JPH0745878B2 - Vane back pressure application device for sliding vane compressor - Google Patents

Vane back pressure application device for sliding vane compressor

Info

Publication number
JPH0745878B2
JPH0745878B2 JP61287930A JP28793086A JPH0745878B2 JP H0745878 B2 JPH0745878 B2 JP H0745878B2 JP 61287930 A JP61287930 A JP 61287930A JP 28793086 A JP28793086 A JP 28793086A JP H0745878 B2 JPH0745878 B2 JP H0745878B2
Authority
JP
Japan
Prior art keywords
vane
pressure
back pressure
chamber
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 - Lifetime
Application number
JP61287930A
Other languages
Japanese (ja)
Other versions
JPS63140877A (en
Inventor
敏雄 松田
隆博 葉瀬垣
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Panasonic Holdings Corp
Original Assignee
Matsushita Electric Industrial Co Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Matsushita Electric Industrial Co Ltd filed Critical Matsushita Electric Industrial Co Ltd
Priority to JP61287930A priority Critical patent/JPH0745878B2/en
Priority to US07/127,468 priority patent/US4936761A/en
Priority to CA000553351A priority patent/CA1318896C/en
Priority to KR1019870013765A priority patent/KR930002464B1/en
Publication of JPS63140877A publication Critical patent/JPS63140877A/en
Publication of JPH0745878B2 publication Critical patent/JPH0745878B2/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • F04C28/06—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids specially adapted for stopping, starting, idling or no-load operation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0818—Vane tracking; control therefor
    • F01C21/0854—Vane tracking; control therefor by fluid means
    • F01C21/0872—Vane tracking; control therefor by fluid means the fluid being other than the working fluid

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Description

【発明の詳細な説明】 産業上の利用分野 本発明は自動車用空調装置等に供されるスライディング
ベーン式圧縮機に使用するベーン背圧付与装置に関する
ものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vane back pressure applying device used in a sliding vane compressor used for an air conditioner for automobiles and the like.

従来の技術 周知のようにスライディングベーン式圧縮機においては
ロータの回転に伴なってベーンがその先端をシリンダ内
壁に接して回転摺動運動をするようベーン後端に高圧の
潤滑油を圧力差により供給する構造が広く用いられてい
る。As is well known in the art, in a sliding vane compressor, high pressure lubricating oil is applied to the rear end of the vane by a pressure difference so that the vane makes a rotary sliding motion by contacting the tip of the vane with the inner wall of the cylinder as the rotor rotates. Supplying structures are widely used.

以下図面を参照しながら、上述した従来のスライディン
グベーン式圧縮機のベーン背圧付与装置の一例について
説明する。An example of the above-mentioned conventional vane back pressure applying device for a sliding vane compressor will be described below with reference to the drawings.

第４図乃至第６図は従来の差圧給油式のベーン背圧付与
装置を有するスライディングベーン式圧縮機の具体構成
を示すものである。同図において、１は円筒内壁を有す
るシリンダ、２はその外周の一部がシリンダ１内壁と微
少隙間を形成するロータ、３はロータ２に設けられた複
数のベーンスロット、４はベーンスロット４内に摺動自
在に挿入された複数のベーン、５はロータ２と一体的に
形成され回転自在に軸支される駆動軸、６および７はそ
れぞれシリンダ１の両端を閉塞して内部に作動室８を形
成する前部側板および後部側板である。９は低圧側の作
動室８に連通する吸入口、10は高圧側の作動室８に連通
する吐出口、11は吐出口に配設された吐出弁、12は高圧
通路13に連通する高圧室14を形成して圧縮された高圧流
体中の潤滑油を分離捕捉するスクリーン15を配設した高
圧ケースである。16は後部側板７に配設されたベーン背
圧付与装置本体で、高圧室14下方の油溜り部の潤滑油を
ベーン背圧室17に供給している。18は高圧室14下方の油
溜り部とベーン背圧室17とを連通する給油通路、19は差
圧による給油量を制限する通路、20は給油通路18途中に
設けられた球座、21は球座20と当接あるいは遊離して給
油通路18を連通遮断する球体、22は球座20に開口するプ
ランジャ室、23はプランジャ室22内部に摺動自在に配設
され球座20側へ移動した時球体21を球座20から遊離させ
るプランジャ、24はプランジャの下端の下部プランジャ
室25と吐出弁11直前の作動室８とを連通する圧力導入路
である。4 to 6 show a specific configuration of a sliding vane type compressor having a conventional differential pressure oil supply type vane back pressure applying device. In FIG. 1, 1 is a cylinder having a cylindrical inner wall, 2 is a rotor whose outer periphery forms a small gap with the inner wall of the cylinder 1, 3 is a plurality of vane slots provided in the rotor 2, and 4 is a vane slot 4. A plurality of vanes 5 slidably inserted into the rotor 5 are drive shafts formed integrally with the rotor 2 and rotatably supported therein. Reference numerals 6 and 7 respectively close both ends of the cylinder 1 to provide a working chamber 8 inside. Are a front side plate and a rear side plate that form a. Reference numeral 9 is an intake port communicating with the low pressure side working chamber 8, 10 is a discharge port communicating with the high pressure side working chamber 8, 11 is a discharge valve arranged at the discharge port, 12 is a high pressure chamber communicating with the high pressure passage 13. This is a high-pressure case in which a screen 15 for forming and forming a screen 14 for separating and capturing the lubricating oil in the compressed high-pressure fluid is arranged. Reference numeral 16 is a main body of the vane back pressure applying device disposed on the rear side plate 7, and supplies the lubricating oil in the oil reservoir below the high pressure chamber 14 to the vane back pressure chamber 17. 18 is an oil supply passage that connects the oil reservoir below the high pressure chamber 14 and the vane back pressure chamber 17, 19 is a passage that limits the amount of oil supplied by the differential pressure, 20 is a ball seat provided in the middle of the oil supply passage 18, and 21 is A sphere that abuts on or separates from the ball seat 20 to cut off the communication of the oil supply passage 18, 22 is a plunger chamber that opens to the ball seat 20, and 23 is slidably arranged inside the plunger chamber 22 and moves to the ball seat 20 side. At this time, the plunger 21 disengages the spherical body 21 from the ball seat 20, and 24 is a pressure introducing passage that connects the lower plunger chamber 25 at the lower end of the plunger and the working chamber 8 immediately before the discharge valve 11.

以上のように構成されたスライディングベーン式圧縮機
のベーン背圧付与装置について、以下その動作について
説明する。The operation of the vane back pressure applying device of the sliding vane type compressor configured as described above will be described below.

エンジンなどの駆動源より動力伝達を受けて駆動軸５お
よびロータ２が第５図において時計方向に回転すると、
これに伴ない低圧流体が吸入口９より作動室８内に流入
する。ロータ２の回転に伴ない圧縮された高圧流体は吐
出口10より吐出弁11を押し上げて高圧通路13より高圧室
14に流入し、スクリーン15によって潤滑油が分離捕捉さ
れる。一方圧力導入路24からは高圧流体の圧力に打ち勝
って吐出弁11を押し上げるだけの圧力を有する作動室８
内の過圧縮ガスが下部プランジャ室25へ供給されるの
で、プランジャ23は球座20側へ移動して球体21を球座20
から遊離させる。したがって給油通路18は連通されるの
で、高圧流体中より分離されて高圧室14下方に貯えられ
た潤滑油は差圧によって通路19、給油通路18からベーン
背圧室17へ供給されてベーン４の押圧に伴されロータ２
と前部側板６および後部側板７との隙間を通り作動室８
内へ流入するのである。また圧縮機が停止した場合には
作動室８内の圧力は急激に低圧側流体の圧力まで降下す
るため、下部プランジャ室25内の圧力も低圧側流体の圧
力まで降下しプランジャ23下端の圧力はプランジャ23上
端の圧力より小さくなるのでプランジャ23は下部プラン
ジャ室25側へ移動する。このため球体21は球座20に当接
し給油通路18は遮断される。したがって潤滑油はそれ以
上供給されないから、作動室８内に潤滑油が滞留するこ
とによって生ずる圧縮機始動時の液圧縮を防止すること
ができる。When power is transmitted from a drive source such as an engine and the drive shaft 5 and the rotor 2 rotate clockwise in FIG. 5,
Along with this, the low-pressure fluid flows into the working chamber 8 through the suction port 9. The high-pressure fluid compressed by the rotation of the rotor 2 pushes up the discharge valve 11 from the discharge port 10 and pushes the discharge valve 11 from the high-pressure passage 13 into the high-pressure chamber.
It flows into 14, and the lubricating oil is separated and captured by the screen 15. On the other hand, from the pressure introducing passage 24, the working chamber 8 having a pressure sufficient to overcome the pressure of the high-pressure fluid and push up the discharge valve 11.
Since the over-compressed gas inside is supplied to the lower plunger chamber 25, the plunger 23 moves to the side of the ball seat 20 and moves the ball 21 into the ball seat 20.
Free from. Therefore, since the oil supply passage 18 is communicated, the lubricating oil separated from the high pressure fluid and stored in the lower portion of the high pressure chamber 14 is supplied to the vane back pressure chamber 17 from the passage 19 and the oil supply passage 18 due to the differential pressure. Rotor 2 accompanied by pressing
Through the gap between the front side plate 6 and the rear side plate 7 and the working chamber 8
It flows in. Further, when the compressor stops, the pressure in the working chamber 8 drops rapidly to the pressure of the low pressure side fluid, so the pressure in the lower plunger chamber 25 also drops to the pressure of the low pressure side fluid, and the pressure at the lower end of the plunger 23 becomes Since the pressure becomes lower than the pressure at the upper end of the plunger 23, the plunger 23 moves to the lower plunger chamber 25 side. Therefore, the spherical body 21 abuts on the spherical seat 20 and the oil supply passage 18 is blocked. Therefore, since the lubricating oil is not supplied any more, it is possible to prevent the liquid compression at the time of starting the compressor, which is caused by the accumulation of the lubricating oil in the working chamber 8.

発明が解決しようとする問題点 しかしながら上記従来のベーン背圧付与装置では、圧縮
機の停止後ある時間が経過した場合のように低圧側の流
体の圧力と高圧側の流体の圧力とが等しくなった状態で
圧縮機を始動すると、ロータ２の回転に伴なってベーン
４が回転しベーンスロット３内を伸張没入しようとして
も潤滑油を供給するための差圧が無いことや潤滑油の水
頭、粘性および慣性による流れ始めの抵抗が大きいこと
などのため、結果としてベーン４の伸張没入の際生ずる
ベーン背圧室17の容積変動に対し十分な潤滑油量が供給
できない。このため特に圧縮機始動時の回転数が低い場
合にベーン背圧室17の圧力低下を生じベーン４がシリン
ダ１内壁から遊離し再び衝突する周知の不調現象や流体
を圧縮しない圧縮不良現象が生ずるという問題点を有し
ていた。DISCLOSURE OF THE INVENTION Problems to be Solved by the Invention However, in the above-mentioned conventional vane back pressure imparting device, the pressure of the fluid on the low pressure side becomes equal to the pressure of the fluid on the high pressure side as in the case where a certain time has elapsed after the compressor is stopped. When the compressor is started in this state, the vane 4 rotates with the rotation of the rotor 2 and there is no differential pressure for supplying the lubricating oil even if the vane slot 3 tries to extend and retract. Due to the large resistance to the beginning of flow due to viscosity and inertia, as a result, a sufficient amount of lubricating oil cannot be supplied with respect to the volume fluctuation of the vane back pressure chamber 17 that occurs when the vane 4 is extended and retracted. For this reason, particularly when the rotational speed at the time of starting the compressor is low, a pressure drop in the vane back pressure chamber 17 occurs, and the well-known malfunction phenomenon in which the vane 4 separates from the inner wall of the cylinder 1 and collides again, or the poor compression phenomenon in which the fluid is not compressed occurs. Had the problem.

また潤滑油量を確保するため通路19の通路面積を拡大す
ることは、定常運転時にベーン４を過度にシリンダ１内
壁に押接せしめベーン４先端部およびシリンダ１内壁の
摩耗増と圧縮機の入力増をひき起こす結果となり圧縮機
の耐久性や効率を悪くするという問題があり、高回転時
には増大するベーン４の遠心力がこの傾向をさらに助長
するという問題点を有していた。Further, increasing the passage area of the passage 19 in order to secure the amount of lubricating oil causes the vane 4 to be excessively pressed against the inner wall of the cylinder 1 during steady operation, resulting in increased wear of the tip of the vane 4 and the inner wall of the cylinder 1 and input of the compressor. As a result, there is a problem that the durability and efficiency of the compressor are deteriorated as a result of the increase, and there is a problem that the centrifugal force of the vane 4 which increases at a high rotation speed further promotes this tendency.

本発明は上記問題点に鑑み、圧縮機の高低圧力差が無い
か小さい場合に低速回転で圧縮機を始動した場合でもベ
ーンの不調現象や圧縮不良現象が防止できかつ耐久性や
効率を損なわないスライディングベーン式圧縮機のベー
ン背圧付与装置を提供するものである。In view of the above problems, the present invention can prevent vane malfunction phenomenon and compression failure phenomenon even when the compressor is started at low speed when there is no or small pressure difference of the compressor and does not impair durability and efficiency. Provided is a vane back pressure applying device for a sliding vane compressor.

問題点を解決するための手段 上記問題点を解決するために本発明のスライディングベ
ーン式圧縮機のベーン背圧付与装置は、ベーン背圧室と
高圧ケースとを連通するガス通路と、一端に高圧ケース
内の圧力を受け他端に定常運転中は高圧ケース内圧力よ
り低い圧力およびばねの付勢力とを受けて移動し、前記
ガス通路を連通、遮断する摺動体とを備えたものであ
る。Means for Solving the Problems In order to solve the above problems, the vane back pressure imparting device of the sliding vane compressor of the present invention has a gas passage communicating between the vane back pressure chamber and the high pressure case, and a high pressure at one end. It is provided with a sliding body which receives the pressure in the case and moves at the other end under the pressure lower than the pressure in the high-pressure case and the urging force of the spring during normal operation to communicate and cut off the gas passage.

作用 本発明は上記構成により、高低圧力差が無いかまたは小
さい状態で圧縮機を始動させた場合でも、摺動体はばね
の付勢力によって移動してガス通路を連通しているので
ロータの回転に伴なってベーンが回転しベーンスロット
内を伸張没入しようとする際生ずるベーン背圧室の容積
変動に対して瞬時にガス通路からガス状流体を供給でき
る。このためベーン背圧室の圧力低下を生じないためベ
ーンの不調現象や圧縮不良現象を防止できる。また始動
後に高圧室内の圧力が上昇すると摺動体は移動してガス
通路を遮断するから、ベーン背圧室へは給油通路から適
正量の潤滑油が供給され、耐久性や効率を損なうことが
ない。Action The present invention has the above-described configuration, and even when the compressor is started in a state where there is no or a small pressure difference, the sliding body moves by the urging force of the spring and communicates with the gas passage. Accordingly, the gaseous fluid can be instantaneously supplied from the gas passage with respect to the volume fluctuation of the vane back pressure chamber which occurs when the vane rotates and tries to extend and retract in the vane slot. Therefore, since the pressure in the back pressure chamber of the vane does not decrease, the phenomenon of malfunction of the vane and the phenomenon of defective compression can be prevented. Also, when the pressure in the high pressure chamber rises after starting, the sliding body moves to block the gas passage, so an appropriate amount of lubricating oil is supplied from the oil supply passage to the vane back pressure chamber, and durability and efficiency are not impaired. .

実施例 以下、本発明の一実施例について添付図面の第１図乃至
第３図を参照しながら説明する。Embodiment An embodiment of the present invention will be described below with reference to FIGS. 1 to 3 of the accompanying drawings.

第１図および第２図は本発明の第１の実施例を示すもの
であるが、同図において前記従来のスライディングベー
ン式圧縮機のベーン背圧付与装置と同一の作用効果を有
するものは同一の符号を記して説明を省略する。FIG. 1 and FIG. 2 show a first embodiment of the present invention. In FIG. 1, those having the same effect as the vane back pressure applying device of the conventional sliding vane type compressor are the same. Is described and the description is omitted.

同図において、26は給油通路18に連通する第１ガス通
路、27は高圧室14に連通する第２ガス通路、33は一端を
高圧室14に開口し他端を通路34により作動室８の吸入側
部分に連通している摺動室、35は摺動室33内に摺動自在
に配設された摺動体、36は摺動体35が当接している時の
み第１ガス通路26と第２ガス通路27とを遮断する弁座、
37は弁座36から遊離する向きに摺動体35を付勢するばね
である。In the figure, 26 is a first gas passage communicating with the oil supply passage 18, 27 is a second gas passage communicating with the high pressure chamber 14, 33 is one end open to the high pressure chamber 14 and the other end is the passage 34 of the working chamber 8. A sliding chamber communicating with the suction side portion, 35 is a sliding body slidably arranged in the sliding chamber 33, and 36 is the first gas passage 26 and the first gas passage 26 only when the sliding body 35 is in contact. 2 A valve seat that shuts off the gas passage 27,
Reference numeral 37 is a spring that biases the sliding body 35 in a direction away from the valve seat 36.

以上のように構成されたスライディングベーン式圧縮機
のベーン背圧付与装置について、以下その動作を説明す
る。The operation of the vane back pressure applying device of the sliding vane type compressor configured as described above will be described below.

圧縮機が停止すると、作動室８内の圧力は急激に低下し
プランジャ23下端の圧力も低下する。このためプランジ
ャ23は下部プランジャ室25側へ移動し球体20に当接する
ので給油通路18が遮断されるのは前記従来のベーン背圧
付与装置と同様である。When the compressor is stopped, the pressure in the working chamber 8 drops sharply and the pressure at the lower end of the plunger 23 also drops. Therefore, the plunger 23 moves to the lower plunger chamber 25 side and contacts the sphere 20, so that the oil supply passage 18 is blocked as in the conventional vane back pressure applying device.

一方、高圧室14内の圧力が高い間は摺動体35は弁座36に
当接したままであるが、圧縮機停止後ある時間が経過し
て高圧側と低圧側との圧力差が小さくなると摺動体35は
ばね37の付勢力によって弁座36から遊離する。その結果
第１ガス通路26と第２ガス通路27とが連通した状態とな
る。On the other hand, while the pressure in the high pressure chamber 14 is high, the sliding body 35 remains in contact with the valve seat 36, but when a certain time elapses after the compressor is stopped and the pressure difference between the high pressure side and the low pressure side becomes small. The sliding body 35 is released from the valve seat 36 by the urging force of the spring 37. As a result, the first gas passage 26 and the second gas passage 27 are in communication with each other.

次に、高圧側と低圧側との圧力差が無いときに圧縮機を
始動した場合について説明する。ロータ２の回転に伴な
ってベーン４が回転しベーンスロット３内を伸張没入す
る際生ずるベーン背圧室17の容積変動によって、ベーン
背圧室17内の圧力が低下しようとする高圧室14から第２
ガス通路27、第１ガス通路26を経てベーン背圧室17にガ
ス状流体が瞬時に供給されるためベーン背圧室17の圧力
低下を防止できる。Next, a case where the compressor is started when there is no pressure difference between the high pressure side and the low pressure side will be described. From the high pressure chamber 14 in which the pressure in the vane back pressure chamber 17 tends to decrease due to the volume fluctuation of the vane back pressure chamber 17 which occurs when the vane 4 rotates as the rotor 2 rotates and expands and retracts in the vane slot 3. Second
Since the gaseous fluid is instantaneously supplied to the vane back pressure chamber 17 through the gas passage 27 and the first gas passage 26, it is possible to prevent the pressure drop in the vane back pressure chamber 17.

また、始動後摺動体35が受ける高圧室14内の圧力が増大
していって作動室８の吸入側部分の圧力とばね37の付勢
力に打ち勝つと、摺動体35が弁座36に当接するため、ベ
ーン背圧室17へは給油通路18から適正量の潤滑油を前記
従来のベーン背圧付与装置と同様に供給できる。Further, when the pressure in the high pressure chamber 14 received by the sliding body 35 after the start-up is increased to overcome the pressure of the suction side portion of the working chamber 8 and the biasing force of the spring 37, the sliding body 35 contacts the valve seat 36. Therefore, an appropriate amount of lubricating oil can be supplied to the vane back pressure chamber 17 from the oil supply passage 18 similarly to the conventional vane back pressure applying device.

以上のように本実施例によれば、ベーン背圧室に連通す
る給油通路と高圧室とを連通する第１および第２ガス通
路と、一端に高圧室の圧力を他端に作動室の吸入側部分
の圧力を受ける摺動体と、第１および第２ガス通路を連
通する方向に摺動体を付勢するばねとを設けることによ
り、高低圧均圧状態から圧縮機を始動した場合でも始動
直後に生ずるベーン背圧室内の圧力低下を第１および第
２ガス供給通路からのガス状流体の供給によって妨げて
ベーンの伸張に必要な押圧を及ぼすことができるので、
ベーンの不調現象や圧縮不良現象を防止できる。また通
常の運転時においても適正量の潤滑油をベーン背圧室へ
供給できるので耐久性や効率を損なうことがない。As described above, according to the present embodiment, the first and second gas passages that connect the oil supply passage communicating with the vane back pressure chamber and the high pressure chamber, and the pressure of the high pressure chamber at one end and the suction of the working chamber at the other end. By providing the sliding body that receives the pressure of the side portion and the spring that biases the sliding body in the direction in which the first and second gas passages communicate with each other, even when the compressor is started from the high-low pressure equalization state, immediately after the starting Since it is possible to prevent the pressure drop in the vane back pressure chamber caused by the supply of the gaseous fluid from the first and second gas supply passages, and to exert the pressure necessary for the expansion of the vane,
It is possible to prevent a vane malfunction phenomenon and a compression failure phenomenon. In addition, since the proper amount of lubricating oil can be supplied to the vane back pressure chamber even during normal operation, durability and efficiency are not impaired.

第３図は本発明の第２の実施例を示すもので、同図にお
いて前記第１の実施例を示す第１図および第２図と同一
の符号を付したものは同一の作用効果を有するものであ
る。FIG. 3 shows a second embodiment of the present invention, in which the same reference numerals as those in FIGS. 1 and 2 showing the first embodiment have the same operational effect. It is a thing.

第１の実施例と異なるのは弁座36を摺動室33の高圧室14
連通側に配設しかつ摺動室33の高圧室14との連通を第２
ガス通路27を経由して行なうようにした点であり、摺動
体35が弁座36に当接している場合高圧室14連通側の摺動
室33には第１ガス通路26を経由して給油通路18内の圧力
が導入されるが、圧縮機停止後高低圧力差が小さくなる
とばね37の付勢力によって第１ガス通路26と第２ガス通
路27とが連通し、圧縮機始動時には第２ガス通路27から
ベーン背圧室に高圧室14内のガス状流体が供給でき、ま
た始動後は高圧室14内の圧力が増大して摺動体35が弁座
36に当接してベーン背圧室へは適正量の潤滑油が供給で
きるので、前記第１の実施例と同様の作用効果を有する
ことは明らかである。The difference from the first embodiment is that the valve seat 36 is mounted in the high pressure chamber 14 of the sliding chamber 33.
It is arranged on the communication side and the communication between the sliding chamber 33 and the high-pressure chamber 14 is the second.
This is done through the gas passage 27. When the sliding body 35 is in contact with the valve seat 36, the sliding chamber 33 on the communication side of the high pressure chamber 14 is refueled via the first gas passage 26. Although the pressure in the passage 18 is introduced, the first gas passage 26 and the second gas passage 27 communicate with each other by the urging force of the spring 37 when the pressure difference between the high and low pressures after the compressor is stopped becomes small, and the second gas is started at the time of starting the compressor. The gaseous fluid in the high pressure chamber 14 can be supplied from the passage 27 to the vane back pressure chamber, and after the start, the pressure in the high pressure chamber 14 increases and the sliding body 35 makes the valve seat.
Since it is possible to supply a proper amount of lubricating oil to the vane back pressure chamber by contacting the 36, it is clear that the vane back pressure chamber has the same operational effect as that of the first embodiment.

なお第１および第２の実施例において第１ガス供給通路
26は給油通路18に連通させたが、第１ガス供給通路26は
給油通路18とは独立にベーン背圧室17に連通させてもよ
い。またこれら二つの実施例においてスライディングベ
ーン式圧縮機は吸入口９、吐出口10が各々一つしかない
真円式を示したが吸入口９、吐出口10が各々複数ある形
式のものでもよいし、ベーン枚数も４枚のものを示した
が何枚あってもよい。The first gas supply passage in the first and second embodiments
Although 26 is communicated with the oil supply passage 18, the first gas supply passage 26 may be communicated with the vane back pressure chamber 17 independently of the oil supply passage 18. Further, in these two embodiments, the sliding vane type compressor has a perfect circular type having only one suction port 9 and one discharge port 10, but may have a plurality of suction ports 9 and discharge ports 10. The number of vanes shown is four, but any number may be used.

さらに第１および第２の実施例において通路34は作動室
８の吸入側部分に開口するようにしたが、圧縮機の定常
運転状態において摺動体35が一端に高圧室14内の圧力を
受けてばね37の付勢力と通路34によって導入される圧力
とに打ち勝って弁座36に当接できるだけの圧力差のある
組合せであれば圧縮機内はもとより冷凍サイクル内のど
の部分の圧力を受けるように構成してもかまわない。Further, in the first and second embodiments, the passage 34 is opened to the suction side portion of the working chamber 8. However, when the sliding body 35 receives the pressure in the high pressure chamber 14 at one end in the steady operation state of the compressor. If the combination has a pressure difference enough to abut the valve seat 36 by overcoming the biasing force of the spring 37 and the pressure introduced by the passage 34, it is configured to receive the pressure not only in the compressor but also in any part of the refrigeration cycle. It doesn't matter.

発明の効果 以上のように本発明は、圧縮機の高低圧力差がないかま
たは小さい場合に圧縮機を始動した場合でも始動直後に
生ずるベーン背部の圧力低下をガス通路からのガス状流
体の供給によって防止することができ、また定常運転状
態においてはガス通路を遮断することによって適正量の
潤滑油をベーン背部へ供給できるので、圧縮機の耐久性
や効率を損なうことなくベーンの不調現象や圧縮不良現
象を防止することができる。EFFECTS OF THE INVENTION As described above, according to the present invention, even if the compressor is started when the pressure difference between the high and low pressures is small or small, the pressure drop at the back of the vane that occurs immediately after the start is supplied by the gaseous fluid from the gas passage. It is possible to prevent this, and in the steady operation state, by shutting off the gas passage, it is possible to supply an appropriate amount of lubricating oil to the back of the vane, so that vane malfunction and compression can be performed without compromising the durability and efficiency of the compressor. It is possible to prevent a defective phenomenon.

【図面の簡単な説明】[Brief description of drawings]

第１図は本発明の第１の実施例におけるベーン背圧付与
装置の要部拡大断面図、第２図は本発明の第１の実施例
におけるベーン背圧付与装置を具備したスライディング
ベーン式圧縮機の断面図、第３図は本発明の第２の実施
例におけるベーン背圧付与装置の要部拡大断面図、第４
図は従来のベーン背圧付与装置を具備したスライディン
グベーン式圧縮機の縦断面図、第５図は第４図のＸ−Ｘ
線による断面図、第６図は従来のベーン背圧付与装置の
要部拡大断面図である。 14……高圧室、17……ベーン背圧室、18……給油通路、
26……第１ガス通路、27……第２ガス通路、35……摺動
体、37……ばね。FIG. 1 is an enlarged cross-sectional view of an essential part of a vane back pressure imparting device according to a first embodiment of the present invention, and FIG. 2 is a sliding vane type compression equipped with a vane back pressure imparting device according to a first embodiment of the present invention. 3 is a sectional view of the machine, FIG. 3 is an enlarged sectional view of an essential part of a vane back pressure applying device according to a second embodiment of the present invention, and FIG.
The figure is a vertical sectional view of a sliding vane type compressor equipped with a conventional vane back pressure applying device, and FIG. 5 is XX of FIG.
FIG. 6 is a cross-sectional view taken along a line, and FIG. 6 is an enlarged cross-sectional view of a main part of a conventional vane back pressure applying device. 14 …… high pressure chamber, 17 …… vane back pressure chamber, 18 …… oil supply passage,
26: first gas passage, 27: second gas passage, 35: sliding body, 37: spring.

Claims (1)

【特許請求の範囲】[Claims] 【請求項１】筒状内壁を有するシリンダと、このシリン
ダ内で偏心回転し、ベーンスロットを有するロータと、
前記ベーンスロット内に摺動自在に挿入されたベーン
と、前記シリンダの両端を閉塞して内部に作動室を形成
する側板と、前記作動室内に開口した吸入口および吐出
口と、前記吐出口に設けられた吐出弁と、前記吐出口に
連通し、下部に油溜り部を有する高圧ケースと、前記ベ
ーンスロットと前記ベーン端部とで形成されるベーン背
圧室と前記油溜り部とを連通する給油通路と、この給油
通路を連通遮断する油路開閉手段と、前記高圧ケースと
前記ベーン背圧室とを連通するガス通路と、一端に高圧
ケース内の圧力を受け他端に定常運転中は高圧ケース内
圧力より低い圧力およびばねの付勢力とを受けて移動
し、前記ガス通路を連通、遮断する摺動体とを備えたス
ライディングベーン式圧縮機のベーン背圧付与装置。1. A cylinder having a cylindrical inner wall, and a rotor having eccentric rotation in the cylinder and having a vane slot,
A vane slidably inserted into the vane slot, a side plate that closes both ends of the cylinder to form a working chamber therein, a suction port and a discharge port opened in the working chamber, and a discharge port. A discharge valve provided, a high-pressure case that communicates with the discharge port and has an oil sump portion at a lower portion, a vane back pressure chamber formed by the vane slot and the vane end portion, and the oil sump portion Oil supply passage, an oil passage opening / closing means for connecting and disconnecting the oil supply passage, a gas passage for connecting the high pressure case and the vane back pressure chamber, a pressure in the high pressure case at one end, and a steady operation at the other end. Is a vane back pressure imparting device for a sliding vane compressor, which is provided with a sliding body that moves by receiving a pressure lower than the pressure in the high-pressure case and a biasing force of a spring, and connects and disconnects the gas passage.
JP61287930A 1986-12-03 1986-12-03 Vane back pressure application device for sliding vane compressor Expired - Lifetime JPH0745878B2 (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
JP61287930A JPH0745878B2 (en) 1986-12-03 1986-12-03 Vane back pressure application device for sliding vane compressor
US07/127,468 US4936761A (en) 1986-12-03 1987-12-02 Vane backpressure providing apparatus for sliding vane type compressor
CA000553351A CA1318896C (en) 1986-12-03 1987-12-02 Apparatus for providing vane backpressure in a sliding vane type of compressor
KR1019870013765A KR930002464B1 (en) 1986-12-03 1987-12-03 Sliding vane type compressor

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP61287930A JPH0745878B2 (en) 1986-12-03 1986-12-03 Vane back pressure application device for sliding vane compressor

Publications (2)

Publication Number Publication Date
JPS63140877A JPS63140877A (en) 1988-06-13
JPH0745878B2 true JPH0745878B2 (en) 1995-05-17

Family

ID=17723569

Family Applications (1)

Application Number Title Priority Date Filing Date
JP61287930A Expired - Lifetime JPH0745878B2 (en) 1986-12-03 1986-12-03 Vane back pressure application device for sliding vane compressor

Country Status (1)

Country Link
JP (1) JPH0745878B2 (en)

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0229880B2 (en) * 1984-07-04 1990-07-03 Matsushita Electric Ind Co Ltd BEENKAITENSHIKIATSUSHUKUKINOKYUYUSOCHI

Also Published As

Publication number Publication date
JPS63140877A (en) 1988-06-13

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