JP2002349458A - Hermetically closed type scroll compressor - Google Patents
Hermetically closed type scroll compressorInfo
- Publication number
- JP2002349458A JP2002349458A JP2001152068A JP2001152068A JP2002349458A JP 2002349458 A JP2002349458 A JP 2002349458A JP 2001152068 A JP2001152068 A JP 2001152068A JP 2001152068 A JP2001152068 A JP 2001152068A JP 2002349458 A JP2002349458 A JP 2002349458A
- Authority
- JP
- Japan
- Prior art keywords
- scroll
- lubricating oil
- check valve
- fixed scroll
- pressure
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
- F04C29/124—Arrangements 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
- F04C29/126—Arrangements 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
- F04C29/128—Arrangements 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 of the elastic type, e.g. reed valves
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Rotary Pumps (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、業務用、家庭用、
車輌用等の冷凍空調、あるいは冷蔵庫などに用いられる
縦型の密閉型スクロール圧縮機に関するものである。TECHNICAL FIELD The present invention relates to business, home,
The present invention relates to a vertical hermetic scroll compressor used for refrigeration and air conditioning for vehicles or a refrigerator.
【０００２】[0002]
【従来の技術】従来の密閉型スクロール圧縮機を図５に
より説明する。固定スクロール１と旋回スクロール２を
対向して組み合わせ、固定スクロール１と軸受フレーム
３とで旋回スクロール２の鏡板を旋回運動が可能な隙間
を有してはさんで保持する。吸入冷媒ガスは固定スクロ
ール１の鏡板外周から半径方向に貫通して設けた吸入管
４より吸入され固定スクロール１と旋回スクロール２と
により形成される吸入室５の外周より圧縮室６に流入す
る。 旋回スクロール２はオルダムリング７によって自
転を防止され、駆動軸８の偏心軸部８ａにより旋回軸受
９を介して旋回運動し、吸入冷媒ガスを吸入室５から順
次圧縮室６の中心方向へ圧縮して、吐出孔１０に導く。
固定スクロール１の背面１ａに逆止弁１１を設け、圧
縮された高圧冷媒ガスが逆止弁１１を押し上げ吐出室１
２へ吐出する。2. Description of the Related Art A conventional hermetic scroll compressor will be described with reference to FIG. The fixed scroll 1 and the orbiting scroll 2 are combined so as to face each other, and the end plate of the orbiting scroll 2 is held between the fixed scroll 1 and the bearing frame 3 with a gap allowing the orbiting movement. The sucked refrigerant gas is sucked from a suction pipe 4 provided through the outer periphery of the end plate of the fixed scroll 1 in the radial direction, and flows into the compression chamber 6 from the outer circumference of a suction chamber 5 formed by the fixed scroll 1 and the orbiting scroll 2. The orbiting scroll 2 is prevented from rotating by an Oldham ring 7, orbits through an orbiting bearing 9 by an eccentric shaft portion 8 a of a drive shaft 8, and compresses the suctioned refrigerant gas sequentially from the suction chamber 5 toward the center of the compression chamber 6. To the discharge hole 10.
A check valve 11 is provided on the back surface 1a of the fixed scroll 1, and the compressed high-pressure refrigerant gas pushes up the check valve 11 to raise the discharge chamber 1
Discharge to 2.
【０００３】その後、圧縮された高圧冷媒ガスは吐出室
１２から固定スクロール１および軸受フレーム３に設け
た冷媒通路１３から電動機側へ流れ電動機１４，１５を
冷却した後、図示されていない配管により機外へ圧送さ
れる。Thereafter, the compressed high-pressure refrigerant gas flows from the discharge chamber 12 through the refrigerant passage 13 provided in the fixed scroll 1 and the bearing frame 3 to the electric motor side to cool the electric motors 14 and 15, and then is cooled by piping not shown. It is pumped out.
【０００４】駆動軸８は軸受フレーム３に固定した主軸
受１６と副軸受１７で支持され電動機１４，１５の駆動
力により回転する。固定スクロール１に鋼球１８とバネ
１９を設けることにより、旋回スクロール２の背面２ａ
と軸受フレーム３との間に形成された背圧室２０の圧力
が吸入室５の圧力と前記吐出室１２の圧力の中間に維持
されており、これにより旋回スクロール２を固定スクロ
ール１に押し付け密着させる構造となっている。The drive shaft 8 is supported by a main bearing 16 and a sub bearing 17 fixed to the bearing frame 3, and is rotated by the driving force of the electric motors 14 and 15. By providing the fixed scroll 1 with the steel ball 18 and the spring 19, the back surface 2a of the orbiting scroll 2
The pressure in the back pressure chamber 20 formed between the pressure chamber and the bearing frame 3 is maintained at an intermediate level between the pressure in the suction chamber 5 and the pressure in the discharge chamber 12. It has a structure to make it.
【０００５】駆動軸８内には油孔２１が設けられてお
り、また駆動軸８の偏心軸部８ａおよび主軸部８ｂには
それぞれ油溝２１ａ，２１ｂが設けられている。さら
に、駆動軸８の下端は潤滑油溜り２２内に浸漬されて、
油孔２１と油溝２１ａ，２１ｂにより背圧室２０と潤滑
油溜り２２は連通している。また、潤滑油溜り２２は吐
出圧力になっているので背圧室２０との圧力差によって
潤滑油は旋回軸受９と主軸受１６に供給された後背圧室
２０に溜り、鋼球１８を押し上げて吸入室５に流入し、
吸入冷媒ガスとともに圧縮室６、吐出室１２、冷媒通路
１３を経て電動機１４，１５に導かれ、潤滑油溜り２２
に戻る。An oil hole 21 is provided in the drive shaft 8, and oil grooves 21a and 21b are provided in the eccentric shaft portion 8a and the main shaft portion 8b of the drive shaft 8, respectively. Further, the lower end of the drive shaft 8 is immersed in the lubricating oil reservoir 22,
The back pressure chamber 20 and the lubricating oil reservoir 22 communicate with each other through the oil hole 21 and the oil grooves 21a and 21b. Further, since the lubricating oil reservoir 22 is at the discharge pressure, the lubricating oil is supplied to the slewing bearing 9 and the main bearing 16 and accumulates in the back pressure chamber 20 due to the pressure difference between the back pressure chamber 20 and pushes up the steel ball 18. Flows into the suction chamber 5,
The lubricating oil reservoir 22 is guided to the electric motors 14 and 15 through the compression chamber 6, the discharge chamber 12, and the refrigerant passage 13 together with the suction refrigerant gas.
Return to
【０００６】ここで圧縮機が運転を停止したとき、逆止
弁１１によって吐出孔１０が閉じられるため、吸入室５
は吸入圧力を、潤滑油溜り２２は吐出圧力を、背圧室２
０は中間圧力を冷凍サイクル全体の圧力が均圧するまで
それぞれ維持しつづけるため、潤滑油は圧力差により吸
入側へ逆流し、潤滑油溜り２２の潤滑油が無くなる。Here, when the compressor stops operating, the discharge port 10 is closed by the check valve 11, so that the suction chamber 5 is closed.
Represents the suction pressure, the lubricating oil reservoir 22 represents the discharge pressure, and the back pressure chamber 2
In the case of 0, since the intermediate pressure is maintained until the pressure of the entire refrigeration cycle is equalized, the lubricating oil flows back to the suction side due to the pressure difference, and the lubricating oil in the lubricating oil reservoir 22 is exhausted.
【０００７】また逆止弁１１を設けないと潤滑油溜り２
２の潤滑油は吸入側へ逆流しないが、停止時、吐出圧力
と吸入圧力の差圧によって旋回スクロール２が逆転し異
常音が発生したり、最悪の場合はスクロールが破壊する
ことにもなり得る。If the check valve 11 is not provided, the lubricating oil sump 2
The lubricating oil No. 2 does not flow back to the suction side, but when stopped, the differential pressure between the discharge pressure and the suction pressure causes the orbiting scroll 2 to reversely rotate, generating an abnormal sound or, in the worst case, breaking the scroll. .
【０００８】[0008]
【発明が解決しようとする課題】以上のような従来の密
閉型スクロール圧縮機においては、潤滑油が吸入側へ逆
流し、潤滑油溜りの潤滑油が無くなることを防止する配
慮がなされておらず、そのために軸受部の潤滑不良によ
る焼き付などを起こす欠点があった。In the conventional hermetic scroll compressor described above, no consideration is given to preventing the lubricating oil from flowing back to the suction side and the lubricating oil from running out of the lubricating oil reservoir. For this reason, there has been a defect that seizure or the like occurs due to poor lubrication of the bearing portion.
【０００９】本発明は圧縮機の停止時に潤滑油溜りの潤
滑油が吸入側へ逆流して無くなることを防止し、かつ旋
回スクロールが逆転することのない密閉型スクロール圧
縮機を提供することを目的とする。SUMMARY OF THE INVENTION It is an object of the present invention to provide a hermetic scroll compressor which prevents lubricating oil in a lubricating oil pool from flowing backward to a suction side when the compressor is stopped, and prevents the orbiting scroll from reversing. And
【００１０】[0010]
【課題を解決するための手段】この課題を解決するため
に本発明は、逆止弁に設けた貫通孔や、逆止弁をバイパ
スするように設けた連通溝により、逆止弁が閉じた状態
でも圧縮機構内部と密閉容器内部とで僅かな量の気体の
流通を可能としたものである。これにより、圧縮機停止
時に旋回スクロールが逆転することなく吐出圧力と吸入
圧力との均圧を早めることができるため、潤滑油の吸入
側への逆流が無く、潤滑油溜りの潤滑油が無くなること
を防止した信頼性の高い圧縮機を得ることができる。According to the present invention, a check valve is closed by a through hole provided in the check valve or a communication groove provided to bypass the check valve. Even in this state, a small amount of gas can flow between the inside of the compression mechanism and the inside of the closed vessel. This makes it possible to accelerate the equalization of the discharge pressure and the suction pressure without reversing the orbiting scroll when the compressor is stopped, so that there is no backflow of the lubricating oil to the suction side and the lubricating oil in the lubricating oil reservoir is eliminated. , And a highly reliable compressor that prevents the occurrence of such problems can be obtained.
【００１１】[0011]
【発明の実施の形態】以下本発明の実施の形態につい
て、図面を用いて説明する。Embodiments of the present invention will be described below with reference to the drawings.
【００１２】（実施の形態１）図１は本発明の一実施の
形態における密閉型圧縮機の断面図、図２は図１におけ
る逆止弁の斜視図である。図１において、固定スクロー
ル１と旋回スクロール２を対向して組み合わせ、前記固
定スクロール１と軸受フレーム３とで前記旋回スクロー
ル２の鏡板を旋回運動が可能な隙間を有してはさんで保
持する。(Embodiment 1) FIG. 1 is a sectional view of a hermetic compressor according to an embodiment of the present invention, and FIG. 2 is a perspective view of a check valve in FIG. In FIG. 1, the fixed scroll 1 and the orbiting scroll 2 are combined to face each other, and the end plate of the orbiting scroll 2 is held between the fixed scroll 1 and the bearing frame 3 with a gap allowing the orbiting movement.
【００１３】吸入冷媒ガスは固定スクロール１の鏡板外
周から半径方向に貫通して設けた吸入管４より吸入され
固定スクロール１と旋回スクロール２とにより形成され
る吸入室５の外周より圧縮室６に流入する。旋回スクロ
ール２はオルダムリング７によって自転を防止され、駆
動軸８の偏心軸部８ａにより旋回軸受９を介して旋回運
動し、吸入冷媒ガスを吸入室５から順次圧縮室６の中心
方向へ圧縮して、吐出孔１０に導く。固定スクロール１
の背面１ａに貫通孔１１ａの開いた逆止弁１１０を設
け、圧縮された高圧冷媒ガスが逆止弁１１０を押し上げ
吐出室１２へ吐出する。The suctioned refrigerant gas is sucked from a suction pipe 4 provided radially from the outer periphery of the end plate of the fixed scroll 1 to the compression chamber 6 from the outer circumference of a suction chamber 5 formed by the fixed scroll 1 and the orbiting scroll 2. Inflow. The orbiting scroll 2 is prevented from rotating by an Oldham ring 7, orbits through an orbiting bearing 9 by an eccentric shaft portion 8 a of a drive shaft 8, and compresses the suctioned refrigerant gas sequentially from the suction chamber 5 toward the center of the compression chamber 6. To the discharge hole 10. Fixed scroll 1
A check valve 110 having a through-hole 11a is provided on the back surface 1a of the refrigeration chamber, and the compressed high-pressure refrigerant gas pushes up the check valve 110 and discharges it to the discharge chamber 12.
【００１４】その後、圧縮された高圧冷媒ガスは吐出室
１２から固定スクロール１および軸受フレーム３に設け
た冷媒通路１３から電動機側へ流れ電動機１４，１５を
冷却した後、図示されていない配管により機外へ圧送さ
れる。Thereafter, the compressed high-pressure refrigerant gas flows from the discharge chamber 12 through the refrigerant passage 13 provided in the fixed scroll 1 and the bearing frame 3 to the electric motor side to cool the electric motors 14 and 15, and then is cooled by piping not shown. It is pumped out.
【００１５】駆動軸８は軸受フレーム３に固定した主軸
受１６と副軸受１７で支持され電動機１４，１５の駆動
力により回転する。固定スクロール１に鋼球１８とバネ
１９を設けることにより、旋回スクロール２の背面２ａ
と軸受フレーム３との間に形成された背圧室２０の圧力
が前記吸入室５の圧力と前記吐出室１２の圧力の中間に
維持されており、これにより旋回スクロール２を固定ス
クロール１に押し付け密着させる構造となっている。The drive shaft 8 is supported by a main bearing 16 and a sub-bearing 17 fixed to the bearing frame 3, and is rotated by the driving force of the electric motors 14 and 15. By providing the fixed scroll 1 with the steel ball 18 and the spring 19, the back surface 2a of the orbiting scroll 2
The pressure of the back pressure chamber 20 formed between the bearing and the bearing frame 3 is maintained at an intermediate level between the pressure of the suction chamber 5 and the pressure of the discharge chamber 12, thereby pressing the orbiting scroll 2 against the fixed scroll 1. It has a structure to be in close contact.
【００１６】駆動軸８内には油孔２１が設けられてお
り、また駆動軸８の備心軸部８ａおよび主軸部８ｂには
それぞれ油溝２１ａ，２１ｂが設けられている。さら
に、駆動軸８の下端は潤滑油溜り２２内に浸漬されて、
油孔２１と油溝２１ａ，２１ｂにより背圧室２０と潤滑
油溜り２２は連通している。また、潤滑油溜り２２は吐
出圧力になっているので背圧室２０との圧力差によって
潤滑油は旋回軸受９と主軸受１６に供給された後背圧室
２０に溜り、鋼球１８を押し上げて吸入室５に流入し、
吸入冷媒ガスとともに圧縮室６、吐出室１２、冷媒通路
１３を経て電動機１４，１５に導かれ、潤滑油溜り２２
に戻る。The drive shaft 8 is provided with an oil hole 21. The drive shaft 8 is provided with oil grooves 21a and 21b in the center shaft 8a and the main shaft 8b, respectively. Further, the lower end of the drive shaft 8 is immersed in the lubricating oil reservoir 22,
The back pressure chamber 20 and the lubricating oil reservoir 22 communicate with each other through the oil hole 21 and the oil grooves 21a and 21b. Further, since the lubricating oil reservoir 22 is at the discharge pressure, the lubricating oil is supplied to the slewing bearing 9 and the main bearing 16 and accumulates in the back pressure chamber 20 due to the pressure difference between the back pressure chamber 20 and pushes up the steel ball 18. Flows into the suction chamber 5,
The lubricating oil reservoir 22 is guided to the electric motors 14 and 15 through the compression chamber 6, the discharge chamber 12, and the refrigerant passage 13 together with the suction refrigerant gas.
Return to
【００１７】上記のような動作を行う圧縮機が停止した
時、吐出室１２の圧力のほうが圧縮室６の圧力よりも高
くなるので、吐出室１２の気体が圧縮室６に向かって逆
流しようとするが、逆止弁１１０が閉じているので小さ
な貫通孔１１ａを通ってその流量を制限されながら逆流
する。この結果、圧縮室６の圧力は急激に上昇すること
が無いので異常音やスクロールの破壊をおこすことがな
い。また、貫通孔１１ａにより比較的速やかに吸入側と
吐出側の圧力がバランスするので、潤滑油が吸入側に逆
流して潤滑油溜り２２の潤滑油が無くなることもない。When the compressor performing the above operation is stopped, the pressure in the discharge chamber 12 becomes higher than the pressure in the compression chamber 6, so that the gas in the discharge chamber 12 tends to flow back toward the compression chamber 6. However, since the check valve 110 is closed, the gas flows back through the small through hole 11a while its flow rate is restricted. As a result, since the pressure in the compression chamber 6 does not rise rapidly, there is no occurrence of abnormal noise or breakage of the scroll. Further, since the pressure on the suction side and the pressure on the discharge side are relatively quickly balanced by the through hole 11a, the lubricating oil does not flow backward to the suction side, and the lubricating oil in the lubricating oil reservoir 22 does not run out.
【００１８】本発明の請求項２に記載の発明は、上記請
求項１に記載の発明において、逆止弁１１０に設けた貫
通孔１１ａの直径を吐出孔直径の１０分の１以下に設定
したものである。貫通孔１１ａの直径は、大きすぎると
気体の逆流が急激になり旋回スクロールが急激な逆転を
行って破壊を起こし、小さすぎると吸入側と吐出側の圧
力がバランスするのに時間がかかってその間に潤滑油溜
りの潤滑油が吸入側に逆流して無くなってしまうという
不都合がある。According to a second aspect of the present invention, in the first aspect of the present invention, the diameter of the through hole 11a provided in the check valve 110 is set to be 1/10 or less of the diameter of the discharge hole. Things. If the diameter of the through hole 11a is too large, the backflow of the gas becomes sharp and the orbiting scroll reverses sharply, causing breakage. If the diameter is too small, it takes time for the pressures on the suction side and the discharge side to balance, and during that time, In addition, there is a disadvantage that the lubricating oil in the lubricating oil pool flows backward to the suction side and disappears.
【００１９】発明者等の実験によると貫通孔１１ａの直
径が吐出孔直径の１０分の１以下の場合には旋回スクロ
ールが安全な速度で逆転を行うので異常音やスクロール
の破壊を防止することができ、それよりも大きな直径と
した場合には旋回スクロールの逆転速度が大きくなって
異常音が発生し、スクロールの破壊の恐れがあることが
確認されている。貫通孔１１ａ直径の下限については気
体が通過できれば特に問題はないが、好ましくは吐出孔
直径の３０分の１以上、更に好ましくは２０分の１以上
に設定することが望ましい。According to experiments by the inventors, when the diameter of the through-hole 11a is less than one-tenth of the diameter of the discharge hole, the orbiting scroll reverses at a safe speed, so that abnormal sound and breakage of the scroll are prevented. It has been confirmed that when the diameter is larger than that, the reversing speed of the orbiting scroll increases, an abnormal sound is generated, and the scroll may be broken. There is no particular problem with the lower limit of the diameter of the through hole 11a as long as gas can pass therethrough.
【００２０】上記実施の形態１により、圧縮機停止時に
旋回スクロール２が逆転することなく吐出圧力と吸入圧
力との均圧を早めることができるため、潤滑油の吸入側
への逆流が無く、潤滑油溜り２２の潤滑油が無くなるこ
とを防止した信頼性の高い圧縮機を得ることができる。According to the first embodiment, when the compressor is stopped, the orbiting scroll 2 does not reversely rotate, and the pressure equalized between the discharge pressure and the suction pressure can be accelerated. A highly reliable compressor in which the lubricating oil in the oil sump 22 is prevented from running out can be obtained.
【００２１】（実施の形態２）図３は本発明の他の実施
形態における密閉型圧縮機の断面図、図４は図３におけ
る逆止弁近傍の斜視図である。本実施の形態が上記説明
した実施の形態１と異なるところは、逆支弁に貫通孔を
設ける代わりに圧縮室１２と吐出室６を連通する連通溝
１１ｂを、逆止弁１１をバイパスするように設けた点で
ある。本実施の形態では連通溝１１ｂが実施の形態１に
おける貫通孔１１ａと同じ働きをし、圧縮室６の圧力が
急激に上昇することが無く、かつ比較的速やかに吸入側
と吐出側の圧力がバランスするので、異常音の発生やス
クロールの破壊をおこさず、潤滑油が吸入側に逆流して
潤滑油溜り２２の潤滑油が無くなることもない。(Embodiment 2) FIG. 3 is a sectional view of a hermetic compressor according to another embodiment of the present invention, and FIG. 4 is a perspective view near the check valve in FIG. This embodiment is different from the first embodiment described above in that a communication groove 11b for communicating the compression chamber 12 with the discharge chamber 6 is provided instead of providing a through hole in the check valve, and the check valve 11 is bypassed. This is the point provided. In the present embodiment, the communication groove 11b has the same function as the through-hole 11a in the first embodiment, and the pressure in the compression chamber 6 does not rapidly increase, and the pressures on the suction side and the discharge side are relatively quickly increased. Since the balance is maintained, no abnormal sound is generated or the scroll is destroyed, and the lubricating oil does not flow backward to the suction side, so that the lubricating oil in the lubricating oil reservoir 22 does not run out.
【００２２】本発明の請求項４に記載の発明は、上記請
求項３に記載の発明において、固定スクロール背面１ａ
の逆止弁取り付け部に設けた連通溝１ｂの断面積を吐出
孔断面積の１００分の１以下に設定したものである。連
通溝１ｂの気体流れ方向直角面での断面積は、大きすぎ
ると気体の逆流が急激になり旋回スクロールが急激な逆
転を行って異常音やスクロールの破壊を起こし、小さす
ぎると吸入側と吐出側の圧力がバランスするのに時間が
かかってその間に潤滑油溜りの潤滑油が吸入側に逆流し
て無くなってしまうという不都合がある。According to a fourth aspect of the present invention, there is provided the fixed scroll back surface 1a according to the third aspect.
The cross-sectional area of the communication groove 1b provided in the check valve mounting portion is set to 1/100 or less of the cross-sectional area of the discharge hole. If the cross-sectional area of the communication groove 1b in the plane perpendicular to the gas flow direction is too large, the backflow of the gas becomes abrupt and the orbiting scroll reverses sharply, causing abnormal noise and destruction of the scroll. There is a disadvantage in that it takes time for the pressure on the side to balance, and during that time the lubricating oil in the lubricating oil pool flows back to the suction side and disappears.
【００２３】発明者等の実験によると連通溝１ｂの気体
流れ方向直角面での断面積が吐出孔断面積の１００分の
１以下の場合には旋回スクロールが安全な速度で逆転を
行うので異常音やスクロールの破壊を防止することがで
き、それよりも大きな断面積とした場合には旋回スクロ
ールの逆転速度が大きくなって異常音やスクロールの破
壊の恐れがあることが確認されている。連通溝１ｂ断面
積の下限については気体が通過できれば特に問題はない
が、好ましくは吐出孔断面積の９００分の１以上、更に
好ましくは４００分の１以上に設定することが望まし
い。According to an experiment by the inventors, if the cross-sectional area of the communication groove 1b on the plane perpendicular to the gas flow direction is less than 1/100 of the cross-sectional area of the discharge hole, the orbiting scroll reverses at a safe speed and is abnormal. It has been confirmed that the sound and the destruction of the scroll can be prevented, and when the cross-sectional area is larger than that, the reversal speed of the orbiting scroll is increased, and there is a possibility of abnormal sound and destruction of the scroll. The lower limit of the cross-sectional area of the communication groove 1b is not particularly limited as long as the gas can pass therethrough. However, it is preferable that the lower limit is set to 1/900 or more, more preferably 1/400 or more of the discharge hole cross-sectional area.
【００２４】上記実施の形態２により、圧縮機停止時に
旋回スクロール２が逆転することなく吐出圧力と吸入圧
力との均圧を早めることができるため、潤滑油の吸入側
への逆流が無く、潤滑油溜り２２の潤滑油が無くなるこ
とを防止した信頼性の高い圧縮機を得ることができる。According to the second embodiment, when the compressor is stopped, the orbiting scroll 2 does not rotate in the reverse direction, and the pressure equalized between the discharge pressure and the suction pressure can be accelerated. A highly reliable compressor in which the lubricating oil in the oil sump 22 is prevented from running out can be obtained.
【００２５】[0025]
【発明の効果】上記から明らかなように、請求項１およ
び請求項２に記載の発明は、固定スクロールの背面側に
貫通孔の開いた逆止弁を設けるもので、この構成によれ
ば、圧縮機停止時に旋回スクロールが逆転することなく
吐出圧力と吸入圧力との均圧を早めることができるた
め、潤滑油の吸入側への逆流が無く、潤滑油溜りの潤滑
油が無くなることを防止した信頼性の高い圧縮機を得る
ことができる。As is apparent from the above description, the first and second aspects of the present invention provide a check valve having a through hole on the back side of a fixed scroll. Since the equalizing pressure between the discharge pressure and the suction pressure can be accelerated without the revolving scroll rotating when the compressor is stopped, there is no backflow of the lubricating oil to the suction side, and the lubricating oil reservoir is prevented from running out of lubricating oil. A highly reliable compressor can be obtained.
【００２６】請求項３および請求項４に記載の発明は、
固定スクロールの背面側に逆止弁を設け、前記固定スク
ロールの逆止弁取り付け部に連通溝を設けるもので、こ
の構成によれば、圧縮機停止時に旋回スクロールが逆転
することなく吐出圧力と吸入圧力との均圧を早めること
ができるため、潤滑油の吸入側への逆流が無く、潤滑油
溜りの潤滑油が無くなることを防止した信頼性の高い圧
縮機を得ることができる。According to the third and fourth aspects of the present invention,
A check valve is provided on the back side of the fixed scroll, and a communication groove is provided in the check valve mounting portion of the fixed scroll. According to this configuration, the discharge pressure and the suction pressure are reduced without the orbiting scroll rotating backward when the compressor stops. Since the pressure equalization with the pressure can be advanced, there is no backflow of the lubricating oil to the suction side, and a highly reliable compressor that prevents the lubricating oil from running out of the lubricating oil reservoir can be obtained.
【図１】本発明の−実施例を示す密閉型スクロール圧縮
機の縦断面図FIG. 1 is a longitudinal sectional view of a hermetic scroll compressor showing an embodiment of the present invention.
【図２】同一実施例の固定スクロール背面斜視図FIG. 2 is a rear perspective view of the fixed scroll of the same embodiment.
【図３】本発明の他の実施例を示す密閉型スクロール圧
縮機の縦断面図FIG. 3 is a longitudinal sectional view of a hermetic scroll compressor showing another embodiment of the present invention.
【図４】同一実施例の固定スクロール背面斜視図FIG. 4 is a rear perspective view of the fixed scroll of the same embodiment.
【図５】従来の密閉型スクロール圧縮機の断面図FIG. 5 is a sectional view of a conventional hermetic scroll compressor.
１ 固定スクロール １ａ 固定スクロール背面 １ｂ 連通溝 ２ 旋回スクロール ２ａ 旋回スクロール背面 ３ 軸受フレーム ４ 吸入管 ５ 吸入室 ６ 圧縮室 ７ オルダムリング ８ 駆動軸 ８ａ 偏心軸部 ８ｂ 主軸部 ９ 旋回軸受 １０ 吐出孔 １１ 逆止弁 １１ 貫通孔 １２ 吐出室 １３ 冷媒通路 １４ 電動機（固定子） １５ 電動機（回転子） １６ 主軸受 １７ 副軸受 １８ 鋼球 １９ バネ ２０ 背圧室 ２１ 油孔 ２１ａ 油溝（備心軸部） ２１ｂ 油溝（主軸部） ２２ 潤滑油溜り DESCRIPTION OF SYMBOLS 1 Fixed scroll 1a Fixed scroll back surface 1b Communication groove 2 Orbiting scroll 2a Orbiting scroll back surface 3 Bearing frame 4 Suction pipe 5 Suction chamber 6 Compression chamber 7 Oldham ring 8 Drive shaft 8a Eccentric shaft portion 8b Main shaft portion 9 Rotating bearing 10 Discharge hole 11 Reverse Stop valve 11 Through hole 12 Discharge chamber 13 Refrigerant passage 14 Motor (stator) 15 Motor (rotor) 16 Main bearing 17 Secondary bearing 18 Steel ball 19 Spring 20 Back pressure chamber 21 Oil hole 21a Oil groove (core shaft) 21b Oil groove (spindle part) 22 Lubricant pool
───────────────────────────────────────────────────── フロントページの続き (72)発明者 河野 博之 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 Ｆターム(参考） 3H029 AA02 AA14 AA21 AB03 BB03 BB05 BB16 BB18 BB50 CC04 CC06 CC15 CC25 CC34 CC66 CC74 3H039 AA03 AA06 AA12 BB04 BB11 BB16 CC29 CC30 CC33 CC42 ──────────────────────────────────────────────────続 き Continued on the front page (72) Inventor Hiroyuki Kono 1006 Kadoma Kadoma, Osaka Prefecture Matsushita Electric Industrial Co., Ltd. (72) Inventor Hiromasa Ashiya 1006 Odaka Kadoma Kadoma City, Osaka Matsushita Electric Industrial Co., Ltd. 72) Inventor Shuichi Yamamoto 1006 Kazuma Kadoma, Kadoma City, Osaka Prefecture F-term in Matsushita Electric Industrial Co., Ltd. CC30 CC33 CC42
Claims (4)
の上側にスクロール圧縮機構、下側に電動機が配置さ
れ、前記スクロール圧縮機構は軸方向に貫通する油孔を
有する駆動軸で電動機に連結駆動され、前記駆動軸の下
端が潤滑油溜りに浸漬され、前記スクロール圧縮機構は
逆止弁を有する吐出孔を備えた固定スクロールと、前記
固定スクロールと噛み合って圧縮室を形成する旋回スク
ロールと、前記固定スクロールとの間で前記旋回スクロ
ールを摺動可能に挟持すると同時に前記駆動軸を軸支す
る主軸受を有する軸受フレームとから構成され、スクロ
ール圧縮機構で圧縮した冷媒ガスを減圧して前記旋回ス
クロール背面と軸受フレームとで形成する背圧室に供給
し、背圧室の圧力を吸入圧力より高く吐出圧力より低い
中間圧力にする事で旋回スクロールを固定スクロールに
密着させると同時に、前記背圧室と潤滑油溜りとは駆動
軸に設けた油孔を介して連通しており、潤滑油溜り油面
に作用する吐出圧力と背圧室の中間圧力との差圧力によ
り各摺動部に給油が行なわれる密閉型スクロール圧縮機
であって、前記逆止弁に貫通孔を設け、逆止弁が閉じた
状態でも僅かな量の気体が圧縮機構内部と密閉容器内部
との間で流通可能としたことを特徴とする密閉型スクロ
ール圧縮機。1. A scroll compression mechanism is disposed on the upper side of a sealed container having a lubricating oil reservoir at the bottom, and a motor is disposed on a lower side. The scroll compression mechanism is connected to the motor by a drive shaft having an oil hole penetrating in the axial direction. Driven, the lower end of the drive shaft is immersed in a lubricating oil reservoir, the scroll compression mechanism is provided with a fixed scroll having a discharge hole having a check valve, and an orbiting scroll that meshes with the fixed scroll to form a compression chamber; A bearing frame having a main bearing that supports the drive shaft at the same time as the orbiting scroll is slidably held between the fixed scroll and the fixed scroll. The pressure is supplied to the back pressure chamber formed by the back of the scroll and the bearing frame. At the same time that the rotary scroll is brought into close contact with the fixed scroll, the back pressure chamber and the lubricating oil reservoir communicate with each other through an oil hole provided in the drive shaft. A closed scroll compressor in which each sliding portion is refueled by a differential pressure from the intermediate pressure of the above, wherein the check valve is provided with a through hole, and a small amount of gas is supplied even when the check valve is closed. A hermetic scroll compressor characterized in that it can flow between the inside of a compression mechanism and the inside of a closed container.
径の１０分の１以下であることを特徴とする請求項１に
記載の密閉型スクロール圧縮機。2. The hermetic scroll compressor according to claim 1, wherein the diameter of the through hole provided in the check valve is one-tenth or less of the diameter of the discharge hole.
の上側にスクロール圧縮機構、下側に電動機が配置さ
れ、前記スクロール圧縮機構は軸方向に貫通する油孔を
有する駆動軸で電動機に連結駆動され、前記駆動軸の下
端が潤滑油溜りに浸漬され、前記スクロール圧縮機構は
逆止弁を有する吐出孔を備えた固定スクロールと、前記
固定スクロールと噛み合って圧縮室を形成する旋回スク
ロールと、前記固定スクロールとの間で前記旋回スクロ
ールを摺動可能に挟持すると同時に前記駆動軸を軸支す
る主軸受を有する軸受フレームとから構成され、スクロ
ール圧縮機構で圧縮した冷媒ガスを減圧して前記旋回ス
クロール背面と軸受フレームとで形成する背圧室に供給
し、背圧室の圧力を吸入圧力より高く吐出圧力より低い
中間圧力にする事で旋回スクロールを固定スクロールに
密着させると同時に、前記背圧室と潤滑油溜りとは駆動
軸に設けた油孔を介して連通しており、潤滑油溜り油面
に作用する吐出圧力と背圧室の中間圧力との差圧力によ
り各摺動部に給油が行なわれる密閉型スクロール圧縮機
であって、前記固定スクロールの逆止弁取り付け部に圧
縮機構内部と密閉容器内部との間を連通する連通溝を設
け、逆止弁が閉じた状態でも僅かな量の気体が圧縮機構
内部と密閉容器内部との間で流通可能としたことを特徴
とする密閉型スクロール圧縮機。3. A scroll compression mechanism is arranged on the upper side inside a sealed container having a lubricating oil reservoir at the bottom, and an electric motor is arranged on the lower side. The scroll compression mechanism is connected to the electric motor by a drive shaft having an oil hole penetrating in the axial direction. Driven, the lower end of the drive shaft is immersed in a lubricating oil reservoir, the scroll compression mechanism has a fixed scroll having a discharge hole having a check valve, and an orbiting scroll that meshes with the fixed scroll to form a compression chamber; A bearing frame having a main bearing that supports the drive shaft at the same time as the orbiting scroll is slidably held between the fixed scroll and the fixed scroll. The pressure is supplied to the back pressure chamber formed by the back of the scroll and the bearing frame. At the same time that the rotary scroll is brought into close contact with the fixed scroll, the back pressure chamber and the lubricating oil reservoir communicate with each other through an oil hole provided in the drive shaft. A closed-type scroll compressor in which oil is supplied to each sliding portion by a pressure difference from an intermediate pressure of the fixed scroll, wherein a check valve mounting portion of the fixed scroll communicates between the inside of the compression mechanism and the inside of the sealed container. A hermetic scroll compressor wherein a groove is provided so that a small amount of gas can flow between the inside of the compression mechanism and the inside of the closed vessel even when the check valve is closed.
に設けた連通溝の気体流通方向に対して直角方向の断面
積が吐出孔断面積の１００分の１以下であることを特徴
とする請求項３記載の密閉型スクロール圧縮機。4. A cross-sectional area in a direction perpendicular to a gas flow direction of a communication groove provided in a check valve mounting portion on a back surface of a fixed scroll is not more than 1/100 of a cross-sectional area of a discharge hole. Item 7. A hermetic scroll compressor according to Item 3.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001152068A JP2002349458A (en) | 2001-05-22 | 2001-05-22 | Hermetically closed type scroll compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001152068A JP2002349458A (en) | 2001-05-22 | 2001-05-22 | Hermetically closed type scroll compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JP2002349458A true JP2002349458A (en) | 2002-12-04 |
Family
ID=18996800
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2001152068A Pending JP2002349458A (en) | 2001-05-22 | 2001-05-22 | Hermetically closed type scroll compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2002349458A (en) |
Cited By (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2007003215A1 (en) * | 2005-07-05 | 2007-01-11 | Vhit S.P.A. | Vacuum vane pump with discharge valve |
| EP1953389A3 (en) * | 2007-01-29 | 2011-11-02 | Pierburg GmbH | Vacuum pump |
| JP2012127321A (en) * | 2010-12-17 | 2012-07-05 | Mitsubishi Electric Corp | Scroll compressor |
| US8469684B2 (en) | 2005-07-07 | 2013-06-25 | Oerlikon Leybold Vacuum Gmbh | Rotary vacuum pump with a discharge compensating channel |
| CN103541901A (en) * | 2012-07-10 | 2014-01-29 | 艾默生环境优化技术(苏州)有限公司 | Pressure control valve and scroll compressor |
| CN104343682A (en) * | 2013-08-07 | 2015-02-11 | 艾默生环境优化技术(苏州)有限公司 | Scroll compressor having a plurality of scroll members |
| US20180202440A1 (en) * | 2017-01-18 | 2018-07-19 | Lg Electronics Inc. | Scroll compressor |
| US10400772B2 (en) | 2013-08-07 | 2019-09-03 | Emerson Climate Technologies (Suzhou) Co., Ltd. | Scroll compressor having valve component arranged in passage of back pressure cavity and providing openings for passage of fluid |
| GB2584005A (en) * | 2019-03-22 | 2020-11-18 | Cummins Inc | Vacuum pump exhaust reed valve with pressure bleed |
| JP2020204302A (en) * | 2019-06-18 | 2020-12-24 | 株式会社クボタ | Engine with blow-by gas recirculation device |
| WO2021215651A1 (en) * | 2020-04-20 | 2021-10-28 | 엘지전자 주식회사 | Compressor |
| US11624531B2 (en) | 2018-06-22 | 2023-04-11 | Carrier Corporation | Oil control system and method for HVAC system |
| EP4180673A1 (en) * | 2021-11-16 | 2023-05-17 | Carrier Corporation | Compressor assembly including a flow-restricting valve |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS58172482A (en) * | 1982-04-05 | 1983-10-11 | Hitachi Ltd | Scroll compressor |
-
2001
- 2001-05-22 JP JP2001152068A patent/JP2002349458A/en active Pending
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS58172482A (en) * | 1982-04-05 | 1983-10-11 | Hitachi Ltd | Scroll compressor |
Cited By (23)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2007003215A1 (en) * | 2005-07-05 | 2007-01-11 | Vhit S.P.A. | Vacuum vane pump with discharge valve |
| US8469684B2 (en) | 2005-07-07 | 2013-06-25 | Oerlikon Leybold Vacuum Gmbh | Rotary vacuum pump with a discharge compensating channel |
| US9017051B2 (en) | 2005-07-07 | 2015-04-28 | Oerlikon Leybold Vacuum Gmbh | Rotary vacuum pump with a discharge compensating channel |
| EP1953389A3 (en) * | 2007-01-29 | 2011-11-02 | Pierburg GmbH | Vacuum pump |
| JP2012127321A (en) * | 2010-12-17 | 2012-07-05 | Mitsubishi Electric Corp | Scroll compressor |
| US10072659B2 (en) | 2012-07-10 | 2018-09-11 | Emerson Climate Technologies (Suzhou) Co., Ltd. | Pressure control valve and scroll compressor |
| CN103541901A (en) * | 2012-07-10 | 2014-01-29 | 艾默生环境优化技术(苏州)有限公司 | Pressure control valve and scroll compressor |
| CN103541901B (en) * | 2012-07-10 | 2015-10-07 | 艾默生环境优化技术(苏州)有限公司 | Pressure control valve and scroll compressor |
| CN104343682A (en) * | 2013-08-07 | 2015-02-11 | 艾默生环境优化技术(苏州)有限公司 | Scroll compressor having a plurality of scroll members |
| US10400772B2 (en) | 2013-08-07 | 2019-09-03 | Emerson Climate Technologies (Suzhou) Co., Ltd. | Scroll compressor having valve component arranged in passage of back pressure cavity and providing openings for passage of fluid |
| KR20180085285A (en) * | 2017-01-18 | 2018-07-26 | 엘지전자 주식회사 | Scroll compressor |
| US20180202440A1 (en) * | 2017-01-18 | 2018-07-19 | Lg Electronics Inc. | Scroll compressor |
| KR102565824B1 (en) * | 2017-01-18 | 2023-08-10 | 엘지전자 주식회사 | Scroll compressor |
| US10890182B2 (en) * | 2017-01-18 | 2021-01-12 | Lg Electronics Inc. | Scroll compressor having check valve and passage that communicates a discharge port with a discharge space when the check valve is closed |
| US11624531B2 (en) | 2018-06-22 | 2023-04-11 | Carrier Corporation | Oil control system and method for HVAC system |
| GB2584005B (en) * | 2019-03-22 | 2022-11-23 | Cummins Inc | Vacuum pump exhaust reed valve with pressure bleed |
| GB2584005A (en) * | 2019-03-22 | 2020-11-18 | Cummins Inc | Vacuum pump exhaust reed valve with pressure bleed |
| JP7099997B2 (en) | 2019-06-18 | 2022-07-12 | 株式会社クボタ | Engine with blow-by gas recirculation device |
| JP2020204302A (en) * | 2019-06-18 | 2020-12-24 | 株式会社クボタ | Engine with blow-by gas recirculation device |
| KR102318551B1 (en) * | 2020-04-20 | 2021-10-28 | 엘지전자 주식회사 | A compressor |
| WO2021215651A1 (en) * | 2020-04-20 | 2021-10-28 | 엘지전자 주식회사 | Compressor |
| EP4180673A1 (en) * | 2021-11-16 | 2023-05-17 | Carrier Corporation | Compressor assembly including a flow-restricting valve |
| CN116136211A (en) * | 2021-11-16 | 2023-05-19 | 开利公司 | Compressor assembly including a restrictor valve |
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