JP3367109B2 - Scroll type fluid machine - Google Patents

Scroll type fluid machine

Info

Publication number
JP3367109B2
JP3367109B2 JP30620491A JP30620491A JP3367109B2 JP 3367109 B2 JP3367109 B2 JP 3367109B2 JP 30620491 A JP30620491 A JP 30620491A JP 30620491 A JP30620491 A JP 30620491A JP 3367109 B2 JP3367109 B2 JP 3367109B2
Authority
JP
Japan
Prior art keywords
scroll
oil
chamber
pressure
center
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
JP30620491A
Other languages
Japanese (ja)
Other versions
JPH05141201A (en
Inventor
幹央 梶原
順英 樋口
弘通 谷和
浩哉 高田
Original Assignee
ダイキン工業株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by ダイキン工業株式会社 filed Critical ダイキン工業株式会社
Priority to JP30620491A priority Critical patent/JP3367109B2/en
Publication of JPH05141201A publication Critical patent/JPH05141201A/en
Application granted granted Critical
Publication of JP3367109B2 publication Critical patent/JP3367109B2/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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Description

【発明の詳細な説明】Detailed Description of the Invention
【0001】[0001]
【産業上の利用分野】本発明は、内部に高圧流体を開放
する高圧ドーム形の密閉ケーシングに一対のスクロール
を内装し、渦巻体間に画成する流体作動室内で冷媒の圧
縮等を行うようにしたスクロール形流体機械に関する。
BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention has a pair of scrolls installed in a high-pressure dome-shaped closed casing for releasing high-pressure fluid therein so that refrigerant can be compressed in a fluid working chamber defined between spirals. The present invention relates to a scroll type fluid machine.
【0002】[0002]
【従来の技術】従来、特公平3−36160号公報に開
示され、且つ図7に示すように、高圧ドーム形の密閉ケ
ーシングDに、固定側の第一スクロールFと可動側の第
二スクロールOとを内装し、これらスクロールF,Oの
渦巻体間に、渦巻外周側の低圧域から渦巻中心側の高圧
域にかけてその圧力が変化する流体作動室Cを画成する
と共に、第二スクロールOの背面に、外周側室Aと中心
側室Bとを区画し、第二スクロールOの自転防止機構を
構成するオルダムリングを用いたシールリングSを介装
して、外周側室Aを低圧連通穴Lを介して低圧流体を導
く吸入管Kに連通させる一方、中心側室Bをハウジング
Gに設ける高圧連通穴Hを介して圧縮後の高圧流体を開
放するケーシングDの内部に連通させている。こうし
て、第二スクロールOの背面外周側に低圧圧力を、又、
中心側に高圧圧力を各々付与することにより、第二スク
ロールOの背面全域に高圧を付与した場合に生じる過剰
な上向きのスラスト力を緩和しながら、流体作動室C側
から作用する下向きの押下げ力に対抗して、適度なスラ
スト力により第二スクロールOを第一スクロールFに常
時押付け、流体作動室C内の気密性を良好に保つように
している。
2. Description of the Related Art Conventionally, as disclosed in Japanese Patent Publication No. 3-36160 and as shown in FIG. 7, a fixed side first scroll F and a movable side second scroll O are provided in a high-pressure dome-shaped hermetic casing D. And a fluid working chamber C in which the pressure changes from the low pressure area on the outer circumference side of the spiral to the high pressure area on the center side of the spiral between the scrolls of the scrolls F and O. An outer peripheral chamber A and a central chamber B are partitioned on the back surface, and a seal ring S using an Oldham ring that constitutes a rotation preventing mechanism of the second scroll O is provided, and the outer peripheral chamber A is provided with a low pressure communication hole L. The center side chamber B is communicated with the inside of the casing D for releasing the compressed high pressure fluid through a high pressure communication hole H provided in the housing G. In this way, low pressure is applied to the outer periphery of the back surface of the second scroll O,
By applying a high pressure to the center side, respectively, the excessive downward thrust force generated when a high pressure is applied to the entire rear surface of the second scroll O is alleviated, and the downward pressing action from the fluid working chamber C side is performed. In opposition to the force, the second scroll O is constantly pressed against the first scroll F by an appropriate thrust force, so that the air tightness in the fluid working chamber C is kept good.
【0003】[0003]
【発明が解決しようとする課題】しかし、以上のもので
は、第二スクロールOの背面中心側に区画した中心側室
Bを単に高圧連通穴Hを介して密閉ケーシングDの内部
に連通させて、この中心側室Bを高圧圧力雰囲気として
いるのみであるから、高圧圧力の低い低差圧時において
も第二スクロールOに上向きのスラスト力を発生させる
ためには、シールリングSの直径を大きくして高圧圧力
の付与面積を比較的大きく確保する必要があり、このた
め、逆に高圧圧力の高い高差圧時にスラスト力が増大
し、このスラスト力を十分に緩和できない問題がある。
However, in the above, the center side chamber B, which is defined on the center side of the rear surface of the second scroll O, is simply communicated with the inside of the closed casing D through the high pressure communication hole H. Since only the high pressure atmosphere is provided in the center side chamber B, in order to generate the upward thrust force in the second scroll O even when the high pressure is low and the differential pressure is low, the diameter of the seal ring S is increased to increase the pressure. It is necessary to secure a relatively large area to which the pressure is applied, and on the contrary, there is a problem that the thrust force increases when the high pressure difference is high and the thrust force cannot be sufficiently relaxed.
【0004】これを、図8に基づいて詳述する。図示の
ものは、横軸に高圧圧力を等間隔目盛で刻み、縦軸に流
体作動室C側から下向きに作用する力Fcと、第二スク
ロールOの背面側から作用する上向きの背圧力Fb及び
これらの差(Fb−Fc)となる上向きのスラスト力F
sを等間隔目盛りで刻み、低圧圧力をパラメータとして
a<b<c<d<eの順にその値を増大させたものであ
る。尚、高圧圧力及び低圧圧力の変化範囲は、冷凍装置
の冷媒圧縮機として用いた場合に通常想定される運転範
囲内で変化させている。こうして、図示のように、高圧
圧力が低く、低圧圧力がdの場合の低差圧条件下(図中
点N)でも正のスラスト力を発生させるためにシールリ
ングSの直径つまり高圧作用面積を設定した場合には、
高圧圧力が高く、低圧圧力がcの場合の高差圧条件下
(図中点M)のスラスト力が極めて増大することにな
り、第二スクロールOと第一スクロールFとの接触力が
過大となり、摺動特性が悪化して性能を低下させる問題
が起こるのである。
This will be described in detail with reference to FIG. In the figure, the horizontal axis indicates high pressure pressure at equal intervals, and the vertical axis indicates a force Fc acting downward from the fluid working chamber C side and an upward back pressure Fb acting from the rear side of the second scroll O. The upward thrust force F that is the difference (Fb-Fc) between them.
s is divided at equal intervals and the value is increased in the order of a <b <c <d <e using the low pressure as a parameter. The change range of the high-pressure pressure and the low-pressure pressure is changed within an operating range that is normally assumed when the refrigerant compressor of the refrigeration system is used. Thus, as shown in the figure, the diameter of the seal ring S, that is, the high-pressure acting area, is increased in order to generate a positive thrust force even under a low differential pressure condition (point N in the figure) when the high-pressure pressure is low and the low-pressure pressure is d. If set,
When the high pressure is high and the low pressure is c, the thrust force under the high differential pressure condition (point M in the figure) increases significantly, and the contact force between the second scroll O and the first scroll F becomes excessive. However, there arises a problem that the sliding characteristics are deteriorated and the performance is lowered.
【0005】本発明では、第二スクロールの背面側の圧
力付与構造を工夫することにより、低差圧時に必要なス
ラスト力を生じさせることができると共に、高差圧時に
スラスト力が過大になるのを防止でき、広い運転条件に
おいて第二スクロールに適正なスラスト力を発生させる
ことができるスクロール形流体機械を提供することを主
な目的とする。
In the present invention, by devising the pressure applying structure on the back side of the second scroll, the required thrust force can be generated at the time of low differential pressure, and the thrust force becomes excessive at high differential pressure. The main object of the present invention is to provide a scroll type fluid machine capable of preventing the above and capable of generating an appropriate thrust force in the second scroll under a wide operating condition.
【0006】[0006]
【課題を解決するための手段】そこで、上記主目的を達
成するため、第一に、高圧ドーム形の密閉ケーシング9
に、第一スクロール1と該第一スクロール1に対して相
対的に公転運動する第二スクロール2とを内装し、これ
らスクロール1,2の渦巻体間に、渦巻外周側の低圧域
から渦巻中心側の高圧域にかけてその圧力が変化する流
体作動室10を画成したスクロール形流体機械におい
て、前記第二スクロール2の背面側に、前記ケーシング
9の内部空間と画成し且つ前記第二スクロール2の背面
側に設ける環状シール体3を介して外周側室41と中心
側室42とに区画する背面室4を設けて、前記外周側室
41を低圧域に連通させると共に、前記中心側室42
に、前記ケーシング9の内部に溜める油を汲み上げる油
ポンプ5から延びる給油通路6を開口する一方、前記中
心側室42を絞り機構7をもつ返油通路8を介して前記
ケーシング9の内部空間に連通させた。
In order to achieve the above main purpose, firstly, a high-pressure dome-shaped hermetic casing 9 is used.
In addition, a first scroll 1 and a second scroll 2 that orbits relative to the first scroll 1 are internally provided, and between the scroll bodies of these scrolls 1 and 2, from the low pressure region on the spiral outer circumference side to the spiral center. In a scroll type fluid machine that defines a fluid working chamber 10 in which the pressure changes toward the high pressure region on the side, the second scroll 2 is defined on the back side of the second scroll 2 with the internal space of the casing 9. The rear side chamber 4 which is divided into the outer peripheral side chamber 41 and the center side chamber 42 via the annular seal body 3 provided on the rear side of the outer peripheral side chamber 41 is provided so as to communicate the outer peripheral side chamber 41 with the low pressure region and the center side chamber 42.
In addition, the oil supply passage 6 extending from the oil pump 5 for pumping the oil stored in the casing 9 is opened, and the center side chamber 42 is communicated with the internal space of the casing 9 through the oil return passage 8 having the throttle mechanism 7. Let
【0007】第二に、上記第一の手段において、返油通
路8に備える絞り機構7をクランク軸93の円筒摺動面
を利用して形成し、摺動部分の潤滑をも兼用して行える
ようにするため、第二スクロール2を連動させるクラン
ク軸93の円筒摺動面に油溝71を開口して、この油溝
71の入口側を中心側室42に連通させると共に、前記
油溝71の出口側を静止部材に設ける返油通路8に連通
させて、前記油溝71を中間部に介在させて前記中心側
室42と返油通路8の入口部とを結ぶ経路により絞り機
構7を構成した。
Secondly, in the first means, the throttle mechanism 7 provided in the oil return passage 8 is formed by utilizing the cylindrical sliding surface of the crankshaft 93, and the sliding portion can also be lubricated. In order to do so, an oil groove 71 is opened in the cylindrical sliding surface of the crank shaft 93 that interlocks the second scroll 2, and the inlet side of this oil groove 71 is communicated with the center side chamber 42, and at the same time, the oil groove 71 The throttle mechanism 7 is configured by a path connecting the center side chamber 42 and the inlet of the oil return passage 8 with the oil passage 71 provided in the stationary member so that the outlet side communicates with the oil groove 71 in the middle. .
【0008】第三に、上記第二の手段において、回転数
に応じて増減する汲み上げ油量に応じて中心側室42の
油を返油通路8に戻し、回転数に応じて中心側室42の
圧力値を適正に保つため、油溝71の出口部と返油通路
8の入口部との間を、クランク軸93の回転に伴い開口
部相互間が間欠的に符合するオーバーラップ構造とし
た。
Thirdly, in the second means, the oil in the center side chamber 42 is returned to the oil return passage 8 in accordance with the pumping oil amount which increases or decreases in accordance with the number of revolutions, and the pressure in the center side chamber 42 is determined in accordance with the number of revolutions. In order to keep the value appropriate, an overlap structure is provided between the outlet of the oil groove 71 and the inlet of the oil return passage 8 so that the openings are intermittently aligned with each other as the crankshaft 93 rotates.
【0009】第四に、上記第一から第三の各手段におい
て、中心側室42の圧力が過剰に増大するのを油の供給
側で抑制し、スラスト力が過大になるのを防止するた
め、給油通路6に、汲み上げ油の異常圧力上昇を逃がす
リリーフ弁60を介装した。
Fourthly, in each of the above-mentioned first to third means, in order to prevent the pressure in the center side chamber 42 from excessively increasing on the oil supply side and prevent the thrust force from becoming excessive, In the oil supply passage 6, a relief valve 60 that releases an abnormal increase in pressure of the pumped oil is provided.
【0010】第五に、上記第一の手段において、中心側
室42の圧力を油戻し側で制御してその値を適正に保つ
ため、絞り機構7を、中心側室42の圧力上昇に伴い開
口面積が拡大する可変絞り弁72により構成した。
Fifthly, in the above first means, in order to control the pressure of the center side chamber 42 on the oil return side and maintain the value appropriately, the throttle mechanism 7 is provided with an opening area corresponding to an increase in the pressure of the center side chamber 42. Is constituted by a variable throttle valve 72 that expands.
【0011】[0011]
【作用】上記第一の手段により、中心側室42の圧力
は、高圧圧力と油ポンプ5による昇圧圧力とが加わった
値となる。この場合、油ポンプ5による昇圧圧力は、運
転条件により変動する高圧圧力とは異なり、常時ほぼ一
定に保たれ、第二スクロール2の背面には、運転条件に
より変動する高圧圧力の他に、ほぼ一定値に保たれる油
ポンプ5の昇圧圧力が相加わって作用することになる。
このため、環状シール体3の径を小さくして、中心側室
42に臨む第二スクロール2の中心側背面の作用面積を
縮小しても、低差圧条件下で上向きの正のスラスト力を
発生させることができ、第二スクロール2を第一スクロ
ール1に適正に押し付けることができる。一方、高差圧
条件下では、中心側室42に接する中心側背面の作用面
積が縮小されて高圧圧力の付与面積が縮小された分だけ
スラスト力が過大になるのを防止することができる。
By the first means, the pressure in the central chamber 42 becomes a value obtained by adding the high pressure and the pressure boosted by the oil pump 5. In this case, unlike the high pressure that fluctuates depending on the operating conditions, the pressure boosted by the oil pump 5 is kept almost constant at all times, and in addition to the high pressure that fluctuates depending on the operating conditions, the back pressure of the second scroll 2 is almost constant. The boosted pressure of the oil pump 5, which is maintained at a constant value, acts in addition.
Therefore, even if the diameter of the annular seal body 3 is reduced to reduce the working area of the center side rear surface of the second scroll 2 facing the center side chamber 42, an upward positive thrust force is generated under a low differential pressure condition. Therefore, the second scroll 2 can be properly pressed against the first scroll 1. On the other hand, under a high differential pressure condition, it is possible to prevent the thrust force from becoming excessively large by the reduction of the acting area of the center side rear surface in contact with the center side chamber 42 and the reduction of the high pressure application area.
【0012】上記第二の手段により、油溝71に流れる
油でクランク軸93の円筒摺動面の潤滑をも兼用して行
うことができる。
By the second means, the oil flowing in the oil groove 71 can also be used to lubricate the cylindrical sliding surface of the crankshaft 93.
【0013】上記第三の手段により、油溝71に流れる
油はクランク軸93の回転に伴い間欠的に返油通路8に
受け渡され、回転数に応じて増減する中心側室42の汲
み上げ油量に応じてその油戻しが行え、回転数に応じて
中心側室42の圧力を適正に保つことができる。
By the third means, the oil flowing in the oil groove 71 is intermittently transferred to the oil return passage 8 as the crankshaft 93 rotates, and the pumping oil amount in the center side chamber 42 increases and decreases according to the rotation speed. The oil can be returned according to the above, and the pressure in the center side chamber 42 can be appropriately maintained according to the number of rotations.
【0014】上記第四の手段により、給油通路6と中心
側室42とを結ぶ経路で異常圧力上昇が生じた場合、リ
リーフ弁60を介してこの圧力を密閉ケーシング9の内
部に逃がすことができ、第二スクロール2の背面に作用
するスラスト力が過大になるのを未然に防止することが
できる。
By the fourth means, when an abnormal pressure rise occurs in the path connecting the oil supply passage 6 and the center side chamber 42, this pressure can be released to the inside of the closed casing 9 through the relief valve 60, It is possible to prevent the thrust force acting on the back surface of the second scroll 2 from becoming excessive.
【0015】上記第五の手段により、中心側室42の圧
力に応じて可変絞り弁72の開口面積が変更されるた
め、中心側室42の圧力値を適正に保つことができ、ス
ラスト力を適正に保持することができる。
By the fifth means, the opening area of the variable throttle valve 72 is changed according to the pressure of the center side chamber 42, so that the pressure value of the center side chamber 42 can be maintained properly and the thrust force can be properly adjusted. Can be held.
【0016】[0016]
【実施例】図1及び図2に示すものは冷凍装置における
冷媒圧縮機として用いるスクロール形流体機械であっ
て、高圧ドーム形の密閉ケーシング9の上部に、鏡板1
1に渦巻体12とこれに連続する外周壁13とを突設し
た固定側の第一スクロール1と、鏡板21に渦巻体22
と背面側ボス部23とを突設し、オルダムリング24を
介してその自転が阻止された状態で第一スクロール1に
対して公転運動する可動側の第二スクロール2とを内装
すると共に、その下部に、ステータ92a及びロータ9
2bを備え、前記ボス部23に嵌合する偏心ピン部93
dをもつクランク軸93を直結したモータ92を内装し
たものである。そして、各渦巻体12,22間に、吸入
管94を開口する渦巻外周側の低圧域から吐出穴95を
開口する吐出渦巻中心側の高圧域にかけてその圧力が変
化する流体作動室10を画成して、該作動室10内で圧
縮した後の高圧流体を密閉ケーシング9の内部に一旦開
放した後、吐出管96から外部に取出すようにしてい
る。
1 and 2 show a scroll type fluid machine used as a refrigerant compressor in a refrigerating machine, in which an end plate 1 is provided on an upper portion of a high pressure dome type closed casing 9.
1, a first scroll 1 on the fixed side in which a spiral body 12 and an outer peripheral wall 13 continuous with the spiral body 12 are projectingly provided;
And a rear side boss portion 23 projecting from the inside, and a movable side second scroll 2 that revolves with respect to the first scroll 1 in a state where its rotation is blocked by an Oldham ring 24, and At the bottom, the stator 92a and the rotor 9
An eccentric pin portion 93 that is equipped with 2b and fits into the boss portion 23
The motor 92 in which a crankshaft 93 having d is directly connected is installed. A fluid working chamber 10 is defined between the spiral bodies 12, 22 in which the pressure changes from a low pressure area on the outer circumference of the spiral opening the suction pipe 94 to a high pressure area on the central side of the discharge spiral opening the discharge hole 95. Then, the high-pressure fluid after being compressed in the working chamber 10 is once released into the closed casing 9 and then taken out from the discharge pipe 96 to the outside.
【0017】以上の構成で、第二スクロール2の背面側
に、上部ハウジング97を介して前記ケーシング9の内
部空間と画成し、且つ、第二スクロール2の背面側に配
設するシールリング31と付勢用のOリング32とを備
える環状シール体3を介して外周側室41と中心側室4
2とに区画する背面室4を設ける。そして、外周側室4
1を低圧連通穴14を介して渦巻外周側の低圧域に連通
させると共に、中心側室42に、クランク軸93内に貫
通状に形成し、下部ハウジング98の下方に設ける油溜
99の油を汲み上げるトロコイド式の油ポンプ5から延
びる給油通路6を、偏心ピン部93dの外周に切欠く連
通溝6aを介して開口する。更に、中心側室42を次記
する絞り機構7を備え、上部ハウジング97に設ける返
油穴81と外付けの返油管82とから成る返油通路8を
介して油溜99に連通させる。
With the above construction, the seal ring 31 is formed on the back side of the second scroll 2 so as to define the internal space of the casing 9 through the upper housing 97 and to be arranged on the back side of the second scroll 2. An outer peripheral side chamber 41 and a center side chamber 4 via an annular seal body 3 including an urging O-ring 32.
A back room 4 is provided which is divided into two parts. And the outer chamber 4
1 is communicated with the low pressure region on the spiral outer circumference side through the low pressure communication hole 14, and the center side chamber 42 is penetratingly formed in the crankshaft 93 and the oil in the oil sump 99 provided below the lower housing 98 is pumped up. An oil supply passage 6 extending from the trochoid type oil pump 5 is opened via a communication groove 6a which is cut out on the outer periphery of the eccentric pin portion 93d. Further, the center side chamber 42 is provided with a throttle mechanism 7 described below, and is communicated with the oil sump 99 via an oil return passage 8 formed of an oil return hole 81 provided in the upper housing 97 and an external oil return pipe 82.
【0018】前記絞り機構7は、オリフィスやキャピラ
リーチューブ等を用いて構成してもよいが、このもの
は、上部軸受メタル97aに臨むクランク軸93の円筒
摺動面93aにD字形のカット部から成る油溝71を設
けて、この油溝71の上部入口部を中心側室42の底部
に開口すると共に、油溝71の出口側を、上部軸受メタ
ル97aに設ける横穴81aを介して前記返油穴81に
連通させて、油溝71を中間部に介在させて中心側室4
2と返油通路8の入口部とを結ぶ経路により該絞り機構
7を構成している。更に、前記油溝71の出口部と返油
通路8の入口部となる横穴81aとの間は、クランク軸
93の回転に伴い開口部相互間が一回転あたり一回の割
合で間欠的に符合するオーバーラップ構造としている。
The throttle mechanism 7 may be constructed by using an orifice, a capillary tube, or the like, but this is constructed from a D-shaped cut portion on the cylindrical sliding surface 93a of the crankshaft 93 facing the upper bearing metal 97a. The oil groove 71 is formed so that the upper inlet portion of the oil groove 71 is opened to the bottom portion of the center side chamber 42, and the outlet side of the oil groove 71 is provided through the lateral hole 81a provided in the upper bearing metal 97a to the oil return hole. 81, and the oil groove 71 is interposed in the middle part so that the central chamber 4
The throttling mechanism 7 is constituted by a path connecting 2 and the inlet of the oil return passage 8. Further, between the outlet of the oil groove 71 and the lateral hole 81a serving as the inlet of the oil return passage 8, the openings are intermittently matched at a rate of once per rotation as the crankshaft 93 rotates. It has an overlapping structure.
【0019】又、クランク軸93の下部に位置する給油
通路6には、径方向の開放穴61を設けて、その開口部
に、汲み上げ油の異常圧力上昇を逃がす板弁62とその
弁押さえ63とをもつカンチレバー形のリリーフ弁60
を介装している。
Further, the oil supply passage 6 located under the crankshaft 93 is provided with a radial opening hole 61, and a plate valve 62 for releasing an abnormal pressure rise of the pumping oil and its valve retainer 63 are provided in the opening. Cantilever type relief valve 60 with and
Is intervening.
【0020】こうして、以上の構成により、中心側室4
2は、高圧圧力と油ポンプ5による昇圧圧力とが加わっ
た圧力となり、この場合、油ポンプ5による昇圧圧力
は、運転条件により変動する高圧圧力の値に拘らず常に
ほぼ一定値に保たれるため、図3に示すように、第二ス
クロール2の背面には、高圧圧力の他にほぼ一定値に保
たれた例えば5kgf/平方センチメートル程度の油ポ
ンプ5による昇圧圧力が相加わって作用することになる
ため、図7及び図8で示した従来のものに比べて環状シ
ール体3の径を20パーセント程度小さくし、中心側室
42に臨む第二スクロール2の中心側背面の作用面積を
縮小しても、低差圧条件下(図中点N)にあっても、上
向きの正で且つ適当な大きさをもつスラスト力を発生さ
せることができ、第二スクロール2を第一スクロール1
に適正に押し付けることができると共に、高差圧条件下
(図中点M)では、中心側室42に接する作用面積が縮
小されて高圧圧力の付与面積が小さい分だけスラスト力
が過大になるのを防止できるのである。尚、図3の特性
図は、図8のものと同一目盛りで刻み、パラメータとす
る低圧圧力の値a,b,c,d,eも同じものに統一し
ている。
Thus, with the above structure, the central chamber 4
2 is a pressure obtained by adding the high pressure and the pressure boosted by the oil pump 5, and in this case, the pressure boosted by the oil pump 5 is always maintained at a substantially constant value regardless of the value of the high pressure that fluctuates depending on the operating conditions. Therefore, as shown in FIG. 3, on the back surface of the second scroll 2, in addition to the high-pressure pressure, an increased pressure by the oil pump 5 of, for example, about 5 kgf / square centimeter, which is maintained at a substantially constant value, acts in addition. Therefore, the diameter of the annular seal body 3 is reduced by about 20% as compared with the conventional one shown in FIGS. 7 and 8, and the action area of the center side rear surface of the second scroll 2 facing the center side chamber 42 is reduced. Even under a low differential pressure condition (point N in the figure), an upward positive thrust force having an appropriate magnitude can be generated, and the second scroll 2 is replaced by the first scroll 1
In addition, it is possible to properly press the roller against the high pressure differential condition (point M in the figure), and the thrusting force becomes excessive due to the reduction of the operating area in contact with the center side chamber 42 and the reduction of the high pressure applied area. It can be prevented. The characteristic diagram of FIG. 3 is divided on the same scale as that of FIG. 8, and the low pressure values a, b, c, d, and e used as parameters are also unified.
【0021】又、以上のものでは、絞り機構7をクラン
ク軸93の円筒摺動面に開口する油溝71を用いて構成
したから、摺動部分の潤滑をも兼用して行うことができ
る。更に、以上のものでは、油溝71の出口部と返油通
路8の入口部との間を、クランク軸93の回転に伴い開
口部相互間が間欠的に符合するオーバーラップ構造とし
たから、例えばインバータ制御等によりモータ92を可
変速とした場合、その回転数に応じて汲み上げ油量が増
減する中心側室42の油をその油量に応じて返油通路8
に戻すことができ、回転数に応じて中心側室42の圧力
を適正に保つこともできる。もっとも、油溝71と返油
通路8とは、図4に示すようにオーバーラップさせるこ
となく設けてもよく、この場合にも、クランク軸93の
摺動部分の潤滑は確保できる。
Further, in the above, since the throttle mechanism 7 is constituted by using the oil groove 71 which is opened in the cylindrical sliding surface of the crank shaft 93, the sliding portion can be also used for lubrication. Further, in the above-described structure, the gap between the outlet of the oil groove 71 and the inlet of the oil return passage 8 has an overlap structure in which the openings are intermittently aligned with each other as the crankshaft 93 rotates. For example, when the motor 92 is set to a variable speed by an inverter control or the like, the oil in the center chamber 42 whose pumping oil amount increases or decreases depending on the rotation speed of the motor 92 is returned in accordance with the oil amount.
Therefore, the pressure in the center side chamber 42 can be appropriately maintained according to the rotation speed. However, the oil groove 71 and the oil return passage 8 may be provided without overlapping as shown in FIG. 4, and even in this case, lubrication of the sliding portion of the crankshaft 93 can be ensured.
【0022】更に、以上のものでは、リリーフ弁60を
設けたから、中心側室42の圧力が回転数の増大や絞り
機構7の目詰まり等の種々の原因により過剰に増大して
しまうのを未然に抑制でき、スラスト力が異常に増大す
るのを未然に防止することもできる。
Further, in the above, since the relief valve 60 is provided, it is possible to prevent the pressure in the central chamber 42 from excessively increasing due to various causes such as an increase in the number of rotations and clogging of the throttle mechanism 7. It can be suppressed, and the thrust force can be prevented from abnormally increasing.
【0023】ところで、上記実施例では、油溝71を用
いて絞り機構7を構成したが、その他、図5に示すよう
に、上部ハウジング97に設ける返油穴81を中心側室
42に開口して、該返油穴81の内部に、絞り開口部7
2aと、これに臨む弁体72b及び該弁体72bを閉側
に付勢する付勢体72cとを備え、中心側室42の圧力
上昇に伴い絞り開口部72aの開口面積が拡大する可変
絞り弁72を用いて構成してもよく、この場合には、中
心側室42の圧力を油戻し側で制御してその圧力値を適
正に保つことができ、スラスト力を適正に保持すること
ができる。
By the way, in the above embodiment, the throttle mechanism 7 is constituted by using the oil groove 71. However, as shown in FIG. 5, the oil return hole 81 provided in the upper housing 97 is opened in the center side chamber 42. , Inside the oil return hole 81, the aperture opening 7
2a, a valve body 72b facing this, and a biasing body 72c that biases the valve body 72b toward the closing side, and the opening area of the throttle opening 72a increases as the pressure in the central chamber 42 increases. 72 may be used, and in this case, the pressure of the center side chamber 42 can be controlled on the oil return side to maintain the pressure value appropriately, and the thrust force can be appropriately maintained.
【0024】更に、以上の実施例では、返油通路8を、
上部ハウジング97に設ける返油穴81と外付けの返油
管82とを用いて、油溜99に直接的に開放する構造と
したが、図6に示すように、上部ハウジング97に設け
る第一返油穴83と、第一スクロール1に連続状に設け
られ、中間圧領域にある流体作動室10にその出口部を
開口する油インジェクション通路から成る第二返油穴8
4とを用い、流体作動室10の内部を経由させて吐出穴
95から密閉ケーシング9の内部空間に連通させる構造
としてもよい。
Further, in the above embodiments, the oil return passage 8 is
Although the oil return hole 81 provided in the upper housing 97 and the external oil return pipe 82 are used to directly open to the oil sump 99, as shown in FIG. A second oil return hole 8 comprising an oil hole 83 and an oil injection passage which is continuously provided in the first scroll 1 and has an outlet opening to the fluid working chamber 10 in the intermediate pressure region.
4 may be used to communicate with the internal space of the closed casing 9 from the discharge hole 95 via the inside of the fluid working chamber 10.
【0025】尚、図6に示したものでは、第二スクロー
ル2の背面に凸形のボス部23を突設して、このボス部
23をクランク軸93の上端部に開口する偏心穴から成
る偏心ピン部93dに嵌合しており、給油通路6に汲み
上げる油を、連結部に介装するシールリング6bを介し
て第二スクロール2のボス部23に設ける連通穴6cに
受け渡し、この連通穴6cを介して中心側室42に開放
するようにしている。又、絞り機構7を構成する油溝7
1は、前記ボス部23と偏心ピン部93dとの間の接触
部に設ける内周側油溝71aと、該内周側油溝71aに
連通穴70を介してその下部を連通させ、上部軸受メタ
ル97aに接する外周側油溝71bとで構成しており、
返油通路8の入口側は、外周側油溝71bの下部側に開
口するようにしている。更に、油ポンプ5には、遠心式
のものを用いている。
In the structure shown in FIG. 6, a convex boss portion 23 is provided on the rear surface of the second scroll 2 and the boss portion 23 is formed of an eccentric hole which is opened at the upper end of the crankshaft 93. The oil that is fitted to the eccentric pin portion 93d and that is pumped into the oil supply passage 6 is delivered to the communication hole 6c provided in the boss portion 23 of the second scroll 2 through the seal ring 6b that is interposed in the connection portion, and this communication hole The central chamber 42 is opened via 6c. Further, the oil groove 7 that constitutes the throttle mechanism 7
Reference numeral 1 denotes an inner peripheral oil groove 71a provided in a contact portion between the boss portion 23 and the eccentric pin portion 93d, and a lower portion thereof communicates with the inner peripheral oil groove 71a through a communication hole 70 to form an upper bearing. The outer peripheral oil groove 71b is in contact with the metal 97a.
The inlet side of the oil return passage 8 is opened to the lower side of the outer peripheral oil groove 71b. Further, the oil pump 5 is of a centrifugal type.
【0026】[0026]
【発明の効果】以上、請求項1記載の発明によれば、第
二スクロール2の背面中心側に高圧圧力と油ポンプ5に
よる昇圧圧力とが加わって作用するため、環状シール体
3の径を小さくして第二スクロール2の背面中心側の作
用面積を縮小しても、低差圧条件下で上向きのスラスト
力を発生でき、第二スクロール2を第一スクロール1に
適正に押し付けることができると共に、高差圧条件下で
は、高圧圧力の付与面積が縮小された分だけスラスト力
が過大になるのを防止することができ、第一スクロール
1と第二スクロール2との間の摺動特性を改善できるの
である。
As described above, according to the first aspect of the invention, since the high pressure and the pressure boosted by the oil pump 5 act on the center side of the rear surface of the second scroll 2, the diameter of the annular seal body 3 is reduced. Even if the action area on the rear center side of the second scroll 2 is reduced to be small, the upward thrust force can be generated under the low differential pressure condition, and the second scroll 2 can be appropriately pressed against the first scroll 1. At the same time, under a high differential pressure condition, it is possible to prevent the thrust force from becoming excessive due to the reduction of the high-pressure applied area, and the sliding characteristic between the first scroll 1 and the second scroll 2 can be prevented. Can be improved.
【0027】請求項2記載の発明によれば、油溝71に
流れる油でクランク軸93の円筒摺動面の潤滑をも兼用
して行うことができる。
According to the second aspect of the invention, the oil flowing in the oil groove 71 can also be used to lubricate the cylindrical sliding surface of the crankshaft 93.
【0028】請求項3記載の発明によれぱ、油溝71と
返油通路8との間のオーバーラップ構造により、回転数
に応じて中心側室42の圧力を適正に保つこともでき
る。
According to the third aspect of the invention, the overlap structure between the oil groove 71 and the oil return passage 8 allows the pressure in the center side chamber 42 to be appropriately maintained according to the number of revolutions.
【0029】請求項4記載の発明によれば、リリーフ弁
60により、第二スクロール2の背面に作用するスラス
ト力が異常上昇するのを未然に防止することもできる。
According to the fourth aspect of the invention, the relief valve 60 can prevent the thrust force acting on the back surface of the second scroll 2 from abnormally rising.
【0030】請求項5記載の発明によれば、可変絞り弁
72により、中心側室42の圧力値を適正に保つことが
でき、スラスト力を適正に保持することもできる。
According to the fifth aspect of the present invention, the variable throttle valve 72 can properly maintain the pressure value of the center side chamber 42 and also properly maintain the thrust force.
【図面の簡単な説明】[Brief description of drawings]
【図1】本発明に係るスクロール形流体機械の第一実施
例を示す上部断面図。
FIG. 1 is an upper sectional view showing a first embodiment of a scroll type fluid machine according to the present invention.
【図2】同下部断面図。FIG. 2 is a bottom sectional view of the same.
【図3】同作用を説明する特性図。FIG. 3 is a characteristic diagram illustrating the same operation.
【図4】同第二実施例を示す要部断面図。FIG. 4 is a sectional view of a main part showing the second embodiment.
【図5】同第三実施例を示す要部断面図。FIG. 5 is a cross-sectional view of a main part showing the third embodiment.
【図6】同第四実施例を示す断面図。FIG. 6 is a sectional view showing the fourth embodiment.
【図7】従来のスクロール形流体機械の断面図。FIG. 7 is a sectional view of a conventional scroll type fluid machine.
【図8】従来の問題点を説明する特性図。FIG. 8 is a characteristic diagram illustrating a conventional problem.
【符号の説明】[Explanation of symbols]
1 第一スクロール 2 第二スクロール 3 環状シール体 4 背面室 5 油ポンプ 6 給油通路 7 絞り機構 8 返油通路 9 密閉ケーシング 10 流体作動室 41 外周側室 42 中心側室 60 リリーフ弁 71 油溝 72 可変絞り弁 93 クランク軸 1 first scroll 2 second scroll 3 annular seal body 4 back room 5 oil pump 6 oil supply passage 7 Aperture mechanism 8 oil return passage 9 closed casing 10 Fluid working chamber 41 Outer chamber 42 Center side chamber 60 relief valve 71 oil ditch 72 Variable throttle valve 93 crankshaft
───────────────────────────────────────────────────── フロントページの続き (72)発明者 梶原 幹央 大阪府堺市築港新町3丁12番地 ダイキ ン工業株式会社堺製作所臨海工場内 (56)参考文献 特開 昭62−139991(JP,A) 特開 平2−173377(JP,A) 特開 昭59−49386(JP,A) 特開 昭56−165788(JP,A) 特開 昭61−169686(JP,A) (58)調査した分野(Int.Cl.7,DB名) F04C 18/00 - 18/077 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor, Mikio Kajiwara, 3-12 Tsukikoshinmachi, Sakai City, Osaka Prefecture Daikin Industry Co., Ltd. Sakai Plant's seaside factory (56) Reference JP 62-139991 (JP, A) JP-A-2-173377 (JP, A) JP-A-59-49386 (JP, A) JP-A-56-165788 (JP, A) JP-A-61-169686 (JP, A) (58) Fields investigated (Int.Cl. 7 , DB name) F04C 18/00-18/077

Claims (5)

    (57)【特許請求の範囲】(57) [Claims]
  1. 【請求項1】高圧ドーム形の密閉ケーシング9に、第一
    スクロール1と該第一スクロール1に対して相対的に公
    転運動する第二スクロール2とを内装し、これらスクロ
    ール1,2の渦巻体間に、渦巻外周側の低圧域から渦巻
    中心側の高圧域にかけてその圧力が変化する流体作動室
    10を画成したスクロール形流体機械において、前記第
    二スクロール2の背面側に、前記ケーシング9の内部空
    間と画成し且つ前記第二スクロール2の背面側に設ける
    環状シール体3を介して外周側室41と中心側室42と
    に区画する背面室4を設けて、前記外周側室41を低圧
    域に連通させると共に、前記中心側室42に、前記ケー
    シング9の内部に溜める油を汲み上げる油ポンプ5から
    延びる給油通路6を開口する一方、前記中心側室42を
    絞り機構7をもつ返油通路8を介して前記ケーシング9
    の内部空間に連通させていることを特徴とするスクロー
    ル形流体機械。
    1. A high-pressure dome-shaped hermetic casing 9 is internally provided with a first scroll 1 and a second scroll 2 which orbits relative to the first scroll 1, and a scroll body of these scrolls 1 and 2. In the scroll type fluid machine, which defines a fluid working chamber 10 in which the pressure changes from a low pressure area on the spiral outer circumference side to a high pressure area on the spiral center side, a casing 9 is provided on the back side of the second scroll 2. A rear chamber 4 is provided which is partitioned from the inner space and is divided into an outer peripheral chamber 41 and a central chamber 42 via an annular seal body 3 provided on the rear face side of the second scroll 2, and the outer peripheral chamber 41 is placed in a low pressure region. While communicating with each other, an oil supply passage 6 extending from an oil pump 5 that pumps up oil stored in the casing 9 is opened in the center side chamber 42, while the center side chamber 42 has a throttle mechanism 7. Wherein through the oil passage 8 casing 9
    A scroll type fluid machine characterized by being communicated with the internal space of the.
  2. 【請求項2】第二スクロール2を連動させるクランク軸
    93の円筒摺動面に油溝71を開口して、この油溝71
    の入口側を中心側室42に連通させると共に、前記油溝
    71の出口側を静止部材に設ける返油通路8に連通させ
    て、前記油溝71を中間部に介在させて前記中心側室4
    2と返油通路8の入口部とを結ぶ経路により絞り機構7
    を構成している請求項1記載のスクロール形流体機械。
    2. An oil groove 71 is opened in a cylindrical sliding surface of a crank shaft 93 for interlocking the second scroll 2, and the oil groove 71 is formed.
    Of the center side chamber 4 by communicating the inlet side of the oil groove 71 with the center side chamber 42 and the outlet side of the oil groove 71 with the oil return passage 8 provided in the stationary member.
    2 is connected to the inlet portion of the oil return passage 8 by a throttle mechanism 7
    The scroll type fluid machine according to claim 1, which is configured as follows.
  3. 【請求項3】油溝71の出口部と返油通路8の入口部と
    の間を、クランク軸93の回転に伴い開口部相互間が間
    欠的に符合するオーバーラップ構造としている請求項2
    記載のスクロール形流体機械。
    3. The overlap structure between the outlet of the oil groove 71 and the inlet of the oil return passage 8 is such that the openings are intermittently aligned with each other as the crankshaft 93 rotates.
    The scroll-type fluid machine described.
  4. 【請求項4】給油通路6に、汲み上げ油の異常圧力上昇
    を逃がすリリーフ弁60を介装している請求項1又は請
    求項2若しくは請求項3記載のスクロール形流体機械。
    4. The scroll type fluid machine according to claim 1, 2 or 3, wherein a relief valve 60 is provided in the oil supply passage 6 to release an abnormal pressure rise of the pumping oil.
  5. 【請求項5】絞り機構7を、中心側室42の圧力上昇に
    伴い開口面積が拡大する可変絞り弁72により構成して
    いる請求項1記載のスクロール形流体機械。
    5. The scroll type fluid machine according to claim 1, wherein the throttle mechanism 7 comprises a variable throttle valve 72 whose opening area increases as the pressure in the central chamber 42 increases.
JP30620491A 1991-11-21 1991-11-21 Scroll type fluid machine Expired - Fee Related JP3367109B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP30620491A JP3367109B2 (en) 1991-11-21 1991-11-21 Scroll type fluid machine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP30620491A JP3367109B2 (en) 1991-11-21 1991-11-21 Scroll type fluid machine

Publications (2)

Publication Number Publication Date
JPH05141201A JPH05141201A (en) 1993-06-08
JP3367109B2 true JP3367109B2 (en) 2003-01-14

Family

ID=17954250

Family Applications (1)

Application Number Title Priority Date Filing Date
JP30620491A Expired - Fee Related JP3367109B2 (en) 1991-11-21 1991-11-21 Scroll type fluid machine

Country Status (1)

Country Link
JP (1) JP3367109B2 (en)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH08159055A (en) * 1994-12-08 1996-06-18 Sanden Corp High pressure type compressor
JP2956509B2 (en) * 1995-01-17 1999-10-04 松下電器産業株式会社 Scroll gas compressor
US6059549A (en) * 1998-03-25 2000-05-09 Rechi Precision Co., Ltd. High-low pressure chamber sealing arrangement of a volute compressor
US6290478B1 (en) 1999-07-16 2001-09-18 Scroll Technologies Eccentric back chamber seals for scroll compressor
JP4697734B2 (en) * 2005-01-14 2011-06-08 日立アプライアンス株式会社 Refrigeration cycle
KR100864754B1 (en) * 2005-11-28 2008-10-22 엘지전자 주식회사 Oil feeding structure for scroll compressor
TWI306920B (en) * 2005-12-09 2009-03-01 Ind Tech Res Inst
JP6167417B2 (en) * 2015-10-30 2017-07-26 三菱重工サーマルシステムズ株式会社 Scroll compressor and air conditioner

Also Published As

Publication number Publication date
JPH05141201A (en) 1993-06-08

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