JPH0311101A - Scroll fluid machine - Google Patents
Scroll fluid machineInfo
- Publication number
- JPH0311101A JPH0311101A JP14522789A JP14522789A JPH0311101A JP H0311101 A JPH0311101 A JP H0311101A JP 14522789 A JP14522789 A JP 14522789A JP 14522789 A JP14522789 A JP 14522789A JP H0311101 A JPH0311101 A JP H0311101A
- Authority
- JP
- Japan
- Prior art keywords
- sealing member
- fluid machine
- pressure
- scroll
- scroll fluid
- 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
- 239000012530 fluid Substances 0.000 title claims abstract description 13
- 238000007789 sealing Methods 0.000 claims abstract description 44
- 230000002093 peripheral effect Effects 0.000 claims description 6
- 230000015572 biosynthetic process Effects 0.000 claims description 5
- 239000000463 material Substances 0.000 claims description 5
- 230000013011 mating Effects 0.000 claims description 3
- 230000000052 comparative effect Effects 0.000 description 8
- 230000000694 effects Effects 0.000 description 6
- 230000006835 compression Effects 0.000 description 4
- 238000007906 compression Methods 0.000 description 4
- 230000002159 abnormal effect Effects 0.000 description 2
- 230000000903 blocking effect Effects 0.000 description 1
- 230000036772 blood pressure Effects 0.000 description 1
- 230000015556 catabolic process Effects 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 238000006731 degradation reaction Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000007774 longterm Effects 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 239000011347 resin Substances 0.000 description 1
- 229920005989 resin Polymers 0.000 description 1
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
- F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
- F04C27/005—Axial sealings for working fluid
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Sealing Devices (AREA)
Abstract
Description
【発明の詳細な説明】
「産業上の利用分野」
本発明は、圧縮機、膨張機、及び真空ポンプとして機能
するスクロール流体機械に係り、特に相手側スクロール
の摺動面と対峙する螺旋状のラップ端面に、断面矩形状
の溝部を介してシール部材を嵌入させたスクロール流体
機械に間する。Detailed Description of the Invention "Field of Industrial Application" The present invention relates to a scroll fluid machine that functions as a compressor, an expander, and a vacuum pump. It is installed in a scroll fluid machine in which a sealing member is fitted into the end face of the wrap via a groove having a rectangular cross section.
「従来の技術」 従来より、第５図（Ａ）（Ｂ）に示すように。"Conventional technology" Conventionally, as shown in FIGS. 5(A) and 5(B).
周壁１１により囲繞された凹状空間１２内に第１のラッ
プ１３を形成した固定スクロールｌＯと、前記第１のラ
ー、ブ１３に嵌合可能な第２のラップ２１を有する旋回
スクロール２０とからなり１例えば前記固定スクロール
１０の凹状空間１２と対面する周壁１１と、凹状空間中
心域に位置する第２のラップ２１の摺動面１４（底面）
上に夫々吸込０１８と吐出口１７を設けるとともに、圧
縮室として機能する両う−、プ間の接点（又は最近接点
）が徐々に中心へ向かって移動するように、旋回スクロ
ール２０を一定の半径で固定スクロール１０のチー２プ
２１の中心の周りを公転運動させる事により、前記吸込
口より凹状空間１２内に導入した気体を第２のラップ２
１の巻き絆り端２１ｂ（外端）を回り込みながら、両ラ
ップ１３．２１によって形成される密閉空間２２に取り
込み、旋回スクロール２０の公転運動とともに徐々にそ
の容積を減少させながら、中心に向かって移動させ、該
密閉空間２２内の気体が高圧化した際に吐出口１７と導
通させて、該吐出口１７より前記高圧気体を外部に排出
可能に構成したスクロール式圧縮機は公知である。It consists of a fixed scroll 1O in which a first wrap 13 is formed in a concave space 12 surrounded by a peripheral wall 11, and an orbiting scroll 20 having a second wrap 21 that can fit into the first roller 13. 1. For example, the peripheral wall 11 facing the concave space 12 of the fixed scroll 10, and the sliding surface 14 (bottom surface) of the second wrap 21 located in the center area of the concave space.
In addition to providing a suction port 018 and a discharge port 17 at the top, the orbiting scroll 20 is set at a certain radius so that the contact point (or closest point) between the two ports, which function as compression chambers, gradually moves toward the center. By causing the fixed scroll 10 to revolve around the center of the tip 21, the gas introduced into the concave space 12 from the suction port is transferred to the second wrap 2.
While going around the wrapping end 21b (outer end) of the wrapper 13.21, it is taken into the sealed space 22 formed by both wraps 13. A scroll type compressor is known that is configured to be able to move and, when the gas in the closed space 22 becomes high pressure, communicate with the discharge port 17 and discharge the high-pressure gas to the outside from the discharge port 17.
この種の圧縮機においては相手側スクロール１０．２０
の摺動面１４（旋回スクロール２０側の摺動面は不図示
）と対峙する螺旋状のラップ端面２１ａに断面矩形状に
凹設した溝部２にシール部材１を嵌入させ、該シール部
材１を介して前記摺動面１４とラップ２１１１ＪＩに形
成される密閉空間のシール性旋の向上を図るとともに、
好ましくは前記シール部材１を帯状自己潤滑材で形成す
る事により、前記圧縮機の無給油化を図った装置も提案
されている。In this type of compressor, the mating scroll 10.20
The seal member 1 is fitted into a groove 2 having a rectangular cross section in the spiral wrap end surface 21a facing the sliding surface 14 (the sliding surface on the orbiting scroll 20 side is not shown). In addition to improving the sealing properties of the closed space formed between the sliding surface 14 and the wrap 2111JI through the
A device has also been proposed in which the seal member 1 is preferably made of a belt-shaped self-lubricating material, thereby eliminating the need for oil supply in the compressor.
そしてかかる無給油式の圧縮機においては第３図（ａ）
に示すように高圧側の密閉空間ＰＩより溝部側壁２ｂ間
の空隙３２を介してシール部材底面ｌａ側に導入された
背圧を利用して前記シール部材ｌを摺動面１４偏に押圧
させる事により前記シール性能を確保するように構成し
ている。In such an oil-free compressor, Fig. 3(a)
As shown in the figure, the seal member l is pressed against the sliding surface 14 using the back pressure introduced from the high-pressure side sealed space PI to the bottom surface la side of the seal member through the gap 32 between the groove side walls 2b. The structure is such that the above-mentioned sealing performance is ensured.
従って前記背圧による円滑な押圧力を得るには少なくと
も前記溝部底面２ａとシール部材１間の空隙３１を確保
する必要があるが、前記空隙３１の存在はラップ２１螺
旋方向に沿って中心域の高圧空気が外周側に漏洩してし
まう事になる。Therefore, in order to obtain a smooth pressing force due to the back pressure, it is necessary to ensure at least a gap 31 between the groove bottom surface 2a and the sealing member 1. High pressure air will leak to the outer periphery.
かかる欠点を解消する為にｗ４２図（ｇ）に示すように
、前記溝部２と対面するシール部材底面ｌａ側に長手方
向に沿って多段状に切込みを入れて形成した輪状突起５
１を設け、該突起５１により前記空隙３１のラップ２１
螺旋方向の導通を遮断し、これにより高圧気体の漏洩を
防止した技術が存在する。In order to eliminate this drawback, as shown in Fig. W42 (g), an annular projection 5 is formed by making multi-stage cuts along the longitudinal direction on the bottom surface la side of the sealing member facing the groove portion 2.
1 is provided, and the protrusion 51 wraps the gap 31 in the wrap 21.
There is a technique in which conduction in the helical direction is interrupted, thereby preventing leakage of high-pressure gas.
（特開昭８３−８１７０１号）
［発明が解決しようとする課題」
しかしながら前記シール部材ｌと溝部２間の空隙は底面
側には空隙３１、側壁側には空隙３２がある為に該側壁
側に漏洩が生じてしまう。(Unexamined Japanese Patent Publication No. 83-81701) [Problems to be Solved by the Invention] However, since the gap between the seal member l and the groove portion 2 has a gap 31 on the bottom side and a gap 32 on the side wall side, leakage will occur.
この為前記シール部材ｌと溝部２間の側壁側のクリアラ
ンスを小にして前記漏洩を極力少なくしようとする試み
がなされているが、自己潤滑材からなるシール部材ｌは
ラップ２１に比較して熱膨張率が大である為に、而も外
周側より中心域側に向け徐々に密閉空間Ｐ１の容積を減
少させながら気体を圧縮するスクロール圧縮機において
はラップ２１外周域側に比較して中心域側が高温化、言
い換えれば螺旋方向に沿ってラップ２１温度が異なる為
に、例吹ばラップ２１外周側に合せて前記側壁面の空隙
３２間隔を設定すると中心域側に位置するシール部材ｌ
が溝部２側壁面に密着し、結果としてチップシールの上
下の動きに対する摺動抵抗が大幅に増大する為に、例え
シール部材ｌの背面側に背圧を印加しても円滑なシール
性能を得る喜が出来ない。For this reason, attempts have been made to reduce the leakage as much as possible by reducing the clearance between the seal member l and the groove 2 on the side wall side. Since the expansion rate is large, in a scroll compressor that compresses gas while gradually decreasing the volume of the closed space P1 from the outer circumference side toward the center area side, the wrap 21 is compressed in the center area compared to the outer circumference side. In other words, since the temperature of the wrap 21 differs along the spiral direction, for example, if the gap 32 of the side wall surface is set to match the outer circumferential side of the wrap 21, the seal member l located on the center area side
is in close contact with the side wall surface of the groove part 2, and as a result, the sliding resistance against the vertical movement of the chip seal is greatly increased, so even if back pressure is applied to the back side of the seal member l, smooth sealing performance is obtained. I can't be happy.
一方うツブ２１中心域側に合せて前記側壁面の空隙３２
間隔を設定すると前記と逆に外周側の空隙３２間隔が必
要以上に大になり、結果として溝部２側壁面を流れる気
体漏洩量が大になるのみならず、第３図に示すようにシ
ール部材ｌが傾斜してその血圧の変化により異常摩耗が
生じる場合がある。On the other hand, a gap 32 in the side wall surface is aligned with the center region side of the knob 21.
If the interval is set, contrary to the above, the interval between the gaps 32 on the outer circumferential side becomes larger than necessary, and as a result, not only does the amount of gas leaking through the side wall surface of the groove 2 increase, but also the sealing member as shown in FIG. 1 may be inclined and abnormal wear may occur due to changes in blood pressure.
かかる欠点を解消する為に本出願人は、例えば第２図（
ｆ）に示すように、＃記シール部材底面ｌａ側に形成し
た多段状の突起５２形成位置と対応させて、シール部材
ｌの高圧側側壁面にも同様の切込み突起５３を形成して
前記螺旋方向の漏洩を完全に遮断するようにしたスクロ
ール圧縮機も検討した（以下比較発明という）が、この
ように構成すると前記溝部２空隙３１．３２の漏洩が底
面２ａ側でも側壁面２ｂ側でも完全に遮断される事にな
る為に、下記のような問題が生じる事になる。In order to eliminate such drawbacks, the present applicant has proposed, for example, Fig. 2 (
As shown in f), a similar cut protrusion 53 is formed on the high-pressure side side wall surface of the seal member l in correspondence with the formation position of the multi-step protrusion 52 formed on the bottom surface la of the seal member 1, and the spiral We also considered a scroll compressor that completely blocks leakage in both directions (hereinafter referred to as a comparative invention), but with this configuration, leakage from the groove 2 gaps 31 and 32 can be completely blocked on both the bottom surface 2a side and the side wall surface 2b side. As a result, the following problems will occur.
即ち前記シール部材１の背圧言い換えれば押圧力は、該
シール部材１によって仕切られる隣接する密閉空間同士
の圧力差によって決定されるものであるが、スクロール
圧縮機の場合は第５図に示しように吐出口１７と連通し
吐出圧力と同圧のｗＩＪｌの密閉空間ＰＯ１高圧状態に
ある第２の密閉空間Ｐ１、圧縮状態にみる低圧側密閉空
間Ｐ２．及びその外側にある常圧化された密閉空間Ｐ３
と、多数の圧力の異なる空間が存在し、従ってＰＯ（吐
出圧）〉〉２口高圧） ）Ｐ２（低圧））Ｐ３ （常圧
）と、隣接する密閉空間同士の圧力差に大きなバラツキ
を有する為に、前記のように各突起５２．５３間隔毎に
完全に遮断してしまうと、前記圧力差に対応して各突起
５２．５３間隔毎のシール部材１の押圧力（面圧）が大
きくバラツキ、結果としてとて突起間隔毎にシール部材
ｌの摩耗量にバラツキが生じ耐久性の低減とともに、結
果として長期に亙る円滑なシール性能の確保が困難にな
る。That is, the back pressure of the seal member 1, in other words, the pressing force, is determined by the pressure difference between adjacent closed spaces partitioned by the seal member 1, and in the case of a scroll compressor, as shown in FIG. A closed space PO1 that communicates with the discharge port 17 and has the same pressure as the discharge pressure wIJ1, a second closed space P1 that is in a high pressure state, and a low pressure side closed space P2 that is seen in a compressed state. and a sealed space P3 at normal pressure outside of it.
, there are many spaces with different pressures, and therefore there is a large variation in the pressure difference between adjacent closed spaces such as PO (discharge pressure)〉〉〉2-port high pressure) P2 (low pressure)) P3 (normal pressure) Therefore, if each projection 52.53 interval is completely shut off as described above, the pressing force (surface pressure) of the sealing member 1 at each projection 52.53 interval will be large in response to the pressure difference. As a result, the amount of wear on the sealing member 1 varies depending on the distance between the protrusions, resulting in reduced durability and, as a result, it becomes difficult to ensure smooth sealing performance over a long period of time.
本発明はかかる従来技術の欠点に鑑み、前記シール部材
の円滑なシール性の確保と耐久の向上を図りつつ前記シ
ール部材の螺旋方向に沿う漏洩を極力防＋）ｌ、圧縮効
率若しくは膨張効率の大幅向上を図ったスクロール流体
機械を提供する事を目的とする。In view of the drawbacks of the prior art, the present invention aims to ensure smooth sealing performance and improve durability of the seal member, while minimizing leakage along the helical direction of the seal member, and improving compression efficiency or expansion efficiency. The purpose is to provide a scroll fluid machine that has been significantly improved.
「課題を解決する為の手段」
本発明は、前記溝部２の底面と（−射的には高圧側）側
壁面と対峙するシール部材ｌの隣接する二面に、前記シ
ール部材ｌの螺旋方向中心域側から外方域側に向け印加
される圧力を受圧して前記溝部２側に弾性的に圧接され
る突起部材５ａ、５ｂを設けた点については前記比較発
明と同様であるが、
前記比較発明のように前記シール部材代部ｌａ側に形成
した突起位置と（高圧側）側壁面に形成した突起位置を
完全に合致させるのではなく前記突起形成位置を第１図
（Ａ）に示すように螺旋方向に位置ずれさせて配設した
車を特徴とするものである。"Means for Solving the Problem" The present invention provides a spiral direction of the sealing member l on two adjacent surfaces of the sealing member l facing the bottom surface and the side wall surface (on the high pressure side in terms of projection) of the groove portion 2. The present invention is similar to the comparative invention in that protruding members 5a and 5b are provided that are elastically pressed against the groove 2 side by receiving pressure applied from the center area side toward the outer area side, but the above-mentioned comparative invention. Unlike the comparative invention, the position of the protrusion formed on the side of the seal member margin la and the position of the protrusion formed on the (high pressure side) side wall surface are not completely matched, but the position of the protrusion is shown in FIG. 1(A). The vehicle is characterized by wheels arranged in a spirally shifted manner.
この場合前記全ての突起部材５ａ、５ｂを相互に千鳥状
に位置ずれさせて形成する必要はなく、必要に応じて前
記位置ずれさせた複数の突起部材５ａ、５ｂ群毎か、若
しくは前記シール部材１の外周側末端側に、他面側の突
起部材５ａの形成位置と合致する突起部材５ａ’を少な
くとも一以上設けてもよい。In this case, it is not necessary to form all of the protruding members 5a, 5b in a staggered manner, and as necessary, the protruding members 5a, 5b may be formed for each group of the plurality of protruding members 5a, 5b shifted in position, or the sealing member At least one protrusion member 5a' may be provided on the outer circumferential end side of 1 to match the formation position of the protrusion member 5a on the other side.
又前記突起部材５ａ、５ｂの配置間隔も等間隔に設定す
る必要はなく、螺旋方向中心域から外周域に進むに連れ
順次大になるように設定するのが好ましい場合がある。Further, the intervals between the protruding members 5a and 5b do not need to be set at equal intervals, and it may be preferable to set the intervals so that they gradually increase from the center area in the spiral direction to the outer circumferential area.
「作用」
かかる技術手段によれば、前記比較発明のように、前記
シール部材１の螺旋方向に沿う漏洩を各突起５２．５３
間隔毎に完全に遮断した状態で、前記シール部材ｌに背
圧を印加するのではなく、第１図に示す如く前記突起部
材５ａ、５ｂを隣接する各面毎に位置ずれさせて配置し
た為に、シール部材１中心域の底面ｌａ側側圧圧空気螺
旋方向に沿って各面を交互に移動しながら千鳥状に漏洩
させる事が可能となり、ラビリンス効果をもって不完全
シール状態を維持する事が出来る。"Operation" According to this technical means, as in the comparative invention, leakage along the helical direction of the sealing member 1 is prevented from occurring at each protrusion 52, 53.
Rather than applying back pressure to the sealing member 1 while completely blocking each interval, the protruding members 5a and 5b are arranged with their positions shifted for each adjacent surface as shown in FIG. In addition, it is possible to cause leakage in a staggered manner while alternately moving each surface along the spiral direction of the pressure air on the bottom surface la side of the center area of the seal member 1, and it is possible to maintain an incomplete seal state with a labyrinth effect. .
この結果、中心域の高圧空気の外周側への漏洩を実質的
に零に近付ける車が回部となるとともに、前記高圧空気
が微小速度で低圧側に移動する為に、中心域側より螺旋
方向に沿って多数の圧力の異なる密閉空間が存在する場
合でも各突起５ａ、５ｂ間隔毎の背圧のアンバランスを
平滑化する市が出来る。As a result, the wheel that makes the leakage of high-pressure air in the center area to the outer circumference side become substantially zero becomes a rotating part, and in order for the high-pressure air to move to the low-pressure side at a minute speed, it flows in a spiral direction from the center area side. Even if a large number of sealed spaces with different pressures exist along the line, it is possible to smooth out the unbalance of back pressure between the protrusions 5a and 5b.
又背圧が加わる側の高圧側壁面！ｂの前記シール部材ｌ
と溝部２間は前記従来技術のように直接面接触にて圧接
しているのではなく、突起部材５ｂを介して弾性的に且
つ所定間隔毎に実質的に線接触にて圧接する構成を取る
為に、シール部材１の摺動面１４側の押圧方向への摺動
抵抗が低減し、その分シール部材ｌの追従性よく摺動面
１４を圧接する事が出来、シール性能が向上する。Also, the high pressure side wall surface where back pressure is applied! The sealing member l of b
The groove portion 2 and the groove portion 2 are not in direct surface contact pressure contact as in the prior art, but are in pressure contact elastically and substantially in line contact at predetermined intervals via the protruding member 5b. Therefore, the sliding resistance in the pressing direction on the sliding surface 14 side of the sealing member 1 is reduced, and the sealing member 1 can be pressed against the sliding surface 14 with good followability, thereby improving sealing performance.
又前記隣接する二面に設けた突起部材５ａ、５ｂ自体に
弾性力を付与し且つ第３図（ｂ）に示すように前記突起
部材５ａ、５ｂが高圧側の受圧力に対応して自在に拡開
可能である為に、前記溝部２の幅方向と深さ方向の表金
精度に狂いが生じても、言い換えれば寸法精度をラフに
設定してもこれを吸収して精度よく圧接させる事が可能
となる。Further, elastic force is imparted to the protruding members 5a and 5b provided on the two adjacent surfaces, and as shown in FIG. Because it can be expanded, even if the surface metal accuracy in the width direction and depth direction of the groove portion 2 is inconsistent, in other words, even if the dimensional accuracy is set to be rough, this can be absorbed and pressure bonding can be performed with high precision. becomes possible.
更に、前記突起部材５ａ、５ｂが前記受圧力により自在
に拡開可能である事は側壁面側の溝空隙３１部のクリア
ランスを余裕をもって形成しても該シール部材１が傾斜
して圧接される事なくこれにより該面圧の変化による異
常摩耗等が完全に防止出来るとともに、この事は逆に前
記シール部材ｌの熱膨張を考慮して余裕をもって前記ク
リアランスを設定出来る為に設計の自由度及び加工に自
由度が大幅に向上する。Furthermore, the fact that the protruding members 5a and 5b can be freely expanded by the receiving pressure means that even if the groove gap 31 on the side wall side is provided with a sufficient clearance, the sealing member 1 is pressed against the inclination. As a result, abnormal wear due to changes in the surface pressure can be completely prevented, and conversely, the clearance can be set with a margin in consideration of the thermal expansion of the sealing member l, which increases the freedom of design and The degree of freedom in machining is greatly improved.
又、長時間運転によりチップシールが摩耗しても、突起
部材５ａの弾力性により性能低下を軽減出来、チップシ
ール自体の寿命を向１−させることが出来る。Furthermore, even if the tip seal wears out due to long-term operation, the elasticity of the protruding member 5a can reduce performance degradation and extend the life of the tip seal itself.
「実施例」
以下、図面を参照して本発明の好適な実施例を例示的に
詳しく説明する。ただしこの実施例に記載されている構
成部品の寸法、材質、形状、その相対配置などは特に特
定的な記載がない限りは、この発明の範囲をそれのみに
限定する趣旨ではなく、単なる説明例に過ぎない。"Embodiments" Hereinafter, preferred embodiments of the present invention will be described in detail by way of example with reference to the drawings. However, unless otherwise specified, the dimensions, materials, shapes, and relative arrangements of the components described in this example are not intended to limit the scope of this invention, but are merely illustrative examples. It's nothing more than that.
第１図は本発明の基本構成を示す実施例で。FIG. 1 is an embodiment showing the basic configuration of the present invention.
２１ａは相手側スクロール摺動面１４と対峙するラップ
端面で、その長手方向中心線に沿って螺旋方向に、断面
矩形状の溝部２が凹設されている。そして前記溝部２に
嵌合されるシール部材１は、自己ｉｔ＋滑性樹脂材を帯
状に形成するとともに、該シール部材ｌの隣接する壁面
に長手方向に沿って交写に楔状の切込み突起を入れ、該
切込み突起が前記螺旋方向中心域側から外方域側に向け
印加される圧力を受圧して拡開方向に変形可能に構成す
る。Reference numeral 21a denotes a wrap end face facing the mating scroll sliding surface 14, and a groove 2 having a rectangular cross section is recessed in the spiral direction along the longitudinal center line. The sealing member 1 to be fitted into the groove 2 is formed of a self-smooth resin material in the form of a band, and wedge-shaped cut protrusions are formed at intervals along the longitudinal direction on the adjacent wall surface of the sealing member 1. , the notch protrusion is configured to be deformable in the expansion direction by receiving pressure applied from the center region side in the spiral direction toward the outer region side.
次に前記本実施例に係るシール部材ｌを装着した場合（
ａ）と、前記比較発明のように隣接する２面に同一切込
み位置で切込み突起５２．５３を設けたシール部材ｌを
装着した場合（ｂ）、及び前記切込みを全く設けない場
合のシール部材を装着した場合（Ｃ）の夫々の面圧変化
について第４図（Ａ）に基づいて調べてみるに、回転角
θ：０゜の場合のＸ印地点での密閉空間間の圧力差がｐ
＋＜ＰＯ（吐出圧）、θ：９０°の地点では圧力差がＰ
Ｉ−ＰＩ’ （高圧）以下θ：１８０°ではＰＩ−Ｐｉ
ｏ、θ：２７０°ではＰｉ＜ＰＯとすると、その面圧変
化は第４図（Ｂ）のようになる、従って前記第４図（Ｂ
）より理解されるように切込み突起５ａ、５ｂ間隔毎に
漏洩を完全に遮断した比較発明（ｂ）においては前記隣
接する密閉空間Ｐｉ、Ｐ２間の差圧に対応して面圧が大
幅に変動する事となり、一方切込み突起なしの場合（Ｃ
）は、完全に漏洩が生じ面圧が低下してしまう、しかし
ながら本実施例（ａ）によれば前記面圧が平滑化され且
つ高圧に維持する事が出来、本発明の作用効果を円滑に
連成している事が理解出来る。Next, when the seal member l according to the present example is installed (
a), a case in which the seal member l is provided with cut protrusions 52 and 53 at the same cut-in position on two adjacent surfaces as in the comparative invention, and a seal member in which the cut protrusions 52 and 53 are not provided at all (b); Examining the changes in surface pressure in the case of mounting (C) based on Fig. 4 (A), we find that the pressure difference between the sealed spaces at the point marked X when the rotation angle θ is 0° is p.
+<PO (discharge pressure), θ: At the point of 90°, the pressure difference is P
I-PI' (high pressure) or less θ: PI-Pi at 180°
o, θ: 270°, if Pi<PO, the surface pressure change will be as shown in Figure 4 (B).
), as can be understood, in the comparative invention (b) in which leakage is completely blocked at every interval between the cut protrusions 5a and 5b, the surface pressure fluctuates significantly in response to the differential pressure between the adjacent sealed spaces Pi and P2. On the other hand, in the case without notch protrusion (C
), the leakage would occur completely and the surface pressure would drop.However, according to this embodiment (a), the surface pressure can be smoothed and maintained at a high pressure, and the effects of the present invention can be smoothly achieved. I can understand that they are connected.
尚１本発明においては、前記全ての切込み突起５ａ、５
ｂを前記実施例に示すように相互に千鳥状に位置ずれさ
せて形成する（第２図（ａ））必要はなく、例えば底面
側に印加される圧力が側壁面側より大な場合は第２図（
ｂ）に示すように底面側の突起５ａ間隔の複数周期毎に
側壁面側側の切込み突起５ｂを形成してもよく、又前記
切込み突起５ａ、５ｂの配置間隔も等間隔に設定する必
要はなく、高圧の中心域側と低圧の外周側の面圧のバラ
ンスを取る為に、第２図（Ｃ）に示すように前記突起５
ａ、５ｂの配置間隔を螺旋方向中心域から外周域に進む
に連れ順次等比級数的に大になるように設定してもよい
。Note that in the present invention, all the cut protrusions 5a, 5
It is not necessary to form the portions b in a staggered manner as shown in the previous embodiment (Fig. 2(a)); for example, if the pressure applied to the bottom side is greater than that to the side wall side, Figure 2 (
As shown in b), the notched protrusions 5b on the side wall side may be formed every plural cycles of the interval between the protrusions 5a on the bottom side, and it is not necessary to set the arrangement intervals of the notched protrusions 5a, 5b at equal intervals. In order to balance the surface pressure between the high pressure central region side and the low pressure outer peripheral side, the protrusion 5 is installed as shown in Fig. 2(C).
The arrangement interval of a and 5b may be set to increase in a geometric progression from the central region in the spiral direction to the outer peripheral region.
更に前記全ての突起５ａ、５ｂを完全に相互に位置ずれ
させる必要もなく、第２図（ｄ）に示すように少なくと
も前記シール部材１の（外周）末端側では開放空間側へ
の漏洩を防止する為に、他面側の切込み突起５ｂの形成
位置と合致させて切込み突起５ａ’を形成する事も可壷
であり、又第２図（ｅ）に示すようにシール部材ｌの一
周回と対応する前記位置ずれさせた複数の切込み突起５
ａ、５ｂ群毎に、他面側の切込み突起５ｂと合致する切
込み突起５Ｃを設ける享により本発明の効果を低減させ
る事なく、前記漏洩駆出効果を一層向上する事が出来、
これにより圧縮効率を向上させる効果を上げる事が可能
となる。Furthermore, there is no need to completely shift the positions of all the protrusions 5a and 5b from each other, and as shown in FIG. 2(d), leakage to the open space side is prevented at least on the (outer periphery) end side of the sealing member 1. In order to do this, it is also possible to form the notch protrusion 5a' to match the formation position of the notch protrusion 5b on the other side, and as shown in FIG. The plurality of cut protrusions 5 whose positions are shifted from each other
By providing a cut protrusion 5C that matches the cut protrusion 5b on the other side for each group a and 5b, the leak ejection effect can be further improved without reducing the effects of the present invention.
This makes it possible to increase the effect of improving compression efficiency.
「発明の効果」
以上記載した如く本発明によれば、ラップ端面に嵌合さ
せたシール部材の円滑なシール性の確保と耐久の向上を
図りつつ前記シール部材の螺旋方向に沿う漏洩を極力防
上し、圧縮効率若しくは膨張効率の大幅向上を図ったス
クロール流体機械を提供する事が出来る０等の種々の著
効を宥し、未発明にして始めて耐久性のよい無給油式ス
クロール圧縮機の提供が可能になり、その実用的価値は
極めて大である。"Effects of the Invention" As described above, according to the present invention, leakage along the helical direction of the sealing member is prevented as much as possible while ensuring smooth sealing performance and improving durability of the sealing member fitted to the end face of the wrap. In addition, it is possible to provide a scroll fluid machine with significantly improved compression efficiency or expansion efficiency. It is now possible to provide this, and its practical value is extremely large.
又前記実施例では圧縮機について詳細に説明したが、こ
れのみに限定されず膨張機や真空ポンプにも適用可能で
ある。Further, although the compressor was explained in detail in the above embodiment, the present invention is not limited to this, and can also be applied to an expander or a vacuum pump.
第１図は本発明の基本構成を示す要部斜視図で（Ａ）は
シール部材（Ｂ）は該シール部材を嵌入したう°ツブ端
面形状を示す、第２図は本発明の各実施例（ａ）〜（ｅ
）と従来技術（ｇ）及び検討発明（ｆ）におけるシール
部材の側壁面と底面の突起形成位置を示す展開図、第３
図（ａ）は本発明と従来技術の摺動面側の圧接状態を示
す作用図、同図（ｂ）本発明に係る突起の受圧状態を示
す作用図である。
第４図（Ａ）（Ｂ）スクロールの各回転角度位置におけ
る従来技術と本実施例及び比較発明の面圧変化状態を示
す作用図、第５図（Ａ）（Ｂ）は本発明が適用されるス
クロール圧縮機を示す。FIG. 1 is a perspective view of the main parts showing the basic structure of the present invention, (A) shows the sealing member (B) shows the shape of the end face of the tongue in which the sealing member is fitted, and FIG. 2 shows each embodiment of the present invention. (a)-(e
), a developed view showing the protrusion formation positions on the side wall surface and bottom surface of the sealing member in the prior art (g) and the examined invention (f), 3rd
Figure (a) is an operational view showing the pressure contact state of the sliding surface side of the present invention and the prior art, and Figure (b) is an operational view showing the pressure receiving state of the protrusion according to the present invention. FIGS. 4(A) and 4(B) are action diagrams showing the state of change in surface pressure of the prior art, this embodiment, and the comparative invention at each rotational angular position of the scroll, and FIGS. This figure shows a scroll compressor.
Claims (1)
プ端面に断面矩形状に凹設した溝部にシール部材を嵌入
させ、該シール部材を介して前記摺動面とラップ間に形
成される囲繞空間の封止を図るスクロール式流体機械に
おいて、 前記溝部の底面と側壁面と対峙するシール部材の隣接す
る二面に、 前記シール部材の螺旋方向中心域側から外周側に向け印
加される圧力を受圧して前記溝部側に弾性的に圧接され
る突起部材を設けるとともに、少なくとも前記シール部
材の一面側に形成した突起部材が他面側に形成した突起
部材に対し前記螺旋方向に沿って位置ずれさせて配設し
た 事を特徴とするスクロール流体機械 ２）前記他面側の突起部材との間で位置ずれさせた複数
の突起部材群毎か、若しくは前記シール部材の外周側末
端側に、他面側の突起部材の形成位置と合致する突起部
材を少なくとも一以上設けた請求項１）記載のスクロー
ル流体機械 ３）前記突起部材の配置間隔を螺旋方向中心域から外周
域に進むに連れ順次大になるように設定した請求項１）
記載のスクロール流体機械 ４）前記シール部材を帯状自己潤滑材で形成するととも
に、該自己潤滑材の隣接する壁面に長手方向に沿って交
互に楔状の切込みを入れ、該切込みが前記螺旋方向中心
域側から外方域側に向け印加される圧力を受圧して拡開
方向に変形可能に構成した請求項１）記載のスクロール
流体機械[Scope of Claims] 1) A sealing member is fitted into a groove with a rectangular cross section in the spiral wrap end face facing the sliding surface of the mating scroll, and the sliding surface is connected to the sliding surface through the sealing member. In a scroll-type fluid machine that attempts to seal a surrounding space formed between wraps, two adjacent surfaces of the sealing member facing the bottom and side wall surfaces of the groove are provided from the center area side in the spiral direction to the outer peripheral side of the sealing member. A protrusion member is provided that is elastically pressed against the groove side by receiving pressure applied toward the seal member, and at least the protrusion member formed on one side of the seal member is opposed to the protrusion member formed on the other side of the seal member. Scroll fluid machine characterized in that the scroll fluid machine is arranged so as to be displaced along the spiral direction. Scroll fluid machine according to claim 1, wherein at least one protrusion member is provided on the outer peripheral end side, the protrusion member matching the formation position of the protrusion member on the other side. Claims 1) that are set to increase in size as the area advances
Scroll fluid machine according to 4) The sealing member is formed of a strip-shaped self-lubricating material, and wedge-shaped cuts are made alternately along the longitudinal direction on adjacent wall surfaces of the self-lubricating material, and the cuts are formed in the central region in the helical direction. The scroll fluid machine according to claim 1, wherein the scroll fluid machine is configured to be deformable in the expansion direction by receiving pressure applied from the side toward the outer region side.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP14522789A JPH0696961B2 (en) | 1989-06-09 | 1989-06-09 | Scroll fluid machinery |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP14522789A JPH0696961B2 (en) | 1989-06-09 | 1989-06-09 | Scroll fluid machinery |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0311101A true JPH0311101A (en) | 1991-01-18 |
| JPH0696961B2 JPH0696961B2 (en) | 1994-11-30 |
Family
ID=15380285
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP14522789A Expired - Lifetime JPH0696961B2 (en) | 1989-06-09 | 1989-06-09 | Scroll fluid machinery |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0696961B2 (en) |
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0597804A1 (en) * | 1992-11-07 | 1994-05-18 | AGINFOR AG für industrielle Forschung | Fluid displacement apparatus with a spiral element |
| JP2001123970A (en) * | 1999-10-25 | 2001-05-08 | Hitachi Ltd | Seal member and scroll-type fluid machine using it |
| US7134852B1 (en) * | 2006-01-18 | 2006-11-14 | Heng Sheng Precision Tech. Co., Ltd. | Seal member for vortex compressor |
| JP2007009818A (en) * | 2005-06-30 | 2007-01-18 | Hitachi Ltd | Scroll type fluid machine |
| JP2008031960A (en) * | 2006-07-31 | 2008-02-14 | Hitachi Ltd | Scroll type fluid machine |
| JP2012163114A (en) * | 2012-06-08 | 2012-08-30 | Hitachi Industrial Equipment Systems Co Ltd | Scroll type fluid machine |
| JP2015175268A (en) * | 2014-03-14 | 2015-10-05 | 株式会社デンソー | compressor |
| JP2018051681A (en) * | 2016-09-28 | 2018-04-05 | 三井精機工業株式会社 | Slit processing machine and processing method of seal member |
| US10451068B2 (en) | 2014-11-07 | 2019-10-22 | Trane International Inc. | Tip seal |
| US10753360B2 (en) | 2016-02-16 | 2020-08-25 | Danfoss Commercial Compressors | Scroll compression device having a sealing device, and scroll compressor including such a scroll compression device |
| WO2023042328A1 (en) * | 2021-09-16 | 2023-03-23 | 株式会社日立産機システム | Scroll type fluid machine |
-
1989
- 1989-06-09 JP JP14522789A patent/JPH0696961B2/en not_active Expired - Lifetime
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0597804A1 (en) * | 1992-11-07 | 1994-05-18 | AGINFOR AG für industrielle Forschung | Fluid displacement apparatus with a spiral element |
| JP2001123970A (en) * | 1999-10-25 | 2001-05-08 | Hitachi Ltd | Seal member and scroll-type fluid machine using it |
| JP2007009818A (en) * | 2005-06-30 | 2007-01-18 | Hitachi Ltd | Scroll type fluid machine |
| US7134852B1 (en) * | 2006-01-18 | 2006-11-14 | Heng Sheng Precision Tech. Co., Ltd. | Seal member for vortex compressor |
| JP2008031960A (en) * | 2006-07-31 | 2008-02-14 | Hitachi Ltd | Scroll type fluid machine |
| JP2012163114A (en) * | 2012-06-08 | 2012-08-30 | Hitachi Industrial Equipment Systems Co Ltd | Scroll type fluid machine |
| JP2015175268A (en) * | 2014-03-14 | 2015-10-05 | 株式会社デンソー | compressor |
| US10451068B2 (en) | 2014-11-07 | 2019-10-22 | Trane International Inc. | Tip seal |
| US10753360B2 (en) | 2016-02-16 | 2020-08-25 | Danfoss Commercial Compressors | Scroll compression device having a sealing device, and scroll compressor including such a scroll compression device |
| JP2018051681A (en) * | 2016-09-28 | 2018-04-05 | 三井精機工業株式会社 | Slit processing machine and processing method of seal member |
| WO2023042328A1 (en) * | 2021-09-16 | 2023-03-23 | 株式会社日立産機システム | Scroll type fluid machine |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0696961B2 (en) | 1994-11-30 |
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