JP3027930B2 - Scroll gas compressor - Google Patents

Scroll gas compressor

Info

Publication number
JP3027930B2
JP3027930B2 JP8026393A JP2639396A JP3027930B2 JP 3027930 B2 JP3027930 B2 JP 3027930B2 JP 8026393 A JP8026393 A JP 8026393A JP 2639396 A JP2639396 A JP 2639396A JP 3027930 B2 JP3027930 B2 JP 3027930B2
Authority
JP
Japan
Prior art keywords
bypass
compression
chamber
scroll
discharge
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
JP8026393A
Other languages
Japanese (ja)
Other versions
JPH09217689A (en
Inventor
勝晴 藤尾
定幸 山田
敬 森本
昭三 長谷
博正 芦谷
修一 山本
澤井  清
Original Assignee
松下電器産業株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 松下電器産業株式会社 filed Critical 松下電器産業株式会社
Priority to JP8026393A priority Critical patent/JP3027930B2/en
Priority claimed from US08/761,085 external-priority patent/US5855475A/en
Publication of JPH09217689A publication Critical patent/JPH09217689A/en
Application granted granted Critical
Publication of JP3027930B2 publication Critical patent/JP3027930B2/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F04C29/124Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
    • F04C29/126Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps of the non-return type

Description

【発明の詳細な説明】DETAILED DESCRIPTION OF THE INVENTION

【0001】[0001]

【発明の属する技術分野】本発明はスクロール気体圧縮
機のバイパス弁の配置に関するものである。
BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an arrangement of a bypass valve of a scroll gas compressor.

【0002】[0002]

【従来の技術】低振動、低騒音特性を備えたスクロール
気体圧縮機は、吸入室が圧縮空間を形成する渦巻きの外
周部に有り、吐出口が渦巻きの中心部に設けられ、吸入
容積と最終圧縮室容積とで決定する圧縮比が一定であ
る。特に、吸入圧力と吐出圧力とで定まる圧縮比の変動
が少ない場合は、それに合わせた容積比を設定すること
によって、往復動圧縮機や回転式圧縮機のような流体を
圧縮するための吐出弁装置を必要とせず、高効率な圧縮
ができる。
2. Description of the Related Art In a scroll gas compressor having low vibration and low noise characteristics, a suction chamber is provided at an outer peripheral portion of a spiral forming a compression space, a discharge port is provided at a central portion of the spiral, and a suction volume and a final volume are reduced. The compression ratio determined by the compression chamber volume is constant. In particular, when the fluctuation of the compression ratio determined by the suction pressure and the discharge pressure is small, a discharge valve for compressing a fluid such as a reciprocating compressor or a rotary compressor by setting a volume ratio corresponding to the fluctuation. Highly efficient compression is possible without the need for a device.

【0003】このスクロール気体圧縮機を空調用冷媒圧
縮機として使用する場合は、可変速運転や空調負荷変動
によって冷媒の吸入圧力と吐出圧力が変化する。そし
て、実際の圧縮比と設定圧縮比との間の差によって、不
足圧縮や過圧縮運転が生じる。不足圧縮時には、吐出室
の高圧冷媒ガスが吐出口から圧縮室に間欠的に逆流し、
圧縮入力の増加を招く。また、液冷媒や多量の潤滑油を
圧縮する、いわゆる液圧縮現象が生じた場合には、超過
圧縮状態となり、圧縮入力の異常上昇、過大な振動と騒
音、圧縮機破損を招くことがある。
When this scroll gas compressor is used as a refrigerant compressor for air conditioning, the suction pressure and discharge pressure of the refrigerant change due to variable speed operation and fluctuations in air conditioning load. The difference between the actual compression ratio and the set compression ratio causes under-compression or over-compression operation. During insufficient compression, the high-pressure refrigerant gas in the discharge chamber intermittently flows back from the discharge port to the compression chamber,
This leads to an increase in compression input. In addition, when a so-called liquid compression phenomenon occurs in which a liquid refrigerant or a large amount of lubricating oil is compressed, an excessive compression state occurs, which may cause an abnormal increase in compression input, excessive vibration and noise, and damage to the compressor.

【0004】このような圧縮不足に起因する圧縮流体の
逆流を防ぐ方策として、吐出口の出口側に逆止弁装置を
設けることもある。また、過圧縮を軽減する方策とし
て、特公平5−49830号公報に記載されているよう
に、吸入室にも吐出口にも間欠的に通じない常時密閉空
間となる圧縮室を有する場合には、超過圧縮発生頻度の
高い常時密閉空間となる圧縮室から吐出室に通じる対称
位置に配置されたバイパス穴を設け、バイパス穴の出口
側に吐出室への流体流出のみを許容するバイパス弁装置
を設けて液圧縮や過圧縮に起因する圧縮機破損を防止す
る手段が知られている。
As a measure for preventing the backflow of the compressed fluid due to the insufficient compression, a check valve device may be provided at the outlet side of the discharge port. Further, as a measure to reduce over-compression, as described in Japanese Patent Publication No. 5-49830, when a compression chamber is provided which is always a closed space that does not intermittently communicate with both the suction chamber and the discharge port. The bypass valve device is provided with a bypass hole arranged at a symmetrical position communicating from the compression chamber, which is a normally closed space with a high frequency of excessive compression, to the discharge chamber, and allows only fluid outflow to the discharge chamber at the outlet side of the bypass hole. Means are provided to prevent compressor damage due to liquid compression or overcompression.

【0005】[0005]

【発明が解決しようとする課題】しかしながら、上記従
来の構成では、超過圧縮となる液圧縮や通常の過圧縮は
上述の常時密閉空間に限らず、圧縮途中の任意の圧縮室
でも生じる可能性がある。
However, in the above-described conventional configuration, the liquid compression or the normal over-compression that causes over-compression may not only occur in the above-mentioned constantly closed space but also in any compression chamber during compression. is there.

【0006】特に、家庭空調用冷媒圧縮機は容積比が小
さく、上述の常時密閉空間は存在せず、逆止弁装置を設
けて圧縮不足運転時の逆流防止を図ると共に、空調負荷
変動によって生じる過圧縮防止を有効的に作用させるた
めに、バイパス穴を吐出口と間欠的に通じる圧縮室に開
設する手段が検討されている。
In particular, the refrigerant compressor for home air-conditioning has a small volume ratio, does not have the above-mentioned closed space, and is provided with a check valve device to prevent a backflow at the time of insufficient compression operation, and is caused by a change in air-conditioning load. In order to effectively prevent over-compression, means for opening a bypass hole in a compression chamber intermittently communicating with the discharge port has been studied.

【0007】この複合構成の場合は、吐出口とバイパス
穴とが接近するために、逆止弁装置とバイパス弁とが干
渉し合うという課題がある。
In the case of this composite structure, there is a problem that the check valve device and the bypass valve interfere with each other because the discharge port and the bypass hole approach each other.

【0008】この課題を解決するために、吐出口への逆
止弁装置およびバイパス穴へのバイパス弁の塞ぎ代を少
なくする必要が生じる。
In order to solve this problem, it is necessary to reduce the amount of blocking of the check valve to the discharge port and the bypass valve to the bypass hole.

【0009】その結果、逆止弁装置とバイパス弁をそれ
ぞれ固定スクロールに組み付ける際の位置ずれによっ
て、吐出口とバイパス穴に対する逆止弁装置とバイパス
弁の閉塞機能が低下するという課題があった。また、逆
止弁装置が開閉する際の吐出気体の拡散によって、バイ
パス弁の閉塞機能が低下する課題もあった。
As a result, there has been a problem that the closing function of the check valve device and the bypass valve with respect to the discharge port and the bypass hole is reduced due to a positional shift when the check valve device and the bypass valve are respectively assembled to the fixed scroll. There is also a problem that the closing function of the bypass valve is reduced due to diffusion of the discharged gas when the check valve device opens and closes.

【0010】本発明はこのような従来の課題を解決する
ものであり、逆止弁装置とバイパス弁を固定スクロール
に組み付ける際の位置決め精度を改善して逆止弁装置と
バイパス弁の閉塞機能低下の防止を図ることを目的とす
る。
The present invention solves such a conventional problem, and improves the positioning accuracy when assembling the check valve device and the bypass valve to the fixed scroll to reduce the closing function of the check valve device and the bypass valve. The purpose is to prevent the occurrence of.

【0011】[0011]

【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、吐出口を開閉する逆止弁装置と、吐出口に
最も近い圧縮室に開設したバイパス穴を開閉し且つ逆止
弁装置に接近したバイパス弁とを一体的に連結したもの
である。逆止弁装置よりも小さいバネ定数を有して変形
し易いバイパス弁は、剛性の高い逆止弁装置に連結され
てバイパス穴とのズレがなくなり、バイパス穴の閉塞機
能を高めることができる。
SUMMARY OF THE INVENTION In order to solve the above problems, the present invention provides a check valve device for opening and closing a discharge port, and a check valve for opening and closing a bypass hole formed in a compression chamber closest to the discharge port. A bypass valve close to the device is integrally connected. The bypass valve having a spring constant smaller than that of the check valve device and being easily deformed is connected to the check valve device having high rigidity so that there is no deviation from the bypass hole, and the function of closing the bypass hole can be enhanced.

【0012】[0012]

【発明の実施の形態】上記の課題を解決するための請求
項1記載の発明は、吐出口から吐出室へのみの流体流れ
を許容し且つ吐出口の出口側を開閉するリード弁形の逆
止弁装置を固定スクロールの鏡板に配置し、吐出口に最
も近い圧縮途中の圧縮室に開口し且つ他端が吐出室に通
じる一対以上のバイパス穴を鏡板に対称配置すると共
に、バイパス穴を介して圧縮室から吐出室へのみの流体
排出を許容し且つバイパス穴の出口側を開閉するリード
弁形のバイパス弁を逆止弁装置に接近して鏡板に設けた
構成で、バイパス弁のバネ定数を逆止弁装置よりも小さ
く設定し、バイパス弁と逆止弁装置とを一体的に連結し
たものである。
BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a perspective view of a reed valve type in which fluid is allowed to flow only from a discharge port to a discharge chamber and the outlet side of the discharge port is opened and closed. The stop valve device is arranged on the end plate of the fixed scroll, and a pair of or more bypass holes which open to the compression chamber in the middle of compression closest to the discharge port and whose other end communicates with the discharge chamber are symmetrically arranged on the end plate, and through the bypass hole. A reed valve type bypass valve that allows fluid discharge only from the compression chamber to the discharge chamber and opens and closes the outlet side of the bypass hole is provided on the end plate close to the check valve device, and the spring constant of the bypass valve Is set smaller than the check valve device, and the bypass valve and the check valve device are integrally connected.

【0013】そして、この構成によれば剛性の高い逆止
弁装置に支えられたバイパス弁が、変形と位置ズレを生
じることなくバイパス穴を閉塞し、バイパス作用を発揮
する。また、逆止弁装置とバイパス弁の取り付け時間短
縮によって、逆止弁装置とバイパス弁の取り付け位置精
度向上に作業時間を付与することができる。
[0013] According to this configuration, the bypass valve supported by the check valve device having high rigidity closes the bypass hole without causing deformation and displacement, and exhibits a bypass effect. In addition, by shortening the time required for mounting the check valve device and the bypass valve, it is possible to provide working time for improving the mounting position accuracy of the check valve device and the bypass valve.

【0014】請求項2記載の発明は、リード弁形の逆止
弁装置とリード弁形のバイパス弁を同じ方向に配列した
ものである。そして、この構成によれば逆止弁装置とバ
イパス弁を省スペースに配置構成することができる。
According to a second aspect of the present invention, the check valve device of the reed valve type and the bypass valve of the reed valve type are arranged in the same direction. According to this configuration, the check valve device and the bypass valve can be arranged and configured in a space-saving manner.

【0015】請求項3記載の発明は、吐出口から吐出室
へのみの流体流れを許容し且つ吐出口の出口側を開閉す
るリード弁形の逆止弁装置を固定スクロールの鏡板に配
置し、吐出口に最も近い圧縮途中の圧縮室に開口し且つ
他端が吐出室に通じる一対以上のバイパス穴を鏡板に対
称配置すると共に、バイパス穴を介して圧縮室から吐出
室へのみの流体排出を許容し且つバイパス穴の出口側を
開閉するリード弁形のバイパス弁を逆止弁装置に接近さ
せて鏡板に設けた構成で、逆止弁装置の吐出弁座をバイ
パス弁のバイパス弁座より高く配置したものである。
According to a third aspect of the present invention, there is provided a reed valve type check valve device which permits fluid flow only from the discharge port to the discharge chamber and opens and closes the outlet side of the discharge port on the end plate of the fixed scroll. A pair of at least one bypass hole that opens to the compression chamber in the middle of compression closest to the discharge port and the other end communicates with the discharge chamber is symmetrically arranged on the end plate, and fluid is discharged only from the compression chamber to the discharge chamber through the bypass hole. A configuration in which a reed valve type bypass valve that allows and opens and closes the outlet side of the bypass hole is provided on the end plate close to the check valve device, and the discharge valve seat of the check valve device is higher than the bypass valve seat of the bypass valve It is arranged.

【0016】そして、この構成によれば吐出口から流出
する圧縮気体流れの拡散作用によってバイパス弁が微小
浮上することなく、バイパス穴の閉塞機能を継続するこ
とができる。
According to this configuration, the function of diffusing the compressed gas flowing out of the discharge port does not cause the bypass valve to slightly float, and the function of closing the bypass hole can be continued.

【0017】請求項4記載の発明は、対称位置に配置さ
れたバイパス穴を開閉する複数のバイパス弁を一体的に
連結し、逆止弁装置の吐出弁座に接近して囲む形態で複
数のバイパス弁を配置したものである。そして、この構
成によれば吐出弁座の側壁によってバイパス弁が位置規
制され、バイパス穴からの位置ズレをなくすることがで
きる。
According to a fourth aspect of the present invention, a plurality of bypass valves for opening and closing bypass holes arranged at symmetrical positions are integrally connected, and a plurality of bypass valves are formed so as to approach and surround a discharge valve seat of a check valve device. This is one in which a bypass valve is arranged. According to this configuration, the position of the bypass valve is regulated by the side wall of the discharge valve seat, and the displacement from the bypass hole can be eliminated.

【0018】請求項5記載の発明は、同一の圧縮室に開
口した複数のバイパス穴を単一のバイパス弁が同時に開
閉する構成において、互いに同機能を有する両方のバイ
パス弁がバイパス穴を同時に開閉すべく、両バイパス弁
のバネ定数を相違させたものである。
According to a fifth aspect of the present invention, in a configuration in which a single bypass valve simultaneously opens and closes a plurality of bypass holes opened in the same compression chamber, both bypass valves having the same function mutually open and close the bypass holes simultaneously. For this reason, the spring constants of the two bypass valves are different.

【0019】そして、この構成によれば圧縮途中気体が
バイパス穴を通じて流出する際に、各バイパス弁に作用
する気体圧力の作用点が異なるが、バネ定数の調整設定
によって、バイパス弁の全開時期がほぼ同時になり、2
つの圧縮空間の圧力分布を同じにすることができる。
According to this configuration, when the gas in the course of compression flows out through the bypass hole, the point of action of the gas pressure acting on each bypass valve is different, but the fully open timing of the bypass valve depends on the adjustment setting of the spring constant. Almost at the same time, 2
The pressure distribution in the two compression spaces can be the same.

【0020】[0020]

【実施例】以下、本発明の実施例の横置形スクロール気
体圧縮機について、図面を参照して説明する。
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A horizontal scroll gas compressor according to an embodiment of the present invention will be described below with reference to the drawings.

【0021】(実施例1)図1において、1は鉄製の密
閉容器で、その内部全体は吐出管(図示なし)に連通す
る高圧雰囲気となり、その中央部にモータ3、右部に圧
縮部が配置され、モータ3の回転子3aを固定した駆動
軸4の一端を支承する圧縮部の本体フレーム5が密閉容
器1に固定されており、その本体フレーム5に固定スク
ロール7が取り付けられている。駆動軸4に設けられた
主軸方向の油穴12は、その一端が給油ポンプ装置(図
示なし)に通じ、他端が最終的に主軸受8に通じてい
る。固定スクロール7と噛み合って圧縮室2を形成する
旋回スクロール13は、渦巻き状の旋回スクロールラッ
プ13aと旋回軸13cとを直立させたラップ支持円板
13bとから成り、固定スクロール7と本体フレーム5
との間に配置されている。
(Embodiment 1) In FIG. 1, reference numeral 1 denotes a closed container made of iron, the entire inside of which is a high-pressure atmosphere communicating with a discharge pipe (not shown), and a motor 3 is provided at the center and a compression section is provided at the right. A main body frame 5 of a compression unit that is arranged and supports one end of a drive shaft 4 to which a rotor 3a of the motor 3 is fixed is fixed to the closed casing 1, and a fixed scroll 7 is attached to the main body frame 5. One end of the main shaft direction oil hole 12 provided in the drive shaft 4 communicates with an oil supply pump device (not shown), and the other end finally communicates with the main bearing 8. The orbiting scroll 13 meshing with the fixed scroll 7 to form the compression chamber 2 is composed of a spiral orbiting scroll wrap 13a and a wrap supporting disk 13b with an orbiting shaft 13c standing upright.
And is located between.

【0022】また、前述の実開昭62−26591号公
報でも開示されているような、渦巻き状溝が旋回スクロ
ールラップ13aの先端に設けられている。この渦巻き
状溝と同形状をした渦巻き状のシール部材13eが渦巻
き状溝内に油膜形成ができる程度の微小隙間を有して遊
合状態で配置されている。
Further, a spiral groove is provided at the tip of the orbiting scroll wrap 13a as disclosed in the aforementioned Japanese Utility Model Application Laid-Open No. 62-26591. A spiral seal member 13e having the same shape as the spiral groove is arranged in a loose state with a small gap in the spiral groove so that an oil film can be formed.

【0023】固定スクロール7は、鏡板7aと渦巻き状
の固定スクロールラップ7bとから成り、固定スクロー
ルラップ7bの中央部に吐出口30、外周部に吸入室3
1が配置されている。吐出口30は、隣接する吐出室3
2を介してモータ3が配置された高圧空間に通じてい
る。吸入室31は、密閉容器1の端壁を貫通する吸入管
33に通じている。
The fixed scroll 7 comprises a head plate 7a and a spiral fixed scroll wrap 7b. The fixed scroll wrap 7b has a discharge port 30 at the center and a suction chamber 3 at the outer periphery.
1 is arranged. The discharge port 30 is connected to the adjacent discharge chamber 3
2 leads to a high-pressure space in which the motor 3 is arranged. The suction chamber 31 communicates with a suction pipe 33 that penetrates the end wall of the closed container 1.

【0024】駆動軸4の主軸から偏芯して駆動軸4の右
端穴部に配置された旋回軸受14は、旋回スクロール1
3の旋回軸13cと係合摺動すべく構成されている。旋
回スクロール13のラップ支持円板13bと本体フレー
ム5に設けられたスラスト軸受19との間は、油膜形成
可能な微小隙間が設けられている。
The orbiting bearing 14 eccentric from the main shaft of the drive shaft 4 and disposed in the right end hole of the drive shaft 4
3 and is configured to engage and slide with the turning shaft 13c. Between the lap support disk 13b of the orbiting scroll 13 and the thrust bearing 19 provided on the main body frame 5, there is provided a minute gap capable of forming an oil film.

【0025】ラップ支持円板13bには旋回軸13cと
ほぼ同芯の環状シール部材18が遊合状態で装着されて
おり、その環状シール部材18はその内側の背面室A2
0と外側とを仕切っている。背面室A20の上流側と下
流側は旋回軸受14の摺動面と駆動軸4の油穴12およ
び主軸受8を介して油溜11に通じている。
An annular seal member 18 which is substantially concentric with the pivot shaft 13c is mounted on the lap support disk 13b in a loose state, and the annular seal member 18 is attached to the inner rear chamber A2.
It separates 0 from the outside. The upstream side and the downstream side of the rear chamber A20 communicate with the oil sump 11 via the sliding surface of the swing bearing 14, the oil hole 12 of the drive shaft 4, and the main bearing 8.

【0026】旋回軸受14の底部の油室15と、ラップ
支持円板13bの外周部空間の背面室C16との間は、
ラップ支持円板13bに設けられた油通路21を介して
通じている。油通路21は、その両端に絞り部A22と
絞り部B23を、その中間にバイパス油穴24を有して
いる。バイパス油穴24は、旋回スクロール13の旋回
運動に伴って、スラスト軸受19面に設けられた環状の
油溝25に間欠的に通じるべく配置されている。
The space between the oil chamber 15 at the bottom of the slewing bearing 14 and the rear chamber C16 in the outer peripheral space of the lap support disk 13b is
It communicates through an oil passage 21 provided in the lap support disk 13b. The oil passage 21 has a narrowed portion A22 and a narrowed portion B23 at both ends thereof, and a bypass oil hole 24 in the middle. The bypass oil hole 24 is arranged to intermittently communicate with an annular oil groove 25 provided on the thrust bearing 19 surface in accordance with the turning movement of the turning scroll 13.

【0027】環状の油溝25と背面室C16とは、環状
の油溝25の一部として設けられた排出油通路26を介
して通じている。スラスト軸受19の環状の油溝25
は、自転阻止部材27と係合する旋回スクロール13の
係止溝(図示なし)にも間欠的に連通すべく配置されて
いる。背面室C16と吸入室31との間は、ラップ支持
円板13bと摺接する鏡板7aの表面に設けられた油溝
50(図2参照)を介して連通している。
The annular oil groove 25 and the rear chamber C16 communicate with each other via a drain oil passage 26 provided as a part of the annular oil groove 25. Annular oil groove 25 of thrust bearing 19
Is arranged to intermittently communicate with a locking groove (not shown) of the orbiting scroll 13 which engages with the rotation preventing member 27. The rear chamber C16 and the suction chamber 31 communicate with each other via an oil groove 50 (see FIG. 2) provided on the surface of the end plate 7a which is in sliding contact with the lap support disk 13b.

【0028】吐出口30の出口側を開閉する逆止弁装置
35が固定スクロール7の鏡板7aの平面上に取り付け
られており、その逆止弁装置35は薄鋼板製のリード弁
35aと弁押え35bとから成る。鏡板7aの中央部に
は、吐出口30と間欠的に連通する第2圧縮室2bと吐
出室32とに開口し、且つ、第2圧縮室2bへの開口部
が旋回スクロールラップ13aの先端部に配置されたシ
ール部材13eの幅Wよりも小径のバイパス穴39が吐
出口30に対して対称配置されている。
A check valve device 35 for opening and closing the outlet side of the discharge port 30 is mounted on the plane of the end plate 7a of the fixed scroll 7, and the check valve device 35 includes a reed valve 35a made of a thin steel plate and a valve retainer. 35b. At the center of the end plate 7a, the second compression chamber 2b and the discharge chamber 32 that intermittently communicate with the discharge port 30 are opened, and the opening to the second compression chamber 2b is formed at the tip of the orbiting scroll wrap 13a. The bypass hole 39 having a smaller diameter than the width W of the seal member 13e disposed symmetrically with respect to the discharge port 30 is disposed.

【0029】バイパス穴39は、一対の第1バイパス穴
39aと一対の第2バイパス穴39bから成り、旋回ス
クロールラップ13aの壁面に沿って圧縮進行に追従す
る形態で順次対称配置されている。第1バイパス穴39
a,第2バイパス穴39bはシール部材13eによって
同時に全閉塞されないように、適正間隔で配置されてい
る。
The bypass holes 39 are composed of a pair of first bypass holes 39a and a pair of second bypass holes 39b, and are sequentially symmetrically arranged along the wall surface of the orbiting scroll wrap 13a so as to follow the progress of compression. First bypass hole 39
a, the second bypass holes 39b are arranged at appropriate intervals so as not to be completely closed at the same time by the seal member 13e.

【0030】一対のバイパス穴39の出口側を開閉する
リード形のバイパス弁40が鏡板7aに取り付けられて
いる。バイパス弁40は、逆止弁装置35と同様に薄鋼
板製のリード弁40aと弁押え40bとから成る。
A lead-type bypass valve 40 for opening and closing the outlet side of the pair of bypass holes 39 is attached to the end plate 7a. The bypass valve 40 includes a reed valve 40a made of a thin steel plate and a valve presser 40b, like the check valve device 35.

【0031】図2は図1におけるA−A線に沿った断面
を示した図で、吐出口30と間欠的に連通する第2圧縮
室2bが吐出口30と開通した直後の圧縮空間の状態を
示す。
FIG. 2 is a cross-sectional view taken along the line AA in FIG. 1. The state of the compression space immediately after the second compression chamber 2b intermittently communicating with the discharge port 30 is opened with the discharge port 30. Is shown.

【0032】この圧縮空間の容積比、すなわち、圧縮室
2の吸入容積と圧縮完了時の圧縮室容積との割合が、圧
縮機定格負荷時の吸入室31の圧力と吐出室32の圧力
との割合、すなわち、運転圧縮比に相当する容積比に最
も近づくように設定されており、定格負荷運転時に過不
足圧縮の少ない渦巻き形状の圧縮空間に設定されてい
る。
The volume ratio of the compression space, that is, the ratio between the suction volume of the compression chamber 2 and the volume of the compression chamber at the time of completion of compression, is determined by the pressure of the suction chamber 31 and the pressure of the discharge chamber 32 at the rated load of the compressor. It is set so as to be closest to the ratio, that is, the volume ratio corresponding to the operation compression ratio, and is set in a spiral compression space with little over / under compression during rated load operation.

【0033】この状態で、第1バイパス穴39a,第2
バイパス穴39bは旋回スクロールラップ13aによっ
て、遮閉されることのない位置に配置されている。
In this state, the first bypass hole 39a and the second bypass hole 39a
The bypass hole 39b is arranged at a position that is not blocked by the orbiting scroll wrap 13a.

【0034】また、第1バイパス穴39a,第2バイパ
ス穴39bは、第2圧縮室2bが図2の状態から進角ま
たは退角した状態でも旋回スクロールラップ13aによ
って、同時に遮閉されることがないような形状と間隔で
配置されている。
The first bypass hole 39a and the second bypass hole 39b can be simultaneously closed and closed by the orbiting scroll wrap 13a even when the second compression chamber 2b is advanced or retracted from the state shown in FIG. They are arranged with no shape and spacing.

【0035】また、鏡板7aには、吸入室31と間欠的
に連通する第1圧縮室2aと吐出室32とに開口する一
対の補助バイパス穴49が対称配置されていると共に、
補助バイパス穴49の出口側を開閉する補助バイパス弁
装置42が取り付けられている。
A pair of auxiliary bypass holes 49 opened to the first compression chamber 2a and the discharge chamber 32 intermittently communicating with the suction chamber 31 are symmetrically arranged in the head plate 7a.
An auxiliary bypass valve device 42 for opening and closing the outlet side of the auxiliary bypass hole 49 is attached.

【0036】補助バイパス弁装置42は、薄鋼板製のリ
ード弁42aと弁押え42bとから成る。
The auxiliary bypass valve device 42 comprises a reed valve 42a made of a thin steel plate and a valve retainer 42b.

【0037】図3に示す如く、逆止弁装置35とバイパ
ス弁40と補助バイパス弁装置42は、同じ方向に配列
されて一体的に連結されて鏡板7aにボルト固定されて
いる。
As shown in FIG. 3, the check valve device 35, the bypass valve 40, and the auxiliary bypass valve device 42 are arranged in the same direction, are integrally connected, and are fixed to the end plate 7a by bolts.

【0038】バイパス穴39が吐出口30の近傍に配置
されているので、逆止弁装置35とバイパス弁40とは
接近状態で配置されている。一対のバイパス弁40が同
じ方向に配列されているために、一対のバイパス弁40
に対して、吐出口30に近い側の第2バイパス穴39b
と吐出口30から離れた第1バイパス穴39aとから排
出した気体圧力の作用点が互いに入れ替わっている。
Since the bypass hole 39 is arranged near the discharge port 30, the check valve device 35 and the bypass valve 40 are arranged close to each other. Since the pair of bypass valves 40 are arranged in the same direction, the pair of bypass valves 40
The second bypass hole 39b on the side close to the discharge port 30
And the point of action of the gas pressure discharged from the first bypass hole 39a distant from the discharge port 30 is interchanged.

【0039】したがって、一対のバイパス弁40がほぼ
同時期に全開口できるように、各リード弁40aのスパ
ン11 ,12 と幅W1 ,W2 を変えてバネ定数がほぼ同
様になるべく設定されている。吐出口30と比較してバ
イパス穴39が小径のために、バイパス弁を開口させ易
いように、バイパス弁のバネ定数は逆止弁よりも小さく
設定されている。
Therefore, the spans 1 1 and 1 2 and the widths W 1 and W 2 of each reed valve 40a are changed so that the spring constants become almost the same so that the pair of bypass valves 40 can be fully opened almost at the same time. Have been. The spring constant of the bypass valve is set smaller than that of the check valve so that the bypass valve can be easily opened because the diameter of the bypass hole 39 is smaller than that of the discharge port 30.

【0040】図5は、横軸に圧縮機運転速度を、縦軸に
圧力と圧縮比を表し、空調装置運転時の圧縮機運転速度
と吸入圧力,吐出圧力,圧縮比の関係を示す実負荷特性
図である。図6は、横軸に圧縮室の容積変化を、縦軸に
圧縮室の圧力変化を表した従来スクロール圧縮機のP−
V線図(指圧線図)である。
FIG. 5 shows the compressor operating speed on the horizontal axis, and the pressure and compression ratio on the vertical axis, and shows the relationship between the compressor operating speed and the suction pressure, discharge pressure, and compression ratio when the air conditioner is operating. It is a characteristic diagram. FIG. 6 is a graph showing the change in the volume of the compression chamber on the horizontal axis and the change in pressure in the compression chamber on the vertical axis.
It is a V diagram (acupressure diagram).

【0041】以上のように構成されたスクロール気体圧
縮機について、その動作を説明する。図1〜図5におい
て、モータ3によって駆動軸4が回転駆動すると本体フ
レーム5のスラスト軸受19に支持された旋回スクロー
ル13が旋回運動をし、圧縮機に接続した冷凍サイクル
から潤滑油を含んだ吸入冷媒ガスが、吸入管33を経由
して吸入室31に流入し、旋回スクロール13と固定ス
クロール7との間に形成された圧縮室2へと圧縮移送さ
れ、中央部の吐出口30,吐出室32を経てモータ3を
冷却しながら吐出管(図示なし)から圧縮機外部に排出
される。
The operation of the scroll gas compressor configured as described above will be described. 1 to 5, when the drive shaft 4 is rotationally driven by the motor 3, the orbiting scroll 13 supported by the thrust bearing 19 of the main body frame 5 orbits, and contains lubricating oil from a refrigeration cycle connected to the compressor. The suction refrigerant gas flows into the suction chamber 31 via the suction pipe 33, is compressed and transferred to the compression chamber 2 formed between the orbiting scroll 13 and the fixed scroll 7, and is discharged from the central discharge port 30, While being cooled through the chamber 32, the motor 3 is discharged to the outside of the compressor from a discharge pipe (not shown).

【0042】潤滑油を含んだ吐出冷媒ガスは、吐出室3
2から吐出管(図示なし)までの通路途中で分離され、
油溜11に収集する。吐出圧力が作用する油溜11の潤
滑油は、駆動軸4の一端に連結された給油ポンプ装置
(図示なし)により、駆動軸4の油穴12を経由して油
室15に送られ、その大部分が主軸受8を経由して油溜
11に帰還する一方、残りの潤滑油が旋回スクロール1
3に設けられた油通路21を経由して最終的に背面室C
16に流入する。
The discharge refrigerant gas containing the lubricating oil is supplied to the discharge chamber 3
2 is separated in the middle of the passage from the discharge pipe (not shown),
Collect in oil sump 11. The lubricating oil in the oil reservoir 11 to which the discharge pressure acts is sent to an oil chamber 15 via an oil hole 12 of the drive shaft 4 by an oil supply pump device (not shown) connected to one end of the drive shaft 4. Most of the lubricating oil returns to the oil sump 11 via the main bearing 8 while the remaining lubricating oil is
3 finally through the oil passage 21 provided in the rear chamber C
Flow into 16.

【0043】油通路21を流れる潤滑油は、その入口部
の絞り部A22で一次減圧され、その一部の潤滑油がバ
イパス油穴24を通じてスラスト軸受19に設けられた
環状の油溝25に流入し、残りの潤滑油が絞り部B23
で二次減圧された後、両経路を経た潤滑油は吸入室31
に通じている背面室C16に流入する。
The lubricating oil flowing through the oil passage 21 is firstly depressurized at the throttle portion A22 at the inlet, and a part of the lubricating oil flows into the annular oil groove 25 provided in the thrust bearing 19 through the bypass oil hole 24. Then, the remaining lubricating oil is
After the secondary decompression in the lubricating oil passing through both paths,
Flows into the rear room C16 which leads to.

【0044】油通路21の潤滑油は、旋回スクロール1
3の旋回運動に伴ってバイパス油穴24が環状の油溝2
5に間欠的に連通する際の通路抵抗の影響を受ける。す
なわち、旋回速度が遅い時には油通路21の潤滑油が環
状の油溝25に多く流入し、旋回速度が速い時には油通
路21の潤滑油が環状の油溝25に少なく流入するよう
に調整される。圧縮室2の冷媒ガス圧力は、駆動軸4の
主軸方向に旋回スクロール13を固定スクロール7から
離反させようと作用する。
The lubricating oil in the oil passage 21 is supplied to the orbiting scroll 1
3, the bypass oil hole 24 is formed into an annular oil groove 2
5 intermittently communicates with the passage resistance. That is, when the turning speed is low, the lubricating oil in the oil passage 21 flows into the annular oil groove 25 more, and when the turning speed is high, the lubricating oil in the oil passage 21 flows into the annular oil groove 25 less. . The refrigerant gas pressure in the compression chamber 2 acts to move the orbiting scroll 13 away from the fixed scroll 7 in the main axis direction of the drive shaft 4.

【0045】一方、旋回スクロール13のラップ支持円
板13bが吐出圧力の作用する背面室A20(環状シー
ル部材18で囲まれた内側部分)からの背圧を受けてい
る。したがって、旋回スクロール13を固定スクロール
7から離反させようとする力と背圧力とが相殺される。
On the other hand, the lap support disk 13b of the orbiting scroll 13 receives a back pressure from the back chamber A20 (the inner part surrounded by the annular seal member 18) where the discharge pressure acts. Therefore, the force for moving the orbiting scroll 13 away from the fixed scroll 7 and the back pressure are offset.

【0046】その結果、旋回スクロール13の離反力よ
りも背圧力が大きい場合には、ラップ支持円板13bは
固定スクロール7の鏡板7aに支持され、反対の場合に
はスラスト軸受19に支持される。
As a result, when the back pressure is larger than the repulsive force of the orbiting scroll 13, the lap support disk 13b is supported by the end plate 7a of the fixed scroll 7, and in the opposite case, the lap support disk 13b is supported by the thrust bearing 19. .

【0047】上述のいずれの場合にもラップ支持円板1
3bとその摺動面の間は微小隙間が保持されて、その摺
動面に供給された潤滑油によって油膜形成されており、
その摺動抵抗が軽減されている。
In any of the above cases, the lap support disk 1
A minute gap is maintained between the sliding surface 3b and the sliding surface, and an oil film is formed by the lubricating oil supplied to the sliding surface,
The sliding resistance is reduced.

【0048】旋回スクロール13のラップ支持円板13
bが固定スクロール7の鏡板7aまたはスラスト軸受1
9のいずれに支持される場合でも、圧縮室2の隙間は微
小で、背面室C16,吸入室31を順次経て圧縮室2に
流入した潤滑油の油膜で密封されている。
The wrap support disk 13 of the orbiting scroll 13
b is the end plate 7a of the fixed scroll 7 or the thrust bearing 1
9, the gap between the compression chambers 2 is very small and is sealed by an oil film of the lubricating oil that has flowed into the compression chamber 2 through the rear chamber C16 and the suction chamber 31 in this order.

【0049】一方、スクロール気体圧縮機は容積比と冷
媒の特性から定まる圧縮比が一定なことから、圧縮機冷
時始動初期には多量の冷媒液が圧縮室2に流入して液圧
縮が生じることが有り、圧縮室2が異常圧力上昇して吐
出室32の圧力より高くなる。吸入室31と間欠的に連
通する第1圧縮室2aで液圧縮が生じた場合には、鏡板
7aに設けた補助バイパス穴39aの出口側を閉塞する
補助バイパス弁装置42および第1バイパス穴39a,
第2バイパス穴39bの出口側を閉塞するバイパス弁4
0のリード弁40aが順次開いて冷媒を吐出室32に流
出させ、圧縮室圧力を降下させる。
On the other hand, in the scroll gas compressor, since the compression ratio determined by the volume ratio and the characteristics of the refrigerant is constant, a large amount of refrigerant liquid flows into the compression chamber 2 at the beginning of the cold start of the compressor, and liquid compression occurs. In some cases, the pressure in the compression chamber 2 rises abnormally and becomes higher than the pressure in the discharge chamber 32. When liquid compression occurs in the first compression chamber 2a intermittently communicating with the suction chamber 31, the auxiliary bypass valve device 42 and the first bypass hole 39a for closing the outlet side of the auxiliary bypass hole 39a provided in the end plate 7a. ,
Bypass valve 4 for closing the outlet side of second bypass hole 39b
The 0 reed valves 40a are sequentially opened to allow the refrigerant to flow out to the discharge chamber 32, thereby lowering the compression chamber pressure.

【0050】なお、バイパス弁40のバネ定数が逆止弁
装置35よりも小さく設定されているので、バイパス弁
40が開き易く、バイパス作用を効果的に行うことがで
きる。
Since the spring constant of the bypass valve 40 is set smaller than that of the check valve device 35, the bypass valve 40 is easily opened, and the bypass operation can be effectively performed.

【0051】また、逆止弁装置35と一体的に連結され
ているので、変形し易い形状のバイパス弁40を鏡板7
aに組み付ける際にバイパス弁40がバイパス穴39か
らずれることもなく、バイパス穴39を確実に閉塞でき
る。
Further, since the bypass valve 40 which is easily deformed is integrally connected to the check valve device 35,
The bypass hole 40 can be reliably closed without the bypass valve 40 being displaced from the bypass hole 39 at the time of assembling to the position a.

【0052】また、吐出口30と間欠的に連通する第2
圧縮室2bで液圧縮が生じた場合には、鏡板7aに設け
た第1バイパス穴39a,第2バイパス穴39bの出口
側を閉塞するバイパス弁40が開き冷媒を吐出室32に
流出させ、圧縮室圧力を降下させる。なお、第1〜第2
バイパス穴(39a,39b)は旋回スクロールラップ
13aの端面によって同時に閉塞されることが無いよう
に配置されているので、バイパス弁40が一部連続的に
必ず開通作動する。
Further, a second communication port intermittently communicating with the discharge port 30 is provided.
When liquid compression occurs in the compression chamber 2b, the bypass valve 40 that closes the outlet side of the first bypass hole 39a and the second bypass hole 39b provided in the end plate 7a opens, causing the refrigerant to flow out to the discharge chamber 32, and compress the refrigerant. Reduce chamber pressure. In addition, the first and second
Since the bypass holes (39a, 39b) are arranged so as not to be simultaneously closed by the end faces of the orbiting scroll wrap 13a, the bypass valve 40 is always partially opened continuously.

【0053】また、補助バイパス弁装置42およびバイ
パス弁40が開通作動するのは、圧縮室2で液圧縮が生
じる場合に限らない。
The opening operation of the auxiliary bypass valve device 42 and the bypass valve 40 is not limited to the case where liquid compression occurs in the compression chamber 2.

【0054】すなわち、図4に示す如く、通常の冷凍サ
イクル運転における吸入圧力は、圧縮機が低速〜高速運
転に変化するのに追従して低下する。一方、吐出圧力は
上昇して、圧縮比が上昇するのが一般的である。
That is, as shown in FIG. 4, the suction pressure in normal refrigeration cycle operation decreases as the compressor changes from low speed to high speed operation. On the other hand, the discharge pressure generally rises, and the compression ratio generally rises.

【0055】したがって、補助バイパス弁装置42およ
びバイパス弁40が設置されない場合の圧縮機低速運転
時などの圧縮比は、定格負荷運転状態で設定された圧縮
比よりも小さくなって図5の斜線部分で示す如く過圧縮
状態となる。
Therefore, when the auxiliary bypass valve device 42 and the bypass valve 40 are not installed, the compression ratio at the time of low-speed operation of the compressor is smaller than the compression ratio set in the rated load operation state, and the hatched portion in FIG. An over-compressed state is obtained as shown by.

【0056】このような場合には上述と同様に、第1バ
イパス穴39a,第2バイパス穴39bの出口側を閉塞
するバイパス弁40のリード弁40aが開いて冷媒を吐
出室32に流出させ、2点鎖線99で示す如く、圧縮室
圧力が途中降下して圧縮負荷が軽減する。
In such a case, as described above, the reed valve 40a of the bypass valve 40 closing the outlet side of the first bypass hole 39a and the second bypass hole 39b opens to allow the refrigerant to flow out to the discharge chamber 32. As indicated by the two-dot chain line 99, the compression chamber pressure drops on the way, and the compression load is reduced.

【0057】なお、一般的には、対称位置に配置された
圧縮室2(圧縮室A,圧縮室B)の各圧力は、圧縮室隙
間密封程度の差から互いに相違する。この圧縮室2の圧
力差は旋回スクロール13に自転力を与えて自転阻止部
材27に回転力を与えることになる。
Generally, the pressures of the compression chambers 2 (compression chambers A and B) arranged at symmetric positions are different from each other due to a difference in the degree of sealing of the compression chamber gap. The pressure difference in the compression chamber 2 applies a rotation force to the orbiting scroll 13 to apply a rotation force to the rotation prevention member 27.

【0058】しかし、補助バイパス弁装置42およびバ
イパス弁40が開通して圧縮負荷軽減する場合には、圧
縮室2(圧縮室A,圧縮室B)の圧力が吐出室32を介
して圧縮行程途中で瞬時的に均圧されて、圧縮室圧力差
が小さくなる。
However, when the auxiliary bypass valve device 42 and the bypass valve 40 are opened to reduce the compression load, the pressure in the compression chamber 2 (compression chamber A, compression chamber B) is increased through the discharge chamber 32 during the compression stroke. And the pressure is instantaneously equalized to reduce the compression chamber pressure difference.

【0059】また、吐出口30から離れた第1バイパス
穴39aが開通することによって、吐出口30に近い側
の第2バイパス穴39bも開通するので、第2圧縮室2
bからのバイパス作用が円滑に作動し、入力低減に寄与
する。
When the first bypass hole 39a remote from the discharge port 30 is opened, the second bypass hole 39b closer to the discharge port 30 is also opened.
The bypass action from b operates smoothly and contributes to the reduction of input.

【0060】一方、圧縮機高速運転時は吸入室31の圧
力が低下、吐出室32の圧力が上昇する結果、実際の冷
凍サイクル運転圧縮比がスクロール気体圧縮機設定圧縮
比よりも大きい圧縮状態(バイパス弁40が開通作動し
ない状態)となる。
On the other hand, when the compressor operates at high speed, the pressure in the suction chamber 31 decreases and the pressure in the discharge chamber 32 increases. As a result, the actual compression ratio of the refrigeration cycle operation is larger than the set compression ratio of the scroll gas compressor. In this state, the bypass valve 40 does not open.

【0061】この状態では、第2圧縮室2bの容積が拡
大する過程で、しかも逆止弁装置35が吐出口30を閉
塞するまでの間に、吐出室32の冷媒ガスが吐出口30
を介して第2圧縮室2bに間欠的に逆流する。この逆流
冷媒ガスは第2圧縮室2bで再圧縮されて圧縮損失とな
る。
In this state, the refrigerant gas in the discharge chamber 32 is discharged from the discharge port 30 during the process of increasing the volume of the second compression chamber 2b and before the check valve device 35 closes the discharge port 30.
And intermittently flows back into the second compression chamber 2b. This backflow refrigerant gas is recompressed in the second compression chamber 2b, resulting in a compression loss.

【0062】しかしながら、吸入室31に供給された潤
滑油が吸入冷媒ガスと共に圧縮室を通過する際の油膜に
よって隣接する圧縮室隙間、渦巻き状溝とシール部材1
3eとの隙間が密封されるので、吐出口30に開通しな
い圧縮室への吐出冷媒ガスの逆流が阻止される。
However, when the lubricating oil supplied to the suction chamber 31 passes through the compression chamber together with the suctioned refrigerant gas, the oil film forms a gap between the adjacent compression chambers, the spiral groove, and the seal member 1.
Since the gap with 3e is sealed, backflow of the discharged refrigerant gas to the compression chamber that is not opened to the discharge port 30 is prevented.

【0063】また、圧縮室に供給された潤滑油がシール
部材13eの幅Wより小径のバイパス穴39に充満し、
バイパス穴39に滞留する冷媒ガス量が少ない。この結
果、バイパス穴39内に残留する冷媒ガスの再膨張,再
圧縮による圧縮損失は極めて少ない。
The lubricating oil supplied to the compression chamber fills the bypass hole 39 having a diameter smaller than the width W of the seal member 13e,
The amount of refrigerant gas staying in the bypass hole 39 is small. As a result, the compression loss due to the re-expansion and re-compression of the refrigerant gas remaining in the bypass hole 39 is extremely small.

【0064】また、第2圧縮室2bが吐出口30と開通
した直後の圧縮冷媒ガス排出通路は狭く、しかも逆止弁
装置35の開口遅延が生じる。したがって、吐出口30
に開通直後の第2圧縮室2b内の圧力が吐出室32より
も圧力上昇しようとする。
Further, the compressed refrigerant gas discharge passage immediately after the second compression chamber 2b opens to the discharge port 30 is narrow, and the opening of the check valve device 35 is delayed. Therefore, the discharge port 30
The pressure in the second compression chamber 2 b immediately after the opening is about to rise more than the discharge chamber 32.

【0065】しかしながら、圧縮冷媒ガスの一部がバイ
パス穴39とバイパス弁40とを介してバイパス吐出室
36に排出され、第2圧縮室2b内の圧力が低下し、過
剰な過圧縮が回避され、圧縮入力が低減する。
However, a part of the compressed refrigerant gas is discharged to the bypass discharge chamber 36 through the bypass hole 39 and the bypass valve 40, and the pressure in the second compression chamber 2b decreases, so that excessive over-compression is avoided. , The compression input is reduced.

【0066】その後、第2圧縮室2bと吐出口との開通
拡大と逆止弁装置35の開口が進行するのに伴って、圧
縮冷媒ガスは吐出口30から吐出室32に排出される。
Thereafter, the compressed refrigerant gas is discharged from the discharge port 30 to the discharge chamber 32 as the opening between the second compression chamber 2b and the discharge port expands and the opening of the check valve device 35 advances.

【0067】なお、実際の容積比(吸入容積と最終圧縮
室容積との割合)が圧縮機定格運転負荷条件に合わせて
設定されているので、バイパス穴39の開設位置が上述
の位置より大幅に吸入側に開設された場合は、旋回スク
ロールラップ13aがバイパス穴39を通過後の第2圧
縮室2bが吐出口30と開通するまでの圧縮室移動範囲
で、密閉空間になる。
Since the actual volume ratio (the ratio between the suction volume and the final compression chamber volume) is set in accordance with the rated operating load condition of the compressor, the opening position of the bypass hole 39 is significantly larger than the above-described position. In the case where the second compression chamber 2b is opened on the suction side, the orbiting scroll wrap 13a passes through the bypass hole 39, and the second compression chamber 2b moves to the discharge port 30 until the discharge chamber 30 is opened.

【0068】その結果、過圧縮発生時の実質的な入力低
減効果が漸次少なくなっていく。また、バイパス穴39
の開設位置が上述の位置より吐出口30の側に近付けた
場合は、圧縮機高速運転時など、吸入圧力と吐出圧力と
の差圧が大きくて実負荷圧縮比が設定圧縮比よりも大き
い場合に、第2圧縮室2bが吐出口30と開通するまで
にバイパス穴39が旋回スクロールラップ13aによっ
て遮閉されることに成るので、バイパス作用も少なくな
る。
As a result, the substantial input reduction effect when over-compression occurs gradually decreases. Also, the bypass hole 39
When the opening position is closer to the discharge port 30 side than the above-described position, when the differential pressure between the suction pressure and the discharge pressure is large and the actual load compression ratio is larger than the set compression ratio, such as during high-speed operation of the compressor. In addition, the bypass hole 39 is blocked by the orbiting scroll wrap 13a before the second compression chamber 2b opens to the discharge port 30, so that the bypass effect is reduced.

【0069】第2圧縮室2bが吐出口30と開通する直
前と直後に生じる過圧縮を回避できなくなり、バイパス
作用による入力低減効果も漸次少なくなる。
It is no longer possible to avoid over-compression occurring immediately before and immediately after the second compression chamber 2b opens to the discharge port 30, and the input reduction effect by the bypass action is gradually reduced.

【0070】なお、上記実施例ではバイパス穴39の第
2圧縮室2bへの開口部の大きさをシール部材13eよ
り小さくしたが、圧力負荷,運転速度,圧縮室への給油
量条件などに応じてシール部材13eの幅W相当まで広
げることができ、潤滑油の油膜形成によって実質的な圧
縮効率低下を招くことがない。
Although the size of the opening of the bypass hole 39 to the second compression chamber 2b is smaller than that of the seal member 13e in the above embodiment, it depends on the pressure load, the operating speed, the condition of the amount of oil supplied to the compression chamber, and the like. As a result, the width can be increased to the width W of the seal member 13e, and the formation of an oil film of the lubricating oil does not substantially reduce the compression efficiency.

【0071】(実施例2)図6は逆止弁装置351 の鏡
板7aへの取り付け面と、バイパス弁401 および補助
バイパス弁装置421 の鏡板7aへの取り付け面との間
に段差を設けている。逆止弁装置351 の吐出弁座35
cは、バイパス弁401 および補助バイパス弁装置42
1 のバイパス弁座40cよりも高い位置に設けられてい
る。一対のバイパス弁401 と補助バイパス弁装置42
1 は同じ方向に配列されて一体的に連結されている。
[0071] and (Example 2) Figure 6 is the mounting surface of the check valve device 35 1 of the end plate 7a, the step between the mounting surface of the bypass valve 40 1 and the auxiliary bypass valve device 42 1 of the end plate 7a Provided. Check valve device 35 1 Discharge valve seat 35
c, the bypass valve 40 1 and the auxiliary bypass valve device 42
It is provided at a position higher than the first bypass valve seat 40c. A pair of the bypass valve 40 1 and the auxiliary bypass valve device 42
1 are arranged in the same direction and are integrally connected.

【0072】実施例1の場合と同様に、一対のバイパス
弁401 のスパン(11 ,12 )と幅(W1 ,W2 )が
互いに相違して、バネ定数の異なる両方のバイパス弁4
1がほぼ同時に全開口すべく設定されている。
[0072] As in Example 1, a pair of the bypass valve 40 1 span (1 1, 1 2) and the width (W 1, W 2) are different from each other, different both of the bypass valve spring constant 4
0 1 is set to be fully open almost simultaneously.

【0073】一対のバイパス弁401 は吐出弁座35c
の側壁に接近して囲むように配置されている。バイパス
弁401 は組み付け時の位置決め精度を高めるべく、そ
の形状が設定されている。
[0073] a pair of the bypass valve 40 1 is a discharge valve seat 35c
Is arranged so as to be close to and surround the side wall. Bypass valve 40 1 is to increase the positioning accuracy during assembly, are set its shape.

【0074】この構成において、バイパス弁401 が開
通作動して第2圧縮室2bから冷媒ガスが流出する際の
圧力によって、逆止弁装置351 が少し開通を始め、第
2圧縮室2bが吐出口30と開通後の吐出冷媒ガスの流
出が円滑になり、吐出口30内の過圧縮を低減できる。
[0074] In this configuration, the pressure at which the bypass valve 40 1 is the refrigerant gas flows out from the second compression chamber 2b by opening operation, the check valve device 35 1 started a little opening, the second compression chamber 2b Outflow of the discharged refrigerant gas after opening the discharge port 30 is smooth, and overcompression in the discharge port 30 can be reduced.

【0075】また、バイパス弁401 が開通作動しない
状態で、吐出口30から吐出冷媒ガスが吐出室32に流
出する際の気流拡散の影響を受けることなく、バイパス
弁401 はバイパス穴39を閉塞することができ、吐出
室32の冷媒ガスがバイパス穴39を経由して第2圧縮
室2bに逆流することによる圧縮効率低下を防止でき
る。
[0075] In a state where the bypass valve 40 1 is not opened operate, without being affected by air flow diffusion when the discharge refrigerant gas from the discharge port 30 flows out into the discharge chamber 32, the bypass valve 40 1 is a bypass hole 39 The compression efficiency can be prevented, and a decrease in compression efficiency due to the refrigerant gas in the discharge chamber 32 flowing back to the second compression chamber 2b via the bypass hole 39 can be prevented.

【0076】なお、上記実施例では吐出弁座35cと鏡
板7aとを一体構成にしたが、別体構成にしても良い。
In the above embodiment, the discharge valve seat 35c and the end plate 7a are integrated, but may be formed separately.

【0077】[0077]

【発明の効果】上記説明から明らかなように、請求項1
記載の発明は、吐出口から吐出室へのみの流体流れを許
容し且つ吐出口の出口側を開閉するリード弁形の逆止弁
装置を固定スクロールの鏡板に配置し、吐出口に最も近
い圧縮途中の圧縮室に開口し且つ他端が吐出室に通じる
一対以上のバイパス穴を鏡板に対称配置すると共に、バ
イパス穴を介して圧縮室から吐出室へのみの流体排出を
許容し且つバイパス穴の出口側を開閉するリード弁形の
バイパス弁を逆止弁装置に接近して鏡板に設けた構成
で、バイパス弁のバネ定数を逆止弁装置よりも小さく設
定し、バイパス弁と逆止弁装置とを一体的に連結したも
のである。
As is apparent from the above description, claim 1
According to the described invention, a reed valve type check valve device that permits fluid flow only from the discharge port to the discharge chamber and opens and closes the outlet side of the discharge port is disposed on the end plate of the fixed scroll, and the compression valve closest to the discharge port is provided. A pair of at least one bypass hole that opens to the compression chamber in the middle and the other end communicates with the discharge chamber is symmetrically arranged on the end plate, and allows the discharge of fluid only from the compression chamber to the discharge chamber through the bypass hole. A reed valve type bypass valve that opens and closes the outlet side is provided on the end plate close to the check valve device, and the spring constant of the bypass valve is set smaller than that of the check valve device. And are integrally connected.

【0078】この構成によれば、逆止弁装置とバイパス
弁の取り付け時間短縮によって、逆止弁装置とバイパス
弁の取り付け位置精度向上に作業時間を付与することが
でき、剛性の高い逆止弁装置に支えられたバネ定数の小
さいバイパス弁を、バイパス穴に対する位置ズレを生じ
ることなく精度よく組み付けることができる。
According to this configuration, by shortening the time required for mounting the check valve device and the bypass valve, it is possible to provide working time for improving the mounting position accuracy of the check valve device and the bypass valve, and to provide a highly rigid check valve. The bypass valve supported by the device and having a small spring constant can be accurately assembled without causing a positional shift with respect to the bypass hole.

【0079】その結果、バイパス穴を経由した吐出室か
ら圧縮室への逆流を防ぎ、バイパス弁設置による弊害を
防止することができる。また、バネ定数の小さいバイパ
ス弁を簡単配置できることによって、効果的なバイパス
作用を発揮させることができる。また、部品,組立コス
トも低減できる。
As a result, the backflow from the discharge chamber to the compression chamber via the bypass hole can be prevented, and the adverse effect due to the installation of the bypass valve can be prevented. In addition, since a bypass valve having a small spring constant can be easily arranged, an effective bypass action can be exhibited. Also, parts and assembly costs can be reduced.

【0080】請求項2記載の発明は、リード弁形の逆止
弁装置とリード弁形のバイパス弁を同じ方向に配列した
もので、この構成によれば部品の取扱いが容易なため、
バイパス穴と吐出口に対する組み付け精度を高めること
ができると共に、取り付け時間も短縮できる。
According to the second aspect of the present invention, the reed valve type check valve device and the reed valve type bypass valve are arranged in the same direction.
The accuracy of assembling the bypass hole and the discharge port can be improved, and the mounting time can be shortened.

【0081】また、リード弁の材料が備えている金属組
織の方向をリード弁の長手方向と一致させることができ
るので、リード弁の強度を向上し信頼性を高めることが
できる。
Further, since the direction of the metal structure of the material of the reed valve can be made to coincide with the longitudinal direction of the reed valve, the strength and reliability of the reed valve can be improved.

【0082】請求項3記載の発明は、吐出口から吐出室
へのみの流体流れを許容し且つ吐出口の出口側を開閉す
るリード弁形の逆止弁装置を固定スクロールの鏡板に配
置し、吐出口に最も近い圧縮途中の圧縮室に開口し且つ
他端が吐出室に通じる一対以上のバイパス穴を鏡板に対
称配置すると共に、バイパス穴を介して圧縮室から吐出
室へのみの流体排出を許容し且つバイパス穴の出口側を
開閉するリード弁形のバイパス弁を逆止弁装置に接近さ
せて鏡板に設けた構成で、逆止弁装置の吐出弁座をバイ
パス弁のバイパス弁座より高く配置したものである。
According to a third aspect of the present invention, a check valve device of a reed valve type that permits fluid flow only from the discharge port to the discharge chamber and opens and closes the outlet side of the discharge port is disposed on the end plate of the fixed scroll. A pair of at least one bypass hole that opens to the compression chamber in the middle of compression closest to the discharge port and the other end communicates with the discharge chamber is symmetrically arranged on the end plate, and fluid is discharged only from the compression chamber to the discharge chamber through the bypass hole. A configuration in which a reed valve type bypass valve that allows and opens and closes the outlet side of the bypass hole is provided on the end plate close to the check valve device, and the discharge valve seat of the check valve device is higher than the bypass valve seat of the bypass valve It is arranged.

【0083】この構成によれば吐出口から流出する圧縮
気体流れの拡散作用によってバイパス弁が微小開口する
ことなく、バイパス穴の閉塞機能を継続することができ
る。
According to this configuration, the function of closing the bypass hole can be continued without the bypass valve being minutely opened by the diffusion action of the compressed gas flow flowing out from the discharge port.

【0084】また、バイパス弁が開通作動して圧縮途中
の圧縮室から気体が吐出室に流出する際の圧力によっ
て、逆止弁装置が少し開通を始めるので、最終行程の圧
縮室が吐出口と開通後の吐出気体の流出が円滑になり、
吐出口内の過圧縮を低減できる。
Further, the check valve device starts to open a little by the pressure when the gas flows out of the compression chamber during compression by the opening operation of the bypass valve to the discharge chamber, so that the compression chamber in the final stroke is connected to the discharge port. Outflow of discharge gas after opening is smooth,
Overcompression in the discharge port can be reduced.

【0085】請求項4記載の発明は、対称位置に配置さ
れたバイパス穴を開閉する複数のバイパス弁を一体的に
連結し、逆止弁装置の吐出弁座に接近して囲む形態で複
数のバイパス弁を配置したもので、この構成によれば吐
出弁座の側壁によってバイパス弁を精度よく位置決めす
ることができ、バイパス弁とバイパス穴の位置ズレをな
くすることができる。
According to a fourth aspect of the present invention, a plurality of bypass valves for opening and closing bypass holes arranged at symmetrical positions are integrally connected, and a plurality of bypass valves are provided so as to approach and surround a discharge valve seat of a check valve device. The bypass valve is arranged, and according to this configuration, the bypass valve can be accurately positioned by the side wall of the discharge valve seat, and the positional deviation between the bypass valve and the bypass hole can be eliminated.

【0086】その結果、バイパス弁設置の弊害を生じる
ことなく、効果的なバイパス機能を作用させることがで
きる。
As a result, an effective bypass function can be exerted without causing the adverse effect of installing the bypass valve.

【0087】請求項5記載の発明は、同一の圧縮室に開
口した複数のバイパス穴を単一のバイパス弁が同時に開
閉する構成において、互いに同機能を有する両方のバイ
パス弁がバイパス穴を同時に開閉すべく、両バイパス弁
のバネ定数を相違させたものである。
According to a fifth aspect of the present invention, in a configuration in which a single bypass valve simultaneously opens and closes a plurality of bypass holes opened in the same compression chamber, both bypass valves having the same function as each other open and close the bypass holes simultaneously. For this reason, the spring constants of the two bypass valves are different.

【0088】この構成によれば圧縮途中気体がバイパス
穴を通じて吐出室に流出する際に、各バイパス弁に作用
する気体圧力の作用点が異っても、バネ定数の調整設定
によって、バイパス弁の全開をほぼ同時に作用させるこ
とができる。
According to this configuration, even when the point of action of the gas pressure acting on each bypass valve is different when the gas during compression flows out to the discharge chamber through the bypass hole, the bypass valve is adjusted by setting the spring constant. Full opening can be performed almost simultaneously.

【0089】さらに、一対のバイパス弁を同じ方向に配
列して一体的に連結する際の弊害(対称な圧縮空間の圧
力分布の差異発生による圧縮トルク変動の増加)を防止
することができる。
Further, it is possible to prevent the adverse effect when the pair of bypass valves are arranged in the same direction and connected integrally (an increase in the compression torque fluctuation due to the occurrence of the difference in the pressure distribution in the symmetrical compression space).

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

【図1】本発明のスクロール気体圧縮機の一実施例の部
分縦断面図
FIG. 1 is a partial longitudinal sectional view of one embodiment of a scroll gas compressor of the present invention.

【図2】図1におけるA−A線に沿った断面図FIG. 2 is a sectional view taken along line AA in FIG.

【図3】逆止弁装置とバイパス弁の配置図FIG. 3 is a layout diagram of a check valve device and a bypass valve.

【図4】圧縮機運転速度と圧力の関係を示す特性図FIG. 4 is a characteristic diagram showing a relationship between compressor operating speed and pressure.

【図5】圧縮室の容積変化と圧力変化状態を示す特性図FIG. 5 is a characteristic diagram showing a change in volume and a change in pressure of a compression chamber.

【図6】本発明のスクロール気体圧縮機の別の実施例の
部分縦断面図
FIG. 6 is a partial longitudinal sectional view of another embodiment of the scroll gas compressor of the present invention.

【図7】別の実施例の逆止弁装置とバイパス弁の配置図FIG. 7 is a layout view of a check valve device and a bypass valve according to another embodiment.

【符号の説明】[Explanation of symbols]

2 圧縮室 4 駆動軸 5 本体フレーム 7 固定スクロール 7a 鏡板 7b 固定スクロールラップ 13 旋回スクロール 13a 旋回スクロールラップ 13b ラップ支持円板 19 スラスト軸受 30 吐出口 31 吸入室 32 吐出室 35 逆止弁装置 35c 吐出弁座 39 バイパス穴 40 バイパス弁 40c バイパス弁座 2 Compression chamber 4 Drive shaft 5 Body frame 7 Fixed scroll 7a End plate 7b Fixed scroll wrap 13 Orbiting scroll 13a Orbiting scroll wrap 13b Lapping support disk 19 Thrust bearing 30 Discharge port 31 Suction chamber 32 Discharge chamber 35 Check valve device 35c Discharge valve Seat 39 Bypass hole 40 Bypass valve 40c Bypass valve seat

───────────────────────────────────────────────────── フロントページの続き (72)発明者 長谷 昭三 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 芦谷 博正 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 山本 修一 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 澤井 清 大阪府門真市大字門真1006番地 松下電 器産業株式会社内 (58)調査した分野(Int.Cl.7,DB名) F04C 18/02 311 F04C 29/00 F04C 29/10 331 ──────────────────────────────────────────────────の Continuing on the front page (72) Shozo Hase, 1006 Kadoma Kadoma, Kadoma, Osaka Prefecture Inside Matsushita Electric Industrial Co., Ltd. (72) Hiromasa Ashiya 1006 Kadoma, Kadoma, Kadoma, Osaka Matsushita Electric Industrial Co., Ltd. (72) Inventor Shuichi Yamamoto 1006 Kadoma Kadoma, Osaka Prefecture Inside Matsushita Electric Industrial Co., Ltd. (72) Inventor Kiyoshi Sawai 1006 Odaka Kadoma, Kadoma City, Osaka Pref. Matsushita Electric Industrial Co., Ltd. (58) Field (Int. Cl. 7 , DB name) F04C 18/02 311 F04C 29/00 F04C 29/10 331

Claims (5)

(57)【特許請求の範囲】(57) [Claims] 【請求項1】 固定スクロールの一部をなす鏡板の一面
に直立して形成された渦巻き状の固定スクロールラップ
に対して、旋回スクロールの一部をなすラップ支持円板
上に直立し且つ前記固定スクロールラップに類似した形
状の旋回スクロールラップを互いに噛み合わせて、両ス
クロール間に渦巻き形の一対の圧縮空間を形成し、前記
固定スクロールラップの中心部に吐出室に通じる吐出口
を設け、前記固定スクロールラップの外側には吸入室を
設け、駆動軸と係合する前記ラップ支持円板と、前記固
定スクロールを締結し且つ前記駆動軸を支持する本体フ
レームとに係合する前記旋回スクロールの自転阻止部材
を介して、前記旋回スクロールが前記固定スクロールに
対し公転運動を行うことによって、前記各圧縮空間が吸
入側より吐出側に向けて連続移行する複数個の圧縮室に
区画されて流体を圧縮すべく容積変化するスクロール圧
縮機構と、吐出圧力が作用する油溜から前記圧縮室と前
記吸入室の内、少なくとも一方への給油通路とを形成
し、前記ラップ支持円板の反圧縮空間側が前記本体フレ
ームに設けたスラスト軸受に支持される形態と、前記旋
回スクロールが前記固定スクロールの側に背圧付勢され
る形態とのうち少なくとも一方の形態とし、前記吐出口
から吐出室へのみの流体流れを許容し且つ前記吐出口の
出口側を開閉するリード弁形の逆止弁装置を前記鏡板に
配置し、前記吐出口に最も近い圧縮途中の前記圧縮室に
開口し且つ他端が前記吐出室に通じる一対以上のバイパ
ス穴を前記鏡板に対称配置すると共に、前記バイパス穴
を介して前記圧縮室から前記吐出室へのみの流体排出を
許容し且つ前記バイパス穴の出口側を開閉するリード弁
形のバイパス弁を前記逆止弁装置に接近して前記鏡板に
設けた構成で、前記バイパス弁のバネ定数を前記逆止弁
装置よりも小さく設定し、前記バイパス弁と前記逆止弁
装置とを一体的に連結したスクロール気体圧縮機。
1. A fixed scroll wrap, which is formed upright on one surface of a mirror plate forming a part of a fixed scroll, stands upright on a wrap supporting disk forming a part of a revolving scroll and is fixed. Orbiting scroll wraps similar in shape to the scroll wraps are meshed with each other to form a pair of spiral compression spaces between the two scrolls, and a discharge port communicating with a discharge chamber is provided in the center of the fixed scroll wrap, and the fixed scroll wrap is provided. A suction chamber is provided outside the scroll wrap to prevent rotation of the orbiting scroll, which engages with the wrap support disk engaged with the drive shaft and the main frame that fastens the fixed scroll and supports the drive shaft. The orbiting scroll makes a revolving motion with respect to the fixed scroll via a member, whereby each compression space is directed from the suction side to the discharge side. A scroll compression mechanism that is divided into a plurality of compression chambers that continuously move and that changes volume to compress fluid, and that oil is supplied from an oil reservoir to which discharge pressure acts to at least one of the compression chamber and the suction chamber. A passage is formed, and the anti-compression space side of the lap support disc is supported by a thrust bearing provided on the main body frame, and the orbiting scroll is back-biased toward the fixed scroll. A reed valve type check valve device that allows fluid flow only from the discharge port to the discharge chamber and opens and closes the outlet side of the discharge port is disposed on the end plate, and the discharge port is A pair of at least one bypass hole that opens to the compression chamber in the middle of the closest compression and the other end communicates with the discharge chamber is symmetrically arranged on the end plate, and the compression chamber is connected to the discharge chamber through the bypass hole. A reed valve-type bypass valve for allowing fluid discharge and opening and closing the outlet side of the bypass hole is provided on the end plate close to the check valve device, and the spring constant of the bypass valve is set to the check. A scroll gas compressor set smaller than a valve device and integrally connecting the bypass valve and the check valve device.
【請求項2】 逆止弁装置とバイパス弁を同じ方向に配
列した請求項1記載のスクロール気体圧縮機。
2. The scroll gas compressor according to claim 1, wherein the check valve device and the bypass valve are arranged in the same direction.
【請求項3】 固定スクロールの一部をなす鏡板の一面
に直立して形成された渦巻き状の固定スクロールラップ
に対して、旋回スクロールの一部をなすラップ支持円板
上に直立し且つ前記固定スクロールラップに類似した形
状の旋回スクロールラップを互いに噛み合わせて、両ス
クロール間に渦巻き形の一対の圧縮空間を形成し、前記
固定スクロールラップの中心部に吐出室に通じる吐出口
を設け、前記固定スクロールラップの外側には吸入室を
設け、駆動軸と係合する前記ラップ支持円板と、前記固
定スクロールを締結し且つ前記駆動軸を支持する本体フ
レームとに係合する前記旋回スクロールの自転阻止部材
を介して、前記旋回スクロールが前記固定スクロールに
対し公転運動を行うことによって、前記各圧縮空間が吸
入側より吐出側に向けて連続移行する複数個の圧縮室に
区画されて流体を圧縮すべく容積変化するスクロール圧
縮機構と、吐出圧力が作用する油溜から前記圧縮室と前
記吸入室の内、少なくとも一方への給油通路とを形成
し、前記ラップ支持円板の反圧縮空間側が前記本体フレ
ームに設けたスラスト軸受に支持される形態と、前記旋
回スクロールが前記固定スクロールの側に背圧付勢され
る形態とのうち少なくとも一方の形態とし、前記吐出口
から吐出室へのみの流体流れを許容し且つ前記吐出口の
出口側を開閉するリード弁形の逆止弁装置を前記鏡板に
配置し、前記吐出口に最も近い圧縮途中の前記圧縮室に
開口し且つ他端が前記吐出室に通じる一対以上のバイパ
ス穴を前記鏡板に対称配置すると共に、前記バイパス穴
を介して前記圧縮室から前記吐出室へのみの流体排出を
許容し且つ前記バイパス穴の出口側を開閉するリード弁
形のバイパス弁を前記逆止弁装置に接近させて前記鏡板
に設けた構成で、前記逆止弁装置の吐出弁座を前記バイ
パス弁のバイパス弁座より高く配置したスクロール気体
圧縮機。
3. A fixed scroll wrap, which is formed upright on one surface of a mirror plate forming a part of a fixed scroll, and stands upright on a wrap supporting disk forming a part of an orbiting scroll and is fixed. The orbiting scroll wraps having a shape similar to the scroll wrap are engaged with each other to form a pair of spiral compression spaces between the two scrolls, and a discharge port communicating with a discharge chamber is provided at the center of the fixed scroll wrap, and the fixed scroll wrap is provided. A suction chamber is provided outside the scroll wrap to prevent rotation of the orbiting scroll, which engages with the wrap support disk engaged with the drive shaft and the main frame that fastens the fixed scroll and supports the drive shaft. The orbiting scroll makes a revolving motion with respect to the fixed scroll via a member, whereby each compression space is directed from the suction side to the discharge side. A scroll compression mechanism that is divided into a plurality of compression chambers that continuously move and that changes volume to compress fluid, and that oil is supplied from an oil reservoir to which discharge pressure acts to at least one of the compression chamber and the suction chamber. A passage is formed, and the anti-compression space side of the lap support disc is supported by a thrust bearing provided on the main body frame, and the orbiting scroll is back-biased toward the fixed scroll. A reed valve type check valve device that allows fluid flow only from the discharge port to the discharge chamber and opens and closes the outlet side of the discharge port is disposed on the end plate, and the discharge port is A pair of at least one bypass hole that opens to the compression chamber in the middle of the closest compression and the other end communicates with the discharge chamber is symmetrically arranged on the end plate, and the compression chamber is connected to the discharge chamber through the bypass hole. A discharge valve seat of the check valve device is provided, wherein a reed valve type bypass valve for allowing fluid discharge and opening / closing the outlet side of the bypass hole is provided on the end plate close to the check valve device. A scroll gas compressor disposed higher than a bypass valve seat of the bypass valve.
【請求項4】 対称位置に配置されたバイパス穴を開閉
する複数のバイパス弁を一体的に連結し、逆止弁装置の
吐出弁座に接近して囲む形態で前記複数のバイパス弁を
配置した請求項3記載のスクロール気体圧縮機。
4. A plurality of bypass valves for opening and closing a bypass hole arranged in a symmetrical position are integrally connected, and the plurality of bypass valves are arranged so as to be close to and surround a discharge valve seat of a check valve device. The scroll gas compressor according to claim 3.
【請求項5】 同一の圧縮室に開口した複数のバイパス
穴を単一のバイパス弁が同時に開閉する構成において、
互いに同機能を有する両方のバイパス弁が前記バイパス
穴を同時に開閉すべく、前記両バイパス弁のバネ定数を
相違させた請求項2から4いずれか1項に記載のスクロ
ール気体圧縮機。
5. A configuration in which a single bypass valve simultaneously opens and closes a plurality of bypass holes opened in the same compression chamber,
The scroll gas compressor according to any one of claims 2 to 4, wherein both bypass valves having the same function mutually open and close the bypass hole at the same time, and have different spring constants of the two bypass valves.
JP8026393A 1996-02-14 1996-02-14 Scroll gas compressor Expired - Lifetime JP3027930B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP8026393A JP3027930B2 (en) 1996-02-14 1996-02-14 Scroll gas compressor

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
JP8026393A JP3027930B2 (en) 1996-02-14 1996-02-14 Scroll gas compressor
US08/761,085 US5855475A (en) 1995-12-05 1996-12-04 Scroll compressor having bypass valves
MYPI96005076A MY119499A (en) 1995-12-05 1996-12-04 Scroll compressor having bypass valves
KR1019960064063A KR100210230B1 (en) 1995-12-05 1996-12-05 Scroll compressor having bypass valve
CN96118600A CN1086778C (en) 1995-12-05 1996-12-05 Eddy gas compressor with by-pass valve

Publications (2)

Publication Number Publication Date
JPH09217689A JPH09217689A (en) 1997-08-19
JP3027930B2 true JP3027930B2 (en) 2000-04-04

Family

ID=12192311

Family Applications (1)

Application Number Title Priority Date Filing Date
JP8026393A Expired - Lifetime JP3027930B2 (en) 1996-02-14 1996-02-14 Scroll gas compressor

Country Status (1)

Country Link
JP (1) JP3027930B2 (en)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH11141475A (en) * 1997-10-31 1999-05-25 Sanyo Electric Co Ltd Scroll type compressor
JP4104047B2 (en) * 2001-05-18 2008-06-18 松下電器産業株式会社 Scroll compressor
JP5097369B2 (en) * 2006-08-11 2012-12-12 三洋電機株式会社 Hermetic scroll compressor
JP4858047B2 (en) * 2006-09-28 2012-01-18 ダイキン工業株式会社 Compressor
JP5386566B2 (en) * 2011-11-14 2014-01-15 日立アプライアンス株式会社 Scroll compressor
JP2019132254A (en) * 2018-02-02 2019-08-08 東芝キヤリア株式会社 Rotary compressor and refrigeration cycle device

Also Published As

Publication number Publication date
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