JP2001280276A - Multistage compressor - Google Patents
Multistage compressorInfo
- Publication number
- JP2001280276A JP2001280276A JP2000093721A JP2000093721A JP2001280276A JP 2001280276 A JP2001280276 A JP 2001280276A JP 2000093721 A JP2000093721 A JP 2000093721A JP 2000093721 A JP2000093721 A JP 2000093721A JP 2001280276 A JP2001280276 A JP 2001280276A
- Authority
- JP
- Japan
- Prior art keywords
- compression element
- compression
- stage
- length
- chamber
- 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.)
- Granted
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
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
- F04C18/3562—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
- F04C18/3564—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
-
- 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
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
-
- 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
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/008—Hermetic pumps
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、圧縮室と吸気室と
を区画するベーンの背後に形成されたバネ孔と、圧縮室
又は吸気室との間で生じる冷媒のリークを効率的に抑制
した多段圧縮機に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention effectively suppresses refrigerant leakage occurring between a compression hole or an intake chamber and a spring hole formed behind a vane that separates a compression chamber and an intake chamber. It relates to a multi-stage compressor.
【０００２】[0002]
【従来の技術】従来、ロータリ圧縮機等の圧縮機は種々
の技術分野に用いられ、冷媒としてはこれまでＲ−２２
等の塩素を含む冷媒（以下、特定フロンガスと記載す
る）が用いられていた。2. Description of the Related Art Conventionally, compressors such as rotary compressors have been used in various technical fields.
A refrigerant containing chlorine (hereinafter, referred to as a specific freon gas) has been used.
【０００３】しかし、このＲ−２２冷媒は、オゾン層を
破壊する原因となることが判明し規制対象となり、特定
フロンガスに代わる冷媒の研究開発が盛んに行われ、二
酸化炭素冷媒がその候補として期待されている。However, this R-22 refrigerant has been found to be a cause of destruction of the ozone layer, and has been subject to regulation. Research and development of refrigerants in place of specific CFCs have been actively conducted, and carbon dioxide refrigerant is expected as a candidate. Have been.
【０００４】このような二酸化炭素冷媒を用いたロータ
リ圧縮機として、圧縮要素を複数備えた多段圧縮機があ
る。以下、二酸化炭素冷媒を特に他の冷媒と区別しなけ
ればならない場合を除き単に冷媒と記載する。As a rotary compressor using such a carbon dioxide refrigerant, there is a multistage compressor provided with a plurality of compression elements. Hereinafter, a carbon dioxide refrigerant is simply referred to as a refrigerant unless it is necessary to distinguish it from other refrigerants.
【０００５】多段圧縮機は、複数の圧縮要素と、これを
駆動する駆動要素とを有し、これらが密閉容器内に収納
された構成となっている。[0005] The multi-stage compressor has a plurality of compression elements and a drive element for driving the compression elements, and these are housed in a closed container.
【０００６】図３は、かかる多段圧縮機のうち２段ロー
タリ圧縮機における前段圧縮要素１３０（図３において
上側の図）及び後段圧縮要素１４０（図３において下側
の図）の要部を示した図である。FIG. 3 shows a main part of a former-stage compression element 130 (upper view in FIG. 3) and a latter-stage compression element 140 (lower view in FIG. 3) of a two-stage rotary compressor among such multi-stage compressors. FIG.
【０００７】このような圧縮要素は、円筒状のシリンダ
１３１，１４１を有し、このシリンダ１３１，１４１内
に図示しない駆動要素から駆動力を受けて偏芯回転運動
するローラ１３３，１４３が配設されている。Such a compressing element has cylindrical cylinders 131 and 141, and rollers 133 and 143 which perform eccentric rotational movement by receiving a driving force from a driving element (not shown) are arranged in the cylinders 131 and 141. Have been.
【０００８】これにより、ローラ１３３，１４３とシリ
ンダ１３１，１４１との間に形成される空間がベーン１
３５，１４５により仕切られて吸気室Ｖ及び圧縮室Ｐが
構成され、吸気室Ｖが拡張することにより冷媒を吸気
し、圧縮室Ｐが縮小することにより冷媒を圧縮するよう
になっている。As a result, the space formed between the rollers 133 and 143 and the cylinders 131 and 141 is
An intake chamber V and a compression chamber P are defined by 35 and 145. The expansion of the intake chamber V takes in the refrigerant, and the compression chamber P contracts to compress the refrigerant.
【０００９】このベーン１３５，１４５は、ベーン孔１
３６、１４６に挿入され、その後端側にはバネ孔１３
８、１４８が形成されて、当該バネ孔１３８、１４８に
バネ１３７、１４７が挿入されると共に、その挿入口に
蓋１３９，１４９が設けられている。The vanes 135 and 145 are provided in the vane holes 1
36, 146, and a spring hole 13 at the rear end side.
8 and 148 are formed, springs 137 and 147 are inserted into the spring holes 138 and 148, and lids 139 and 149 are provided in the insertion openings.
【００１０】そして、バネ孔１３８、１４８がなす空間
は、その圧縮要素における吐出圧になるように形成され
ている。[0010] The space defined by the spring holes 138 and 148 is formed to have the discharge pressure of the compression element.
【００１１】これにより、ベーン１３５，１４５はバネ
１３７，１４７とバネ孔１３８，１４８の圧力によりロ
ーラ１３３，１４３側に付勢されて、その先端がローラ
１３３，１４３に当接して圧縮室Ｐと吸気室Ｖとの機密
性を維持するようになっている。As a result, the vanes 135 and 145 are urged toward the rollers 133 and 143 by the pressures of the springs 137 and 147 and the spring holes 138 and 148. The confidentiality with the intake chamber V is maintained.
【００１２】なお、バネ孔１３８，１４８は、原則とし
て機密性の蓋１３９，１４９により密閉容器内と連通し
ないように形成されるが、密閉容器内の圧力を特定の圧
縮要素におけるバネ孔１３８，１４８の圧力と略等しく
なるように設定されている場合には、かかる機密性は当
該圧縮要素において必ずしも必要でない。The spring holes 138 and 148 are formed in principle so as not to communicate with the inside of the closed container by the airtight covers 139 and 149. If set to be approximately equal to the pressure of 148, such confidentiality is not necessary in the compression element.
【００１３】[0013]
【発明が解決しようとする課題】しかしながら、従来は
多段圧縮機における各圧縮要素におけるベーン１３５，
１４５のストローク（移動距離）がそれぞれ異なるにも
関わらず、バネ孔１３８，１４８の長さが同じに設定さ
れているために、圧縮室Ｐ又は吸気室Ｖとバネ孔１３
８，１４８との間で発生するリークを適切に低減するこ
とができない問題があった。However, conventionally, the vanes 135 and 135 in each compression element in the multi-stage compressor are used.
Although the strokes (moving distances) of the spring holes 145 are different, the lengths of the spring holes 138 and 148 are set to be the same.
However, there has been a problem in that the leakage occurring between the first and second fins cannot be appropriately reduced.
【００１４】即ち、リーク量はバネ孔１３８，１４８の
圧力と吸気室Ｖ又は圧縮室Ｐの圧力との差圧及びリーク
抵抗により決る。That is, the amount of leakage is determined by the pressure difference between the pressure in the spring holes 138 and 148 and the pressure in the intake chamber V or the compression chamber P and the leak resistance.
【００１５】このリーク抵抗はリークパスに依存し、当
該リークパスはベーン１３５，１４５がシリンダ１３
１，１４１と接する領域であり、シリンダ１３１，１４
１の大きさが一定の場合には、バネ孔１３８，１４８の
長さにより略決る。The leak resistance depends on the leak path, and the leak path is formed by the vanes 135 and 145 that are connected to the cylinder 13.
1, 141, and the cylinders 131, 14
When the size of 1 is constant, it is substantially determined by the length of the spring holes 138 and 148.
【００１６】従って、バネ孔１３８，１４８の長さを短
くするればリークパスが長くなるので、リーク量を低減
させることができることになるが、従来はこのバネ孔１
３８，１４８の長さを同じ長さにしているのでリーク量
を適切に低減することができなかった。Accordingly, if the lengths of the spring holes 138 and 148 are shortened, the leak path becomes longer, so that the amount of leak can be reduced.
Since the lengths of 38 and 148 were set to the same length, the leak amount could not be reduced appropriately.
【００１７】そこで、本発明は、圧縮室又は吸気室とバ
ネ孔との間で生じるリーク量を適切に低減させて圧縮効
率の高い多段圧縮機を提供することを目的とする。Accordingly, an object of the present invention is to provide a multi-stage compressor having a high compression efficiency by appropriately reducing the amount of leak generated between a compression chamber or an intake chamber and a spring hole.
【００１８】[0018]
【課題を解決するための手段】上記課題を解決するた
め、請求項１にかかる発明は、シリンダ内をローラが偏
芯回転運動し、当該ローラにベーンが当接して吸気室及
び圧縮室が区画されてなる圧縮要素が２以上連結された
多段圧縮機において、ローラの偏芯回転運動に従いベー
ンが動く際の移動距離に対応して当該ベーンの背圧側に
形成されたバネ孔の長さを変えたことを特徴とする。According to a first aspect of the present invention, a roller rotates eccentrically in a cylinder and a vane abuts on the roller to partition an intake chamber and a compression chamber. In a multi-stage compressor in which two or more compression elements are connected, the length of a spring hole formed on the back pressure side of the vane is changed according to the moving distance when the vane moves according to the eccentric rotation of the roller. It is characterized by having.
【００１９】請求項２にかかる発明は、後段側の圧縮要
素におけるバネ孔の長さを、前段側の圧縮要素における
バネ孔の長さより短くしたことを特徴とする。The invention according to claim 2 is characterized in that the length of the spring hole in the rear compression element is shorter than the length of the spring hole in the front compression element.
【００２０】[0020]
【発明の実施の形態】本発明の実施の形態を図を参照し
て説明する。図１は多段圧縮機の例として２段ロータリ
圧縮機の側断面図である。なお、本発明は２段圧縮機に
限定されるものではなく、それ以上の段数を有する圧縮
機であっても良い。DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be described with reference to the drawings. FIG. 1 is a side sectional view of a two-stage rotary compressor as an example of a multi-stage compressor. Note that the present invention is not limited to a two-stage compressor, and may be a compressor having more stages.
【００２１】図１に示すロータリ圧縮機は駆動手段であ
るモータ２０、このモータ２０の下方に設けられた圧縮
手段である前段圧縮要素３０及び後段圧縮要素４０等を
有して、これらが密閉容器１０内に収納され、冷媒とし
て二酸化炭素冷媒（冷媒）が用いられている。The rotary compressor shown in FIG. 1 has a motor 20 as a driving means, a first-stage compression element 30 and a second-stage compression element 40 as compression means provided below the motor 20, and the like. A carbon dioxide refrigerant (refrigerant) is used as the refrigerant.
【００２２】なお、密閉容器１０の底部には潤滑油１５
が貯留しており、各圧縮要素３０，４０における摺動部
等を潤滑するようになっている。The lubricating oil 15 is provided at the bottom of the closed container 10.
Is stored, and lubricates the sliding portions and the like in each of the compression elements 30 and 40.
【００２３】前段圧縮要素３０には吸入管１１が設けら
れて、機外からの冷媒が当該前段圧縮要素３０に吸気さ
れ、圧縮されて連結管１６を介して後段圧縮要素４０に
吸入され、当該後段圧縮要素４０で圧縮されて機外に吐
出される。図１における矢印はこのような冷媒の流れを
示している。The front-stage compression element 30 is provided with a suction pipe 11, and a refrigerant from outside the machine is sucked into the front-stage compression element 30, compressed and sucked into the rear-stage compression element 40 via the connecting pipe 16. It is compressed by the latter-stage compression element 40 and discharged outside the machine. The arrows in FIG. 1 indicate such a flow of the refrigerant.
【００２４】このような前段圧縮要素３０及び後段圧縮
要素４０における吸気及び圧縮機構は同じで、シリンダ
３１，４１と該シリンダ３１，４１に内設されたローラ
３３，４３等を有している。The intake and compression mechanisms of the first compression element 30 and the second compression element 40 are the same, and include cylinders 31 and 41 and rollers 33 and 43 provided in the cylinders 31 and 41.
【００２５】図２は、かかるシリンダ３１，４１とロー
ラ３３，４３との関係を明示するための模式図で、上側
が前段圧縮要素３０、下側が後段圧縮要素４０を示して
いる。FIG. 2 is a schematic diagram for clearly showing the relationship between the cylinders 31 and 41 and the rollers 33 and 43. The upper side shows the front compression element 30 and the lower side shows the rear compression element 40.
【００２６】ローラ３３，４３には、ベーン３５，４５
が当接して、ローラ３３，４３とシリンダ３１，４１と
の間に形成される三日月状の空間を圧縮室Ｐと吸気室Ｖ
とに区画している。The rollers 33 and 43 have vanes 35 and 45, respectively.
Are brought into contact with each other to form a crescent-shaped space formed between the rollers 33 and 43 and the cylinders 31 and 41 in the compression chamber P and the intake chamber V.
And divided into
【００２７】ベーン３５，４５は、ベーン孔３６，４６
に挿入され、後端部がバネ３７，４７により付勢され
て、先端部がローラ３３，４３に当接している。The vanes 35 and 45 have vane holes 36 and 46, respectively.
The rear end is urged by springs 37 and 47, and the front end contacts the rollers 33 and 43.
【００２８】このバネ３７，４７はバネ孔３８，４８に
挿入され、当該バネ孔３８，４８が蓋３９，４９により
塞がれている。The springs 37, 47 are inserted into spring holes 38, 48, and the spring holes 38, 48 are closed by lids 39, 49.
【００２９】なお、バネ孔３８，４８は、その圧縮要素
のおける吐出圧力になるように図示しない流路が設けら
れている。The spring holes 38 and 48 are provided with a flow path (not shown) so that the discharge pressure of the compression element is attained.
【００３０】これにより、ベーン３５，４５はバネ３
７，４７とバネ孔３８，４８の圧力とによりローラ３
３，４３側に付勢されて、圧縮室Ｐと吸気室Ｖとの機密
性が保持されるようになっている。As a result, the vanes 35 and 45 are
7 and 47 and the pressure of the spring holes 38 and 48, the roller 3
Energized to the sides 3 and 43, the confidentiality between the compression chamber P and the intake chamber V is maintained.
【００３１】ローラ３３，４３の内部には、クランク３
２，４２が配設され、当該クランク３２，４２がモータ
２０の回転軸２１と連結されて、モータ２０が回転する
ことによりローラ３３，４３はクランク３２，４２から
力を受けて偏芯回転運動するようになる。Inside the rollers 33 and 43, there is a crank 3
The cranks 32 and 42 are connected to the rotating shaft 21 of the motor 20, and when the motor 20 rotates, the rollers 33 and 43 receive the force from the cranks 32 and 42 and perform eccentric rotational movement. I will be.
【００３２】ローラ３３，４３が偏芯回転運動すると、
先に述べた三日月状の空間は向きを変え、これに伴い圧
縮室Ｐと吸気室Ｖとの容積比が変化して冷媒を吸気し、
圧縮するようになる。When the rollers 33 and 43 move eccentrically,
The crescent-shaped space described above changes direction, and the volume ratio between the compression chamber P and the suction chamber V changes in accordance with the direction, thereby sucking the refrigerant,
Become compressed.
【００３３】多段圧縮機では、前段の圧縮要素が吐出し
た冷媒を後段の圧縮要素が吸気して圧縮するため、後段
側の排除容積を小さくする必要がある。In the multi-stage compressor, the refrigerant discharged from the upstream compression element is taken in by the downstream compression element and compressed, so that it is necessary to reduce the displacement volume on the downstream side.
【００３４】例えば、図１に示す２段構成の場合、前段
圧縮要素３０の排除容積を３ｃｃとすれば、後段圧縮要
素４０は３ｃｃ未満としないと前段圧縮要素３０の意味
がなくなってしまう。For example, in the case of the two-stage configuration shown in FIG. 1, if the excluded volume of the first-stage compression element 30 is 3 cc, the significance of the first-stage compression element 30 will be lost unless the second-stage compression element 40 is less than 3 cc.
【００３５】無論、前段圧縮要素３０から吐出された冷
媒の全てが後段圧縮要素４０に吸気されないとすると、
吸気されない分だけ圧縮効率が低下するので、現実には
後段圧縮要素４０は吐出された冷媒を略全て吸気するよ
うになっている。Of course, if not all of the refrigerant discharged from the first-stage compression element 30 is taken into the second-stage compression element 40,
Since the compression efficiency is reduced by the amount not taken in, the post-stage compression element 40 actually takes in almost all of the discharged refrigerant.
【００３６】従って、多段圧縮機においては、後段側に
なるほど排除容積を小さくしなければならず、このため
ローラ４３の直径Ｄ２をローラ３３の直径Ｄ１より大き
くしている（Ｄ２＞Ｄ１）。Accordingly, in the multi-stage compressor, the displacement volume must be reduced toward the rear stage, and therefore, the diameter D2 of the roller 43 is made larger than the diameter D1 of the roller 33 (D2> D1).
【００３７】このように、ローラ３３，４３の大きさが
異なるため、ベーン３５，４５のストロークも異なる。As described above, since the sizes of the rollers 33 and 43 are different, the strokes of the vanes 35 and 45 are also different.
【００３８】そこで、本実施の形態では、後段圧縮要素
４０におけるバネ孔４８の長さＬ２を前段圧縮要素３０
におけるバネ孔３８の長さＬ１より短くして（Ｌ２＜Ｌ
１）、リークパスをながくすることによりリーク量の低
減を図っている。Therefore, in the present embodiment, the length L2 of the spring hole 48 in the rear compression element 40 is
(L2 <L)
1) The leak amount is reduced by reducing the length of the leak path.
【００３９】即ち、ベーン３５，４５のストロークが異
なる場合には、バネの変位量も当然異なり、当該バネ３
７，４７を収納するバネ孔３８，４８の長さもこれに応
じて変えることができる。That is, when the strokes of the vanes 35 and 45 are different, the displacement amounts of the springs are naturally different.
The length of the spring holes 38, 48 for accommodating 7, 47 can also be changed accordingly.
【００４０】例えば、図２に示す場合には、ベーン３５
とベーン４５とが同じ長さであると、ベーン３５，４５
とバネ３７，４７とが接する位置は、後段圧縮要素４０
の方がシリンダ外周部側に位置することになる。For example, in the case shown in FIG.
And the vane 45 are the same length, the vanes 35, 45
The position where the springs 37 and 47 come into contact with each other
Is located on the outer peripheral side of the cylinder.
【００４１】従って、このバネ４７を収納するバネ孔４
８の長さをもっと小さくすることができるようになる。Therefore, the spring hole 4 for accommodating the spring 47 is provided.
8 can be made even smaller.
【００４２】このような観点から、上述したようにバネ
孔４８をバネ孔３８より短くして、これによりリークパ
スを長くすることによりリーク量の低減を図っている。From such a viewpoint, as described above, the amount of leak is reduced by making the spring hole 48 shorter than the spring hole 38 and thereby lengthening the leak path.
【００４３】なお、バネ孔４８を短くすることはベーン
４５がシリンダ４１と接する領域（上述したリークパ
ス）が長くなることを意味するので、ベーン３５，４５
の摺動抵抗の増大が懸念される。It should be noted that shortening the spring hole 48 means that the region where the vane 45 is in contact with the cylinder 41 (the above-described leak path) becomes longer.
There is a concern that the sliding resistance will increase.
【００４４】しかし、シリンダ３１，４１は略円盤状に
形成されており、従来用いられていたＲ−２２冷媒のと
きのシリンダ厚は１６ｍｍであるが、二酸化炭素冷媒の
ときのシリンダ厚は約９ｍｍであるので、基本的に摺動
面積が小さくなっている。However, the cylinders 31 and 41 are formed in a substantially disk shape, and the cylinder thickness of the conventionally used R-22 refrigerant is 16 mm, while the cylinder thickness of the carbon dioxide refrigerant is about 9 mm. Therefore, the sliding area is basically small.
【００４５】従って、冷媒として二酸化炭素冷媒を用い
る場合には、バネ孔４８の長さを多少長くすることによ
る摺動抵抗の増大よりもリーク量が押えられる効果の方
が大きい。Therefore, when a carbon dioxide refrigerant is used as the refrigerant, the effect of suppressing the leak amount is larger than the increase in the sliding resistance due to the length of the spring hole 48 being somewhat increased.
【００４６】なお、上記説明では各圧縮要素におけるバ
ネ孔３８，４８の圧力はその圧縮要素の吐出圧力に略等
しく設定されている場合について説明したが、本発明は
これに限定されるものではなく、当該圧縮要素の吐出圧
以上の圧力に設定されている場合にも適用できることは
言うまでもない。In the above description, a case has been described where the pressure of the spring holes 38 and 48 in each compression element is set substantially equal to the discharge pressure of the compression element. However, the present invention is not limited to this. Needless to say, the present invention can be applied to the case where the pressure is set to be equal to or higher than the discharge pressure of the compression element.
【００４７】[0047]
【発明の効果】以上説明したように請求項１にかかる発
明によれば、ローラの偏芯回転運動に従いベーンが動く
際の移動距離に対応してバネ孔の長さを変えたので、圧
縮室又は吸気室とバネ孔との間で生じるリーク量を適切
に低減させることができ、圧縮効率が向上する。As described above, according to the first aspect of the present invention, the length of the spring hole is changed in accordance with the moving distance when the vane moves in accordance with the eccentric rotation of the roller. Alternatively, the amount of leak generated between the intake chamber and the spring hole can be appropriately reduced, and the compression efficiency is improved.
【００４８】請求項２にかかる発明によれば、後段側の
圧縮要素におけるバネ孔の長さを前段側の圧縮要素にお
けるバネ孔より短くしたので、圧縮室又は吸気室とバネ
孔との間で生じるリーク量を低減でき、圧縮効率が向上
する。According to the second aspect of the present invention, since the length of the spring hole in the compression element on the rear stage is shorter than the length of the spring hole in the compression element on the front stage, the distance between the compression chamber or the suction chamber and the spring hole can be reduced. The generated leak amount can be reduced, and the compression efficiency is improved.
【図１】本発明の実施の形態の説明に適用される２段ロ
ータリ圧縮機の断面図である。FIG. 1 is a sectional view of a two-stage rotary compressor applied to an embodiment of the present invention.
【図２】図１における圧縮要素の詳細図である。FIG. 2 is a detailed view of a compression element in FIG.
【図３】従来の技術の説明に適用される２段ロータリ圧
縮機における圧縮要素の詳細図である。FIG. 3 is a detailed view of a compression element in a two-stage rotary compressor applied to the description of the related art.
１０ 密閉容器 ３０ 前段圧縮要素 ３１，４１ シリンダ ３３，４３ ローラ ３５，４５ ベーン ３６，４６ ベーン孔 ３７，４７ バネ ３８，４８ バネ孔 ３９，４９ 蓋 ４０ 後段圧縮要素 DESCRIPTION OF SYMBOLS 10 Closed container 30 Front compression element 31, 41 Cylinder 33, 43 Roller 35, 45 Vane 36, 46 Vane hole 37, 47 Spring 38, 48 Spring hole 39, 49 Lid 40 Post compression element
───────────────────────────────────────────────────── フロントページの続き (72)発明者 只野 昌也 大阪府守口市京阪本通２丁目５番５号 三 洋電機株式会社内 (72)発明者 小田 淳志 大阪府守口市京阪本通２丁目５番５号 三 洋電機株式会社内 Ｆターム(参考） 3H029 AA04 AA13 AB03 AB08 BB16 CC02 ──────────────────────────────────────────────────続 き Continued on the front page (72) Inventor Masaya Tadano 2-5-5 Keihanhondori, Moriguchi-shi, Osaka Sanyo Electric Co., Ltd. (72) Atsushi Oda 2-chome, Keihanhondori, Moriguchi-shi, Osaka No. 5 Sanyo Electric Co., Ltd. F term (reference) 3H029 AA04 AA13 AB03 AB08 BB16 CC02
Claims (2)
当該ローラにベーンが当接して吸気室及び圧縮室が区画
されてなる圧縮要素が２以上連結された多段圧縮機にお
いて、 前記ローラの偏芯回転運動に従い前記ベーンが動く際の
移動距離に対応して当該ベーンの背圧側に形成されたバ
ネ孔の長さを変えたことを特徴とする多段圧縮機。A roller eccentrically rotating within a cylinder;
In a multi-stage compressor in which two or more compression elements each having a suction chamber and a compression chamber defined by contacting a vane with the roller are connected, the multi-stage compressor corresponds to a moving distance when the vane moves according to the eccentric rotation of the roller. The length of a spring hole formed on the back pressure side of the vane is changed.
長さを、前段側の前記圧縮要素におけるバネ孔の長さよ
り短くしたことを特徴とする請求項１記載の多段圧縮
機。2. The multi-stage compressor according to claim 1, wherein the length of the spring hole in the compression element on the rear stage is shorter than the length of the spring hole in the compression element on the front stage.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2000093721A JP3579324B2 (en) | 2000-03-30 | 2000-03-30 | Multi-stage compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2000093721A JP3579324B2 (en) | 2000-03-30 | 2000-03-30 | Multi-stage compressor |
Related Child Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2004167906A Division JP3685798B2 (en) | 2004-06-07 | 2004-06-07 | Multistage compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JP2001280276A true JP2001280276A (en) | 2001-10-10 |
| JP3579324B2 JP3579324B2 (en) | 2004-10-20 |
Family
ID=18608868
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2000093721A Expired - Fee Related JP3579324B2 (en) | 2000-03-30 | 2000-03-30 | Multi-stage compressor |
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| Country | Link |
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| JP (1) | JP3579324B2 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2004053335A1 (en) * | 2002-12-11 | 2004-06-24 | Matsushita Electric Industrial Co., Ltd. | Rotary compressor |
| CN109026699A (en) * | 2018-08-21 | 2018-12-18 | 珠海凌达压缩机有限公司 | Pump body, compressor and pump body manufacturing method |
-
2000
- 2000-03-30 JP JP2000093721A patent/JP3579324B2/en not_active Expired - Fee Related
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2004053335A1 (en) * | 2002-12-11 | 2004-06-24 | Matsushita Electric Industrial Co., Ltd. | Rotary compressor |
| CN109026699A (en) * | 2018-08-21 | 2018-12-18 | 珠海凌达压缩机有限公司 | Pump body, compressor and pump body manufacturing method |
| CN109026699B (en) * | 2018-08-21 | 2024-03-29 | 珠海凌达压缩机有限公司 | Pump body, compressor and manufacturing method of pump body |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3579324B2 (en) | 2004-10-20 |
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