JP2001165078A - Sliding vane compressor and refrigerating or cooling device possessed of refrigerating cycle with the compressor - Google Patents
Sliding vane compressor and refrigerating or cooling device possessed of refrigerating cycle with the compressorInfo
- Publication number
- JP2001165078A JP2001165078A JP35129899A JP35129899A JP2001165078A JP 2001165078 A JP2001165078 A JP 2001165078A JP 35129899 A JP35129899 A JP 35129899A JP 35129899 A JP35129899 A JP 35129899A JP 2001165078 A JP2001165078 A JP 2001165078A
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- Prior art keywords
- pressure
- compressor
- vane
- chamber
- sphere
- 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.)
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Abstract
Description
【０００１】[0001]
【発明の属する技術分野】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関するもの
である。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a sliding vane type compressor for use in air conditioners for automobiles and the like.
【０００２】[0002]
【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成が広く
用いられている。2. Description of the Related Art As is well known, in a sliding vane type compressor, a high pressure lubricating oil is applied to the rear end of a vane so that the vane makes a rotary sliding motion with the tip of the vane contacting the inner wall of the cylinder as the rotor rotates. Is widely used.
【０００３】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。図
６、図７、図８、図９および図１０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の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３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１０に
配接された吐出弁、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を配接した高圧ケースである。
１６は後部側板７に配接されたベーン背圧付与装置本体
で、高圧室１４の下方の油溜ま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の下方の油
溜まり部とベーン背圧室１７とを連通する給油通路、１
９は差圧による給油量を制限する通路、２０は給油通路
１８の途中に設けられた第１球座、２１は第１球座２０
と遊離したり当接して給油通路１８を遮断する第１球
体、２２は第１球座２０に第１球体２１と反対側で開口
する第１プランジャ室、２３は第１プランジャ室２２の
内部に摺動自在に配接され第１球座２０側へ移動した時
第１球体２１を第１球座２０から遊離させる第１プラン
ジャ、２４は第１プランジャ２３の下端の第１上部プラ
ンジャ室２５と吐出弁１１の直前の作動室８とを連通す
る第１圧力導入路、２６はその一端をベーン背圧室１７
に連通する第１ガス供給通路、２７はその一端を高圧室
１４の上方部分に連通する第２ガス供給通路、２８は第
１ガス供給通路２６と第２ガス供給通路２７の連通部に
設けられた第２球座、２９は第２球座２８と遊離したり
当接して第１ガス供給通路２６と第２ガス供給通路２７
とを連通したり遮断する第２球体、３０は第２球体２９
の動きを制限するストッパー、３１は第２球座２８に第
２球体２９と反対側で開口する第２プランジャ室、３２
は第２プランジャ室３１の内部に摺動自在に配接され第
２球座２８側へ移動した時第２球体２９を第２球座２８
から遊離させる第２プランジャ、３３は第２プランジャ
３２の下端の第２下部プランジャ室３４にあって第２プ
ランジャ３２を介して第２球体２９を第２球座２８から
遊離する向きに付勢するばね、３５は第２プランジャ３
２の下端の第２下部プランジャ室３４と作動室８の中間
圧部分に連通する第２圧力導入路、３６はベーン背圧室
１７と連通する第１ガス供給通路２６の途中に設けられ
た第３球座、３７は第１ガス供給通路２６内のガス流体
の流れを一方のみとするとともに第１ガス供給通路２６
内の流れを連通したり遮断する第３球体である。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。An example of a conventional vane back pressure applying device for a sliding vane type compressor will be described. FIGS. 6, 7, 8, 9 and 10 show a specific configuration of a sliding vane type compressor having a conventional differential pressure refueling type vane back pressure applying device. In the figure, 1
Is a cylinder having a cylindrical inner wall, 2 is a rotor in which a part of the outer periphery forms a minute gap with the inner wall of the cylinder 1, 3 is a plurality of vane slots provided in the rotor 2, and 4 is slidable in the vane slot 3. A plurality of vanes 5 are formed integrally with the rotor 2, a driving shaft integrally formed with the rotor 2 and rotatably supported, and 6 and 7 respectively before and after closing both ends of the cylinder 1 to form a working chamber 8 therein. A part side plate and a rear side plate. 9 is a suction 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 connected to the discharge port 10, 12 is a high-pressure passage communicating with the high-pressure passage 13. This is a high-pressure case in which a screen 15 that forms a chamber 14 and separates and captures lubricating oil in a compressed high-pressure fluid is connected.
Reference numeral 16 denotes a main body of the vane back pressure applying device disposed on the rear side plate 7, and supplies lubricating oil in an oil reservoir below the high pressure chamber 14 to the vane back pressure chamber 17. Reference numeral 18 denotes an oil supply passage which communicates an oil reservoir below the high pressure chamber 14 with the vane back pressure chamber 17.
Reference numeral 9 denotes a passage for limiting the amount of refueling due to the differential pressure, reference numeral 20 denotes a first ball seat provided in the middle of the fueling passage 18, and reference numeral 21 denotes a first ball seat 20.
A first sphere 22 which is separated or abuts to block the refueling passage 18, a first plunger chamber 22 which is opened in the first sphere 20 on the opposite side to the first sphere 21, and 23 is inside the first plunger chamber 22. A first plunger 24, which is slidably connected and releases the first sphere 21 from the first sphere 20 when moved toward the first sphere 20, is provided with a first upper plunger chamber 25 at the lower end of the first plunger 23. A first pressure introducing passage 26 communicating with the working chamber 8 immediately before the discharge valve 11 has one end connected to the vane back pressure chamber 17.
The first gas supply passage 27 communicates with the first gas supply passage 27, a second gas supply passage having one end communicating with the upper portion of the high-pressure chamber 14, and 28 is provided at a communication portion between the first gas supply passage 26 and the second gas supply passage 27. The second ball seats 29 are released from or abutted on the second ball seats 28 to contact the first gas supply passage 26 and the second gas supply passage 27.
A second sphere 30 for communicating with or blocking the second sphere 29
A stopper 31 for restricting the movement of the second plunger chamber, which opens in the second ball seat 28 on the side opposite to the second ball 29, 32
Is slidably disposed inside the second plunger chamber 31 and moves the second sphere 29 when moved to the second ball seat 28 side.
The second plunger 33 to be released from the second plunger 32 is located in the second lower plunger chamber 34 at the lower end of the second plunger 32 and urges the second sphere 29 through the second plunger 32 in a direction to be released from the second ball seat 28. Spring, 35 is the second plunger 3
A second pressure introduction passage communicating with a second lower plunger chamber at the lower end of the second and an intermediate pressure portion between the working chamber 8 and a second pressure introduction passage provided in the middle of the first gas supply passage communicating with the vane back pressure chamber 17. The three ball seats 37 are provided with only one flow of the gas fluid in the first gas supply passage 26 and the first gas supply passage 26.
It is a third sphere that communicates or blocks the flow inside. The operation of the vane back pressure applying device of the sliding vane type compressor configured as described above will be described below.
【０００４】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が図７において時計方向に回
転すると、これに伴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を押し上げて図６に示す
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。圧縮機始動後ある時
間経過して分離捕捉された潤滑油を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、第１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内の過圧縮ガスが第１上部プランジャ室２５へ供給
されるので、第１プランジャ２３は第１球座２０側へ移
動して第１球体２１を第１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の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の押圧に供されロータ２と前部側
板６および後部側板７との作動室８内へ流入するのであ
る。また第２ガス供給通路２７は高圧室１４の上方部分
に連通しているため、第２圧力導入路３５から第２下部
プランジャ室３４に流入する作動室８の中間圧の圧力と
ばね３３の付勢力に打ち勝って図１０に示す位置に第２
プランジャ３２を保持する。すなわち、第２球体２９は
第２球座２８に当接し第１ガス供給通路２６と第２ガス
供給通路２７は遮断される。また第１ガス供給通路２６
の途中に設けられた第３球体３７は第１ガス供給通路２
６のベーン背圧室１７側の圧力が高いため第３球座３６
に当接し第１ガス供給通路２６を遮断する。When the drive shaft 5 and the rotor 2 are rotated clockwise in FIG. 7 by receiving power from a drive source such as an engine, a low-pressure fluid is supplied from the suction port 9 to the working chamber 8.
Flows into. The high-pressure fluid compressed with the rotation of the rotor 2 pushes up the discharge valve 11 from the discharge port 10 and flows into the high-pressure chamber 14 through the high-pressure passage 13 shown in FIG.
As a result, the lubricating oil is separated and captured. In a steady operation state in which there is a sufficient pressure difference between the high pressure side and the low pressure side to supply the lubricating oil separated and captured after a certain time has elapsed since the start of the compressor, the high pressure fluid is supplied from the first pressure introduction passage 24. Is supplied to the first upper plunger chamber 25, which has a pressure enough to push up the discharge valve 11 by overcoming the pressure of the first plunger 23, so that the first plunger 23 moves to the first ball seat 20 side. To release the first sphere 21 from the first sphere 20. Therefore, since the oil supply passage 18 is communicated, the lubricating oil separated from the high-pressure fluid and stored below the high-pressure chamber 14 is supplied from the oil supply passage 18 to the vane back pressure chamber 17 by a differential pressure.
Is supplied to the vane 4 and is supplied to the working chamber 8 of the rotor 2 and the front side plate 6 and the rear side plate 7. Further, since the second gas supply passage 27 communicates with the upper part of the high pressure chamber 14, the pressure of the intermediate pressure of the working chamber 8 flowing into the second lower plunger chamber 34 from the second pressure introduction passage 35 and the spring 33 are attached. In the position shown in FIG.
Hold the plunger 32. That is, the second sphere 29 abuts the second sphere 28, and the first gas supply passage 26 and the second gas supply passage 27 are shut off. Also, the first gas supply passage 26
The third sphere 37 provided in the middle of the first gas supply passage 2
6 because the pressure on the side of the vane back pressure chamber 17 is high.
And the first gas supply passage 26 is shut off.
【０００５】また圧縮機が停止すると、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、第１上
部プランジャ室２５内の圧力も低圧側流体の圧力まで降
下し第１プランジャ２３の下端の圧力は第１プランジャ
２３の上端の圧力より大きくなるので第１プランジャ２
３は上側へ移動して第１球体２１は第１球座２０に当接
する。また、冷凍サイクル内の高圧側と圧縮機内部は第
１球体２１を境に仕切られているため高圧室１４の上方
部分の圧力は高く図９に示す位置に第２プランジャ３２
を保持する。すなわち第２球体２９は第２球座２８に当
接し、第１ガス供給通路２６と第２ガス供給通路２７は
遮断される。また、圧縮機内部の圧力は低圧側流体の圧
力まで降下するため第３球体３７は第３球座３６から遊
離する。したがって作動室８内へ潤滑油は供給されない
ため、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出来る。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３３は第２プランジャ３２を第２球座
２８側に移動させるため図８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第
２ガス供給通路２７から第１ガス供給通路２６、給油通
路１８を介してベーン背圧室１７に供給される。When the compressor is stopped, the pressure in the working chamber 8 rapidly drops to the pressure of the low-pressure side fluid, so that the pressure in the first upper plunger chamber 25 also drops to the pressure of the low-pressure side fluid. The pressure at the lower end of the first plunger 23 is greater than the pressure at the upper end of the first plunger 23.
3 moves upward, and the first sphere 21 contacts the first sphere 20. Further, since the high pressure side in the refrigeration cycle and the inside of the compressor are separated by the first sphere 21, the pressure in the upper part of the high pressure chamber 14 is high and the second plunger 32 is located at the position shown in FIG.
Hold. That is, the second sphere 29 abuts the second sphere 28, and the first gas supply passage 26 and the second gas supply passage 27 are shut off. Further, since the pressure inside the compressor drops to the pressure of the low-pressure side fluid, the third sphere 37 is released from the third sphere seat 36. Therefore, no lubricating oil is supplied into the working chamber 8, so that it is possible to prevent liquid compression at the start of the compressor caused by the lubricating oil remaining in the working chamber 8. When a certain time elapses after the compressor stops and the pressure difference between the high pressure side and the low pressure side becomes small, the spring 33 moves the second plunger 32 to the second ball seat 28 side, as shown in FIG. When the machine is started, the gaseous fluid is instantaneously supplied from the second gas supply passage 27 to the vane back pressure chamber 17 via the first gas supply passage 26 and the oil supply passage 18.
【０００６】[0006]
【発明が解決しようとする課題】しかしながら上記の構
成では、圧縮機の停止後ある時間が経過し、高圧側と低
圧側の圧力差が第２球体２９が第２球座２８より遊離す
る圧力より若干大きい状態で、特に給油通路内に潤滑油
が充満している時に圧縮機を起動すると、第２球体２９
が第２球座２８に当接しているためガス状流体を第２ガ
ス供給通路２７よりベーン背圧室１７へ供給できず、給
油通路１８より潤滑油を供給する。しかしながら、高圧
側と低圧側の圧力差が小さく、かつ潤滑油の水頭、粘性
および慣性による流れはじめの抵抗が大きい場合には、
結果としてベーン４の伸張没入の際に生ずるベーン背圧
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に圧縮機の回転数が低い
場合ベーン背圧室１７にベーン４を伸張させるに必要な
圧力を供給できず、ベーン４がシリンダ内壁１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。圧縮機始
動時のベーン背圧室１７の圧力を確保するには、第２プ
ランジャ３２の下部に配設したばね３３の荷重を大きく
し、高圧側と低圧側の差圧が潤滑油の流れはじめの抵抗
より小さい場合にはガス状流体をベーン背圧室１７へ供
給する方法がある。しかしながら、ばね３３の荷重を大
きくすると、高圧側と低圧側の差圧が第２球体２９を第
２球座２８へ当接させる差圧より小さい状態での定常運
転時には、常時ベーン背圧室１７へガス状流体を供給す
るため潤滑油の供給がなされず圧縮機の異常摩耗等を引
き起こしたり、高圧側と低圧側の差圧が第２球体２９を
第２球座２８へ当接させる差圧より大きい状態での運転
後、圧縮機を停止し高圧側と低圧側の差圧が小さくなる
とばね３３は第２プランジャ３２を第２球座２８側に移
動させるため、高圧側流体と低圧側流体の圧力差により
高圧側流体が第２ガス供給通路２７から第１ガス供給通
路２６、給油通路１８を介してベーン背圧室１７へ流れ
る際に高圧側流体が流れる音が発生するという問題点を
有していた。However, in the above configuration, after a certain period of time has elapsed since the compressor was stopped, the pressure difference between the high pressure side and the low pressure side is greater than the pressure at which the second sphere 29 is released from the second ball seat 28. When the compressor is started in a slightly large state, particularly when the oil supply passage is filled with lubricating oil, the second spherical body 29
Is in contact with the second ball seat 28, gaseous fluid cannot be supplied from the second gas supply passage 27 to the vane back pressure chamber 17, and lubricating oil is supplied from the oil supply passage 18. However, if the pressure difference between the high pressure side and the low pressure side is small and the resistance at the beginning of flow due to the head, viscosity and inertia of the lubricating oil is large,
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 generated when the vane 4 is extended and retracted. For this reason, particularly when the rotation speed of the compressor is low at the time of starting the compressor, it is not possible to supply the pressure necessary for extending the vane 4 to the vane back pressure chamber 17, and the vane 4 is separated from the cylinder inner wall 1 and collides again. There is a problem that a phenomenon or a compression failure phenomenon that does not compress the fluid occurs. In order to secure the pressure in the vane back pressure chamber 17 at the time of starting the compressor, the load of the spring 33 disposed below the second plunger 32 is increased, and the differential pressure between the high pressure side and the low pressure side starts to flow the lubricating oil. Is smaller than the resistance, there is a method of supplying a gaseous fluid to the vane back pressure chamber 17. However, if the load of the spring 33 is increased, the differential pressure between the high-pressure side and the low-pressure side is always smaller than the differential pressure that causes the second sphere 29 to abut on the second ball seat 28. The lubricating oil is not supplied because the gaseous fluid is supplied to the compressor, causing abnormal wear of the compressor, or the differential pressure between the high pressure side and the low pressure side causes the second ball 29 to contact the second ball seat 28. After the operation in the larger state, when the compressor is stopped and the differential pressure between the high pressure side and the low pressure side decreases, the spring 33 moves the second plunger 32 to the second ball seat 28 side. When the high-pressure side fluid flows from the second gas supply passage 27 through the first gas supply passage 26 and the oil supply passage 18 to the vane back pressure chamber 17 due to the pressure difference, a noise is generated in which the high-pressure side fluid flows. Had.
【０００７】本発明はこのような従来の課題を解決する
ものであり、高圧側と低圧側の流体の圧力差がいかなる
場合においても、圧縮機始動時に前記ベーン背圧室１７
にガス状流体を供給し、かつ圧縮機停止後、高圧側流体
の流れる音の発生しないスライディングベーン式圧縮機
を提供することを目的とする。The present invention solves such a conventional problem. In any case where the pressure difference between the high-pressure side and the low-pressure side fluid is any, when starting the compressor, the vane back-pressure chamber 17 is required.
It is an object of the present invention to provide a sliding vane compressor that supplies a gaseous fluid to a compressor and that does not generate a sound of the high-pressure fluid after the compressor stops.
【０００８】[0008]
【課題を解決するための手段】上記課題を解決するため
に本発明はベーン背圧空間への高圧流体供給のためのガ
ス通路をベーン背圧室と吐出弁近傍の作動室またはベー
ン背圧室と吐出口とを連通するように配設したものであ
る。In order to solve the above-mentioned problems, the present invention provides a gas passage for supplying a high-pressure fluid to a vane back pressure space by providing a vane back pressure chamber and a working chamber or a vane back pressure chamber near a discharge valve. And a discharge port.
【０００９】[0009]
【発明の実施の形態】請求項１に記載の発明は、ベーン
背圧空間へガス状流体を供給するガス通路をベーン背圧
室と吐出弁近傍の作動室とを連通するように配設したも
のである。この構成によれば、作動室内の高圧流体は圧
縮機の停止後急激に低圧流体の圧力まで低下するため、
圧縮機停止後、ガス通路を通りベーン背圧室へ流れる高
圧流体の流れを防止することができる。また、圧縮機の
始動時には高圧側と低圧側の流体の圧力差がいかなる場
合においても流体と作動室の吐出弁近傍のガス状流体を
供給するためベーンがシリンダの内壁から遊離し、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
象を防止することが出来る。According to the first aspect of the present invention, a gas passage for supplying a gaseous fluid to the vane back pressure space is provided so as to communicate the vane back pressure chamber with the working chamber near the discharge valve. Things. According to this configuration, the high-pressure fluid in the working chamber rapidly decreases to the pressure of the low-pressure fluid after the compressor stops,
After the compressor stops, the flow of the high-pressure fluid flowing through the gas passage to the vane back pressure chamber can be prevented. In addition, when the compressor is started, the vane is released from the inner wall of the cylinder and collides again to supply the fluid and the gaseous fluid near the discharge valve of the working chamber in any case where the pressure difference between the high pressure side and the low pressure side fluid is high. It is possible to prevent a well-known malfunction phenomenon and a poor compression phenomenon that does not compress the fluid.
【００１０】請求項２に記載の発明は、ガス通路をベー
ン背圧室と吐出口を連通するように配設したものであ
り、この構成においても請求項１と同様の効果が得られ
る。According to a second aspect of the present invention, the gas passage is disposed so as to communicate the vane back pressure chamber with the discharge port. In this configuration, the same effect as in the first aspect is obtained.
【００１１】請求項３に記載の発明は、上記する請求項
１または２に記載の発明によって構成されたスライディ
ングベーン式圧縮機を備えた冷凍サイクルを具備する冷
凍または冷却装置を実現し、優れた冷凍または冷却装置
とすることができる。According to a third aspect of the present invention, there is provided a refrigeration or cooling apparatus having a refrigeration cycle having a sliding vane type compressor constructed according to the first or second aspect of the present invention. It can be a refrigeration or cooling device.
【００１２】[0012]
【実施例】以下本発明の実施例について図１ないし図５
を参照して説明する。図１ないし図５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部分は同一の符号を記して重
複説明を省略する。FIG. 1 to FIG. 5 show an embodiment of the present invention.
This will be described with reference to FIG. 1 to 5, portions having the same functions and effects as those of the conventional vane back pressure applying device of the sliding vane type compressor are denoted by the same reference numerals, and redundant description will be omitted.
【００１３】（実施例１）図１において５０は一端を第
１ガス供給通路２６に連通し、他端を吐出弁近傍の作動
室に連通したガス通路である。その他の構成は従来のス
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
一である。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。圧縮機始動後ある時間経過して分離捕捉さ
れた潤滑油を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、第１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
第１上部プランジャ室２５へ供給されるので、第１プラ
ンジャ２３は第１球座２０側へ移動して第１球体２１を
第１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
の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
の押圧に供される。またガス通路５０は第１圧力導入路
２４と同様に吐出弁近傍の作動室内８に連通しているた
め、第２圧力導入路３５から第２下部プランジャ室３４
に流入する作動室８の中間圧の圧力とばね３３の付勢力
に打ち勝って図４に示す位置に第２プランジャ３２を保
持する。すなわち、第２球体２９は第２球座２８に当接
し第１ガス供給通路２６と第２ガス供給通路２７は遮断
される。また圧縮機が停止すると、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、第１上部プ
ランジャ室２５内の圧力も低圧側流体の圧力まで降下し
第１プランジャ２３の下端の圧力は第１プランジャ２３
上端の圧力より大きくなるので図３のように第１プラン
ジャ２３は上側へ移動して第１球体２１は第１球座２０
に当接する。またガス通路５０も作動室８へ連通してい
るため、ガス通路５０内の圧力も低圧側流体の圧力まで
急激に降下する。第２下部プランジャ室３４の圧力も低
圧側流体の圧力となるため、第２プランジャ３２は、ば
ね３３により第２球体２９を第２球座２８から遊離させ
る方向に移動する。したがって、ガス通路５０と第１ガ
ス供給通路２６およびベーン背圧室１７との間の流体の
圧力差は急激に小さくなるため、ガス通路５０からの流
体の流れは生じない。また、停止時間が経過しいかなる
圧力状態で起動しても、図２に示すようにガス通路５０
は起動直前は常に第１ガス供給通路２６と連通している
ため、圧縮機始動時に発生する作動室８内の過圧縮ガス
を瞬時にベーン背圧室に供給することができる。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は、圧縮機停止後高圧側と低圧側
の圧力差がいかなる場合でも、高圧流体のベーン背圧室
１７への流れは発生しない。また、始動時には瞬時に過
圧縮ガス流体をベーン背圧室１７に供給する。(Embodiment 1) In FIG. 1, reference numeral 50 denotes a gas passage having one end communicating with the first gas supply passage 26 and the other end communicating with the working chamber near the discharge valve. Other configurations are the same as those of the conventional vane back pressure applying device of the sliding vane type compressor. The operation of the vane back pressure applying device of the sliding vane type compressor configured as described above will be described below. In a steady operation state in which there is a sufficient pressure difference between the high pressure side and the low pressure side to supply the lubricating oil separated and captured after a certain time has elapsed since the start of the compressor, the high pressure fluid is supplied from the first pressure introduction passage 24. Is supplied to the first upper plunger chamber 25, which has a pressure enough to push up the discharge valve 11 by overcoming the pressure of the first plunger 23, so that the first plunger 23 moves to the first ball seat 20 side. To release the first sphere 21 from the first sphere 20. Therefore, the refueling passage 18
Are separated from the high-pressure fluid and communicate with the high-pressure chamber 14.
The lubricating oil stored below is supplied to the vane back pressure chamber 17 from the passage 19 and the oil supply passage 18 by the differential pressure, and
To be pressed. Since the gas passage 50 communicates with the working chamber 8 near the discharge valve similarly to the first pressure introduction passage 24, the gas passage 50 is connected to the second lower plunger chamber 34 from the second pressure introduction passage 35.
The second plunger 32 is held at the position shown in FIG. 4 by overcoming the intermediate pressure of the working chamber 8 flowing into the second chamber and the urging force of the spring 33. That is, the second sphere 29 abuts the second sphere 28, and the first gas supply passage 26 and the second gas supply passage 27 are shut off. When the compressor stops, the pressure in the working chamber 8 rapidly drops to the pressure of the low-pressure side fluid, so that the pressure in the first upper plunger chamber 25 also drops to the pressure of the low-pressure side fluid and the lower end of the first plunger 23. Of the first plunger 23
Since the pressure becomes higher than the upper end pressure, the first plunger 23 moves upward as shown in FIG.
Abut. Since the gas passage 50 also communicates with the working chamber 8, the pressure in the gas passage 50 also rapidly drops to the pressure of the low-pressure side fluid. Since the pressure in the second lower plunger chamber 34 also becomes the pressure of the low-pressure side fluid, the second plunger 32 moves in a direction in which the second sphere 29 is released from the second sphere 28 by the spring 33. Therefore, the fluid pressure difference between the gas passage 50, the first gas supply passage 26, and the vane back pressure chamber 17 is sharply reduced, so that no fluid flows from the gas passage 50. Also, no matter what pressure state the engine is started after the stop time elapses, as shown in FIG.
Is always in communication with the first gas supply passage 26 immediately before startup, so that the over-compressed gas in the working chamber 8 generated at the time of starting the compressor can be instantaneously supplied to the vane back pressure chamber. As described above, according to the present embodiment, the vane back pressure applying device of the sliding vane type compressor is capable of supplying the high pressure fluid to the vane back pressure chamber 17 regardless of the pressure difference between the high pressure side and the low pressure side after the compressor stops. No flow occurs. Further, at the time of starting, the over-compressed gas fluid is supplied to the vane back pressure chamber 17 instantaneously.
【００１４】さらに、実施例１ではガス通路５０は、吐
出弁近傍の作動室に連通しているが、第１圧力導入路２
４に連通しても良い。さらに、実施例においてスライデ
ィングベーン圧縮機は吸入口９、吐出口１０が各々一つ
しかない真円式であっても吸入口９、吐出口１０が各々
複数ある型式のものでもよいし、ベーンは何枚あっても
よい。Further, in the first embodiment, the gas passage 50 communicates with the working chamber near the discharge valve.
4 may be connected. Further, in the embodiment, the sliding vane compressor may be a perfect circular type having only one suction port 9 and one discharge port, or a type having a plurality of suction ports 9 and plural discharge ports 10. There can be any number.
【００１５】（実施例２）実施例１に対して、ガス通路
５０の一端を第１ガス供給通路２６へ連通し、他端を吐
出口１０へ連通させたものであり、前記実施例１と同様
の作用効果を示す。(Embodiment 2) In contrast to Embodiment 1, one end of the gas passage 50 communicates with the first gas supply passage 26 and the other end communicates with the discharge port 10. It shows the same effect.
【００１６】[0016]
【発明の効果】上記説明から明らかなように請求項１、
請求項２記載の発明によれば、圧縮機停止後高圧流体の
ベーン背圧空間への流れは生じないため、高圧流体がガ
ス供給通路を通りベーン背圧室に流れる際に生じる流通
音を防止できる。また始動時には瞬時に過圧縮ガスを流
体をベーン背圧室に供給するため、ベーンがシリンダ内
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防止できる。As apparent from the above description, claim 1
According to the second aspect of the present invention, since the high-pressure fluid does not flow into the vane back pressure space after the compressor stops, the flow noise generated when the high-pressure fluid flows through the gas supply passage to the vane back pressure chamber is prevented. it can. Further, since the fluid is supplied to the vane back pressure chamber instantaneously at the time of starting, the well-known malfunctioning phenomenon in which the vane is released from the inner wall of the cylinder and collides again and the poor compression phenomenon in which the fluid is not compressed can be prevented.
【図１】本発明の実施例１を示す圧縮機の側断面図FIG. 1 is a side sectional view of a compressor showing a first embodiment of the present invention.
【図２】圧縮機起動時のベーン背圧付与装置の断面図FIG. 2 is a sectional view of the vane back pressure applying device when the compressor is started.
【図３】圧縮機停止時のベーン背圧付与装置の断面図FIG. 3 is a sectional view of the vane back pressure applying device when the compressor is stopped.
【図４】圧縮機運転時のベーン背圧付与装置の断面図FIG. 4 is a sectional view of the vane back pressure applying device during operation of the compressor.
【図５】本発明の実施例２を示す圧縮機の側断面図FIG. 5 is a side sectional view of a compressor according to a second embodiment of the present invention.
【図６】従来例の圧縮機の側断面図FIG. 6 is a side sectional view of a conventional compressor.
【図７】図６のｘ−ｘ線における縦断面図FIG. 7 is a longitudinal sectional view taken along line xx of FIG. 6;
【図８】圧縮機起動時の従来のベーン背圧付与装置の断
面図FIG. 8 is a sectional view of a conventional vane back pressure applying device when the compressor is started.
【図９】圧縮機停止時の従来のベーン背圧付与装置の断
面図FIG. 9 is a sectional view of a conventional vane back pressure applying device when the compressor is stopped.
【図１０】圧縮機運転時の従来のベーン背圧付与装置の
断面図FIG. 10 is a cross-sectional view of a conventional vane back pressure applying device during compressor operation.
１ シリンダ ２ ロータ ３ ベーンスロット ４ ベーン ５ 駆動軸 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 １３ 高圧通路 １４ 高圧室 １５ スクリーン １６ ベーン背圧付与装置本体 １７ ベーン背圧室 １８ 給油通路 １９ 通路 ２０ 第１球座 ２１ 第１球体 ２２ 第１プランジャ室 ２３ 第１プランジャ ２４ 第１圧力導入路 ２５ 第１上部プランジャ室 ２６ 第１ガス供給通路 ２７ 第２ガス供給通路 ２８ 第２球座 ２９ 第２球体 ３０ ストッパー ３１ 第２プランジャ室 ３２ 第２プランジャ ３３ ばね ３４ 第２下部プランジャ室 ３５ 第２圧力導入路 ３６ 第３球座 ３７ 第３球体 ５０ ガス通路 Reference Signs List 1 cylinder 2 rotor 3 vane slot 4 vane 5 drive shaft 6 front side plate 7 rear side plate 8 working chamber 9 suction port 10 discharge port 11 discharge valve 12 high pressure case 13 high pressure passage 14 high pressure chamber 15 screen 16 vane back pressure applying device body 17 Vane back pressure chamber 18 Oil supply passage 19 Passage 20 First ball seat 21 First sphere 22 First plunger chamber 23 First plunger 24 First pressure introduction path 25 First upper plunger chamber 26 First gas supply path 27 Second gas supply Passage 28 Second spherical seat 29 Second spherical body 30 Stopper 31 Second plunger chamber 32 Second plunger 33 Spring 34 Second lower plunger chamber 35 Second pressure introduction path 36 Third spherical seat 37 Third spherical body 50 Gas passage
フロントページの続き (72)発明者 松田 敏雄 大阪府門真市大字門真1006番地 松下電器 産業株式会社内 (72)発明者 広瀬 孝司 大阪府門真市大字門真1006番地 松下電器 産業株式会社内 (72)発明者 葉瀬垣 隆博 大阪府門真市大字門真1006番地 松下電器 産業株式会社内 Ｆターム(参考） 3H040 AA09 BB01 BB11 CC05 CC10 CC20 DD03 DD08 DD11 DD19 DD20 DD29 DD33 Continued on the front page (72) Inventor Toshio Matsuda 1006 Kazuma Kadoma, Osaka Pref.Matsushita Electric Industrial Co., Ltd. (72) Inventor Koji Hirose 1006 Okadoma Kadoma, Kadoma City, Osaka Pref. Person Takahiro Hasegaki 1006 Kazuma Kadoma, Kadoma City, Osaka Prefecture F-term in Matsushita Electric Industrial Co., Ltd. (reference) 3H040 AA09 BB01 BB11 CC05 CC10 CC20 DD03 DD08 DD11 DD19 DD20 DD29 DD33
Claims (3)
リンダの内壁に設けられていて外周の一部分が前記シリ
ンダの内壁と微少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る
複数のベーンと、前記ロータに設けられ回転自在に軸支
される駆動軸と、前記ロータの外周とシリンダの内壁が
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まり部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まり部とを連通する給油通路
と、前記給油通路を連通したり遮断する油路開閉手段
と、一端を前記ベーン背圧室に連通する第１ガス供給通
路と、一端をこの第１ガス供給通路に連通していて他端
を前記吐出弁近傍の作動室に連通するガス通路と、前記
第１ガス供給通路とガス通路の連通部に設けられた球座
と、前記球座と遊離あるいは当接して前記第１ガス供給
通路とガス通路とを連通遮断する球体と、前記球座に対
して前記球体と反対側で開口するプランジャ室と、前記
プランジャ室内部に摺動自在に配設され球座側へ移動し
たとき球体を球座から遊離させるプランジャと、前記プ
ランジャの下端の下部プランジャ室にあってプランジャ
を介して球体を球座から遊離する向きに付勢するばね
と、圧縮機の定常運転時には、少なくとも前記ガス通路
内より低い圧力を前記下部プランジャ室に導入する圧力
導入路とを備えたスライディングベーン式圧縮機。1. A cylinder having a cylindrical inner wall, a rotor provided on the inner wall of the cylinder, a part of the outer periphery of which forms a minute gap with the inner wall of the cylinder, and a vane slot provided in the rotor. A plurality of vanes slidably inserted, a drive shaft provided on the rotor and rotatably supported, and communicating with the working chamber across a portion where the outer periphery of the rotor is close to the inner wall of the cylinder. A high-pressure case having an oil reservoir in a lower portion thereof, which separates the lubricating oil in the high-pressure fluid compressed and communicated with the discharge port, and a discharge valve provided in the discharge port. ,
An oil supply passage communicating between a vane back pressure chamber formed by the vane slot and a vane end and an oil reservoir of the high pressure chamber; an oil passage opening / closing means for communicating or blocking the oil supply passage; A first gas supply passage communicating with the vane back pressure chamber, a gas passage having one end communicating with the first gas supply passage, and a second end communicating with the working chamber near the discharge valve; and the first gas supply passage. A sphere provided at a communication portion between the first gas supply passage and the gas passage, the sphere being free or in contact with the sphere, and a sphere opposite to the sphere. A plunger chamber that opens on the side, a plunger that is slidably disposed inside the plunger chamber and releases the sphere from the ball seat when moved to the ball seat side, and a plunger in the lower plunger chamber at the lower end of the plunger. Sphere through sphere A spring biasing in a direction in which al liberated during steady operation of the compressor, sliding vane compressor having a pressure introducing passage for introducing a pressure lower than at least the gas passage in the lower plunger chamber.
通し、他端は吐出口に連通する請求項１記載のスライデ
ィングベーン式圧縮機。2. The sliding vane compressor according to claim 1, wherein one end of the gas passage communicates with the first gas supply passage, and the other end communicates with the discharge port.
ングベ−ン式圧縮機を有する冷凍サイクルを具備した冷
凍または冷却装置。3. A refrigeration or cooling apparatus comprising a refrigeration cycle having the sliding vane type compressor according to claim 1.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP35129899A JP2001165078A (en) | 1999-12-10 | 1999-12-10 | Sliding vane compressor and refrigerating or cooling device possessed of refrigerating cycle with the compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP35129899A JP2001165078A (en) | 1999-12-10 | 1999-12-10 | Sliding vane compressor and refrigerating or cooling device possessed of refrigerating cycle with the compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JP2001165078A true JP2001165078A (en) | 2001-06-19 |
Family
ID=18416369
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP35129899A Pending JP2001165078A (en) | 1999-12-10 | 1999-12-10 | Sliding vane compressor and refrigerating or cooling device possessed of refrigerating cycle with the compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2001165078A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2006112298A (en) * | 2004-10-14 | 2006-04-27 | Matsushita Electric Ind Co Ltd | Compressor |
-
1999
- 1999-12-10 JP JP35129899A patent/JP2001165078A/en active Pending
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2006112298A (en) * | 2004-10-14 | 2006-04-27 | Matsushita Electric Ind Co Ltd | Compressor |
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