JPS6360235B2 - - Google Patents
Info
- Publication number
- JPS6360235B2 JPS6360235B2 JP25092383A JP25092383A JPS6360235B2 JP S6360235 B2 JPS6360235 B2 JP S6360235B2 JP 25092383 A JP25092383 A JP 25092383A JP 25092383 A JP25092383 A JP 25092383A JP S6360235 B2 JPS6360235 B2 JP S6360235B2
- Authority
- JP
- Japan
- Prior art keywords
- vane
- compressor
- valve body
- cylinder
- pressure
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
- 230000002265 prevention Effects 0.000 claims description 4
- 239000012530 fluid Substances 0.000 description 11
- 238000005461 lubrication Methods 0.000 description 11
- 239000003921 oil Substances 0.000 description 10
- 230000007423 decrease Effects 0.000 description 7
- 239000010687 lubricating oil Substances 0.000 description 5
- 230000006835 compression Effects 0.000 description 4
- 238000007906 compression Methods 0.000 description 4
- 230000000694 effects Effects 0.000 description 4
- 230000007257 malfunction Effects 0.000 description 4
- 230000005540 biological transmission Effects 0.000 description 1
- 210000000078 claw Anatomy 0.000 description 1
- 239000010725 compressor oil Substances 0.000 description 1
- 230000002542 deteriorative effect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
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
- F01C21/0827—Vane tracking; control therefor by mechanical means
- F01C21/0845—Vane tracking; control therefor by mechanical means comprising elastic means, e.g. springs
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、自動車用空調機等に供されるベーン
回転式圧縮機における吸入逆流防止装置に関する
ものである。DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The present invention relates to a suction backflow prevention device for a vane rotary compressor used in automobile air conditioners and the like.
従来例の構成とその問題点
周知のようにベーン回転式圧縮機においてはロ
ータの回転に伴なつ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底
部に常時高圧の潤滑油を作用させる構造が用いら
れている。Conventional configuration and its problems As is well known, in vane rotary compressors, high-pressure lubrication is constantly applied to the bottom of the vane so that as the rotor rotates, the vane rotates and slides with its tip in contact with the inner wall of the cylinder. A structure that allows oil to act is used.
これを実現する手段として一般に、圧縮機の駆
動軸上に装備したポンプ等により強制的に給油す
る強制給油式と、圧縮機により圧縮された高圧流
体の圧力を利用して圧縮機の高低圧力差により給
油する差圧給油式とが広く利用されている。 Generally, the means to achieve this are the forced lubrication system, which uses a pump installed on the drive shaft of the compressor to forcibly supply lubrication, and the other, which uses the pressure of high-pressure fluid compressed by the compressor to create a pressure difference between the high and low pressures of the compressor. A differential pressure lubrication system is widely used.
しかしながら、強制給油式では圧縮機の回転数
上昇に伴なつて給油量も増大しベーンに作用する
遠心力とあいまつてベーンを過度にシリンダ内壁
に押接せしめベーン先端部およびシリンダ内壁の
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欠点
がある。 However, in the forced lubrication type, as the rotation speed of the compressor increases, the amount of lubrication also increases, which, together with the centrifugal force acting on the vanes, causes the vanes to be pushed into excessive contact with the cylinder inner wall, resulting in increased wear on the vane tips and the cylinder inner wall. This results in an increase in the input power of the compressor, which has the disadvantage of deteriorating the durability and efficiency of the compressor.
一方、差圧給油式では上記強制給油式の場合と
同様の欠点をひき起こす過剰な給油を排して、給
油通路に給油量を制限する機構を設けることによ
つて上記現象を軽減している。 On the other hand, the differential pressure lubrication system eliminates excessive lubrication, which causes the same drawbacks as the forced lubrication system, and reduces the above phenomenon by providing a mechanism in the lubrication passage to limit the amount of lubrication. .
第１図，第２図は従来の差圧給油式の給油装置
を有するベーン回転式圧縮機の具体構成を示すも
のである。 FIGS. 1 and 2 show a specific configuration of a vane rotary compressor having a conventional differential pressure oil supply system.
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
れたベーンスロツト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である。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、９は
低圧側の作動室に連通する吸入口、１０は高圧側
の作動室８に連通する吐出口、１１は吐出口１０
に配設された吐出弁、１２はケースで、その内部
において、高圧通路１３に連通しかつ圧縮された
高圧流体中の潤滑油を分離捕捉するスクリーン１
５を配設した高圧室１４とその両端が吸入配管接
続口２０と吸入口９に連通する低圧通路１９とを
有する。１６は高圧室１４の下方の油溜り部とベ
ーン底部空間１７とを連通する給油通路、１８は
給油量を制限する通路である。 In the figure, 1 is a cylinder having a cylindrical inner wall, 2 is a rotor whose outer circumference partially forms a minute gap with the inner wall of cylinder 1, and 3 is slidably inserted into a vane slot 4 provided in rotor 2. The plurality of vanes 5 are a drive shaft formed integrally with the rotor 2 and rotatably supported. 6 and 7
9 is a front side plate and a rear side plate that close both ends of the cylinder 1 to form a working chamber 8 therein, 9 is an inlet port communicating with the working chamber 8 on the low pressure side, and 10 is a discharge port communicating with the working chamber 8 on the high pressure side. Outlet, 11 is discharge port 10
A discharge valve 12 is a case in which a screen 1 is connected to the high pressure passage 13 and separates and captures lubricating oil in the compressed high pressure fluid.
The high pressure chamber 14 has a high pressure chamber 14 in which a pipe 5 is disposed, and a low pressure passage 19 that communicates with the suction pipe connection port 20 and the suction port 9 at both ends thereof. Reference numeral 16 indicates an oil supply passage that communicates the oil reservoir below the high pressure chamber 14 with the vane bottom space 17, and 18 indicates a passage that limits the amount of oil supply.
以上のように構成されたベーン回転式圧縮機の
給油装置について、以下その動作を説明する。 The operation of the vane rotary compressor oil supply system 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２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によつて潤滑油が分離捕
捉される。高圧流体中より分離された潤滑油は高
圧室１４下方に貯えられ、差圧によつて給油通路
１６および通路１８からベーン底部空間１７へ供
給されてベーン３の押圧に供される
しかしながら圧縮機が停止してからある時間が
経過して低圧側の流体の圧力と高圧側の流体の圧
力とが等しくなつた場合に圧縮機を始動すると、
圧縮機始動直後の差圧が小さいため、上記従来の
給油装置では特に圧縮機始動の回転数が低い場合
にベーンの押圧不足を生じベーンがシリンダの内
壁から遊離して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欠点
があつた。 When the drive shaft 5 and rotor 2 rotate clockwise in FIG. 2 due to power transmission from a drive source such as an engine, low-pressure fluid flows into the suction port 9.
It flows into the working chamber 8. 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. The lubricating oil separated from the high-pressure fluid is stored below the high-pressure chamber 14, and is supplied to the vane bottom space 17 from the oil supply passage 16 and the passage 18 due to the pressure difference, and is used to press the vane 3. However, the compressor When the compressor is started after a certain period of time has passed since the compressor was stopped and the pressure of the fluid on the low pressure side becomes equal to the pressure of the fluid on the high pressure side,
Because the differential pressure immediately after the compressor starts is small, the conventional oil supply system described above is a well-known malfunction phenomenon in which the vane is insufficiently pressed, especially when the rotation speed at the start of the compressor is low, causing the vane to separate from the inner wall of the cylinder and collide again. This method has the disadvantage that a compression failure phenomenon occurs in which the fluid is not compressed.
発明の目的
本発明は上記従来の給油装置の欠点に鑑みなさ
れたもので、上記従来の給油装置とともに使用し
て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
損なわないベーン回転式圧縮機の吸入逆流防止装
置を提供するものである。Purpose of the Invention The present invention has been made in view of the drawbacks of the conventional oil supply system described above, and is used together with the conventional oil supply system to start the compressor at low speed rotation when there is no or small pressure difference between the high and low pressures of the compressor. However, the present invention provides a suction backflow prevention device for a rotary vane compressor that can prevent vane malfunctions and compression failures and does not impair durability or efficiency.
発明の構成
この目的を達成するために本発明は、ベーン回
転式圧縮機の圧縮機の外部より圧縮機内への流れ
を許容し逆流を防止する如く配設される弁体と、
弁体が微小隙間を介して摺動自在に保持される弁
保持体と、弁体および弁保持体で形成される空間
内に前記弁体が吸入通路を遮断するよう付勢する
ばねとを設けたものである。Structure of the Invention In order to achieve this object, the present invention provides a valve body of a vane rotary compressor that is arranged to allow flow from the outside of the compressor into the compressor and prevent backflow;
A valve holder is provided in which the valve element is slidably held through a small gap, and a spring is provided in a space formed by the valve element and the valve holder to urge the valve element to block the suction passage. It is something that
この構成によつて圧縮機が長時間停止して圧縮
機の高低圧力差が無いか小さい場合には弁体は吸
入通路を遮断しており、圧縮機始動の直後におい
ては弁体が吸入通路を遮断し続けようとするため
吸入側の作動室内の圧力はベーンの回転に伴なう
作動室の容積増加によつて低下し、したがつてベ
ーンの先端に作用するベーンをベーンスロツト内
に投入させようとする力も著しく小さくなるので
ベーンをシリンダの内壁に確実に押接せしめるこ
とができる。 With this configuration, when the compressor is stopped for a long time and there is no or small pressure difference between the high and low pressures of the compressor, the valve body blocks the suction passage, and immediately after the compressor starts, the valve body blocks the suction passage. In order to continue to shut off, the pressure in the working chamber on the suction side decreases due to the increase in volume of the working chamber as the vane rotates, and therefore the vane acting on the tip of the vane is forced into the vane slot. Since the force required to do so is also significantly reduced, the vane can be reliably pressed against the inner wall of the cylinder.
また始動後ある時間が経過した時点においては
弁体と弁保持体で形成する空間内の圧力が低下し
て弁体は吸入通路を徐々に連通しようとするた
め、吸入側の作動室内の圧力も徐々に上昇し、し
たがつてベーンを先端に作用する力も急激に増大
することがないのでベーンはシリンダの内壁に押
接せしめられて正常な運転を継続することができ
る。 Furthermore, after a certain period of time has passed after startup, the pressure in the space formed by the valve element and the valve holder decreases, and the valve element gradually tries to communicate with the suction passage, so the pressure in the working chamber on the suction side also decreases. The vane gradually rises, and therefore the force acting on the tip of the vane does not suddenly increase, so that the vane is pressed against the inner wall of the cylinder and can continue normal operation.
このように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る。 In this way, even when the compressor is started at low rotation speed when there is no or small pressure difference between the high and low pressures of the compressor, vane malfunctions and poor compression phenomena can be prevented.
実施例の説明
以下本発明の一実施例について図面を参照しな
がら説明する。DESCRIPTION OF EMBODIMENTS An embodiment of the present invention will be described below with reference to the drawings.
第３図，第４図は本発明の一実施例における吸
入逆止弁を具備したベーン回転式圧縮機を示すも
ので、前記従来の差圧給油式の給油装置を具備す
るベーン回転式圧縮機と同一の部品でかつ同一の
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。 Figures 3 and 4 show a vane rotary compressor equipped with a suction check valve according to an embodiment of the present invention; Components that are the same as and have the same functions and effects are designated by the same reference numerals and their explanations will be omitted.
同図において、２１は吸入配管接続口２０に接
続され通路２１ａを有する吸入配管、２２は配管
接続口２０に設けられその両端が通路２１ａおよ
び吸入通路１９と連通する通路２２ａを有する弁
座、２３は弁座２２に当接離脱して通路２２ａと
吸入通路１９を遮断連通する弁体、２４は微小隙
間２５を介して弁体２３を摺動自在に保持する弁
保持体、２６は前記弁保持体と一体的に固着され
その外周面に多数の開口部２７を有しかつ複数の
爪部２８が弁座２２の溝に係止されて保持される
保持金具、２９は弁体２３と弁保持体２４とで形
成される空間３０内に配設され弁体２３を弁座２
２に当接させる方向に付勢するばねである。 In the figure, 21 is a suction pipe connected to the suction pipe connection port 20 and has a passage 21a, 22 is a valve seat provided in the pipe connection port 20 and has a passage 22a whose both ends communicate with the passage 21a and the suction passage 19, and 23 24 is a valve holding body that slidably holds the valve body 23 via a minute gap 25; 26 is the valve holding body that contacts and separates from the valve seat 22 to cut off communication between the passage 22a and the suction passage 19; A retainer 29 is integrally fixed to the valve body and has a large number of openings 27 on its outer peripheral surface, and a plurality of claws 28 are engaged with grooves in the valve seat 22 to hold the valve. The valve body 23 is disposed in a space 30 formed by the valve body 24 and the valve seat 2.
This is a spring that urges the member 2 in the direction of contacting the member 2.
以上のように構成された吸入逆止弁を具備した
ベーン回転圧縮機について以下その動作を説明す
る。 The operation of the vane rotary compressor equipped with the suction check valve configured as described above will be described below.
圧縮機が停止してからある時間が経過して低圧
側の流体の圧力と高圧側の流体の圧力とが等しい
場合には空間３０内の圧力も吸入通路１９内の圧
力と等しくしたがつて弁体２３はばね２９の付勢
力によつて弁座２２に当接されている。 If a certain period of time has passed since the compressor stopped and the pressure of the fluid on the low pressure side and the pressure of the fluid on the high pressure side are equal, the pressure in the space 30 will also be equal to the pressure in the suction passage 19, and the valve will close. The body 23 is brought into contact with the valve seat 22 by the biasing force of a spring 29.
この状態で圧縮機を始動すると、吸入通路１９
内の流体はベーン３の回転に伴なう吸入側の作動
室８の容積増加によつて作動室８内に吸入され吐
出される。この時同時にベーン底部空間１７には
ベーン底部空間１７の容積増大によるわずかな差
圧によつて高圧室１４より通路１８および給油通
路１６を経てわずかな潤滑油しか供給されないの
であるが、吸入通路１９の容積が小さいことと、
空間３０内の圧力が始動後瞬時には変化しないこ
とから、弁体２３は弁座２２に当接されたままで
ある。これによつて吸入通路１９内の圧力は始動
後瞬時にして低下し、その圧力低下に対応して作
動室８内の圧力も低下し、その分だけベーン３の
先端に作用するベーン３をベーンスロツト４内に
投入させようとする力も小さくなる。そのため、
ベーン３はシリンダ１の内壁に押接せしめられて
正常な運転を継続することができるのである。 When the compressor is started in this state, the suction passage 19
The fluid inside is sucked into the working chamber 8 and discharged as the volume of the working chamber 8 on the suction side increases as the vane 3 rotates. At the same time, only a small amount of lubricating oil is supplied to the vane bottom space 17 from the high pressure chamber 14 via the passage 18 and the oil supply passage 16 due to a slight pressure difference due to the increase in the volume of the vane bottom space 17, but the suction passage 19 The volume of the is small and
Since the pressure within the space 30 does not change instantaneously after starting, the valve body 23 remains in contact with the valve seat 22. As a result, the pressure inside the suction passage 19 drops instantaneously after startup, and the pressure inside the working chamber 8 also drops correspondingly to the pressure drop, and the vane 3 acting on the tip of the vane 3 is moved by that amount into the vane slot. 4. The force that forces it to enter into the body also becomes smaller. Therefore,
The vane 3 is pressed against the inner wall of the cylinder 1, allowing normal operation to continue.
さらに運転を継続して、空間３０内の圧力が微
小隙間２５によつて徐々に低下し、ついには通路
２２ａ内の圧力が空間３０内の圧力およびばね２
９の付勢力に打ち勝つと、弁体２３は弁座２２か
ら離脱して通路２２ａ内のガスが吸入通路１９内
に徐々に流入し、作動室８に吸入され、圧縮され
て吐出され、高圧室１４の圧力も上昇する。これ
によつてベーン底部空間１７に供給される潤滑油
量も増大するので、ベーン３はシリンダ１の内壁
に押接せしめられて正常な運転を継続することが
できる。 As the operation continues, the pressure in the space 30 gradually decreases due to the small gap 25, and finally the pressure in the passage 22a decreases due to the pressure in the space 30 and the spring 2.
9, the valve body 23 separates from the valve seat 22, and the gas in the passage 22a gradually flows into the suction passage 19, is sucked into the working chamber 8, is compressed and discharged, and is discharged from the high pressure chamber. 14 pressure also increases. This also increases the amount of lubricating oil supplied to the vane bottom space 17, so that the vane 3 is pressed against the inner wall of the cylinder 1 and can continue normal operation.
さらに時間が経過して弁体２３が第４図におけ
る２点鎖線で示す位置まで移動した場合には、そ
の動作は前記従来のベーン回転式圧縮機の動作と
何ら変わることはない。 When further time passes and the valve body 23 moves to the position shown by the two-dot chain line in FIG. 4, its operation is no different from that of the conventional vane rotary compressor.
このように圧縮機が長時間停止して圧縮機の高
低圧力差が無いか小さい時に圧縮機を始動した場
合にも、弁体２３が弁座２２に当接して吸入通路
１９を遮断し続けようとするため、吸入側の作動
室８内の圧力はベーン３の回転に伴なう作動室８
の容積増加によつて低下し、したがつてベーン３
の先端に作用するベーン３をベーンスロツト４内
へ投入させようとする力も著しく小さくなる。そ
の結果ベーン３をシリンダ１の内壁に確実に押接
せしめることができ、さらに圧縮機始動後ある時
間が経過した時点においても弁体２３と弁保持体
２４で形成される空間内の圧力が低下して弁体２
３は弁座２２より徐々に離脱しようとする。その
ため、吸入側の作動室８内の圧力も徐々に上昇
し、したがつてベーン３の先端に作用する力も急
激に増大することがないのでベーン３はシリンダ
１の内壁に押接せしめられて正常な運転を継続す
ることができ、圧縮機の高低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
ンの不調現象が防止できる。 In this way, even if the compressor is stopped for a long time and the compressor is started when there is no or only a small pressure difference between the high and low pressures of the compressor, the valve body 23 will come into contact with the valve seat 22 and continue to block the suction passage 19. Therefore, the pressure in the working chamber 8 on the suction side increases due to the rotation of the vane 3.
is reduced due to the increase in the volume of vane 3.
The force acting on the tip of the vane 3 to force the vane 3 into the vane slot 4 is also significantly reduced. As a result, the vane 3 can be reliably pressed against the inner wall of the cylinder 1, and the pressure in the space formed by the valve body 23 and the valve holder 24 decreases even after a certain period of time has passed after the compressor is started. and valve body 2
3 tries to gradually separate from the valve seat 22. Therefore, the pressure in the working chamber 8 on the suction side gradually increases, and therefore the force acting on the tip of the vane 3 does not increase suddenly, so the vane 3 is pressed against the inner wall of the cylinder 1 and is maintained normally. Even if the compressor is started at a low rotation speed when there is no or only a small difference between the high and low forces of the compressor, it is possible to prevent the vane from malfunctioning.
なお本実施例においては、弁体２３が弁座２２
に当接した状態において吸入通路１９と通路２２
ａとを遮断したが吸入通路１９と通路２２ａまた
は通路２１ａとを連通する微小断面積を有するバ
イパス通路を設けても前記実施例と同様の作用効
果を有することは明らかである。 Note that in this embodiment, the valve body 23 is connected to the valve seat 22.
The suction passage 19 and the passage 22 are in contact with each other.
It is clear that even if a bypass passage having a small cross-sectional area is provided to communicate the suction passage 19 and the passage 22a or the passage 21a, although the suction passage 19 and the passage 22a or the passage 21a are disconnected from each other, the same effect as in the above embodiment can be obtained.
さらに先の実施例においては弁体２３と弁保持
体２４との間に微小隙間を設けたが、弁体２３ま
たは弁保持体２４に吸入通路１９と空間３０とを
連通する微小断面積を有する貫通孔を設けても前
記実施例と同様の作用効果を有することは明らか
である。 Furthermore, in the previous embodiment, a minute gap was provided between the valve body 23 and the valve holder 24, but the valve body 23 or the valve holder 24 has a minute cross-sectional area that communicates the suction passage 19 and the space 30. It is clear that even if a through hole is provided, the same effect as in the above embodiment can be obtained.
発明の効果
以上の説明から明らかなように本発明は、ベー
ン回転式圧縮機の吸入通路中に圧縮機の外部より
圧縮機内への流れを許容し逆流を防止する如く配
設される弁体と、弁体が微小隙間を介して摺動自
在に保持される弁保持体と、弁体および弁保持体
で形成される空間内に前記弁体が吸入通路を遮断
するよう付勢するばねとを設けたもので、圧縮機
が長時間停止して圧縮機の高低圧力差が無いか小
さい場合において圧縮機を始動してもベーンの先
端に作用するベーンをベーンスロツト内に投入さ
せようとする力が著しく小さく、ベーンをシリン
ダの内壁に確実に押接せしめることができる。ま
た始動後ある時間が経過した時点においては、弁
体と弁保持体で形成する空間内の圧力が低下して
弁体が吸入通路を徐々に連通しようとするため、
吸入側の作動室内の圧力も徐々に上昇してベーン
の先端に作用する力も急激に増大することもな
く、ベーンをシリンダの内壁に押接して正常な運
転を継続することができる。このように、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る効果を奏する。Effects of the Invention As is clear from the above description, the present invention has a valve body disposed in the suction passage of a vane rotary compressor to allow flow from the outside of the compressor into the compressor and prevent reverse flow. , a valve holding body in which the valve body is slidably held through a minute gap, and a spring that urges the valve body to block the suction passage within a space formed by the valve body and the valve holding body. This prevents the force acting on the tip of the vane from forcing the vane into the vane slot even if the compressor is started when the compressor has stopped for a long time and there is no or small pressure difference between the high and low pressures of the compressor. It is extremely small and the vane can be reliably pressed against the inner wall of the cylinder. Furthermore, after a certain period of time has passed after startup, the pressure in the space formed by the valve body and the valve holding body decreases, and the valve body gradually tries to communicate with the suction passage.
The pressure in the working chamber on the suction side also gradually increases, and the force acting on the tip of the vane does not suddenly increase, making it possible to press the vane against the inner wall of the cylinder and continue normal operation. In this way, even when the compressor is started at a low rotation speed when there is no or a small pressure difference between the high and low pressures of the compressor, it is possible to prevent vane malfunction and poor compression.
第１図は従来のベーン回転式圧縮機の縦断面
図、第２図は同圧縮機において前部側板をはずし
た平面図、第３図は本発明の一実施例の吸入逆流
防止装置を具備したベーン回転式圧縮機の縦断面
図、第４図は第３図のＹ―Ｙ線による要部拡大断
面図である。
１……シリンダ、２……ロータ、３……ベー
ン、４……ベーンスロツト、５……駆動軸、６…
…前部側板、７……後部側板、８……作動室、１
９……吸入通路、２３……弁体、２４……弁保持
体、２５……微小隙間、２９……ばね。
Fig. 1 is a longitudinal sectional view of a conventional vane rotary compressor, Fig. 2 is a plan view of the same compressor with the front side plate removed, and Fig. 3 is a diagram showing a suction backflow prevention device according to an embodiment of the present invention. FIG. 4 is an enlarged sectional view of the main part taken along the line Y--Y in FIG. 3. 1... Cylinder, 2... Rotor, 3... Vane, 4... Vane slot, 5... Drive shaft, 6...
...Front side plate, 7...Rear side plate, 8...Working chamber, 1
9...Suction passage, 23...Valve body, 24...Valve holding body, 25...Minute gap, 29...Spring.
Claims (1)
の内部に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ツ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
する吸入通路および吐出通路とから成るベーン回
転式圧縮機を構成し、圧縮機の外部より圧縮機内
への流れを許容し逆流を防止する如く吸入通路に
配設される弁体と、弁体が微小隙間を介して摺動
自在に保持される弁保持体と、弁体および弁保持
体で形成される空間内に前記弁体が吸入通路を遮
断するよう付勢するばねとを設けたベーン回転式
圧縮機の吸入逆流防止装置。1. 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 formed integrally with the rotor and rotatably supported; a front side plate and a rear side plate that close both ends of the cylinder to form an operating chamber therein; and an outer periphery of the rotor. A vane rotary compressor consists of a suction passage and a discharge passage that communicate with the working chamber across the adjacent inner cylinder wall, allowing flow into the compressor from outside the compressor and preventing backflow. a valve body disposed in the suction passage so as to prevent the valve body from sliding, a valve holder in which the valve body is slidably held through a minute gap, and the valve body in a space formed by the valve body and the valve holder. A suction backflow prevention device for a vane rotary compressor, which is equipped with a spring that urges the air to block the suction passage.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP25092383A JPS60142082A (en) | 1983-12-28 | 1983-12-28 | Suction counterflow preventing device in vane type rotary compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP25092383A JPS60142082A (en) | 1983-12-28 | 1983-12-28 | Suction counterflow preventing device in vane type rotary compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS60142082A JPS60142082A (en) | 1985-07-27 |
| JPS6360235B2 true JPS6360235B2 (en) | 1988-11-22 |
Family
ID=17215030
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP25092383A Granted JPS60142082A (en) | 1983-12-28 | 1983-12-28 | Suction counterflow preventing device in vane type rotary compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS60142082A (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2000346241A (en) | 1999-06-07 | 2000-12-15 | Toyota Autom Loom Works Ltd | Check valve |
| WO2023074389A1 (en) * | 2021-10-28 | 2023-05-04 | ダイキン工業株式会社 | Scroll compressor and refrigeration device |
-
1983
- 1983-12-28 JP JP25092383A patent/JPS60142082A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS60142082A (en) | 1985-07-27 |
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| Date | Code | Title | Description |
|---|---|---|---|
| EXPY | Cancellation because of completion of term |