JPH06108979A - Fluid machine - Google Patents

Fluid machine

Info

Publication number
JPH06108979A
JPH06108979A JP25768992A JP25768992A JPH06108979A JP H06108979 A JPH06108979 A JP H06108979A JP 25768992 A JP25768992 A JP 25768992A JP 25768992 A JP25768992 A JP 25768992A JP H06108979 A JPH06108979 A JP H06108979A
Authority
JP
Japan
Prior art keywords
cylinder
piston
discharge port
suction port
suction
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
JP25768992A
Other languages
Japanese (ja)
Inventor
Naoya Morozumi
尚哉 両角
Tsugio Itami
次男 伊丹
Kanji Sakata
寛二 坂田
Katsuya Minami
克哉 南
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Toshiba Corp
Original Assignee
Toshiba Corp
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 Toshiba Corp filed Critical Toshiba Corp
Priority to JP25768992A priority Critical patent/JPH06108979A/en
Publication of JPH06108979A publication Critical patent/JPH06108979A/en
Pending legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • 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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 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 groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 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 groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C2/3441—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 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 groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • F04C2/3442—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 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 groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Abstract

PURPOSE:To increase the quantity of suction and discharge so as to eliminate pressure loss and facilitate clearance control between a cylinder and a piston. CONSTITUTION:A fluid machine is provided with a rotatable cylinder 9 with both ends thereof supported on bearing members 11 having suction ports 17 and discharge ports 19; a rotatable cylindrical piston 27 eccentrically disposed in the cylinder 9; and blades 37 forming plural expandable operating chambers between the cylinder 9 and the piston 27. The piston 27 is provided at its edge with plural cutout recessed parts 35 communicated with the operating chambers and cut off from the discharge port 19 on the other side at the time of being communicated with the suction port 17 on one side. The fluid machine is thus provided with the rotatable cylinder 9 with the suction ports and discharge ports at the side parts; a shaft 15 piercing the cylinder 9, and supported at both ends thereof by a closed casing 7; the cylindrical piston 27 mounted eccentrically to the shaft 15 and brought into contact, at both side faces thereof, with both side walls of the cylinder 9 so as to be constrained in its axial movement; and the blades 37 forming plural expandable operating chambers between the cylinder 9 and the piston 27.

Description

【発明の詳細な説明】Detailed Description of the Invention

【０００１】[0001]

【産業上の利用分野】この発明は、送風、圧縮ポンプ等
に適する流体機械に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a fluid machine suitable for blowers, compression pumps and the like.

【０００２】[0002]

【従来の技術】従来、圧縮用の機械として、例えば、ロ
ータリベーン式コンプレッサが知られている。2. Description of the Related Art Conventionally, a rotary vane compressor is known as a compression machine.

【０００３】ロータリベーン式コンプレッサの概要は、
固定されたシリンダ内に、回転可能な回転体が偏心して
配置され、その回転体に、前記シリンダと回転体との間
に複数の作動室を形成するブレードが設けられている。
作動室を形成するブレードは、偏心して配置された前記
回転体の回転にともない、シリンダの内周面と接触しな
がら進退することで、作動室の拡縮を図り、最圧縮時に
吐出口から外へ送り出す構造となっている。The outline of the rotary vane compressor is as follows.
A rotatable rotating body is eccentrically arranged in a fixed cylinder, and the rotating body is provided with blades that form a plurality of working chambers between the cylinder and the rotating body.
The blade forming the working chamber moves forward and backward while coming into contact with the inner peripheral surface of the cylinder with the rotation of the eccentrically arranged rotating body, thereby expanding and contracting the working chamber, and at the time of the most compression, it moves outward from the discharge port. It has a structure to send out.

【０００４】[0004]

【発明が解決しようとする課題】前記した如く作動中の
ブレードは、固定されたシリンダの内周面と常に摺動し
ながら回転するため、その摺動抵抗によって損失が大き
く、効率の面でも望ましくないことから、シリンダとブ
レードとを同期回転させることでブレードの摺動抵抗を
軽減させる提案がなされている。As described above, the blade in operation always rotates while sliding on the inner peripheral surface of the fixed cylinder, so that the sliding resistance causes a large loss and is desirable in terms of efficiency. Therefore, it has been proposed to reduce the sliding resistance of the blade by synchronously rotating the cylinder and the blade.

【０００５】しかしながら、シリンダ側を回転させる手
段は、設置スペースの関係で大きな制約を受けるシリン
ダの側方に、吸込口と吐出口とを設けるようになり、流
量に対する十分な吸込面積、吐出面積の確保が難しく、
圧力損失を招来するようになること、また、運転時と停
止時とでは密閉ケース側と回転体側との温度差が大き
く、密閉ケースの熱膨張量に対して回転体側の熱膨張量
が大きくなる。However, the means for rotating the cylinder side is provided with a suction port and a discharge port on the side of the cylinder which is greatly restricted by the installation space, so that a sufficient suction area and discharge area for the flow rate can be obtained. Difficult to secure,
Pressure loss is caused, and the temperature difference between the sealed case side and the rotating body side during operation and stop is large, and the thermal expansion amount on the rotating body side is larger than the thermal expansion amount on the sealed case side. .

【０００６】この熱膨張量は、軸線方向と直交する方向
のものは、ブレードの伸縮により吸収可能となるが、軸
線方向の熱膨脹量にあっては、吸収する手段がなく、作
動室の両側壁となる左右の軸受部材と、回転体の両側面
とのクリアランスを熱膨張量に対応して正しく確保する
必要がある。The thermal expansion amount in the direction orthogonal to the axial direction can be absorbed by the expansion and contraction of the blade, but the thermal expansion amount in the axial direction has no means for absorbing the thermal expansion amount, and both side walls of the working chamber can be absorbed. It is necessary to properly secure the clearance between the left and right bearing members and both side surfaces of the rotating body in accordance with the amount of thermal expansion.

【０００７】ところが、回転体の両側面と接触し合う軸
受部材は、熱膨張量の異なる密閉ケースに固定されるた
めに、密閉ケース、軸受部材、回転体の順に精度を出さ
なくてはならず、クリアランスの精度管理が非常に難し
く、圧縮漏れを起こす要因となっていたものである。However, since the bearing members that come into contact with both side surfaces of the rotating body are fixed in the sealed case having different amounts of thermal expansion, it is necessary to provide accuracy in the order of the sealed case, the bearing member and the rotating body. However, it was very difficult to control the precision of the clearance, which was a factor causing compression leakage.

【０００８】そこで、この発明は、前記問題を解消する
新たな流体機械を提供することを目的とする。Therefore, an object of the present invention is to provide a new fluid machine that solves the above problems.

【０００９】[0009]

【課題を解決するための手段】前記目的を達成するため
に、この発明は、駆動手段により回転動力が与えられ、
吸込口と吐出口とを有する軸受部材に両端支持された回
転可能なシリンダ内に偏心した円柱状のピストンを設
け、このピストンにシリンダとピストンとの間に拡縮可
能な複数の作動室を形成するブレードを設ける一方、前
記ピストンの端縁に作動室と連通し合うと共に、一方の
吸込口との連通時に、他方の吐出口と遮断状態となる切
欠凹部を複数設ける。In order to achieve the above-mentioned object, the present invention provides rotational power by a driving means,
An eccentric cylindrical piston is provided in a rotatable cylinder supported at both ends by a bearing member having a suction port and a discharge port, and a plurality of expandable and contractable working chambers are formed between the cylinder and the piston. While the blade is provided, a plurality of cutout recesses are provided at the end edge of the piston so as to communicate with the working chamber and to be in a closed state with the other discharge port when communicating with the one suction port.

【００１０】また、駆動手段により回転動力が与えら
れ、側方に吸込口と吐出口とを有する回転可能なシリン
ダと、シリンダ内を貫通し密閉ケースに両端支持された
シャフトと、シャフトに偏心して装着され両側面が前記
シリンダの両側壁と接触し軸方向の動きが拘束された円
柱状のピストンと、ピストンから放射方向に沿って延長
されシリンダとピストンとの間に拡縮可能な複数の作動
室を形成するブレードとを備えている。Further, a rotating cylinder is provided with a rotational power by a driving means and has a suction port and a discharge port on its side, a shaft penetrating the inside of the cylinder and supported at both ends in a sealed case, and eccentric to the shaft. A cylindrical piston that is mounted and has both side surfaces in contact with both side walls of the cylinder and is constrained from axial movement, and a plurality of working chambers that extend from the piston in the radial direction and that can be expanded and contracted between the cylinder and the piston. And a blade that forms a.

【００１１】[0011]

【作用】かかる流体機構によれば、ピストンの端縁に設
けられた切欠凹部の領域分、吸込口、吐出口への連通面
積の拡大が図れるようになり、圧力損失の軽減が図れ
る。According to such a fluid mechanism, it is possible to increase the area of the notch recess provided in the end edge of the piston, the communication area to the suction port and the discharge port, and to reduce the pressure loss.

【００１２】一方、作動中において、シリンダ及びピス
トンは密閉ケースから独立しており、シリンダ内に組込
まれたピストンは、シリンダとほぼ同一の熱膨張量とな
る。したがって、ピストンとシリンダのクリアランスの
精度管理が非常に楽になると共に、運転初期時から効率
のよい圧縮状態が得られるようになる。On the other hand, during operation, the cylinder and the piston are independent of the sealed case, and the piston incorporated in the cylinder has substantially the same amount of thermal expansion as the cylinder. Therefore, it becomes very easy to control the accuracy of the clearance between the piston and the cylinder, and an efficient compressed state can be obtained from the initial stage of operation.

【００１３】[0013]

【実施例】以下、図１乃至図５の図面を参照しながらこ
の発明の一実施例を詳細に説明する。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below in detail with reference to the drawings of FIGS.

【００１４】図１において１はステータ３とロータ５と
から成る駆動手段を示しており、ステータ３は密閉ケー
ス７内に固定支持されている。ロータ５は、前記ステー
タ３に電流が流れることで回転可能となっており、ロー
タ５の内側にはロータ５と一緒に回転する円筒状のシリ
ンダ９が一体に結合固着されている。In FIG. 1, reference numeral 1 denotes a driving means composed of a stator 3 and a rotor 5, and the stator 3 is fixedly supported in a sealed case 7. The rotor 5 is rotatable when an electric current flows through the stator 3, and a cylindrical cylinder 9 that rotates together with the rotor 5 is integrally fixed to the inside of the rotor 5.

【００１５】シリンダ９の両端は軸受部材１１によって
回転自在に両端支持され、軸受部材１１の軸心ａはシリ
ンダ９の回転中心となっている。また、軸受部材１１の
領域は潤滑油による油膜によってシールが確保されてい
る。Both ends of the cylinder 9 are rotatably supported by bearing members 11, and an axis a of the bearing member 11 is the center of rotation of the cylinder 9. In addition, a seal is secured in the area of the bearing member 11 by an oil film of lubricating oil.

【００１６】軸受部材１１は、一方（図面左側）が前記
密閉ケース７から延長された支持ブラケット１５に固定
支持され、他方（図面右側）の軸受部材１１は前記密閉
ケース７の側壁７ａに固定支持されている。One (left side in the drawing) of the bearing member 11 is fixedly supported by a support bracket 15 extending from the closed case 7, and the other bearing member 11 (right side in the drawing) is fixedly supported by a side wall 7a of the closed case 7. Has been done.

【００１７】さらに、軸受部材１１は後述する作動室２
１と連通し合う吸込口１７と吐出口１９とがそれぞれ設
けられると共に吸込口１７は、軸受部材１１から密閉ケ
ース７の外へ延長された吸込パイプ２３と接続連通して
いる。Further, the bearing member 11 has a working chamber 2 which will be described later.
1 is provided with a suction port 17 and a discharge port 19, respectively, and the suction port 17 is connected and communicated with a suction pipe 23 extending from the bearing member 11 to the outside of the sealed case 7.

【００１８】吐出口１９は、軸受部材１１内を貫通し、
前記密閉ケース１内に開放されていて、密閉ケース７に
設けられた吐出パイプ２５と連通している。これによ
り、密閉ケース７内に送り出された冷媒は前記吐出パイ
プ２５を介して外へ送り出されるようになっている。The discharge port 19 penetrates through the inside of the bearing member 11,
It is opened in the closed case 1 and communicates with a discharge pipe 25 provided in the closed case 7. As a result, the refrigerant sent into the closed case 7 is sent out through the discharge pipe 25.

【００１９】一方、シリンダ９内にはピストン２７がα
分偏心して軸心ｂを中心として回転自在に配置されてい
る。On the other hand, in the cylinder 9, the piston 27 is α
It is eccentrically divided and rotatably arranged around the axis b.

【００２０】ピストン２７は、円柱状に形成され、それ
の両軸端部２９，２９は前記軸受部材１１の軸受孔３
１，３１内に回転自在に嵌挿支持されている。The piston 27 is formed in a cylindrical shape, and both shaft end portions 29, 29 of the piston 27 are formed in the bearing hole 3 of the bearing member 11.
It is rotatably fitted and supported in the insides of 1, 31.

【００２１】ピストン２７には、ほぼ９０度の間隔で放
射方向に４つのブレード溝３３と切欠凹部３５が複数設
けられている。The piston 27 is provided with a plurality of four blade grooves 33 and a plurality of cutout recesses 35 in the radial direction at intervals of approximately 90 degrees.

【００２２】切欠凹部３５は、図３に示すように、吐出
口１９及び吸込口１７側となるピストン２７の端縁に設
けられ長さＬは、一方の切欠凹部３５が吸込口１７との
連通時に、他方の吐出口１９と遮断状態となり、吸込口
１７と吐出口１９とに同時に連通し合うことのない寸法
に設定されている。As shown in FIG. 3, the notch recess 35 is provided at the end edge of the piston 27 on the discharge port 19 and suction port 17 sides. The length L is such that one notch recess 35 communicates with the suction port 17. At some times, the other discharge port 19 is shut off, and the suction port 17 and the discharge port 19 are set so as not to communicate with each other at the same time.

【００２３】また、切欠凹部３５の切欠き幅Ｔは、図５
に示すように値の高い図面左側領域において最適値があ
ることがわかる。最適値は、回転速度や圧力条件などに
よって変るため、それぞれの用途に適した寸法とするこ
とが望ましい。The notch width T of the notch recess 35 is shown in FIG.
It can be seen that there is an optimum value in the left area of the drawing where the value is high, as shown in FIG. Since the optimum value changes depending on the rotation speed, pressure conditions, etc., it is desirable that the optimum value be a size suitable for each application.

【００２４】なお、図５は、切欠き幅Ｔを変化させた時
の吐出口１９での流路抵抗による過圧縮損失と切欠き容
積による体積効率と理論仕事量の変化を計算し、作動室
２１の効率を予測計算し、最高効率の時の入力を１．０
とした比で表わした一例をグラフとして表わしたもので
ある。In FIG. 5, when the cutout width T is changed, the overcompression loss due to the flow path resistance at the discharge port 19 and the change in the volumetric efficiency and theoretical work due to the cutout volume are calculated, and the working chamber is calculated. The efficiency of 21 is predicted and calculated, and the input at the time of maximum efficiency is 1.0
The graph is an example of the ratio.

【００２５】また、ピストン２７に設けられた各ブレー
ド溝３３には進退自在にブレード３７が組入れられてい
る。ブレード３７の先端部は後述する潤滑用のトロコロ
イド式ポンプ３９からの油圧によって前記シリンダ９の
内周面と常時接触する状態が確保され、シリンダ９とピ
ストン２７との間に前記切欠凹部３５と連通し合う４つ
の作動室２１が形成されるようになっている。A blade 37 is incorporated in each blade groove 33 formed in the piston 27 so as to be able to move back and forth. The tip of the blade 37 is always kept in contact with the inner peripheral surface of the cylinder 9 by the hydraulic pressure from a trocolloid pump 39 for lubrication, which will be described later, and the notch recess 35 is formed between the cylinder 9 and the piston 27. Four working chambers 21 that communicate with each other are formed.

【００２６】各作動室２１は前記した如く吸込口１７及
び吐出口１９とそれぞれ連通し合うと共に、吸込口１７
及び吐出口１９との関係は、前記ピストン２７の回転運
動にともない図４（ａ），（ｂ），（ｃ），（ｄ）に示
すように各作動室２１の最拡大時までに、吸込口１７か
ら冷媒を取り込むようになる。また、作動室２１の最縮
小時までに圧縮された冷媒が吐出口１９から送り出され
るように設定されている。Each working chamber 21 communicates with the suction port 17 and the discharge port 19 respectively as described above, and at the same time, the suction port 17
The relationship between the discharge port 19 and the discharge port 19 is that the suction chamber is sucked by the maximum expansion of each working chamber 21 as shown in FIGS. 4 (a), 4 (b), 4 (c) and 4 (d). The refrigerant comes to be taken in through the port 17. Further, the refrigerant compressed by the time when the working chamber 21 is reduced to the minimum size is set to be discharged from the discharge port 19.

【００２７】ピストン２７は、前記シリンダ９の回転動
力が動力伝達機構４１を介して伝達されるようになって
いる。この動力伝達機構４１は、図２に示すようにピス
トン２７側に設けられたピン孔４３内に伝達ピン４５が
嵌挿され、それの先端部がピボットのような動きが可能
となるよう前記シリンダ９の係合孔４７内に浅く臨む伝
達ピンタイプの構造となっている。これにより、ピスト
ン２７には、シリンダ９の回転運動とほぼ同期した回転
運動が与えられるようになる。The piston 27 is adapted to transmit the rotational power of the cylinder 9 via a power transmission mechanism 41. In this power transmission mechanism 41, as shown in FIG. 2, a transmission pin 45 is inserted into a pin hole 43 provided on the piston 27 side, and the tip end portion of the transmission pin 45 can be moved like a pivot. 9 has a transmission pin type structure that shallowly faces the engagement hole 47. As a result, the piston 27 is given a rotary motion substantially in synchronization with the rotary motion of the cylinder 9.

【００２８】なお、シリンダ９からの回転動力をほぼ同
期してピストン２７に伝達する動力伝達機構４１は必ず
しも伝達ピンタイプに限定されるものではない。例えば
シリンダ９側に内歯歯車を、ピストン２７側に前記内歯
歯車と噛み合う外歯歯車を設けたギヤタイプとしたり
（この場合歯数が同じ方が望ましい）、その他オルダム
継手等適宜の手段を採用することも可能である。The power transmission mechanism 41 for transmitting the rotational power from the cylinder 9 to the piston 27 substantially in synchronization is not necessarily limited to the transmission pin type. For example, an internal gear is provided on the cylinder 9 side, and an external gear that meshes with the internal gear is provided on the piston 27 side (in this case, it is desirable that the number of teeth is the same), or other appropriate means such as Oldham coupling is adopted. It is also possible to do so.

【００２９】一方、トロコロイド式ポンプ３９は、前記
軸受部材１１（図１左側）内に組付けられている。トロ
コロイド式ポンプ３９は波板ばね４９により常時付勢さ
れた両側板５１，５１によってケーシング５３が挟持さ
れ、ケーシング５３内には、吸込ポート（図示していな
い）から取入れた潤滑油を吐出ポート（図示していな
い）から送り出すギヤ５５が設けられている。吸込ポー
トは、下端部が潤滑油の液面内に臨む吸込管５７と連通
している。また、吐出ポートは前記ピストン２７内を貫
通した連絡通路５９を介して左右の軸受部材１１及び軸
受孔３１とそれぞれ連通し、仕事を終えた潤滑油は密閉
ケース７内へ落下するようになっている。なお、ケーシ
ング５３内のギヤ５５は、前記ピストン２７の軸端部２
９から延長された延長軸６１に嵌挿固着され、ピストン
２７からの回転動力が与えられる。なお、このポンプ機
構を駆動力伝達機構として使ってもよい。On the other hand, the trocolloid pump 39 is assembled in the bearing member 11 (left side in FIG. 1). The trocoloid pump 39 has a casing 53 sandwiched by both side plates 51, 51 which are constantly urged by a corrugated leaf spring 49, and a lubricating oil taken in from a suction port (not shown) is discharged into the casing 53. A gear 55 that feeds from (not shown) is provided. The lower end of the suction port communicates with the suction pipe 57 that faces the liquid surface of the lubricating oil. Further, the discharge port communicates with the left and right bearing members 11 and the bearing holes 31 through the communication passages 59 penetrating the inside of the piston 27, and the lubricating oil which has finished the work falls into the sealed case 7. There is. In addition, the gear 55 in the casing 53 is the shaft end portion 2 of the piston 27.
9 is fitted and fixed to an extension shaft 61 extended from 9, and rotational power is applied from the piston 27. In addition, you may use this pump mechanism as a driving force transmission mechanism.

【００３０】次に動作について説明する。駆動手段１に
よってシリンダ９が回転すると、そのシリンダ９の回転
動力は動力伝達機構４１により、ほぼ同期してピストン
２７に伝達される。このピストン２７の回転運動にとも
ない、例えば作動室２１は反時計方向に回動しながら、
冷媒を吸込口１７から吸込（図３（ａ））、吸込み完了
（ｂ）後、圧縮状態（ｃ）に入る。そして、吐出口１９
から吐出（ｄ）するサイクルを繰返すようになる。Next, the operation will be described. When the cylinder 9 is rotated by the driving means 1, the rotational power of the cylinder 9 is transmitted to the piston 27 by the power transmission mechanism 41 almost in synchronization. As the piston 27 rotates, for example, the working chamber 21 rotates counterclockwise,
The refrigerant is sucked from the suction port 17 (FIG. 3A), and after the suction is completed (b), the compressed state (c) is entered. Then, the discharge port 19
The discharge (d) cycle is repeated.

【００３１】この動作時において、切欠凹部３５の領域
分、吸込口１７、吐出口１９への連通面積が拡大するた
め、吸込時の圧力損失によるガス流量の低下と、吐出時
の過圧縮による損失仕事の低減が図れる。During this operation, the area of the notch recess 35 increases the communication area to the suction port 17 and the discharge port 19, so that the gas flow rate decreases due to the pressure loss during suction and the loss due to overcompression during discharge. Work can be reduced.

【００３２】一方、ブレード３７の先端と、シリンダ９
の内周面との相対速度は小さく抑えられ、高速運転時で
も焼き付きが起きなくなると共に摺動による摩耗損失や
騒音も低く抑えられる。On the other hand, the tip of the blade 37 and the cylinder 9
The relative speed to the inner peripheral surface of the is suppressed to be small, seizure does not occur even at high speed operation, and wear loss due to sliding and noise are also suppressed to a low level.

【００３３】図６，図７は流体機械の別の実施例を示し
たものである。6 and 7 show another embodiment of the fluid machine.

【００３４】即ち、図において１はステータ３とロータ
５とから成る駆動手段を示しており、ステータ３は密閉
ケース７内に固定支持されている。ロータ５は、前記ス
テータ３に電流が流れることで回転可能となっており、
ロータ５の内側にはロータ５と一緒に回転するシリンダ
９が一体に結合固着されている。That is, in the figure, reference numeral 1 denotes a driving means composed of a stator 3 and a rotor 5, and the stator 3 is fixedly supported in a sealed case 7. The rotor 5 is rotatable by passing a current through the stator 3,
Inside the rotor 5, a cylinder 9 that rotates together with the rotor 5 is integrally fixed.

【００３５】シリンダ９の両側は軸受部材１１，１３と
なっており、一方の軸受部材１３はシリンダ９と一体成
形された形状となっている。シリンダ９の軸受部材１
１，１３には、前記密閉ケース７に両端が固定支持され
たシャフト１５が貫通し、軸受部材１１，１３の軸心ａ
はシリンダ９の回転中心となっている。また、軸受部材
１１，１３の領域は潤滑油による油膜によってシールが
確保されている。Bearing members 11, 13 are provided on both sides of the cylinder 9, and one bearing member 13 has a shape integrally formed with the cylinder 9. Bearing member 1 of cylinder 9
Shafts 15, both ends of which are fixedly supported by the sealed case 7, pass through the shafts 1, 13 and the shaft center a of the bearing members 11, 13.
Is the center of rotation of the cylinder 9. In addition, a seal is secured in the regions of the bearing members 11 and 13 by an oil film of lubricating oil.

【００３６】さらに、軸受部材１３には後述する作動室
２１と連通し合う吸込口１７と吐出口１９とがそれぞれ
設けられると共に吸入口１７は、周方向に沿ってリング
状に形成され、シャフト１５に設けられた連絡通路２０
を介して密閉ケース７の外へ延長された吸込パイプ２３
と接続連通している。吐出口１９は、軸受部材１３内を
貫通し、前記密閉ケース７内に開放されていて、密閉ケ
ース７に設けられた吐出パイプ２５と連通している。こ
れにより、密閉ケース７内に送り出された冷媒は前記吐
出パイプ２５を介して外へ送り出されるようになってい
る。Further, the bearing member 13 is provided with a suction port 17 and a discharge port 19 which communicate with a working chamber 21 described later, and the suction port 17 is formed in a ring shape along the circumferential direction, and the shaft 15 is provided. Communication passage 20 provided in
Suction pipe 23 extended to the outside of the closed case 7 via
It is in communication with. The discharge port 19 penetrates through the bearing member 13, is opened in the closed case 7, and communicates with a discharge pipe 25 provided in the closed case 7. As a result, the refrigerant sent into the closed case 7 is sent out through the discharge pipe 25.

【００３７】一方、シリンダ９内にはピストン２７がα
分偏心して軸心ｂを中心として回転自在に配置されてい
る。On the other hand, in the cylinder 9, the piston 27 is α
It is eccentrically divided and rotatably arranged around the axis b.

【００３８】ピストン２７は、軸筒状に形成され、それ
の両端部２７ａ，２７ａは前記シリンダ９の両軸受部材
１１，１３と接触している。The piston 27 is formed in the shape of a shaft cylinder, and both ends 27a, 27a thereof are in contact with both bearing members 11, 13 of the cylinder 9.

【００３９】ピストン２７には、ほぼ９０度の間隔で放
射方向に４つのブレード溝３３が設けられ、各ブレード
溝３３には進退自在にブレード３７が組入れられてい
る。ブレード３７の先端部は潤滑用のトロコロイド式ポ
ンプ（図示していない）からの油圧によって前記シリン
ダ９の内壁面と常時接触する状態が確保され、シリンダ
９とピストン２７との間に３つの作動室２１が形成され
るようになっている。The piston 27 is provided with four blade grooves 33 in the radial direction at intervals of approximately 90 degrees, and blades 37 are incorporated in each blade groove 33 so as to be movable back and forth. The tip of the blade 37 is kept in constant contact with the inner wall surface of the cylinder 9 by hydraulic pressure from a trocolloid pump for lubrication (not shown), and three operations are performed between the cylinder 9 and the piston 27. A chamber 21 is formed.

【００４０】作動室２１は前記した如く吸込口１７及び
吐出口１９とそれぞれ連通し合うと共に吸込口１７及び
吐出口１９との関係は、前記ピストン２７の回転運動に
ともない各作動室２１の最拡大時までに、吸込口１７か
ら冷媒を取り込むようになる。また、作動室２１の最縮
小時までに圧縮された冷媒が吐出口１９から送り出され
るよう設定されている。The working chamber 21 communicates with the suction port 17 and the discharge port 19, respectively, as described above, and the relationship between the suction port 17 and the discharge port 19 is the maximum expansion of each working chamber 21 as the piston 27 rotates. By the time, the refrigerant is taken in from the suction port 17. Further, the refrigerant compressed by the time when the working chamber 21 is reduced to the minimum size is set to be discharged from the discharge port 19.

【００４１】次に動作について説明する。駆動手段１に
よってシリンダ９が回転すると、そのシリンダ９の回転
運動にともない、例えば作動室２１は時計方向に回動し
ながら、冷媒を吸込口１７から吸込み、吸込み完了後、
圧縮状態に入る。そして、吐出口１９から吐出するサイ
クルを繰返すようになる。Next, the operation will be described. When the cylinder 9 is rotated by the drive means 1, the working chamber 21 is rotated clockwise, for example, while the cylinder 9 is being rotated, while sucking the refrigerant from the suction port 17, and after the suction is completed,
Enters the compressed state. Then, the cycle of discharging from the discharge port 19 is repeated.

【００４２】この動作時において、シリンダ９とピスト
ン２７とはほぼ同一の熱膨張量となるため、大きなクリ
アランスは発生せず、運転初期時から効率のよい圧縮状
態が得られる。したがって、ほぼ同一の熱膨張量となる
シリンダ９とピストン２７のクリアランス管理を行なえ
ばよく、クリアランス管理が非常に容易となる。In this operation, since the cylinder 9 and the piston 27 have substantially the same thermal expansion amount, no large clearance is generated and an efficient compressed state is obtained from the initial stage of operation. Therefore, it is sufficient to manage the clearance between the cylinder 9 and the piston 27, which have substantially the same thermal expansion amount, and the clearance management becomes very easy.

【００４３】[0043]

【発明の効果】以上説明したようにこの発明によれば、
切欠凹部の領域分、吸込口及び吐出口への連通面積の拡
大が図れるようになり、圧力損失によるガス流量の低下
と、過圧縮による損失仕事を低減することができる。As described above, according to the present invention,
It is possible to increase the area of communication with the suction port and the discharge port by the area of the cutout recess, and it is possible to reduce the gas flow rate due to pressure loss and the loss work due to overcompression.

【００４４】また、ほぼ同一の熱膨張量となるピストン
とシリンダのクリアランス管理をすればよいため、組付
け時の精度管理が容易になると共に運転初期時から効率
のよい圧縮状態が得られる。Since the clearance between the piston and the cylinder having substantially the same thermal expansion amount may be managed, the accuracy management during the assembling can be facilitated and an efficient compressed state can be obtained from the initial stage of the operation.

【図面の簡単な説明】[Brief description of drawings]

【図１】この発明を実施した流体機械の切断面図であ
る。FIG. 1 is a sectional view of a fluid machine embodying the present invention.

【図２】ピストンとシリンダと一方の軸受部材を示した
分解斜視図である。FIG. 2 is an exploded perspective view showing a piston, a cylinder, and one bearing member.

【図３】図１のＡ−Ａ線切断面図である。3 is a sectional view taken along the line AA of FIG.

【図４】動作説明図である。FIG. 4 is an operation explanatory diagram.

【図５】コンプレッサ入力、体積効率、コンプレッサ効
率の特性図である。FIG. 5 is a characteristic diagram of compressor input, volume efficiency, and compressor efficiency.

【図６】別の実施例を示した図１と同様の切断面図であ
る。FIG. 6 is a sectional view similar to FIG. 1, showing another embodiment.

【図７】図６のＢ−Ｂ線切断面図である。FIG. 7 is a sectional view taken along line BB of FIG.

【符号の説明】[Explanation of symbols]

９ シリンダ １１ 軸受部材 １５ シャフト １７ 吸込口 １９ 吐出口 ２１ 作動室 ２７ ピストン ３５ 切欠凹部 ３７ ブレード ４１ 動力伝達機構 9 Cylinder 11 Bearing Member 15 Shaft 17 Suction Port 19 Discharge Port 21 Working Chamber 27 Piston 35 Notch Recess 37 Blade 41 Power Transmission Mechanism

フロントページの続き (72)発明者 南 克哉 神奈川県横浜市磯子区新杉田町８番地 株 式会社東芝住空間システム技術研究所内Front page continuation (72) Inventor Katsuya Minami 8 Shinsugita-cho, Isogo-ku, Yokohama, Kanagawa Prefecture

Claims (2)

【特許請求の範囲】[Claims] 【請求項１】 駆動手段により回転動力が与えられ、吸
込口と吐出口とを有する軸受部材に両端支持された回転
可能なシリンダと、シリンダ内に偏心して配置された回
転可能な円柱状のピストンと、前記シリンダの内周面と
接触するようピストンから放射方向に沿って延長されシ
リンダとピストンとの間に拡縮可能な複数の作動室を形
成するブレードと、前記シリンダの回転動力をほぼシリ
ンダの回転と同期して前記ピストンに伝達する動力伝達
機構とを具備し、前記ピストンの端縁に作動室と連通し
合うと共に、一方の吸込口との連通時に、他方の吐出口
と遮断状態となる切欠凹部を複数設けたことを特徴とす
る流体機械。1. A rotatable cylinder supported by a bearing member having a suction port and a discharge port, which is rotationally driven by a driving means, and a rotatable cylindrical piston eccentrically arranged in the cylinder. A blade that extends in a radial direction from the piston so as to be in contact with the inner peripheral surface of the cylinder and forms a plurality of working chambers that can be expanded and contracted between the cylinder and the piston; A power transmission mechanism that transmits to the piston in synchronism with rotation, communicates with the working chamber at the end edge of the piston, and is in a cutoff state from the other discharge port when communicating with one suction port. A fluid machine having a plurality of cutout recesses. 【請求項２】 駆動手段により回転動力が与えられ、側
方に吸込口と吐出口とを有する回転可能なシリンダと、
シリンダ内を貫通し密閉ケースに両端支持されたシャフ
トと、シャフトに偏心して装着され両側面が前記シリン
ダの両側壁と接触し軸方向の動きが拘束された円柱状の
ピストンと、ピストンから放射方向に沿って延長されシ
リンダとピストンとの間に拡縮可能な複数の作動室を形
成するブレードとを備えていることを特徴とする流体機
械。2. A rotatable cylinder which is given rotational power by a driving means and has a suction port and a discharge port on its side,
A shaft that penetrates through the cylinder and is supported at both ends in a sealed case; a cylindrical piston that is eccentrically mounted on the shaft and that has both side surfaces in contact with both side walls of the cylinder and is constrained from axial movement; A fluid machine comprising: a plurality of blades extending along the cylinder to form a plurality of expandable and contractable working chambers between a cylinder and a piston.
JP25768992A 1992-09-28 1992-09-28 Fluid machine Pending JPH06108979A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP25768992A JPH06108979A (en) 1992-09-28 1992-09-28 Fluid machine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP25768992A JPH06108979A (en) 1992-09-28 1992-09-28 Fluid machine

Publications (1)

Publication Number Publication Date
JPH06108979A true JPH06108979A (en) 1994-04-19

Family

ID=17309746

Family Applications (1)

Application Number Title Priority Date Filing Date
JP25768992A Pending JPH06108979A (en) 1992-09-28 1992-09-28 Fluid machine

Country Status (1)

Country Link
JP (1) JPH06108979A (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013146177A1 (en) * 2012-03-29 2013-10-03 ジヤトコ株式会社 Vane pump

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013146177A1 (en) * 2012-03-29 2013-10-03 ジヤトコ株式会社 Vane pump

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