JPS6258085A - Vane back pressure applying device for sliding vane type compressor - Google Patents
Vane back pressure applying device for sliding vane type compressorInfo
- Publication number
- JPS6258085A JPS6258085A JP19803085A JP19803085A JPS6258085A JP S6258085 A JPS6258085 A JP S6258085A JP 19803085 A JP19803085 A JP 19803085A JP 19803085 A JP19803085 A JP 19803085A JP S6258085 A JPS6258085 A JP S6258085A
- Authority
- JP
- Japan
- Prior art keywords
- vane
- chamber
- supply passage
- pressure chamber
- back 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.)
- Pending
Links
Classifications
-
- 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
- F01C21/0863—Vane tracking; control therefor by fluid means the fluid being the working fluid
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
Abstract
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。DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The present invention relates to a vane backpressure applying device used in a sliding vane compressor used in automobile air conditioners 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
潤滑油を圧力差にょシ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 with a pressure difference so that as the rotor rotates, the vane rotates and slides with its tip in contact with the inner wall of the cylinder. Structures that supply water 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 a vane back pressure applying device for the above-mentioned conventional sliding vane compressor will be described below with reference to the drawings.
第９図乃至第１１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
するシリング、２はその外周の一部がシリング１内壁と
微小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
それぞれシリング１０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に連通ずる吸入口、１０は高圧側の作動室８に
連通ずる吐出口、１１は吐出口に配設された吐出弁、１
２は高圧通路１３に連通ずる高圧室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１
５を配設した高圧ケースである。１６け後部側板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。FIG. 9 to FIG. 11 show the specific structure of a sliding vane compressor having a conventional differential pressure oil supply type vane back pressure applying device. In the figure, 1 is a sill having a cylindrical inner wall, 2 is a rotor whose outer periphery partially forms a minute gap with the inner wall of the sill 1, 3 is a plurality of vane slots provided in the rotor 2, and 4 is inside the vane slot 4. A plurality of vanes are slidably inserted into the rotor 2, 5 is a drive shaft formed integrally with the rotor 2 and rotatably supported, and 6 and 7 are a sill 10 with both ends closed to form a working chamber 8 inside. A front side plate and a rear side plate are formed. Reference numeral 9 denotes an inlet port communicating with the working chamber 8 on the low pressure side, 10 a discharge port communicating with the working chamber 8 on the high pressure side, 11 a discharge valve disposed at the discharge port, 1
A screen 1 2 forms a high pressure chamber 14 communicating with the high pressure passage 13 and separates and captures lubricating oil in the compressed high pressure fluid.
This is a high-pressure case equipped with 5. A main body of the vane back pressure applying device disposed on the rear side plate 7 supplies lubricating oil from an oil reservoir below the high pressure chamber 14 to the vane back pressure chamber 17.
１８け高圧室１４下方の油溜り部とベーン背圧室１７と
を連通ずる給油通路・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、２
１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直助の作動室８とを連通ずる圧
力導入路である。18 oil supply passages that communicate 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 supply due to differential pressure; 20 is a ball seat provided in the middle of the oil supply passage 18;
1 is a sphere that comes into contact with or separates from the spherical seat 20 to interrupt communication with the oil supply passage 18; 22 is a plunger chamber that opens into the spherical seat 20; and 23 is slidably disposed inside the plunger chamber 22 on the spherical seat 20 side. A plunger 24 that releases the sphere 21 from the sphere seat 20 when moved to is a pressure introduction passage that communicates the lower plunger chamber 25 at the lower end of the plunger with the working chamber 8 directly assisting 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 for a sliding vane 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 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因に流入
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の抑圧に供されロータ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
小さくなるノテフランジャ２３は下部プランジャ室２５
（ＩＩＪ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 the drive shaft 5 and rotor 2 rotate clockwise in the figure due to power transmission from a drive source such as an engine,
Accordingly, low pressure fluid flows into the working chamber 8 through the suction port 9. The high-pressure fluid compressed as the rotor 2 rotates pushes up the discharge valve 11 through the discharge port 10 and flows into the high-pressure chamber 14 through the high-pressure passage 13, and the lubricating oil is separated and captured by the screen 15. On the other hand, from the pressure introduction path 24, the overcompressed gas in the working chamber 8, which has enough pressure to overcome the pressure of the high-pressure fluid and push up the discharge valve 11, flows into the lower plunger chamber 25.
The plunger 23 moves toward the spherical seat 20 and releases the spherical body 21 from the spherical seat 20. Therefore, the oil supply passage 18 is communicated with the lubricating oil separated from the high pressure fluid and stored below the high pressure chamber 14, and is supplied from the passage 19 and the oil supply passage 18 to the vane back pressure chamber 17 due to the differential pressure, and the It is subjected to suppression and flows into the working chamber 8 through the gap between the rotor 2 and the front side plate 6 and rear side plate 7. Furthermore, when the compressor stops, the pressure in the working chamber 8 rapidly drops 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 decreases. Note that the pressure of the flange 23 is smaller than the pressure at the upper end of the plunger 23 in the lower plunger chamber 25.
(Moves to IIJ. As a result, the sphere 21 contacts the sphere seat 20 and the oil supply passage 18 is cut off. Therefore, no more lubricant is supplied, and the lubricant remains in the working chamber 8. It is possible to prevent the liquid from being compressed when starting the compressor.
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
体の圧力上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４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の伸張没入の原生ずるベ
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
ング１内壁から遊離し再び衝突する周知の不調現象や流
体全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。Problems to be Solved by the Invention However, in the conventional vane backpressure applying device described above, the pressure of the fluid on the low pressure side becomes equal to the pressure of the fluid on the high pressure side, such as when a certain period of time has passed after the compressor is stopped. When the compressor is started in a state where the rotor 2 rotates, the vanes 4 rotate, and even if the vane 4 attempts to extend and retract into the vane slot 4, there is no differential pressure to supply lubricating oil, and the head viscosity of the lubricating oil Also, because the resistance at the beginning of the flow due to inertia is large, as a result, a sufficient amount of lubricating oil cannot be supplied to cope with the volume fluctuation of the vane back pressure chamber 17, which is caused by expansion and retraction of the vane 4. For this reason, especially when the rotational speed at the time of starting the compressor is low, the pressure in the vane back pressure chamber 17 decreases, causing the well-known malfunction phenomenon in which the vane 4 separates from the inner wall of the sill 1 and collides with it again, and the compression failure phenomenon in which the fluid is not fully compressed. There was a problem.
また潤滑油量を確保するため通路１９０通路面積を拡大
することは、定常運転時にベーン４を過度にシリング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間型があり、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。In addition, expanding the passage area of the passage 190 in order to secure the amount of lubricating oil means that the vane 4 is heated to an excessive 1 shilling during steady operation.
There is a gap in the vane 4 that presses against the inner wall, causing increased wear on the tip of the vane 4 and the inner wall of the cylinder 1, and an increase in compressor input, which reduces the durability and efficiency of the compressor. There was a problem in that the centrifugal force of
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-mentioned problems, the present invention is capable of preventing vane malfunction or poor compression even when the compressor is started at low speed when there is no or small pressure difference between the high and low pressures of the compressor, and does not impair durability or efficiency. A vane back pressure applying device for a sliding vane compressor is provided.
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
高圧室の油溜り部とを連通ずる給油通路と一端が前記ベ
ーン背圧室に連通し他端が摺動室に開口したガス供給通
路、前記ガス供給通路と前記高圧室の上方部分とを連通
ずる摺動室と、この摺動室のガス供給通路の開口部に設
けられた弁座と、前記摺動室内に摺動自在に嵌挿された
弁体と、この弁体に設けられ弁体の上下空間を連通ずる
通路と、前記弁座から遊離する向きに前記弁体を付勢す
るばね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 applying device for a sliding vane compressor of the present invention includes an oil supply passage that communicates the vane back pressure chamber with the oil reservoir portion of the high pressure chamber. a gas supply passage whose one end communicates with the vane backpressure chamber and whose other end opens into the sliding chamber; a sliding chamber which communicates the gas supply passage with the upper part of the high pressure chamber; and a gas supply to the sliding chamber. A valve seat provided at the opening of the passage, a valve body slidably inserted into the sliding chamber, a passage provided in the valve body that communicates the upper and lower spaces of the valve body, and a passageway from the valve seat. The valve body is provided with a spring that biases the valve body in a direction in which the valve body is released.
作 用
本発明は上記構成により、高低圧力差が無いか小さい状
態で圧縮機を始動させた場合でも、弁体ｔ／ｉばねの付
勢力により弁座より遊離し、ガス供給通路を連通してい
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外生ずるベーン背圧室
の容積変動に対して瞬時にガス供給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
ないからベーンの不調現象や圧縮不良現象を防止できる
。また始動後に弁体は通路抵抗によりばねの付勢力に打
ち勝って弁座に当接しているためガス供給通路を遮断し
、ベーン背圧室へは給油通路から適正量の潤滑油が供給
されるので耐久性や効率を損なうことがない。With the above-described configuration, the present invention allows the valve body to be released from the valve seat due to the biasing force of the t/i spring and communicate with the gas supply passage even when the compressor is started with no or small pressure difference between high and low pressures. Therefore, gaseous fluid can be instantaneously supplied from the gas supply passage in response to volume fluctuations in the vane back pressure chamber that occur when the vane rotates with the rotation of the rotor and attempts to expand and retract into the vane slot. Therefore, since no pressure drop occurs in the vane back pressure chamber, it is possible to prevent vane malfunction and compression failure. In addition, after startup, the valve body overcomes the biasing force of the spring due to passage resistance and comes into contact with the valve seat, cutting off the gas supply passage, and an appropriate amount of lubricating oil is supplied from the oil supply passage to the vane back pressure chamber. No loss in durability or efficiency.
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〜第８
図を参照しながら説明する。Embodiment Below, an embodiment of the present invention is shown in FIGS. 1 to 8 of the attached drawings.
This will be explained with reference to the figures.
第１図〜第４図は本発明の第１の実施例におけるスライ
ディングベーン式圧縮機のベーン背圧付与装置を示すも
ので、同図に示す部品のうち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Ｆ３Ａを省略する。1 to 4 show a vane back pressure applying device for a sliding vane compressor according to a first embodiment of the present invention. Those having the same functions and effects as the pressure applying device are denoted by the same reference numerals, and the explanation F3A is omitted.
同図において、２６は後部側板７に配設されたベーン背
圧付与装置本体、２７はその一端がベーン背圧室１７に
連通するガス供給通路、２８はガス供給通路２７の他端
が開口しかつガス供給通路２７と高圧室１４との上方部
分とを連通ずる摺動室、２９は摺動室２８のガス供給通
路２７の開口部に設けられた弁座、３０は摺動室２８内
に摺動自在に嵌挿された弁体、３１は弁体３０が弁座２
９に当接していないときのみガス供給通路２７と高圧室
１４の上方部分とを連通ずる通路、３２は弁座２９から
遊離する向きに弁体３０を付勢するばねである。In the figure, 26 is the main body of the vane back pressure applying device disposed on the rear side plate 7, 27 is a gas supply passage whose one end communicates with the vane back pressure chamber 17, and 28 is a gas supply passage 27 whose other end is open. and a sliding chamber that communicates the gas supply passage 27 with the upper part of the high pressure chamber 14; 29 is a valve seat provided at the opening of the gas supply passage 27 of the sliding chamber 28; 30 is a valve seat provided in the sliding chamber 28; The valve body 31 is slidably inserted into the valve seat 2.
A passage 32 communicates the gas supply passage 27 with the upper part of the high pressure chamber 14 only when the valve element 30 is not in contact with the valve seat 29.
以上のように構［ａれ念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 for the sliding vane compressor constructed as described above will be explained below.
圧縮機始動後ある時間経過して給油するのに十分な高圧
側と低圧側の圧力差が存在するような定常運転状態では
、ガス状流体が高圧室１４の上方部分に連通する通路３
１より摺動室３２内に流入して、このガス状流体の通路
抵抗により弁体３０のガス供給通路２７側端にかかる高
圧室１４内の圧力およびばね３２の付勢力に抗して弁体
３０を第１図に示す位置に保持している。したがって弁
体３０は弁座２９に当接して通路３１とガス供給通路２
７とを遮断しているから、ベーン背圧室１７へは高圧室
１７下方の油溜り部に貯えられた潤滑油が通路１９、給
油通路１８から供給されてベーン４の押上に供されるの
は前記従来のスライディングベーン式圧縮機のベーン背
圧付与装置と同様である。In steady-state operating conditions, where there is a pressure difference between the high-pressure side and the low-pressure side sufficient for refueling after a certain period of time after starting the compressor, the passage 3 through which the gaseous fluid communicates with the upper part of the high-pressure chamber 14
1 into the sliding chamber 32, and the passage resistance of this gaseous fluid causes the valve body to move against the pressure in the high pressure chamber 14 and the biasing force of the spring 32, which is applied to the gas supply passage 27 side end of the valve body 30. 30 is held in the position shown in FIG. Therefore, the valve body 30 contacts the valve seat 29 and connects the passage 31 and the gas supply passage 2.
7, the lubricating oil stored in the oil reservoir below the high pressure chamber 17 is supplied to the vane back pressure chamber 17 from the passage 19 and the oil supply passage 18, and is used to push up the vane 4. is similar to the vane back pressure applying device of the conventional sliding vane compressor.
また圧縮機が停止すると、ばね３２によって弁体３０は
第２図に示す位置まで移動する。したがって通路３１と
ガス供給通路２７とが連通ずるので高圧室１４からベー
ン背圧室１７への流れとしては、通路１９および通路１
８を通る潤滑油の流れよりも潤滑油に比して粘性及び水
頭の小さなガス状流体の通路３１、ガス供給通路２７お
よび給油通路１８を通る流れが優先的となり、この場合
でも作動室内への潤滑油の流入が防止できることも従来
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
と同様である。When the compressor stops, the spring 32 moves the valve body 30 to the position shown in FIG. Therefore, since the passage 31 and the gas supply passage 27 communicate with each other, the flow from the high pressure chamber 14 to the vane back pressure chamber 17 is limited to the passage 19 and the gas supply passage 1.
The flow of gaseous fluid having a smaller viscosity and head than the lubricating oil through the passage 31, the gas supply passage 27, and the oil supply passage 18 takes precedence over the flow of the lubricating oil through the passage 8, and even in this case, the flow into the working chamber is The ability to prevent the inflow of lubricating oil is also similar to the vane back pressure applying device of a conventional sliding vane compressor.
圧縮機停止後ある時間が経過して高圧側と低圧側の圧力
差が無いときに圧縮機を始動した場合には、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ａ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内の圧力が低くなれば瞬時にガス
状流体が高圧室１４上方に開口するガス供給通路２７か
らベーン背圧室１７に供給されるので、ベーン背圧室１
７の圧力低下を防止できる。そしてその後前述のように
、弁体３０が弁座２９に当接して通路ａ１とガス供給通
路２７とが遮断される。If the compressor is started after a certain period of time has passed after the compressor was stopped and there is no pressure difference between the high pressure side and the low pressure side, the vane 4 rotates as the rotor 2 rotates and extends inside the vane slot a. When the pressure inside the vane back pressure chamber 17 becomes low due to a volume change in the vane back pressure chamber 17 that occurs when the vane is immersed, gaseous fluid is instantly supplied to the vane back pressure chamber 17 from the gas supply passage 27 that opens above the high pressure chamber 14. Therefore, vane back pressure chamber 1
7 pressure drop can be prevented. Then, as described above, the valve body 30 comes into contact with the valve seat 29, and the passage a1 and the gas supply passage 27 are cut off.
以上のように本実施例によれば、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して、ベーン背圧室に
一端が連通し、他端が摺動室に開口したガス供給通路と
、前記ガス供給通路と高圧室の上方部分とを連通ずる摺
動室と、この摺動室のガス供給通路の開口部に設けられ
た弁座と、摺動室内に摺動自在に嵌挿された弁体と、こ
の弁体に設けられ、弁体の上下空間を連通ずる通路と、
弁座から遊離する向きて弁体を付勢するばねを設けるこ
とにより、少なくとも高圧側流体と低圧側流体との圧力
差が無いか小さい状態からの圧縮機始動時には弁体はば
ねの付勢力により弁座よシ遊離しているためガス供給通
路を連通し、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供給通路からガス
状流体を供給できるため、ベーン背圧室の圧力低下を生
じず、ベーンの不調現象や圧縮不良現象を防止できる。As described above, according to this embodiment, the vane back pressure imparting device for a sliding vane compressor includes a gas supply passage whose one end communicates with the vane back pressure chamber and whose other end opens into the sliding chamber; A sliding chamber that communicates the supply passage with the upper part of the high pressure chamber, a valve seat provided at the opening of the gas supply passage of this sliding chamber, and a valve body that is slidably inserted into the sliding chamber. and a passage provided in the valve body that communicates the upper and lower spaces of the valve body,
By providing a spring that biases the valve body away from the valve seat, at least when the compressor is started from a state where there is no or small pressure difference between the high-pressure side fluid and the low-pressure side fluid, the valve body is biased by the biasing force of the spring. Since the valve seat is separated from the valve seat, it communicates with the gas supply passage, and instantly responds to changes in the volume of the vane back pressure chamber that occur when the vane rotates as the rotor rotates and attempts to extend and retract into the vane slot. Since the gaseous fluid can be supplied from the gas supply passage, there is no pressure drop in the vane back pressure chamber, and vane malfunctions and poor compression phenomena can be prevented.
また始動後に弁体は、通路抵抗によりばねの付勢力に打
ち勝って弁座に当接しているためガス供給通路を遮断す
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。In addition, after startup, the valve body overcomes the biasing force of the spring due to passage resistance and contacts the valve seat, cutting off the gas supply passage, so the appropriate amount of lubricating oil is supplied from the oil supply passage to the vane back pressure chamber. , without compromising durability or efficiency.
次に本発明の第２の実施例について、第５図乃至第８図
を参照しながら説明する。Next, a second embodiment of the present invention will be described with reference to FIGS. 5 to 8.
同図において従来のスライディングベーン式圧縮機のベ
ーン背圧付与装置を示す第９図乃至第１１図および前記
第１の実施例を示す第１図乃至第４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。同図に
おいて、３３は後部側板７に配設されたベーン背圧付与
装置本体、３４は下部プランジャ室２５内に配設されプ
ランジャ２Ｇを球座２０側へ付勢するばねである。In the figure, the same reference numerals as in FIGS. 9 to 11 showing a vane back pressure applying device of a conventional sliding vane compressor and FIGS. 1 to 4 showing the first embodiment are given the same reference numerals as those in FIGS. They have the same effects. In the figure, 33 is a main body of the vane backpressure applying device disposed on the rear side plate 7, and 34 is a spring disposed within the lower plunger chamber 25 for biasing the plunger 2G toward the spherical seat 20 side.
第１の実施例と異なるのは給油通路１８とガス供給通路
２７との連通部からベーン背圧室１７までの給油通路１
８の途中にプランジャ室２２、プランジャ２３．圧力導
入路２４、球体２１および球座２０から成る油路開閉手
段とプランジャ２３を球座２０側へ付勢するバネとを設
けた点であるが、定常運転状態では第５図に示すように
、弁体３０は弁座２９に当接゛して適正量の潤滑油が通
路１９、給油通路１８からベーン背圧室１７へ供給でき
、圧縮機停止時には第６図に示すように、弁体３０が弁
座２９から遊離させられるが球体２１は高圧室１４内の
圧力を受けてプランジャ２３をばねａ２の付勢力に打ち
勝って球座２０に当接するので、作動室８内への高圧室
１４内のガス状流体の流入が防止でき、圧縮機停止後あ
る時間が経過して高圧側と低圧側の圧力差が小さくなる
と、ばね３４はプランジャ２３を球座２０側へ移動させ
るため第７図に示す状態となり、この状態から圧縮機を
始動した場合には瞬時にガス状流体が通路３１からガス
供給通路２７、給油通路１８を介してベーン背圧室１７
に供給されるので、ベーン背圧室１７の圧力低下を防止
できるなど第１の実施例と同様の作用効果を有する。The difference from the first embodiment is that the oil supply passage 1 extends from the communication portion between the oil supply passage 18 and the gas supply passage 27 to the vane back pressure chamber 17.
8, a plunger chamber 22, a plunger 23. The oil passage opening/closing means consisting of the pressure introduction passage 24, the sphere 21, and the sphere seat 20, and the spring that urges the plunger 23 toward the sphere seat 20 are provided, but in the steady operating state, as shown in FIG. The valve body 30 is in contact with the valve seat 29 so that an appropriate amount of lubricating oil can be supplied from the passage 19 and the oil supply passage 18 to the vane back pressure chamber 17. When the compressor is stopped, the valve body 30 is in contact with the valve seat 29. 30 is released from the valve seat 29, but the sphere 21 receives the pressure in the high pressure chamber 14, and the plunger 23 overcomes the urging force of the spring a2 and comes into contact with the ball seat 20, so that the high pressure chamber 14 enters the working chamber 8. When the pressure difference between the high-pressure side and the low-pressure side becomes small after a certain period of time has passed after the compressor is stopped, the spring 34 moves the plunger 23 toward the ball seat 20, as shown in FIG. When the compressor is started from this state, gaseous fluid instantly flows from the passage 31 through the gas supply passage 27 and the oil supply passage 18 to the vane back pressure chamber 17.
Since the pressure is supplied to the vane back pressure chamber 17, it has the same effect as the first embodiment, such as being able to prevent a pressure drop in the vane back pressure chamber 17.
なお、第１．２′の実施例においてガス供給通路２７は
給油通路１８に連通させたが、ガス供給通路２７ｒ／′
ｉ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。In addition, in the embodiment 1.2', the gas supply passage 27 was communicated with the oil supply passage 18, but the gas supply passage 27r/'
It may be communicated with the vane back pressure chamber 17 independently of the i-oil supply passage 18.
また、第２の実施例において下部プランジャ室２５内の
ばね３４はなくてもよい。さらにプランジャ室２２、プ
ランジャ２３、圧力導入路２４、球体２１および球座２
ｏから成る油路開閉手段を給油通路１８とガス供給通路
２７との連通部からベーン背圧室１７までの給油通路１
８の途中に設けたが、給油通路１８とガス供給通路２７
との連通部から通路１９までの給油通路１８の途中に設
けても良い。Further, in the second embodiment, the spring 34 in the lower plunger chamber 25 may be omitted. Furthermore, plunger chamber 22, plunger 23, pressure introduction path 24, sphere 21 and sphere seat 2
The oil passage opening and closing means consisting of o is connected to the oil supply passage 1 from the communication part between the oil supply passage 18 and the gas supply passage 27 to the vane back pressure chamber 17.
8, but the fuel supply passage 18 and the gas supply passage 27
It may be provided in the middle of the oil supply passage 18 from the communication part with the passage 19 to the passage 19.
妊らに、第１および第２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。In the first and second embodiments, the sliding vane type compressor was shown as a perfect circular type having only one suction port 9 and one discharge port 10, but it was shown that the sliding vane compressor had only one suction port 9 and one discharge port 10. It may be of a certain type, and although the number of vanes is shown as four, it may have any number of vanes.
発明の効果
以上のように本発明は、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して、ベーン背圧室と高圧室の
油溜り部とを連通ずる給油通路と、ペース背圧室と高圧
室の上方部分とを連通ずるガス供給通路と、少なくとも
高圧側流体と低圧側流体との圧力差が無いか小さい状態
からの圧縮機始動時には前記ガス供給通路を連−通しか
つ少なくとも始動時を除く圧縮機運転中は前記ガス供給
通路を遮断する弁体とを備えることにより、高圧圧力差
が無いか小さい状態で圧縮機を始動させた場合でも、弁
体はばねの付勢力により弁座より遊離しているためガス
供給通路を連通し、ロータの回転に伴なってベーンが回
転する。そしてベーンスロット内を伸張没入しようとす
る原生ずるベーン背圧室の容積変動に対して瞬時にガス
状流体を供給できるので、ベーン背圧室の圧力低下を生
じないからベーンの不調現象や圧縮不良現象を除土でき
、始動後に弁体は通路抵抗によりばねの付勢力に打ち勝
って弁座に当接しているためガス供給通路を遮断し、ベ
ーン背圧室へは給油通路から適正量の潤滑等が供給され
、耐久性や効率を損なうことがなく、その実用的効果は
大なるものがある。Effects of the Invention As described above, the present invention provides a vane backpressure applying device for a sliding vane compressor, which includes an oil supply passage communicating a vane backpressure chamber and an oil reservoir portion of a high pressure chamber, and a pace backpressure chamber and a high pressure chamber. A gas supply passage that communicates with the upper part and at least when the compressor is started from a state where there is no or small pressure difference between the high pressure side fluid and the low pressure side fluid, the gas supply passage is communicated with the gas supply passage and at least the compression except at the time of startup is performed. By providing a valve body that shuts off the gas supply passage during machine operation, even if the compressor is started with no or small high pressure difference, the valve body will be released from the valve seat due to the biasing force of the spring. The gas supply passages are connected to each other, and the vanes rotate as the rotor rotates. In addition, gaseous fluid can be instantly supplied to respond to volume fluctuations in the vane back pressure chamber that occur when the vane tries to expand and retract into the vane slot, so there is no pressure drop in the vane back pressure chamber, resulting in vane malfunction or compression failure. After startup, the valve body overcomes the biasing force of the spring due to the passage resistance and comes into contact with the valve seat, cutting off the gas supply passage, and the appropriate amount of lubrication is delivered from the oil supply passage to the vane back pressure chamber. is supplied without compromising durability or efficiency, and its practical effects are significant.
第１図、第２図は本発明の第１の実施例におけるベーン
背圧付与装置の要部拡大断面図、第３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縦断面図、第４図は第３図の
Ｙ−Ｙ線による断面図、第５図〜第７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８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９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１０図は第
８．９図のＸ−Ｘ線による断面図、第１１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。
１・・・・・・シリング、２・・・・・・ロータ、３・
・・・・・ベーンスロット、４・・・・・・ベーン、５
・・・・・・［動軸、６・・・・・。
前部側板、７・・・・・・後部側板、８・・・・・・作
動室、９・・・・・・吸入口、１０・・・・・・吐出口
、１１・・・・・・吐出弁、１２・・・・高圧ケース、
１４・・・・・・高圧室、１７・・・・・・ベーン背圧
室、１８・・・・・・給油通路、２７・・・・・・ガス
供給通路、２８・・・・−・摺動室、２９・・・・・・
弁座、３０・・・・・・弁体、３１・・・・・・通路、
３２・・・・・・ばね。
代理人の氏名 弁理士 中 尾 歓 男 ほか１名第２
図
（−７，’／ワングー
２−一一ローグ
第 ３ 図 ３−
一一へ゛−ンストロット１２−−−局ルクース
第４図
第５図
第６図
第７図
第８図
第９図
第１０図1 and 2 are enlarged sectional views of main parts of a vane back pressure applying device according to a first embodiment of the present invention, and FIG.
FIG. 4 is a longitudinal sectional view of a sliding vane compressor equipped with a vane back pressure applying device according to an embodiment of the present invention, FIG. 2
FIG. 8 is an enlarged cross-sectional view of essential parts of a vane back pressure applying device in the second embodiment of the present invention, and FIG. 9 is a longitudinal cross-sectional view of a sliding vane compressor equipped with a vane back pressure applying device in a second embodiment of the present invention. 10 is a longitudinal sectional view of a sliding vane compressor equipped with a conventional vane back pressure applying device, FIG. 10 is a sectional view taken along the line X-X of FIG. 8.9, and FIG. 11 is a conventional vane back pressure applying device. FIG. 1... Schilling, 2... Rotor, 3.
... Vane slot, 4 ... Vane, 5
...[Moving axis, 6...] Front side plate, 7...Rear side plate, 8...Working chamber, 9...Suction port, 10...Discharge port, 11...・Discharge valve, 12...high pressure case,
14... High pressure chamber, 17... Vane back pressure chamber, 18... Oil supply passage, 27... Gas supply passage, 28... Sliding room, 29...
Valve seat, 30... valve body, 31... passage,
32... Spring. Name of agent: Patent attorney Ken Nakao and 1 other person 2nd
Figure (-7,'/Wangoo 2-11 Rogue No. 3 Figure 3-
11 Main Stroke 12---Local Luxury Figure 4 Figure 5 Figure 6 Figure 7 Figure 8 Figure 9 Figure 10
Claims (1)
配設されその外周の一部がシリンダ内壁と微小隙間を形
成するロータと、このロータに設けられたベーンスロッ
ト内に摺動自在に挿入された複数のベーンと、前記ロー
タと一体的に形成され回転自在に軸支される駆動軸と、
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
前部側板および後部側板と、前記ロータ外周とシリンダ
内壁が近接している部分をはさんで作動室に連通する吸
入口および吐出口と、この吐出口に設けられた吐出弁と
、前記吐出口に連通し圧縮された高圧流体中の潤滑油を
分離しかつその下方部分に油溜り部を含む高圧室を有す
る高圧ケースと、前記ベーンスロットとベーン端部とで
形成されるベーン背圧室と前記高圧室の油溜り部とを連
通する給油通路と、一端が前記ベーン背圧室に連通し他
端が摺動室に開口したガス供給通路と、前記ガス供給通
路と前記高圧室の上方部分とを連通する摺動室と、この
摺動室のガス供給通路の開口部に設けられた弁座と、前
記摺動室内に摺動自在に嵌挿された弁体と、この弁体に
設けられ、弁体の上下空間を連通する通路と、前記弁座
から遊離する向きに前記弁体を付勢するばねとを備えた
スライディングベーン式圧縮機のベーン背圧付与装置。A cylinder having a cylindrical inner wall, a rotor disposed inside the cylinder and having a part of its outer periphery forming a minute gap with the cylinder inner wall, and a rotor slidably inserted into a vane slot provided in the rotor. a plurality of vanes, a drive shaft integrally formed with the rotor and rotatably supported;
A front side plate and a rear side plate that close both ends of the cylinder to form a working chamber therein, and an inlet and a discharge port that communicate with the working chamber across a portion where the outer periphery of the rotor and the inner wall of the cylinder are close to each other. , a discharge valve provided at the discharge port, a high-pressure case having a high-pressure chamber communicating with the discharge port and separating lubricating oil in compressed high-pressure fluid and including an oil reservoir in a lower portion thereof, and the vane. an oil supply passage that communicates a vane back pressure chamber formed by a slot and a vane end with an oil reservoir of the high pressure chamber; and a gas passage that communicates with the vane back pressure chamber at one end and opens into a sliding chamber at the other end. a supply passage; a sliding chamber that communicates the gas supply passage with the upper part of the high pressure chamber; a valve seat provided at the opening of the gas supply passage of the sliding chamber; A sliding vane comprising a freely inserted valve body, a passage provided in the valve body that communicates the upper and lower spaces of the valve body, and a spring that biases the valve body in a direction to be released from the valve seat. Vane back pressure application device for type compressor.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP19803085A JPS6258085A (en) | 1985-09-06 | 1985-09-06 | Vane back pressure applying device for sliding vane type compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP19803085A JPS6258085A (en) | 1985-09-06 | 1985-09-06 | Vane back pressure applying device for sliding vane type compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS6258085A true JPS6258085A (en) | 1987-03-13 |
Family
ID=16384356
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP19803085A Pending JPS6258085A (en) | 1985-09-06 | 1985-09-06 | Vane back pressure applying device for sliding vane type compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6258085A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US8333609B2 (en) | 2000-03-06 | 2012-12-18 | Sony Corporation | Connector, multi-channel audio system, electronic apparatus, and cable for connection |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS56107992A (en) * | 1980-01-31 | 1981-08-27 | Nippon Denso Co Ltd | Rotary compressor |
| JPS57206792A (en) * | 1981-06-11 | 1982-12-18 | Toyoda Autom Loom Works Ltd | Vane compressor |
-
1985
- 1985-09-06 JP JP19803085A patent/JPS6258085A/en active Pending
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS56107992A (en) * | 1980-01-31 | 1981-08-27 | Nippon Denso Co Ltd | Rotary compressor |
| JPS57206792A (en) * | 1981-06-11 | 1982-12-18 | Toyoda Autom Loom Works Ltd | Vane compressor |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US8333609B2 (en) | 2000-03-06 | 2012-12-18 | Sony Corporation | Connector, multi-channel audio system, electronic apparatus, and cable for connection |
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