to separate from the lubricating oil, or gases where it is desired to avoid contamination with oil at all. Further, since the screw compressor has no contact between the rotor, the rotor case, and the rotor, the gas compression path can be operated without oil supply, but high compression cannot be achieved and the discharged gas has a relatively low pressure. However, since this low-pressure discharged gas can be cooled by using the second refrigeration cycle in which the compressor is not restricted in any way, the condensation effect of the first refrigeration cycle can be achieved. Furthermore, a liquid injection hole for injecting a part of the condensate cooled in the second refrigeration cycle is provided at a position after gas confinement in the oil-free gas compression path of the screw compressor of the first refrigeration cycle, so that low-temperature By injecting condensate from the liquid injection hole, the low temperature and high viscosity condensate liquid seals the non-contact rotor gap in the gas compression path, making the rotor non-contact and 3000r/m.
Although the rotation speed is relatively low, about 4000 r/m, a pressure of about 2 Kg/cm 2 to 3 Kg/cm 2 can be obtained. This is conventionally equipped with a speed increaser.
The capacity is comparable to that of an oil-free, non-contact screw compressor that operates at over 10,000 r/m. and 2Kg/cm 2 ~3
By cooling and condensing the gas compressed to kg/cm 2 in the second refrigeration cycle, it is possible to obtain an ultra-low temperature of 40°C or less using an oil-free, non-contact screw compressor. In addition, the condensate injected into the gas compression path of the screw compressor in the first refrigeration cycle can be condensed at a low temperature using the second refrigeration cycle, so the temperature of the liquid is low and the viscosity is high, so it has a lubricating effect. The gas sealing effect can be further improved, and the compressed gas compressed in the gas compression path can be cooled. Therefore, in conventional oil-free, non-contact screw compressors, a water-cooling jacket is installed on the body or the rotor is hollow and cold water is passed inside to cool the compressor. The compressor does not require high-speed rotation, is directly connected to a two-pole motor, and does not require a speed increaser, and the compressor can be made smaller with a simple structure, requiring less driving force, which is economically advantageous.
第１図ないし第３図は本考案の夫々異る実施例
を示すフローシートダイヤグラムである。
Ａ……第１の冷凍サイクル、Ｂ……第２の冷凍
サイクル、１……無接触式スクリユー圧縮機、１
２……液噴射孔。
1 through 3 are flow sheet diagrams showing different embodiments of the present invention. A...First refrigeration cycle, B...Second refrigeration cycle, 1...Contactless screw compressor, 1
2...Liquid injection hole.
Claims (1)
サイクルに挿入された無接触、無給油式スクリユ
ー圧縮機のガス圧縮路程のガス閉じ込み後の位置
に、前記第２の冷凍サイクルで冷却、凝縮させた
第１の冷凍サイクルの凝縮液の一部が噴射される
液噴射孔を設けたことを特徴とするガス圧縮装
置。 The second refrigeration cycle cools the gas at a position after the gas is trapped in the gas compression path of the non-contact, oil-free screw compressor inserted into the first refrigeration cycle. A gas compression device characterized in that a liquid injection hole is provided through which a part of the condensed liquid of the first refrigeration cycle is injected.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1981007009U JPS6135754Y2 (en) | 1981-01-21 | 1981-01-21 |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1981007009U JPS6135754Y2 (en) | 1981-01-21 | 1981-01-21 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS56118992U JPS56118992U (en) | 1981-09-10 |
| JPS6135754Y2 true JPS6135754Y2 (en) | 1986-10-17 |
Family
ID=29603669
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1981007009U Expired JPS6135754Y2 (en) | 1981-01-21 | 1981-01-21 |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6135754Y2 (en) |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US229981A (en) * | 1880-07-13 | Island |
-
1981
- 1981-01-21 JP JP1981007009U patent/JPS6135754Y2/ja not_active Expired
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US229981A (en) * | 1880-07-13 | Island |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS56118992U (en) | 1981-09-10 |
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