JPH0552439B2 - - Google Patents
Info
- Publication number
- JPH0552439B2 JPH0552439B2 JP57158110A JP15811082A JPH0552439B2 JP H0552439 B2 JPH0552439 B2 JP H0552439B2 JP 57158110 A JP57158110 A JP 57158110A JP 15811082 A JP15811082 A JP 15811082A JP H0552439 B2 JPH0552439 B2 JP H0552439B2
- Authority
- JP
- Japan
- Prior art keywords
- slide valve
- piston
- cylinder chamber
- slide
- pressure
- 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 - Lifetime
Links
- 238000006073 displacement reaction Methods 0.000 claims description 4
- 230000006835 compression Effects 0.000 description 10
- 238000007906 compression Methods 0.000 description 10
- 230000007423 decrease Effects 0.000 description 4
- 210000005240 left ventricle Anatomy 0.000 description 2
- 210000005241 right ventricle Anatomy 0.000 description 2
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 230000000087 stabilizing effect 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
- F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
- F04C28/10—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
- F04C28/12—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using sliding valves
- F04C28/125—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using sliding valves with sliding valves controlled by the use of fluid other than the working fluid
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
〔産業上の利用分野〕
本発明スクリユー圧縮機の容量制御装置に係
り、特にスライド弁の移動の容易性をはかつたス
クリユー圧縮機の容量制御装置に関する。
〔従来の技術〕
スクリユー圧縮機の容量制御はスライド弁によ
つて行なわれることが多い。このスライド弁式の
容量制御方式は、該スライド弁をスクリユーロー
タの軸の方向に移動させ、圧縮カスの一部をスラ
イド弁の位置により吸入側にバイパスさせること
により容量を制御する方式である。上記のスライ
ド弁を移動させる機構はスライド弁にスライドピ
ストンを連結し、このピストンの左右に油圧等に
より圧力差を付与し、ピストンを移動させる駆動
力を得ている。
第１図を参考して従来のスクリユー圧縮機及び
その容量制御機構について説明する。
吸入口１より吸入された低温、低圧のガスは一
対のスクリユーロータ２の回転圧縮により高温、
高圧なガスに圧縮される。スクリユーロータは、
ラジアル軸受３とスラスト軸受４によつて保持さ
れる。圧縮室は、ロータ２とケーシング６および
吸入側カバ９とスライド弁１１により形成され
る。又、図に示す圧縮機の場合、大気との密封の
ため軸シール５およびシールカバ７、吐出側カバ
８を有する。高温高圧のガスは、吐出口１０より
吐出される。
次に容量制御機構について説明する。
圧縮機の一部を形成するスライド弁１１にはロ
ツド１２を介してスラスト方向にピストン１３が
連結され、このピストン１３の前後の室１４、室
１５に油圧により圧力差を生じさせ、スライド弁
１１を図示左方向にピストン１３を介し動かして
容量を制御する方式である。運転中のスライド弁
１１前後には吐出圧力と吸入圧力が作用するが、
シリンダ室１４に電磁弁１６、を介し給油管１８
から高圧油２０を導き、またシリンダ室１５から
は電磁弁２２を介して、排油管１９を経て吸入側
１に接続すると、ピストン１３の前後に圧力差が
生じ図示の左方向に力が作用する。この力が吐出
圧力による右方向の力より大きい場合はスライド
弁１１は左方向に動き、圧縮容量は少なくなる。
逆に容量を多くする場合は、シリンダ室１５に電
磁弁１７を介して給油管から高圧油２０を導き、
またシリンダ室１４から電磁弁２３を介し排油管
１９を経て吸入側１に接続するとピストン１３の
前後に圧力差が生じ、図示の右方向に力が作用す
る。この力がスライド弁にかかる左方向の力より
大きい場合は、スライド弁１１は右方向に動き、
圧縮容量は多くなる。又、ピストン１３を中間位
置で保持したい場合は、全ての電磁弁１６，１
７，２２，２３を閉めれば、ピストン前後のシリ
ンダ室の油はにげることが出来ないため、ピスト
ンは動かなく、中間位置で保持する。電磁弁１
６，１７，２２，２３と容量の関係を纏めると次
の表に示される。
[Industrial Application Field] The present invention relates to a capacity control device for a screw compressor, and particularly to a capacity control device for a screw compressor that facilitates the movement of a slide valve. [Prior Art] The capacity of a screw compressor is often controlled by a slide valve. This slide valve type capacity control system controls the capacity by moving the slide valve in the direction of the axis of the screw rotor and bypassing a portion of the compressed scum to the suction side depending on the position of the slide valve. . The mechanism for moving the slide valve described above connects a slide piston to the slide valve, and applies a pressure difference between the left and right sides of the piston using hydraulic pressure or the like to obtain a driving force for moving the piston. A conventional screw compressor and its capacity control mechanism will be explained with reference to FIG. The low-temperature, low-pressure gas inhaled through the suction port 1 is compressed by the rotation of a pair of screw rotors 2, resulting in high temperature and low-pressure gas.
Compressed into high pressure gas. The screw rotor is
It is held by a radial bearing 3 and a thrust bearing 4. The compression chamber is formed by the rotor 2, the casing 6, the suction side cover 9, and the slide valve 11. Further, the compressor shown in the figure has a shaft seal 5, a seal cover 7, and a discharge side cover 8 for sealing against the atmosphere. The high temperature and high pressure gas is discharged from the discharge port 10. Next, the capacity control mechanism will be explained. A piston 13 is connected in the thrust direction via a rod 12 to a slide valve 11 forming a part of the compressor, and a pressure difference is created between a chamber 14 and a chamber 15 before and after the piston 13 by hydraulic pressure. This is a system in which the displacement is controlled by moving the piston 13 to the left in the figure via a piston 13. Discharge pressure and suction pressure act before and after the slide valve 11 during operation.
An oil supply pipe 18 is connected to the cylinder chamber 14 through a solenoid valve 16.
When high-pressure oil 20 is introduced from the cylinder chamber 15 and connected to the suction side 1 via the solenoid valve 22 and the oil drain pipe 19, a pressure difference is generated before and after the piston 13, and a force acts in the left direction as shown in the figure. . If this force is larger than the rightward force due to the discharge pressure, the slide valve 11 moves to the left and the compression capacity decreases.
On the other hand, when increasing the capacity, high pressure oil 20 is introduced into the cylinder chamber 15 from the oil supply pipe via the solenoid valve 17.
Further, when the cylinder chamber 14 is connected to the suction side 1 via the electromagnetic valve 23 and the oil drain pipe 19, a pressure difference is generated before and after the piston 13, and a force acts in the right direction in the drawing. If this force is greater than the leftward force on the slide valve, the slide valve 11 moves to the right;
Compression capacity increases. Also, if you want to hold the piston 13 at an intermediate position, all solenoid valves 16, 1
If 7, 22, and 23 are closed, the oil in the cylinder chambers before and after the piston cannot escape, so the piston does not move and is held at an intermediate position. Solenoid valve 1
The relationship between 6, 17, 22, 23 and capacity is summarized in the following table.
上記構造によると運転中スライド弁１１には、
常時、吐出圧により右方向の力が、作用している
ので、左方向に動かす力と右方向に動かす力は、
右方向の方がはるか大きい。この力関係に応じて
ピストンの動く速さも、この力に比例するので、
中間で停止する制御がむずかしい事及び電磁弁を
含んだ配管が複雑になる問題点を有する。
また、本出願人は、特開昭54−162222号公報に
記載のように、ピストンの反スライド弁側区画室
にスプリング或いは空気圧によるばね手段を設け
て容量増大の駆動力として利用し、スライド弁側
区画室に高圧油を流通してスライド弁を調整する
装置を考案したが、スライド弁側区画室に高圧油
を常時流さなければならないため、消費油量が多
く、エネルギー効率に問題があつた。
本発明は上記問題点に鑑みなされたもので、ス
クリユー圧縮機の容量制御装置において、ピスト
ンの動く速さを安定させ、電磁弁を含んだ配管を
簡略にすると共に、消費油量を少なくしてエネル
ギー効率を向上させた容量制御装置を提供するこ
とを目的とする。
〔課題を解決するための手段〕
上記目的を達成するために本発明は、ケーシン
グ６内に配設された雌雄一対のスクリユーロータ
２の下部にスライド弁１１が配置され、該スライ
ド弁１１の吐出側端面にロツド１２を連接し、該
ロツドにスライドピストン１３が配設され、該ス
ライドピストンにより油圧シリンダ内にスライド
弁側シリンダ室１４と反スライド弁側シリンダ室
１５とを有するスクリユー圧縮機の容量制御装置
において、前記スライド弁側シリンダ室１４と反
スライド弁側シリンダ室１５とは液密に区分さ
れ、且つ該スライド弁側シリンダ室１４にのみ押
圧バネ２１が配設されているとともに、前記反ス
ライド弁側シリンダ室１５は配管２４を介して吸
入ガス側へのみ常時連通され、且つ前記スライド
弁側シリンダ室１４には給油及び排油を兼用する
配管のみが接続され、この配管を分岐して一方が
電磁弁１６を介在させて圧油源２０に接続すると
ともに他方が電磁弁２３を介在させて前記配管２
４を介して吸入ガス側に接続されていることを特
徴とするものである。
〔作用〕
上記の構成によれば、圧縮機の圧縮容量を多く
する場合の容量制御は、電磁弁１６を閉の状態で
電磁弁２３を開き、スライド弁側シリンダ室１４
にある油を吸入側に排圧すると、ピストン前後の
圧力はバランスし、シリンダ室１５はシリンダ室
１４と同様に低圧になる。スライド弁１１には運
転中の吐出圧力としてスライド弁１１が開く方向
の力が常時作用しており、この力によつてスライ
ド弁１１は反シリンダ側に動き、圧縮機の圧縮容
量は多くなる。逆に圧縮容量を少なくする場合の
容量制御は、電磁弁２３を閉の状態で電磁弁１６
を開いて給油管１８から高圧油２０をスライド弁
側シリンダ室１４に導き、ピストン１３の前後の
圧力差により、ピストン１３は反スライド弁側に
動き、圧縮容量は少なくなる。ピストン１３を中
間位置で保持したい場合は、二個の電磁弁１６，
２３を閉めることにより、スライド弁側シリンダ
室１４内の油量が固定され、ピストン１３は動か
なくなり、シリンダ室１４内の固定された油量に
応じた位置で保持される。また、圧縮機の運転停
止中はピストン１３は押圧バネ２１によつて反ス
ライド弁側に移動し、少ない圧縮容量から起動で
きるようにセツトされる。
したがつて、ピストンの動く距離は電磁弁前後
の圧力差と通電時間に限定される。ここで圧力差
は圧縮機の運転状態により刻々変化するが、制御
因子である電磁弁の通電時間が単純化されるの
で、圧縮機の運転状態に対する追従性が向上す
る。すなわち、吐出ガスの容量は、スライドピス
トンへの給油量だけ減少すると共に、排油量だけ
増大し、給油を停止すれば一定のなる。そのた
め、容量制御に用いる高圧油はスライドピストン
のシリンダ容積分だけで済み、圧縮機を含めたエ
ネルギー効率が向上する。また、電磁弁を含む油
圧配管が簡略化され、油圧ピストン自体も単純化
することができるので、制御の変動要因少なくす
ることができる。
通常、スライドピストンの大きさは、スライド
弁の断面図より約１〜３割大きく設計されてお
り、従つて、従来例におけるスライド弁の駆動力
は次のような関係にある。
容量を少なくする制御の場合の力の関係式：
駆動力＝［ピストン断面積−スライド弁断面積］
×［高圧油の圧力−低圧の圧力］
容量を多くする制御の場合の力の関係式：
駆動力＝［ピストン断面積＋スライド弁断面図］
×［高圧油の圧力−低圧の圧力］
これに対して、本発明の上記によれば、容量を
多くする場合の制御は、反スライド弁側へ高圧油
を供給するのをやめて低圧に連通させたので、駆
動力＝［スライド弁断面積］×［高圧油の圧力−低
圧の圧力］となり、容量を多くする場合と少なく
する場合との駆動力のバランスを維持することが
できる。
〔実施例〕
以下本発明の一実施例を第２図に基づき説明す
る。図は第１図と相異する部分のみを示し、その
他の第１図と同様な部分は省略してある。
ケーシング６内に配設された雌雄一対のスクリ
ユーロータ２の下部にはスライド弁１１が配置さ
れ、スライド弁１１の吐出側端面にはロツド１２
を連接しその先端にスライドピストン１３が配設
されている。該ピストン１３の反スライド弁側室
（左室）１５は配管２４を介し図示されていない
吸入ガス側へ常時接続連通されている。ピストン
１３の反対側のスライド弁側室（右室）１４には
押圧バネ２１が配設されていると共に、該室１４
は電磁弁１６を介在した配管にて圧油源２０に接
続され、また電磁弁２３を介して上記配管２４
（吸入ガス側）にも接続されている。
次に上記構造の装置の作用について説明する。
圧縮機の圧縮容量を少なくする場合の容量制御
は、電磁弁１６を開いて給油管１８から高圧油２
０をシリンダ右室１４に導き、シリンダ左室１５
は、常時低圧と連結されているので、ピストン１
３の前後の圧力差が生じ、ピストン１３は左方向
に力が作用する。この力はスライド弁１１の右方
向の力より大きいので、スライド弁は左方向に動
き、容量は少なくなる。逆に容量を多くする場合
の容量制御は、シリンダ右室１４にある油を、電
磁弁２３を開き、吸入側に排圧すると、ピストン
前後はバランスし、低圧になる。この時スライド
弁１１前後には高圧と低圧の圧力差により、スラ
イド弁１１は図示の右方向に力が作用するので、
スライド弁は右方向に動き、圧縮容量は多くな
る。ピストン１３を中間位置で保持したい場合
は、二個の電磁弁１６，２３を閉めれば、シリン
ダ室１４を油はにげることができないため、ピス
トンは動かなく、中間位置で保持される。電磁弁
１６，２３と容量の関係を次の表に示す。
According to the above structure, during operation, the slide valve 11 has:
Since a rightward force is always acting due to the discharge pressure, the force to move it to the left and the force to move it to the right are:
The one on the right is much larger. Depending on this force relationship, the speed at which the piston moves is also proportional to this force, so
There are problems in that it is difficult to control the stop in the middle and that the piping including the solenoid valve is complicated. Furthermore, as described in Japanese Patent Application Laid-Open No. 162222/1982, the present applicant provided a spring or pneumatic spring means in the compartment chamber on the opposite side of the slide valve of the piston and used it as a driving force to increase the capacity of the slide valve. We devised a device to adjust the slide valve by flowing high-pressure oil into the side compartment, but since high-pressure oil had to be constantly flowing into the slide valve side compartment, the amount of oil consumed was large and there were problems with energy efficiency. . The present invention was made in view of the above problems, and is used in a capacity control device for a screw compressor by stabilizing the moving speed of the piston, simplifying the piping including the solenoid valve, and reducing the amount of oil consumed. The purpose of the present invention is to provide a capacity control device with improved energy efficiency. [Means for Solving the Problems] In order to achieve the above object, the present invention includes a slide valve 11 disposed at the lower part of a pair of male and female screw rotors 2 disposed in a casing 6. A screw compressor having a rod 12 connected to the discharge side end face, a slide piston 13 disposed on the rod, and a slide valve side cylinder chamber 14 and a non-slide valve side cylinder chamber 15 in the hydraulic cylinder by the slide piston. In the capacity control device, the slide valve side cylinder chamber 14 and the non-slide valve side cylinder chamber 15 are liquid-tightly divided, and a pressing spring 21 is disposed only in the slide valve side cylinder chamber 14, and the pressure spring 21 is disposed only in the slide valve side cylinder chamber 14. The anti-slide valve side cylinder chamber 15 is always in communication only with the suction gas side via piping 24, and only a piping for both oil supply and oil drainage is connected to the slide valve side cylinder chamber 14, and this piping is branched. One side is connected to the pressure oil source 20 through a solenoid valve 16, and the other side is connected to the piping 2 through a solenoid valve 23.
It is characterized in that it is connected to the intake gas side via 4. [Operation] According to the above configuration, capacity control when increasing the compression capacity of the compressor is performed by opening the solenoid valve 23 with the solenoid valve 16 closed, and opening the solenoid valve 23 in the slide valve side cylinder chamber 14.
When the oil in the piston is discharged to the suction side, the pressures before and after the piston are balanced, and the pressure in the cylinder chamber 15 becomes low as in the cylinder chamber 14. A force in the direction of opening the slide valve 11 is constantly acting on the slide valve 11 as discharge pressure during operation, and this force moves the slide valve 11 toward the side opposite to the cylinder, increasing the compression capacity of the compressor. Conversely, when reducing the compression capacity, the capacity control is performed by closing the solenoid valve 23 and turning on the solenoid valve 16.
When opened, high pressure oil 20 is introduced from the oil supply pipe 18 into the slide valve side cylinder chamber 14, and due to the pressure difference between the front and rear sides of the piston 13, the piston 13 moves toward the side opposite to the slide valve, and the compression capacity decreases. If you want to hold the piston 13 in an intermediate position, use two solenoid valves 16,
By closing 23, the amount of oil in the cylinder chamber 14 on the slide valve side is fixed, the piston 13 does not move, and is held at a position corresponding to the fixed amount of oil in the cylinder chamber 14. Further, while the compressor is stopped, the piston 13 is moved by the pressure spring 21 toward the side opposite to the slide valve, and is set so that the compressor can be started from a small compression capacity. Therefore, the distance the piston moves is limited to the pressure difference before and after the solenoid valve and the energization time. Here, the pressure difference changes moment by moment depending on the operating state of the compressor, but since the energization time of the solenoid valve, which is a control factor, is simplified, the ability to follow the operating state of the compressor is improved. That is, the volume of discharged gas decreases by the amount of oil supplied to the slide piston, increases by the amount of oil discharged, and remains constant when the oil supply is stopped. Therefore, the amount of high-pressure oil used for capacity control is only the cylinder volume of the slide piston, improving energy efficiency including the compressor. Further, the hydraulic piping including the electromagnetic valve is simplified, and the hydraulic piston itself can be simplified, so that control fluctuation factors can be reduced. Usually, the size of the slide piston is designed to be about 10 to 30% larger than the cross-sectional view of the slide valve, and therefore, the driving force of the slide valve in the conventional example has the following relationship. Force relational expression for control to reduce capacity: Driving force = [piston cross-sectional area - slide valve cross-sectional area] × [high pressure oil pressure - low pressure pressure] Force relational expression for control to increase capacity: Driving force = [piston cross-sectional area + slide valve cross-sectional view] × [pressure of high pressure oil - pressure of low pressure] On the other hand, according to the above aspect of the present invention, control when increasing the capacity is performed on the opposite side of the slide valve. Since we stopped supplying high pressure oil to low pressure and connected it to low pressure, driving force = [slide valve cross-sectional area] x [pressure of high pressure oil - pressure of low pressure], and the drive when increasing the capacity and when decreasing it. Able to maintain power balance. [Example] An example of the present invention will be described below based on FIG. 2. The figure shows only parts that are different from FIG. 1, and other parts that are similar to FIG. 1 are omitted. A slide valve 11 is disposed at the bottom of a pair of male and female screw rotors 2 disposed inside the casing 6, and a rod 12 is disposed at the discharge side end surface of the slide valve 11.
A slide piston 13 is disposed at the tip of the piston. The anti-slide valve side chamber (left chamber) 15 of the piston 13 is constantly connected to the suction gas side (not shown) via a pipe 24. A pressure spring 21 is disposed in the slide valve side chamber (right chamber) 14 on the opposite side of the piston 13, and
is connected to the pressure oil source 20 through a piping with a solenoid valve 16 interposed therebetween, and is connected to the piping 24 through a solenoid valve 23.
(Suction gas side) is also connected. Next, the operation of the device having the above structure will be explained.
Capacity control when reducing the compression capacity of the compressor is performed by opening the solenoid valve 16 and supplying high pressure oil 2 from the oil supply pipe 18.
0 into the cylinder right ventricle 14 and into the cylinder left ventricle 15.
is always connected to low pressure, so piston 1
A pressure difference occurs between the front and rear sides of piston 13, and a force acts on the piston 13 in the left direction. Since this force is greater than the rightward force on the slide valve 11, the slide valve moves to the left and its capacity decreases. On the other hand, to control the capacity when increasing the capacity, open the electromagnetic valve 23 to discharge the oil in the cylinder right chamber 14 to the suction side, and the front and rear of the piston are balanced and the pressure becomes low. At this time, a force acts on the slide valve 11 in the right direction as shown in the figure due to the pressure difference between the high pressure and the low pressure before and after the slide valve 11.
The slide valve moves to the right and the compression capacity increases. If it is desired to hold the piston 13 at an intermediate position, the two electromagnetic valves 16 and 23 are closed. Since oil cannot escape from the cylinder chamber 14, the piston does not move and is held at the intermediate position. The relationship between the solenoid valves 16 and 23 and their capacity is shown in the following table.
以上説明したように本発明によれば、容量制御
の変動要因を減少することができたので、スライ
ドピストンの動く速さは従来技術に比べてはるか
に安定し、中間位置による容量制御も簡単にな
り、同時に電磁弁の個数が半減されるので配管を
簡単にすることができるばかりか、容量制御に用
いる消費油量が減少するので、圧縮機を含めた機
械のエネルギー効率が向上する。
As explained above, according to the present invention, the fluctuation factors in displacement control can be reduced, so the moving speed of the slide piston is much more stable than in the conventional technology, and displacement control at intermediate positions can be easily performed. At the same time, the number of solenoid valves is halved, which not only simplifies piping, but also reduces the amount of oil consumed for capacity control, improving the energy efficiency of the machine including the compressor.
第１図は従来のスクリユー圧縮機の縦断面図
で、第２図は本発明の一実施例を示す容量制御機
構の部分断面図である。
２……ロータ、６……ケーシング、１１……ス
ライド弁、１２……ロツド、１３……ピストン、
１４……右室、１５……左室、１６……電磁弁、
１８……給油管、２０……高圧油、２１……バ
ネ、２３……電磁弁、２４……配管。
FIG. 1 is a longitudinal sectional view of a conventional screw compressor, and FIG. 2 is a partial sectional view of a capacity control mechanism showing an embodiment of the present invention. 2... Rotor, 6... Casing, 11... Slide valve, 12... Rod, 13... Piston,
14... Right ventricle, 15... Left ventricle, 16... Solenoid valve,
18... Oil supply pipe, 20... High pressure oil, 21... Spring, 23... Solenoid valve, 24... Piping.
Claims (1)
リユーロータ２の下部にスライド弁１１が配置さ
れ、該スライド弁１１の吐出側端面にロツド１２
を連接し、該ロツドにスライドピストン１３が配
設され、該スライドピストンにより油圧シリンダ
内にスライド弁側シリンダ室１４と反スライド弁
側シリンダ室１５とを有するスクリユー圧縮機の
容量制御装置において、 前記スライド弁側シリンダ室１４と反スライド
弁側シリンダ室１５とは液密に区分され、且つ該
スライド弁側シリンダ室１４にのみ押圧バネ２１
が配設されているとともに、前記反スライド弁側
シリンダ室１５は配管２４を介して吸入ガス側へ
のみ常時連通され、且つ前記スライド弁側シリン
ダ室１４には給油及び排油を兼用する配管のみが
接続され、この配管を分岐して一方が電磁弁１６
を介在させて圧油源２０に接続するとともに他方
が電磁弁２３を介在させて前記配管２４を介して
吸入ガス側に接続されていることを特徴とするス
クリユー圧縮機の容量制御装置。[Claims] 1. A slide valve 11 is disposed at the bottom of a pair of male and female screw rotors 2 disposed in a casing 6, and a rod 12 is disposed on the discharge side end surface of the slide valve 11.
A displacement control device for a screw compressor, in which a slide piston 13 is arranged on the rod, and a slide valve side cylinder chamber 14 and a non-slide valve side cylinder chamber 15 are formed in a hydraulic cylinder by the slide piston, The slide valve side cylinder chamber 14 and the anti-slide valve side cylinder chamber 15 are separated in a liquid-tight manner, and the pressing spring 21 is installed only in the slide valve side cylinder chamber 14.
The cylinder chamber 15 on the non-slide valve side is always in communication only with the intake gas side via the piping 24, and the cylinder chamber 14 on the slide valve side is provided with only piping for both oil supply and oil drainage. is connected, and this piping is branched and one end is connected to the solenoid valve 16.
A capacity control device for a screw compressor, characterized in that one end is connected to a pressure oil source 20 through an intervening solenoid valve 23, and the other is connected to the suction gas side through the piping 24 through an electromagnetic valve 23.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP15811082A JPS5949391A (en) | 1982-09-13 | 1982-09-13 | Volume control device of screw compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP15811082A JPS5949391A (en) | 1982-09-13 | 1982-09-13 | Volume control device of screw compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5949391A JPS5949391A (en) | 1984-03-21 |
| JPH0552439B2 true JPH0552439B2 (en) | 1993-08-05 |
Family
ID=15664516
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP15811082A Granted JPS5949391A (en) | 1982-09-13 | 1982-09-13 | Volume control device of screw compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5949391A (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH068312Y2 (en) * | 1988-10-29 | 1994-03-02 | 北越工業株式会社 | Screw compressor |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS54162222A (en) * | 1978-06-14 | 1979-12-22 | Hitachi Ltd | Device for controlling capacity of screw compressor |
-
1982
- 1982-09-13 JP JP15811082A patent/JPS5949391A/en active Granted
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS54162222A (en) * | 1978-06-14 | 1979-12-22 | Hitachi Ltd | Device for controlling capacity of screw compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5949391A (en) | 1984-03-21 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| EXPY | Cancellation because of completion of term |