JPS5862302A - Rotary blade type expander - Google Patents
Rotary blade type expanderInfo
- Publication number
- JPS5862302A JPS5862302A JP16164681A JP16164681A JPS5862302A JP S5862302 A JPS5862302 A JP S5862302A JP 16164681 A JP16164681 A JP 16164681A JP 16164681 A JP16164681 A JP 16164681A JP S5862302 A JPS5862302 A JP S5862302A
- Authority
- JP
- Japan
- Prior art keywords
- blade
- holes
- hole
- pressure
- cylinder
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- 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
- F01C21/0809—Construction of vanes or vane holders
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Turbine Rotor Nozzle Sealing (AREA)
Abstract
Description
【発明の詳細な説明】
本発明はロータに複数枚の羽根を有する回転羽根式(容
積型)膨張機に関し、その目的とするところは製作が容
易で性能の優れ゛た前記膨張機の羽根構造を提供するも
のであるg
回転羽根式膨張機は回転中に羽根先端を常にシリンダ内
周部に押しつけておく必要性があり、排気行程ではその
ための背圧力を羽根底部から逃が4す目的で、従来は第
1図の様な羽根1の片側に溝2を形成していたが、精密
加工」〕に難があったり運動時の気体の漏洩が大きいな
どの問題があったそこで本発明はそれらの欠点を全て解
消するもので、以下図面に従って本発萌の一実施例を説
明する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a rotary vane type (positive displacement type) expander having a plurality of blades on a rotor, and an object thereof is to provide a blade structure of the expander that is easy to manufacture and has excellent performance. In a rotary vane type expander, it is necessary to keep the blade tip pressed against the inner circumference of the cylinder at all times during rotation, and during the exhaust stroke, the purpose is to release the back pressure from the bottom of the blade. Conventionally, a groove 2 was formed on one side of the blade 1 as shown in Fig. 1, but there were problems such as difficulty in precision machining and large gas leakage during movement, so the present invention was developed. An embodiment of the present invention which eliminates all of these drawbacks will be described below with reference to the drawings.
第2図は本5咽の一実施例を利用した膨張機の全体図で
ある。流入路3からの高圧気体がシリンダ4の流入ポー
ト6を通過して作動空間6に流通し、膨張することによ
ってロータ了を矢印の方向へ回転させる。複数の羽根8
A〜8Dのうち、羽根8ムは回転角」二羽根の先端がシ
リンダ4の内周面から離れる遊蜂現象を生じやすい。そ
こでンリ/タ°4.ロータ了の後3側に構成する後側板
(図示せず)に高圧気体導入孔9を設け、ロータ7の羽
根溝底部10を通して羽498Aの底部へ高圧気体を付
勢し前記羽根8人を押し出し、先端シリンダ4の内周面
に密接してシリンダ4の内周面と羽根8ムの先端との間
に反力を生じさせて遊離現象を防ぐ。羽根8Dはもう少
し回転角が進むとその羽根溝底部が高圧気体導入孔9と
連通し羽根8Dはシリンダ4の内周面に沿って押し出さ
れる。FIG. 2 is an overall view of an expander using one embodiment of the present five-way valve. High-pressure gas from the inlet passage 3 passes through the inlet port 6 of the cylinder 4 and flows into the working space 6, and expands to rotate the rotor in the direction of the arrow. multiple feathers 8
Among the blades A to 8D, the blade 8 is likely to cause a floating phenomenon in which the tip of the two blades separates from the inner peripheral surface of the cylinder 4. So, I/T°4. A high-pressure gas introduction hole 9 is provided in the rear plate (not shown) on the third side behind the rotor, and high-pressure gas is forced through the blade groove bottom 10 of the rotor 7 to the bottom of the blade 498A to push out the eight blades. The distal end cylinder 4 is brought into close contact with the inner circumferential surface of the cylinder 4 to generate a reaction force between the inner circumferential surface of the cylinder 4 and the tip of the blade 8 to prevent the detachment phenomenon. When the rotation angle of the blade 8D advances a little further, the bottom of the blade groove communicates with the high pressure gas introduction hole 9, and the blade 8D is pushed out along the inner peripheral surface of the cylinder 4.
。 羽根8ムは回転角が進んで羽根8Bの位置゛に
壕力が不要となり、高圧導入孔9との連係をはずれコす
るように前記高圧導入孔9が構成される。Wi根8Bは
前述の如く高圧導入孔9を通過しているが、その羽根溝
底部1dKは依然として高圧気体が滞留していて、この
圧力で羽根8Bを必要以上に強く押し出すことになる。. The high pressure introduction hole 9 is configured so that the rotation angle of the blade 8M advances and no trenching force is required at the position of the blade 8B, and the connection with the high pressure introduction hole 9 is removed. Although the Wi root 8B has passed through the high pressure introduction hole 9 as described above, high pressure gas still remains at the bottom 1dK of the blade groove, and this pressure pushes out the blade 8B more forcefully than necessary.
そこでもはや不要となった羽根溝底部1σの高圧気体を
羽根8Bの先端の摩耗防止と膨張機の機械効率を増加さ
せるために、羽根8Bの内部に形成した圧力均衡穴11
を通して作動空間へ逃がす。また羽根8Bは少し回転角
が進めば作動空間dは排気行程となり、すでに排気行程
中にある羽根8Cとともに膨張を終了した低圧気体を排
出部12から流出゛させる。Therefore, a pressure balancing hole 11 is formed inside the blade 8B to prevent wear of the tip of the blade 8B and increase the mechanical efficiency of the expander by discharging the high-pressure gas in the bottom 1σ of the blade groove that is no longer needed.
through to the working space. Further, when the rotation angle of the blade 8B advances a little, the working space d enters the exhaust stroke, and the low-pressure gas that has completed expansion flows out from the exhaust portion 12 together with the blade 8C, which is already in the exhaust stroke.
排出行程にある羽根aB(若干回転角が進んで)と羽根
8Gは力学的に羽根の底部と先端との圧力を均衡させた
方が遊離現象が生じにくくなり、羽根8Bに形成した圧
力均衡穴11を通して圧力を平衡させ良好なる作動を得
る。The release phenomenon is less likely to occur when the pressure between the bottom and the tip of the blade aB (with a slightly advanced rotation angle) and the blade 8G are dynamically balanced during the discharge stroke, and the pressure balancing hole formed in the blade 8B is 11 to balance the pressure and obtain good operation.
第3図、第4図は本実施例による膨張機の羽根(第2図
の8ム〜8D)の゛部品図とその横断面を示す。羽根構
造体12の底部13から先端14にい。また羽根構造体
12の高圧気体面16(第2図の羽根8Bの高圧気体面
17には常に高圧側の気体が作用する)から短穴18を
形成して長穴16と連通し、長穴16と短穴18とで圧
力均衡穴(第2図の11)を構成する。短大18はロー
タ7の羽根溝内面としカラ動接゛触するので、ドリル等
であけられた後に加工によるパリを更に大きなドリルで
除きそのエツジ部19に面取り加工を圧力均衡穴を機械
工作が穴易なドリル工作で簡単にあけることが出来て、
全体的に精密機械加工が必要な従来方式より極めて製造
原価が下がる。FIGS. 3 and 4 show a component diagram and a cross section of the expander blade (8m to 8D in FIG. 2) according to this embodiment. From the bottom 13 of the vane structure 12 to the tip 14. In addition, a short hole 18 is formed from the high-pressure gas surface 16 of the blade structure 12 (high-pressure gas always acts on the high-pressure gas surface 17 of the blade 8B in FIG. 2) and communicates with the long hole 16. 16 and the short hole 18 constitute a pressure balancing hole (11 in FIG. 2). The short diameter 18 is in contact with the inner surface of the blade groove of the rotor 7, so after it is drilled with a drill, the machining holes are removed using a larger drill, and the edge 19 is chamfered and a pressure balancing hole is machined. It can be easily opened with a simple drill,
Manufacturing costs are significantly lower than conventional methods that require precision machining throughout.
羽根8ム〜8Dの高圧気体面には短穴18だけしか露出
せず、高気体面に溝加工を施した従来方式に比べて羽根
高圧気体面にエツジ部が無ぐ滑らかとなり、羽根8ム〜
8Dがロータ7の羽根溝を滑りやすくなり機械効率が高
まる。Only the short hole 18 is exposed on the high-pressure gas surface of the blades 8mm to 8D, and compared to the conventional method in which the high-pressure gas surface is grooved, the high-pressure gas surface of the blade has no edges and is smoother. ~
8D easily slides in the blade groove of the rotor 7, increasing mechanical efficiency.
長穴16を羽根構造体の内部に構成したことで、短穴1
8の開口部に至るまで他に気体が漏洩することが無く、
圧力逃しと羽根先端、底部の圧力平行が効果的に行われ
総合的に膨張機の効率が高まる0
以上のように本発明によれば製造原価が下がるとともに
、効率も高まる。By configuring the long hole 16 inside the blade structure, the short hole 1
No other gas leaks until reaching the opening of 8.
Pressure relief and pressure parallelization at the tips and bottoms of the blades are effectively performed, and the efficiency of the expander is increased overall.As described above, according to the present invention, manufacturing costs are reduced and efficiency is also increased.
第1図は従来例を示す斜視図、第2図は本発明の一実施
例を示す断面図、第3図、第4図は羽根の斜視図と拡大
断面図である。
4・・・・・・シリンダ、7・・・・・・ロニタ、8ム
〜8D・・パ。
・・・羽根、11・・・・・・圧力均衡穴、16・・・
・・・長穴、18・・・・・・短穴。FIG. 1 is a perspective view showing a conventional example, FIG. 2 is a sectional view showing an embodiment of the present invention, and FIGS. 3 and 4 are a perspective view and an enlarged sectional view of a blade. 4...Cylinder, 7...Ronita, 8m~8D...Pa. ...Blade, 11...Pressure balance hole, 16...
...Long hole, 18...Short hole.
Claims (1)
はシリンダ内面に当接する羽根を設け、この羽根は底部
から先端に長穴を形成し、前記長穴へ羽根の高圧気体面
から短穴を連通して圧力均衡穴を構成した回転羽根式膨
張機。Cylinder 1) A rotor is rotatably provided in the cylinder, and this rotor is provided with blades that come into contact with the inner surface of the cylinder.This blade has an elongated hole from the bottom to the tip, and a short hole is connected to the elongated hole from the high-pressure gas surface of the blade. A rotary vane expander with communicating holes to form a pressure balancing hole.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP16164681A JPS5862302A (en) | 1981-10-09 | 1981-10-09 | Rotary blade type expander |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP16164681A JPS5862302A (en) | 1981-10-09 | 1981-10-09 | Rotary blade type expander |
Publications (1)
Publication Number | Publication Date |
---|---|
JPS5862302A true JPS5862302A (en) | 1983-04-13 |
Family
ID=15739135
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP16164681A Pending JPS5862302A (en) | 1981-10-09 | 1981-10-09 | Rotary blade type expander |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS5862302A (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO1999002862A2 (en) * | 1997-07-11 | 1999-01-21 | Thermo King Corporation | High efficiency rotary vane motor |
-
1981
- 1981-10-09 JP JP16164681A patent/JPS5862302A/en active Pending
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO1999002862A2 (en) * | 1997-07-11 | 1999-01-21 | Thermo King Corporation | High efficiency rotary vane motor |
WO1999002862A3 (en) * | 1997-07-11 | 1999-04-01 | Thermo King Corp | High efficiency rotary vane motor |
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