JP3028054B2 - Scroll gas compressor - Google Patents

Scroll gas compressor

Info

Publication number
JP3028054B2
JP3028054B2 JP8026395A JP2639596A JP3028054B2 JP 3028054 B2 JP3028054 B2 JP 3028054B2 JP 8026395 A JP8026395 A JP 8026395A JP 2639596 A JP2639596 A JP 2639596A JP 3028054 B2 JP3028054 B2 JP 3028054B2
Authority
JP
Japan
Prior art keywords
chamber
compression
bypass
discharge
scroll
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 - Fee Related
Application number
JP8026395A
Other languages
Japanese (ja)
Other versions
JPH09217691A (en
Inventor
勝晴 藤尾
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Panasonic Corp
Panasonic Holdings Corp
Original Assignee
Panasonic Corp
Matsushita Electric Industrial Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Panasonic Corp, Matsushita Electric Industrial Co Ltd filed Critical Panasonic Corp
Priority to JP8026395A priority Critical patent/JP3028054B2/en
Priority claimed from MYPI96005076A external-priority patent/MY119499A/en
Publication of JPH09217691A publication Critical patent/JPH09217691A/en
Application granted granted Critical
Publication of JP3028054B2 publication Critical patent/JP3028054B2/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

Links

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
機のバイパス弁に関するものである。
The present invention relates to a bypass valve for 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容積比が一定であ
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 volume ratio determined by the compression chamber volume is constant.

【0003】特に、吸入圧力と吐出圧力とで定める圧縮
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。
[0003] In particular, when the fluctuation of the compression ratio determined by the suction pressure and the discharge pressure is small, the volume ratio is set in accordance therewith to compress a fluid such as a reciprocating compressor or a rotary compressor. High-efficiency compression can be performed without the need for a discharge valve device.

【0004】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とが変化する。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。
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.

【0005】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。
[0005] It also compresses a liquid refrigerant and a large amount of lubricating oil.
When a so-called liquid compression phenomenon occurs, an excessive compression state occurs, which may lead to an abnormal increase in compression input, excessive vibration and noise, and damage to the compressor.

【0006】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。
As a measure to prevent 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.

【0007】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、圧縮
途中の一対の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を設ける手段が
知られている。
As a measure for reducing over-compression, as described in Japanese Patent Publication No. 5-49830, a bypass hole is provided at a symmetrical position from a pair of compression chambers in the middle of compression to a discharge chamber. Means for providing a bypass valve on the outlet side of a bypass hole to allow only fluid to flow out to a discharge chamber are known.

【0008】[0008]

【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、吐出口に逆止弁装置を設けた状態で吐出
口に近い圧縮室にもバイパス弁を設ける場合や、吐出口
に近い圧縮室に多数のバイパス穴を設ける場合には、逆
止弁装置とバイパス弁とが互いに干渉し合うので、吐出
口に近い所要の位置にバイパス穴を配置できなくなり、
吐出口から離れた位置にバイパス穴を開設する結果、運
転圧縮比によっては効率的な過圧縮防止ができないとい
う課題があった。
However, in the above-mentioned conventional structure, a check valve is provided at the discharge port, and a bypass valve is also provided at the compression chamber near the discharge port. When a large number of bypass holes are provided, the check valve device and the bypass valve interfere with each other, so that the bypass hole cannot be arranged at a required position near the discharge port,
As a result of opening the bypass hole at a position distant from the discharge port, there has been a problem that over-compression cannot be effectively prevented depending on the operation compression ratio.

【0009】さらに重要な課題として、バイパス穴を設
置することは圧縮途中ガスのバイパス穴内残留を生じさ
せ、その結果、圧縮効率低下を招き易いという課題があ
った。
[0009] As an even more important problem, the installation of the bypass hole has a problem that the gas during compression remains in the bypass hole, and as a result, the compression efficiency tends to be reduced.

【0010】また、最終圧縮室が吐出室に開通後、遅延
して逆止弁装置が開作動することから、吐出口内で過圧
縮が発生し、バイパス弁が開作動以降の吐出行程で、効
果的な圧縮入力の低減を実現できないという課題があっ
た。
In addition, since the check valve device is opened with a delay after the final compression chamber is opened to the discharge chamber, over-compression occurs in the discharge port, and the effect is reduced in the discharge stroke after the bypass valve is opened. There is a problem that it is not possible to achieve a substantial reduction in the compression input.

【0011】また、複数個のバイパス穴を個別にバイパ
ス作用させる複数個のバイパス弁の配置構成が複雑で省
スペース化が困難であると共に、複数個のバイパス弁の
開閉音が大きいという課題もあった。
Further, there is a problem that the arrangement of a plurality of bypass valves for individually bypassing the plurality of bypass holes is complicated, space saving is difficult, and the opening and closing noise of the plurality of bypass valves is large. Was.

【0012】本発明はこのような従来の課題を解決する
ものであり、バイパス弁の開通作動に追従して、吐出口
を開閉する逆止弁装置を予め開状態にさせるバイパス弁
と、バイパス穴開通応答性にすぐれたバイパス弁を提供
することを目的とする。
SUMMARY OF THE INVENTION The present invention solves such a conventional problem. A bypass valve for opening a check valve device for opening and closing a discharge port in advance in accordance with the opening operation of the bypass valve, and a bypass hole. An object of the present invention is to provide a bypass valve having excellent opening response.

【0013】[0013]

【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、逆止弁装置よりも圧縮室側の鏡板に設けた
バイパス吐出室のバイパス弁が開くことによって逆止弁
装置の弁体を押し上げて吐出口を開通させるものであ
る。上記バイパス弁の配置によって、圧縮完了圧縮室が
吐出口に開通した後の逆止弁装置の開通遅延を防止する
ことができる。
SUMMARY OF THE INVENTION In order to solve the above-mentioned problems, the present invention provides a valve of a check valve device in which a bypass valve of a bypass discharge chamber provided on a head plate closer to a compression chamber than a check valve device is opened. The body is pushed up to open the discharge port. By the arrangement of the bypass valve, it is possible to prevent a delay in opening the check valve device after the compression completion compression chamber is opened to the discharge port.

【0014】[0014]

【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、底面にバイパス穴が開口し且つ他端
が吐出室に通じるバイパス吐出室を逆止弁装置よりも圧
縮室側の鏡板に設け、バイパス吐出室の底部にバイパス
弁を配置して圧縮室からバイパス吐出室へのみの流体排
出を許容した構成で、バイパス弁が開くことによって逆
止弁装置の弁体を押し上げて吐出口を開通させるべくバ
イパス弁を構成したものである。
BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a perspective view of a first embodiment of the present invention; The bypass valve is located at the bottom of the bypass discharge chamber and the bypass valve is arranged at the bottom of the bypass discharge chamber to allow fluid discharge only from the compression chamber to the bypass discharge chamber. When the bypass valve opens, the valve element of the check valve device is pushed up A bypass valve is configured to open the discharge port.

【0015】そして、この構成によれば運転圧縮比が設
定圧縮比より小さい場合には、圧縮途中気体がバイパス
穴とバイパス吐出室を介して吐出室に一部排出して過圧
縮が少なくなると共に、逆止弁装置の弁体が押し上げら
れ、吐出口が予め開通するので、圧縮室が吐出口に開通
した直後から圧縮気体の円滑な吐出室側への排出が始ま
り、吐出口での過圧縮を防止することができる。
According to this configuration, when the operating compression ratio is smaller than the set compression ratio, the gas during compression is partially discharged into the discharge chamber through the bypass hole and the bypass discharge chamber, and overcompression is reduced, and Since the valve body of the check valve device is pushed up and the discharge port is opened beforehand, the discharge of the compressed gas to the discharge chamber side starts immediately after the compression chamber is opened to the discharge port, and overcompression at the discharge port. Can be prevented.

【0016】請求項2記載の発明は、底面にバイパス穴
が開口し且つ他端が吐出室に通じるバイパス吐出室を逆
止弁装置よりも圧縮室側の鏡板に設け、バイパス吐出室
の底部にリード弁形のバイパス弁を配置して圧縮室から
バイパス吐出室へのみの流体排出を許容した構成で、バ
イパス弁が少なくとも一対以上のバイパス穴を同時に開
閉すべく、バイパス弁のリード弁体の頭部を吐出口を囲
む形態で配置したものである。
According to a second aspect of the present invention, a bypass discharge chamber having a bypass hole opened in the bottom surface and the other end communicating with the discharge chamber is provided on the end plate closer to the compression chamber than the check valve device, and is provided at the bottom of the bypass discharge chamber. A reed valve type bypass valve is arranged to allow fluid discharge only from the compression chamber to the bypass discharge chamber, and the head of the reed valve body of the bypass valve so that the bypass valve simultaneously opens and closes at least one or more bypass holes. Are arranged so as to surround the discharge port.

【0017】そして、この構成によれば複数個のバイパ
ス穴が同時に開閉され、圧縮途中気体を排出するのに必
要な通路を遅延なく確保することができる。また、低コ
ストで省スペースな構成で配置することができる。
According to this configuration, a plurality of bypass holes are simultaneously opened and closed, and a passage necessary for discharging the gas during compression can be secured without delay. In addition, they can be arranged in a low-cost and space-saving configuration.

【0018】[0018]

【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.

【0019】(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。
(Embodiment 1) In FIG. 1, reference numeral 1 denotes an iron hermetically sealed container, the entire interior 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.

【0020】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1
3cとを直立させたラップ支持円板13bとからなり、
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。
The main shaft direction oil hole 12 provided in the drive shaft 4
Has one end communicating with a refueling pump device (not shown), and the other end finally communicating with the main bearing 8. Fixed scroll 7
Scroll 13 which forms compression chamber 2 by meshing with
Is a spiral orbiting scroll wrap 13a and the orbiting shaft 1
3c and a lap support disk 13b which is upright.
It is arranged between the fixed scroll 7 and the main body frame 5.

【0021】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とからなり、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。
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.

【0022】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。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13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13
b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 suction chamber 31 communicates with a suction pipe 33 penetrating the end wall of the closed casing 1. The orbiting bearing 14 eccentrically arranged from the main shaft of the drive shaft 4 and disposed in the right end hole of the drive shaft 4 is configured to engage and slide with the orbital shaft 13 c of the orbiting scroll 13. Wrap support disk 13 for orbiting scroll 13
A small gap is formed between b and the thrust bearing 19 provided on the main body frame 5 so that an oil film can be formed.

【0023】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.

【0024】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。
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.

【0025】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。
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。
The bypass oil hole 24 is provided in the orbiting scroll 13
Are arranged so as to intermittently communicate with an annular oil groove 25 provided on the thrust bearing 19 surface with the turning motion of the thrust bearing 19.
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.

【0026】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1
3bと摺接する鏡板7aの表面に設けられた油溝43
(図2参照)を介して連通している。
The annular oil groove 25 of the 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.
Between the rear chamber C16 and the suction chamber 31, the lap support disc 1
Oil groove 43 provided on the surface of the end plate 7a that is in sliding contact with the end plate 3b
(See FIG. 2).

【0027】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とからなる。吐出口30を囲むバ
イパス吐出室36が逆止弁装置35に隣接して鏡板7a
に凹設されている。
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. A bypass discharge chamber 36 surrounding the discharge port 30 is adjacent to the check valve device 35 and has a head plate 7a.
Is recessed.

【0028】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とバイパス吐出室36とに
開口するバイパス穴39が吐出口30の近傍に設けら
れ、バイパス穴39の出口側を開閉するバイパス弁40
がバイパス吐出室36の底部に配置されている。
In the center of the end plate 7a, a bypass hole 39 opening to the second compression chamber 2b intermittently communicating with the discharge port 30 and the bypass discharge chamber 36 is provided in the vicinity of the discharge port 30. Valve 40 that opens and closes the outlet side of the
Are arranged at the bottom of the bypass discharge chamber 36.

【0029】バイパス穴39は、吐出口30に対して対
称に配置された各一対の第2バイパス穴39b,第3バ
イパス穴39c,第4バイパス穴39dが圧縮進行に追
従する形態で吐出口30の周囲に順次対称配置されてい
る。バイパス弁40は薄鋼板製のリード弁体40aと弁
押え40bとからなる。
The bypass hole 39 is formed in such a manner that a pair of second bypass holes 39b, third bypass holes 39c, and fourth bypass holes 39d arranged symmetrically with respect to the discharge port 30 follow the progress of compression. Are sequentially arranged symmetrically. The bypass valve 40 includes a reed valve body 40a made of a thin steel plate and a valve retainer 40b.

【0030】リード弁体40aの頭部40a1は、吐出
口30を囲み且つ第2バイパス穴39b,第3バイパス
穴39c,第4バイパス穴39dを閉塞できる形態をな
している。
The head 40a1 of the reed valve body 40a is configured to surround the discharge port 30 and close the second bypass hole 39b, the third bypass hole 39c, and the fourth bypass hole 39d.

【0031】図5のように、バイパス穴39を閉塞する
リード弁体40aが最大に開いた時、逆止弁装置35の
リード弁35aを押上げ、吐出口30の閉塞が解除でき
る位置関係でバイパス弁40と逆止弁装置35とが配置
されている。
As shown in FIG. 5, when the reed valve body 40a for closing the bypass hole 39 is opened to the maximum, the reed valve 35a of the check valve device 35 is pushed up, and the position of the discharge port 30 can be released. The bypass valve 40 and the check valve device 35 are arranged.

【0032】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
対の第1バイパス穴39aが対称配置されていると共
に、第1バイパス穴39a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。
In the head plate 7a, a pair of first bypass holes 39a opened to the first compression chamber 2a and the discharge chamber 32 intermittently communicating with the suction chamber 31 are symmetrically arranged, and the first bypass hole 39a is opened. An auxiliary bypass valve device 42 for opening and closing the outlet side of the hole 39a is attached.

【0033】図6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。
FIG. 6 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.

【0034】図7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気体圧縮機
のP−V線図(指圧線図)である。
FIG. 7 is a PV diagram (acupressure diagram) of a conventional scroll gas compressor in which the horizontal axis represents the volume change of the compression chamber and the vertical axis represents the pressure change of the compression chamber.

【0035】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。
The operation of the scroll gas compressor configured as described above will be described.

【0036】図1〜図7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3
0,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。
In FIGS. 1 to 7, 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 frame 5 orbits.
From the refrigerating cycle connected to the compressor, the suction refrigerant gas containing the lubricating oil flows into the suction chamber 31 via the suction pipe 33 and flows into the compression chamber 2 formed between the orbiting scroll 13 and the fixed scroll 7. Compressed and transferred to the central outlet 3
0, and is discharged to the outside of the compressor from a discharge pipe (not shown) while cooling the motor 3 through the discharge chamber 32.

【0037】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。
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.

【0038】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。旋回軸受14を経た潤滑油の一部は、環状シー
ル部材18で区画された内側の背面室A20に充満す
る。
The lubricating oil in the oil reservoir 11 to which the discharge pressure acts is
The oil is supplied to an oil chamber 15 through 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, and most of the oil is sent to an oil reservoir 11 through a main bearing 8. Return to. Part of the lubricating oil that has passed through the slewing bearing 14 fills the inner rear chamber A <b> 20 partitioned by the annular seal member 18.

【0039】また、油室15の潤滑油の一部は環状シー
ル部材18の切口部と摺動部および旋回スクロール13
に設けられた油通路21を経由して最終的に背面室C1
6に流入する。
A part of the lubricating oil in the oil chamber 15 is supplied to the cut portion and the sliding portion of the annular seal member 18 and the orbiting scroll 13.
Finally via the oil passage 21 provided in the rear chamber C1
Flow into 6.

【0040】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 by 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.

【0041】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。
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.

【0042】すなわち、旋回速度が遅い時には油通路2
1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。
That is, when the turning speed is low, the oil passage 2
A large amount of lubricating oil flows into the annular oil groove 25 and is adjusted so that a small amount of lubricating oil in the oil passage 21 flows into the annular oil groove 25 when the turning speed is high.

【0043】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。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。
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. On the other hand, the wrap support disk 13b of the orbiting scroll 13 has the rear chamber A20 where the discharge pressure acts.
(The inner part surrounded by the annular seal member 18).

【0044】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雑
される。
Therefore, the force for moving the orbiting scroll 13 away from the fixed scroll 7 and the back pressure are complicated.

【0045】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. .

【0046】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.

【0047】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。バイパス穴3
9には圧縮室2に流入した潤滑油が滞留しており、圧縮
途中冷媒ガスがバイパス穴39に侵入,流出する気体量
は少ない。
Wrap support disk 13 of 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. Bypass hole 3
The lubricating oil that has flowed into the compression chamber 2 is retained in 9, and a small amount of refrigerant gas enters and exits the bypass hole 39 during compression.

【0048】一方、スクロール気体圧縮機は吸入容積と
最終圧縮室容積との割合、すなわち、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3
2の圧力より高くなる。
On the other hand, in the scroll gas compressor, since the ratio of the suction volume to the final compression chamber volume, that is, the compression ratio determined by the volume ratio and the characteristics of the refrigerant is constant, a large amount of refrigerant is generated at the beginning of the cold start of the compressor. When the liquid flows into the compression chamber 2 and the liquid is compressed, the pressure in the compression chamber 2 rises abnormally and the discharge chamber 3
2 pressure.

【0049】図2のように、吸入室31と間欠的に連通
する第1圧縮室2aが吐出口30に開通直前,直後に液
圧縮が生じた場合には、図2〜図4のように、鏡板7a
に設けた第1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2バイパス穴39b,第3
バイパス穴39c,第4バイパス穴39dの出口側を閉
塞するバイパス弁40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。
As shown in FIG. 2, when the first compression chamber 2a intermittently communicating with the suction chamber 31 is compressed immediately before and immediately after the discharge port 30 is opened, as shown in FIGS. , End plate 7a
The auxiliary bypass valve device 42 and the second bypass hole 39b for closing the outlet side of the first bypass hole 39a provided in the
The bypass valves 40 closing the outlet sides of the bypass hole 39c and the fourth bypass hole 39d are sequentially opened to allow the refrigerant to flow out to the discharge chamber 32, thereby lowering the compression chamber pressure.

【0050】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2バイパス穴39b,第3バイパス穴39c,第4
バイパス穴39dの出口側を閉塞するバイパス弁40の
リード弁体40aが図5のように開いて、逆止弁装置3
5のリード弁35aを二点鎖線のように押し開き、吐出
口30の端部を解放する。
Further, a second intermittent communication with the discharge port 30 is provided.
If liquid compression occurs in the compression chamber 2b, the second bypass hole 39b, the third bypass hole 39c, and the fourth
The reed valve body 40a of the bypass valve 40 closing the outlet side of the bypass hole 39d is opened as shown in FIG.
The reed valve 35a of No. 5 is pushed open like a two-dot chain line to release the end of the discharge port 30.

【0051】図2に示す第2圧縮室2bが吐出口30に
開通直後の状態から、図3に示す如く、さらに90度進
角した状態までの間に、逆止弁装置35の通路抵抗もな
く、圧縮冷媒ガスが吐出口30とバイパス穴39から円
滑に排出する。
From the state immediately after the second compression chamber 2b is opened to the discharge port 30 shown in FIG. 2 to the state where the second compression chamber 2b is advanced by 90 degrees as shown in FIG. Instead, the compressed refrigerant gas is smoothly discharged from the discharge port 30 and the bypass hole 39.

【0052】したがって、圧縮冷媒ガスは第2圧縮室2
bが吐出口30に開通前から継続的に吐出室に流出し、
第2圧縮室2bと吐出口30内で過剰な過圧縮が生じる
ことがない。
Therefore, the compressed refrigerant gas is supplied to the second compression chamber 2
b continuously flows into the discharge chamber before opening to the discharge port 30,
Excessive over-compression does not occur in the second compression chamber 2b and the discharge port 30.

【0053】また、圧縮冷媒ガスが第2圧縮室2bから
吐出口30,吐出室32へと吐出口開通前から継続的に
流出するので、冷媒ガスの流出音と吐出室32内の圧力
脈動が小さくなり、圧縮機の騒音と振動が低減する。
Further, since the compressed refrigerant gas continuously flows from the second compression chamber 2b to the discharge port 30 and the discharge chamber 32 before the discharge port is opened, the outflow noise of the refrigerant gas and the pressure pulsation in the discharge chamber 32 are reduced. Smaller, reducing compressor noise and vibration.

【0054】なお、第2〜第4バイパス穴(39b,3
9c,39d)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ないように配置されている。それ
によって、第2〜第4バイパス穴(39b,39c,3
9d)を同時に開閉するバイパス弁40は継続的に開通
作動する。
The second to fourth bypass holes (39b, 3b)
9c, 39d) are arranged so as not to be simultaneously closed by the end faces of the orbiting scroll wrap 13a. Thereby, the second to fourth bypass holes (39b, 39c, 3
The bypass valve 40 that opens and closes at the same time as 9d) is continuously opened.

【0055】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.

【0056】すなわち、図6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。
That is, as shown in FIG. 6, the suction pressure in the normal refrigeration cycle operation decreases as the compressor changes from low speed to high speed operation.

【0057】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。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7の斜線部分で示す
如く過圧縮状態となる。
On the other hand, the discharge pressure generally rises, and the compression ratio generally rises. 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 or the like is smaller than the compression ratio set in the rated load operation state, as indicated by the hatched portion in FIG. It becomes overcompressed.

【0058】このような場合には上述と同様に、第2バ
イパス穴39b,第3バイパス穴39c,第4バイパス
穴39dの出口側を閉塞するバイパス弁40のリード弁
体40aが開いて冷媒を吐出室32に流出させ、二点鎖
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, similarly to the above, the reed valve element 40a of the bypass valve 40 that closes the outlet side of the second bypass hole 39b, the third bypass hole 39c, and the fourth bypass hole 39d opens to allow the refrigerant to flow. The gas is discharged into the discharge chamber 32, and the pressure in the compression chamber drops on the way, as shown by the two-dot chain line 99, so that the compression load is reduced.

【0059】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。
Generally, the pressures of the compression chambers 2 (compression chambers A and B) arranged at symmetric positions are different from each other due to the difference in the degree of sealing of the compression chamber gap.

【0060】この圧縮室2の圧力差は旋回スクロール1
3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。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。
The pressure difference in the compression chamber 2 is
The rotation force is applied to the rotation preventing member 27 by applying the rotation force to the rotation prevention member 3. However, when the auxiliary bypass valve device 42 and the bypass valve 40 are opened to reduce the compression load, the pressure of the compression chamber 2 (compression chamber A, compression chamber B) is instantaneously generated during the compression stroke via the discharge chamber 32. And the compression chamber pressure difference is reduced.

【0061】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, during high-speed operation of the compressor, the pressure in the suction chamber 31 is decreased and the pressure in the discharge chamber 32 is increased. 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.

【0062】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.

【0063】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
よって圧縮室隙間が密封されるので、吐出室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, since the gap between the compression chambers is sealed by the oil film when the lubricating oil supplied to the suction chamber 31 passes through the compression chamber together with the suction refrigerant gas, the refrigerant gas discharged to the compression chamber that is not opened to the discharge chamber 30 Backflow is prevented.

【0064】また、圧縮室に供給された潤滑油がバイパ
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。
Further, the lubricating oil supplied to the compression chamber fills the bypass hole 39, and the amount of the refrigerant gas retained 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.

【0065】また、バイパス吐出室36が鏡板7aに凹
設されることによって第2バイパス穴39b,第3バイ
パス穴39c,第4バイパス穴39dの通路が短くなっ
た結果、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が無視できるまでに低減され
ている。
Further, since the bypass discharge chamber 36 is recessed in the end plate 7a, the passages of the second bypass hole 39b, the third bypass hole 39c, and the fourth bypass hole 39d are shortened. The compression loss due to the re-expansion and re-compression of the refrigerant gas is reduced to a negligible level.

【0066】[0066]

【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逆止弁装置を配置
し、吐出口に最も近い圧縮途中の圧縮室に開口し且つ他
端が最終的に吐出室に通じる少なくとも一対以上のバイ
パス穴を固定スクロールの鏡板に対称配置して設け、底
面にバイパス穴が開口し且つ他端が吐出室に通じるバイ
パス吐出室を逆止弁装置よりも圧縮室側の鏡板に設け、
バイパス吐出室の底部にバイパス弁を配置して圧縮室か
らバイパス吐出室へのみの流体排出を許容した構成で、
バイパス弁が開くことによって逆止弁装置の弁体を押し
上げて吐出口を開通させるべくバイパス弁を構成したも
のである。
As is apparent from the above description, claim 1
According to the invention described above, a 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 arranged, and is opened to the compression chamber in the middle of compression closest to the discharge port and At least one pair of bypass holes each having an end finally communicating with the discharge chamber are provided symmetrically on the end plate of the fixed scroll, and the bypass discharge chamber having an opening at the bottom surface and the other end communicating with the discharge chamber is a check valve device. Than on the end plate on the compression chamber side,
With a configuration in which a bypass valve is arranged at the bottom of the bypass discharge chamber to allow fluid discharge only from the compression chamber to the bypass discharge chamber,
By opening the bypass valve, the valve body of the check valve device is pushed up to open the discharge port, thereby forming a bypass valve.

【0067】この構成によれば圧縮室圧力が吐出室圧力
よりも高くなった時、バイパス弁が開いて圧縮途中気体
の一部がバイパス吐出室を経由して吐出室に排出するの
で、圧縮室での圧力上昇を抑制し、圧縮入力の増加を防
止できる。
According to this configuration, when the pressure in the compression chamber becomes higher than the pressure in the discharge chamber, the bypass valve is opened and a part of the gas during compression is discharged to the discharge chamber via the bypass discharge chamber. , The pressure increase in the compressor can be suppressed, and an increase in compression input can be prevented.

【0068】また、圧縮室が吐出口に開口する前に、バ
イパス弁が吐出口を閉塞していた逆止弁装置を開通させ
るので、吐出口に最も近い圧縮室で異常圧力上昇した気
体の一部を圧縮室隙間と吐出口を通じて吐出室に排出し
始め、さらに、圧縮室と吐出口とが開通直後からは、気
体通路抵抗の少ない状態で吐出室へ排出できるので、圧
縮室および吐出口内での過圧縮を抑制できる。それによ
って、上述のバイパス効果に付加して圧縮入力低減を図
ることができる。
Also, before the compression chamber opens to the discharge port, the bypass valve opens the non-return valve device closing the discharge port. The discharge section starts to be discharged into the discharge chamber through the compression chamber gap and the discharge port.Furthermore, immediately after the compression chamber and the discharge port are opened, it can be discharged to the discharge chamber with a low gas passage resistance. Over-compression can be suppressed. Thereby, the compression input can be reduced in addition to the above-described bypass effect.

【0069】請求項2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
る逆止弁装置を配置し、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最終的に吐出室に通じる少なく
とも一対以上のバイパス穴を鏡板に対称配置して設け、
底面にバイパス穴が開口し且つ他端が吐出室に通じるバ
イパス吐出室を逆止弁装置よりも圧縮室側の固定スクロ
ールの鏡板に設け、バイパス吐出室の底部にリード弁形
のバイパス弁を配置して圧縮室からバイパス吐出室への
みの流体排出を許容した構成である。
According to a second aspect of the present invention, there is provided a check valve device which permits a fluid flow only from the discharge port to the discharge chamber and opens and closes the outlet side of the discharge port, and the compression valve in the middle of compression closest to the discharge port. At least one pair or more bypass holes that open to the chamber and the other end finally communicates with the discharge chamber are provided symmetrically in the end plate,
A bypass discharge chamber with a bypass hole opened at the bottom and the other end communicating with the discharge chamber is provided on the end plate of the fixed scroll closer to the compression chamber than the check valve device, and a reed valve type bypass valve is arranged at the bottom of the bypass discharge chamber. Thus, the fluid discharge from the compression chamber to only the bypass discharge chamber is allowed.

【0070】バイパス弁が少なくとも一対以上のバイパ
ス穴を同時に開閉すべく、バイパス弁のリード弁体の頭
部を吐出口を囲む形態で配置したもので、この構成によ
れば、低コストで省スペースなバイパス弁を提供するこ
とができる。
The head of the reed valve body of the bypass valve is arranged so as to surround the discharge port so that the bypass valve opens and closes at least one or more bypass holes at the same time. A simple bypass valve can be provided.

【0071】また、吐出口の近傍に複数個のバイパス穴
を適宜簡単配置でき、バイパス通路の適正確保によって
圧縮入力低減などに効果的なバイパス作用を得ることが
できる。
Further, a plurality of bypass holes can be appropriately arranged in the vicinity of the discharge port as appropriate, and an effective bypass action for reducing the compression input can be obtained by appropriately securing the bypass passage.

【0072】さらに、継続的なバイパス作用ができバイ
パス弁の開閉頻度が少なくなるので、圧縮機騒音,振動
低減に寄与できるという効果を奏する。
Further, since a continuous bypass operation can be performed and the frequency of opening and closing the bypass valve is reduced, it is possible to reduce the compressor noise and vibration.

【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】同要部拡大縦断面図FIG. 2 is an enlarged vertical sectional view of the main part of the same.

【図3】同要部拡大縦断面図FIG. 3 is an enlarged vertical sectional view of the main part of the same.

【図4】図1におけるA−A線に沿った断面図FIG. 4 is a sectional view taken along line AA in FIG. 1;

【図5】バイパス弁の外観図FIG. 5 is an external view of a bypass valve.

【図6】圧縮機運転速度と圧力の関係を示す特性図FIG. 6 is a characteristic diagram showing a relationship between compressor operating speed and pressure.

【図7】圧縮室の容積変化と圧力変化状態を示す特性図FIG. 7 is a characteristic diagram showing a volume change and a pressure change state of a compression chamber.

【符号の説明】[Explanation of symbols]

2 圧縮室 2b 第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 30 吐出口 31 吸入室 32 吐出室 35 逆止弁装置 35a リード弁 35b 弁押え 36 バイパス吐出室 39 バイパス穴 39a 第1バイパス穴 39b 第2バイパス穴 39c 第3バイパス穴 39d 第4バイパス穴 40 バイパス弁 40a リード弁体 40a1 頭部 42 補助バイパス弁装置 Reference Signs List 2 compression chamber 2b second compression chamber 4 drive shaft 5 main frame 7 fixed scroll 7a end plate 7b fixed scroll wrap 13 orbiting scroll 13a orbiting scroll wrap 13b lap support disk 30 discharge port 31 suction chamber 32 discharge chamber 35 check valve device 35a Reed valve 35b Valve retainer 36 Bypass discharge chamber 39 Bypass hole 39a First bypass hole 39b Second bypass hole 39c Third bypass hole 39d Fourth bypass hole 40 Bypass valve 40a Reed valve element 40a1 Head 42 Auxiliary bypass valve device

Claims (2)

(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、前記圧縮室と前記吸入室のうち少なくとも一
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逆止弁装置を
配置し、前記吐出口に最も近い圧縮途中の前記圧縮室に
開口し且つ他端が最終的に前記吐出室に通じる少なくと
も一対以上のバイパス穴を前記鏡板に前記吐出口に対し
て対称配置して設け、底面に前記バイパス穴が開口し且
つ他端が前記吐出室に通じるバイパス吐出室を前記逆止
弁装置よりも圧縮室側の前記鏡板に設け、前記バイパス
吐出室の底部にバイパス弁を配置して前記圧縮室から前
記バイパス吐出室へのみの流体排出を許容した構成で、
前記バイパス弁が開くことによって前記逆止弁装置の弁
体を押し上げて前記吐出口を開通させるべく前記バイパ
ス弁を構成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 an oil supply passage to at least one of the compression chamber and the suction chamber is formed. The disk has at least one of a form in which the anti-compression space side of the disc is supported by a thrust bearing provided in the main body frame and a form in which the orbiting scroll is urged against the fixed scroll by back pressure. A check valve device that allows fluid flow only from the outlet to the discharge chamber and opens and closes the outlet side of the discharge port is disposed, and is open to the compression chamber in the middle of compression closest to the discharge port, and the other end is final. At least one pair of bypass holes communicating with the discharge chamber are provided in the end plate symmetrically with respect to the discharge port, the bypass having an opening at the bottom surface and the other end communicating with the discharge chamber. An outlet is provided on the end plate closer to the compression chamber than the check valve device, and a bypass valve is arranged at the bottom of the bypass discharge chamber to allow fluid discharge only from the compression chamber to the bypass discharge chamber. ,
A scroll gas compressor, wherein the bypass valve is configured to push up a valve element of the check valve device to open the discharge port by opening the bypass valve.
【請求項2】 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、前記圧縮室と前記吸入室のうち少なくとも一
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逆止弁装置を
配置し、前記吐出口に最も近い圧縮途中の前記圧縮室に
開口し且つ他端が最終的に前記吐出室に通じる少なくと
も一対以上のバイパス穴を前記鏡板に前記吐出口に対し
て対称配置して設け、底面に前記バイパス穴が開口し且
つ他端が前記吐出室に通じるバイパス吐出室を前記逆止
弁装置よりも圧縮室側の前記鏡板に設け、前記バイパス
吐出室の底部にリード弁形のバイパス弁を配置して前記
圧縮室から前記バイパス吐出室へのみの流体排出を許容
した構成で、前記バイパス弁が少なくとも一対以上の前
記バイパス穴を同時に開閉すべく、前記バイパス弁のリ
ード弁体の頭部を前記吐出口を囲む形態で配置したスク
ロール気体圧縮機。
2. A fixed scroll wrap, which is formed upright on one surface of a mirror plate forming a part of a fixed scroll, and is fixed upright on a wrap supporting disk forming a part of an orbiting scroll. 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 a center portion 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 an oil supply passage to at least one of the compression chamber and the suction chamber is formed. The disk has at least one of a form in which the counter compression space side of the disc is supported by a thrust bearing provided in the main body frame and a form in which the orbiting scroll is urged against the fixed scroll by back pressure. A check valve device that allows fluid flow only from the outlet to the discharge chamber and opens and closes the outlet side of the discharge port is disposed, and is open to the compression chamber in the middle of compression closest to the discharge port, and the other end is final. At least one pair of bypass holes communicating with the discharge chamber are provided in the end plate symmetrically with respect to the discharge port, the bypass having an opening at the bottom surface and the other end communicating with the discharge chamber. An outlet chamber is provided on the end plate closer to the compression chamber than the check valve device, and a reed valve type bypass valve is arranged at the bottom of the bypass discharge chamber to discharge fluid only from the compression chamber to the bypass discharge chamber. A scroll gas compressor having a permissible configuration, wherein a head of a reed valve body of the bypass valve is arranged so as to surround the discharge port so that the bypass valve simultaneously opens and closes at least one or more of the bypass holes.
JP8026395A 1996-02-14 1996-02-14 Scroll gas compressor Expired - Fee Related JP3028054B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP8026395A JP3028054B2 (en) 1996-02-14 1996-02-14 Scroll gas compressor

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
JP8026395A JP3028054B2 (en) 1996-02-14 1996-02-14 Scroll gas compressor
MYPI96005076A MY119499A (en) 1995-12-05 1996-12-04 Scroll compressor having bypass valves
US08/761,085 US5855475A (en) 1995-12-05 1996-12-04 Scroll compressor having bypass valves
CN96118600A CN1086778C (en) 1995-12-05 1996-12-05 Eddy gas compressor with by-pass valve
KR1019960064063A KR100210230B1 (en) 1995-12-05 1996-12-05 Scroll compressor having bypass valve

Publications (2)

Publication Number Publication Date
JPH09217691A JPH09217691A (en) 1997-08-19
JP3028054B2 true JP3028054B2 (en) 2000-04-04

Family

ID=12192367

Family Applications (1)

Application Number Title Priority Date Filing Date
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Country Link
JP (1) JP3028054B2 (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3028473B2 (en) * 1997-06-02 2000-04-04 株式会社ゼクセル Horizontal scroll compressor
JPH11141475A (en) * 1997-10-31 1999-05-25 Sanyo Electric Co Ltd Scroll type compressor
DE69817130T2 (en) * 1997-12-18 2004-06-09 Mitsubishi Heavy Industries, Ltd. scroll compressor
JP2000291573A (en) * 1999-04-05 2000-10-17 Matsushita Electric Ind Co Ltd Scroll compressor
KR100455419B1 (en) * 2002-03-14 2004-11-06 주식회사 엘지이아이 Device for reducing noise of scroll compressor
CN100371598C (en) 2003-08-11 2008-02-27 三菱重工业株式会社 Scroll compressor
KR100652588B1 (en) * 2004-11-11 2006-12-07 엘지전자 주식회사 Discharge valve system of scroll compressor
JP4624201B2 (en) * 2005-07-13 2011-02-02 三菱電機株式会社 Scroll compressor
JP2008138575A (en) * 2006-11-30 2008-06-19 Mitsubishi Electric Corp Scroll compressor
JP4379489B2 (en) * 2007-05-17 2009-12-09 ダイキン工業株式会社 Scroll compressor
CN102367798A (en) * 2011-11-05 2012-03-07 佛山市广顺电器有限公司 Vortex compressor with balancing and energy saving device
JP6634584B2 (en) * 2015-03-13 2020-01-22 パナソニックIpマネジメント株式会社 Scroll compressor

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