JPH0718381B2 - Multi-cylinder Stirling engine - Google Patents
Multi-cylinder Stirling engineInfo
- Publication number
- JPH0718381B2 JPH0718381B2 JP3829486A JP3829486A JPH0718381B2 JP H0718381 B2 JPH0718381 B2 JP H0718381B2 JP 3829486 A JP3829486 A JP 3829486A JP 3829486 A JP3829486 A JP 3829486A JP H0718381 B2 JPH0718381 B2 JP H0718381B2
- Authority
- JP
- Japan
- Prior art keywords
- pressure
- gas pipe
- pressure gas
- valve
- 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.)
- Expired - Fee Related
Links
- 238000001816 cooling Methods 0.000 claims description 3
- 238000010438 heat treatment Methods 0.000 claims description 3
- 230000008929 regeneration Effects 0.000 claims description 3
- 238000011069 regeneration method Methods 0.000 claims description 3
- 238000000034 method Methods 0.000 description 4
- 230000007423 decrease Effects 0.000 description 3
- 230000001105 regulatory effect Effects 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 238000002474 experimental method Methods 0.000 description 2
- 230000001276 controlling effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
- 230000037431 insertion Effects 0.000 description 1
- 239000011800 void material Substances 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
- F02G1/00—Hot gas positive-displacement engine plants
- F02G1/04—Hot gas positive-displacement engine plants of closed-cycle type
- F02G1/043—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Description
【発明の詳細な説明】 （イ）産業上の利用分野 本発明は多気筒スターリングエンジン、詳しくは各気筒
間の圧力のアンバランスを効果的に解消しそれによって
生ずるマイナスの現象を最低限に押さえるようにした多
気筒スターリングエンジンの改良に関する。The present invention relates to a multi-cylinder Stirling engine, and more specifically, it effectively eliminates the pressure imbalance between the cylinders and minimizes the negative phenomenon caused thereby. The improvement of the multi-cylinder Stirling engine.
（ロ）従来の技術及び問題点 スターリングエンジンを実用化するに当たり、多気筒直
列型スターリングエンジンの場合は各気筒間の圧力バラ
ンスが重要であるが、一般にその圧力バランスはくずれ
易い出力、効率の低下、騒音、振動の増大を引き起こ
す。従来は圧力アンバランスを解消する方法として主に
ピストン内の空所を利用したもの（参考；特公昭55−86
62号公報）が多く、その他としては高圧ガス配管と低圧
ガス配管との間（第１図に示す弁Ｘの所）にキャピラリ
ーチューブを置く方法、あるいは同箇所に電磁弁を設置
しタイマーでオン−オフさせる方法等があったが、いず
れも確実性に欠けるか逆にアンバランスは解消するもの
の出力も大幅に低下するものが殆どであった。(B) Conventional technology and problems When a Stirling engine is put into practical use, in the case of a multi-cylinder in-line Stirling engine, the pressure balance between the cylinders is important. Generally, the pressure balance is easily broken and the output and efficiency decrease. , Increase noise and vibration. Conventionally, a method that mainly uses a void in the piston as a method for eliminating the pressure imbalance (reference; Japanese Patent Publication No. 55-86).
62), and the other method is to put a capillary tube between the high-pressure gas pipe and the low-pressure gas pipe (at the valve X shown in FIG. 1), or install a solenoid valve at the same place and turn it on with a timer. -There were methods such as turning off, but in most cases there was lack of certainty, or conversely, the imbalance was resolved, but the output was largely reduced in most cases.
（ハ）問題点を解決するための手段 本発明は前述の問題点を解決するためになされたもので
あり、高圧ガス配管と低圧ガス配管との間に微量流量弁
を介装しておき、予め実験で求めておいたエンジン回転
数及び平均封入圧（高圧ガス配管及び低圧ガス配管のガ
ス圧力の平均値）と微量流量弁の弁開度との最良の関係
を例えば数式化しデータとして制御回路のメモリに入力
しておくことにより、実際の利用システムで運転する場
合、あらゆる回転数及び平均封入圧の下で確実に最適弁
開度を得ることができるようにしたものである。(C) Means for Solving the Problems The present invention has been made to solve the above problems, and a minute flow valve is provided between the high-pressure gas pipe and the low-pressure gas pipe, The best relationship between the engine speed and the average charging pressure (the average value of the gas pressures of the high-pressure gas pipe and the low-pressure gas pipe) and the valve opening of the minute flow valve, which has been obtained in advance by experiments, is for example expressed as a formula and data is used as a control circuit. By inputting the data into the memory, it is possible to surely obtain the optimum valve opening degree under all rotational speeds and average enclosed pressures when operating in an actual utilization system.
（ニ）実施例 以下本発明による多気筒スターリングエンジンの実施例
について図面を参照して説明する。(D) Embodiments Embodiments of a multi-cylinder Stirling engine according to the present invention will be described below with reference to the drawings.
第１図には多気筒スターリングエンジンのガス回路が示
されており、加熱室（Ｈ）１、再生室（Ｒ）２および冷
却室（Ｃ）３よりなる熱交換室４とピストン（Ｐ）５を
有するシリンダ６とが交互に複数個（本実施例において
は４個）環状に継続接続されている。一方コンプレッサ
７の吐出側に付設されたタンク８に作動ガス供給用の低
圧ガス配管９が接続されるとともにコンプレッサ７の吸
入側に作動ガス回収用の高圧ガス配管10が接続され、熱
交換室４とシリンダ６との各中間接続点がそれぞれ図示
のように逆止弁9a,10aを介して低圧ガス配管９と高圧ガ
ス配管10とに接続されている。また低圧ガス配管９及び
高圧ガス配管10の図示位置に電磁弁（Ｓ）11a,11b,11c
が配設されるとともに、スターリングエンジンのロッド
挿通部にロッドシール12が配設されている。FIG. 1 shows a gas circuit of a multi-cylinder Stirling engine, which includes a heat exchange chamber 4 including a heating chamber (H) 1, a regeneration chamber (R) 2 and a cooling chamber (C) 3 and a piston (P) 5. And a plurality of cylinders 6 (in this embodiment, four cylinders) are continuously connected in an annular shape. On the other hand, a low-pressure gas pipe 9 for supplying a working gas is connected to a tank 8 attached to the discharge side of the compressor 7, and a high-pressure gas pipe 10 for collecting a working gas is connected to the suction side of the compressor 7, and the heat exchange chamber 4 Each intermediate connection point between the cylinder 6 and the cylinder 6 is connected to the low-pressure gas pipe 9 and the high-pressure gas pipe 10 via check valves 9a and 10a as shown in the drawing. In addition, solenoid valves (S) 11a, 11b, 11c are installed at the positions shown in the low pressure gas pipe 9 and the high pressure gas pipe 10.
And a rod seal 12 is provided in the rod insertion portion of the Stirling engine.
電磁弁の動作については、電磁弁11a〜11cは常時は閉で
あり、エンジン出力を増大させるときは電磁弁11bを開
としてタンク８内の高圧作動ガスをエンジンに補給し、
エンジン出力を減少させるときは電磁弁11aを開として
エンジンの作動ガスをコンプレッサ７で加圧してタンク
８に回収する。またロッドシール12を介して漏れたガス
を回収するときは11cを開としコンプレッサ７を運転し
て漏れた作動ガスを加圧してタンク８に回収する。Regarding the operation of the solenoid valve, the solenoid valves 11a to 11c are normally closed, and when increasing the engine output, the solenoid valve 11b is opened to replenish the engine with the high-pressure working gas in the tank 8,
When reducing the engine output, the solenoid valve 11a is opened and the working gas of the engine is pressurized by the compressor 7 and collected in the tank 8. When the leaked gas is collected through the rod seal 12, 11c is opened and the compressor 7 is operated to pressurize the leaked working gas and collect it in the tank 8.
一方低圧ガス配管９と高圧ガス配管10との間にはバイパ
ス弁として微量流量弁（Ｘ）13が介装されており、微量
流量弁13は本実施例においては第２図に示される精密流
量調整弁が使用され、その流量調整弁13は例えばギア14
を介してアクチュエータ15（この場合はステッピングモ
ータ）と結合されており、その開度は正確にステッピン
グモータの回転によって制御することができるようにな
っている。ステッピングモータ15によりギヤ14が矢印イ
方向へ移動すると弁開度が小さくなり、ギヤ14が矢印ロ
方向へ移動すると弁開度が大きくなる。On the other hand, a minute flow rate valve (X) 13 is provided as a bypass valve between the low pressure gas pipe 9 and the high pressure gas pipe 10. The minute flow rate valve 13 in this embodiment is a precise flow rate shown in FIG. A regulating valve is used, and its flow regulating valve 13 is, for example, a gear 14
Is connected to the actuator 15 (in this case, a stepping motor) via the, and its opening can be accurately controlled by the rotation of the stepping motor. When the gear 14 moves in the arrow A direction by the stepping motor 15, the valve opening decreases, and when the gear 14 moves in the arrow B direction, the valve opening increases.
第３図はアクチュエータ制御回路ブロック図であり、第
４図は実験で求められたエンジン回転数及び平均封入圧
（高圧ガス配管９及び低圧ガス配管10のガス圧力の平均
値）と精密流量調整弁13の弁開度との最良の関係を示し
ており、第４図の最良の関係を例えば数式化しデータと
して第３図の制御回路のメモリに入力しておく。第３図
の圧力センサが低圧ガス配管９及び高圧ガス配管10のガ
ス圧力を検出するとともに、回転数センサがエンジン回
転数を検出し、マイコンの中央処理装置（CPU）が両圧
力の平均値及び回転数とメモリ内のデータとを比較して
最適弁開度を求め、モータへの最適出力を決定すること
ができるようになっている。FIG. 3 is a block diagram of an actuator control circuit, and FIG. 4 is an engine speed and average filling pressure (average value of gas pressure of the high-pressure gas pipe 9 and the low-pressure gas pipe 10) and a precise flow rate control valve, which are experimentally obtained. 13 shows the best relationship with the valve opening degree, and the best relationship shown in FIG. 4 is converted into, for example, a mathematical formula and input as data into the memory of the control circuit shown in FIG. The pressure sensor in FIG. 3 detects the gas pressure in the low-pressure gas pipe 9 and the high-pressure gas pipe 10, the rotation speed sensor detects the engine rotation speed, and the central processing unit (CPU) of the microcomputer measures the average value of both pressures. The optimum valve opening can be determined by comparing the number of revolutions and the data in the memory to determine the optimum output to the motor.
手動による精密流量調整弁を使用した実験によれば、弁
を開くことによりごく僅か（約１％）の出力低下はみら
れるものの気筒間の圧力バラツキはほぼ解消、またエン
ジンの運転効率の上昇は２〜３％あり、当初のねらいは
概ね実現できた。According to an experiment using a manual precision flow control valve, opening the valve causes a slight decrease in output (about 1%), but almost eliminates pressure variations between cylinders and increases engine operating efficiency. It was 2 to 3%, and the initial aim was almost achieved.
（ホ）発明の効果 本発明による多気筒スターリングエンジンは、上述のよ
うに構成されているので、出力低下を最小限に押えなが
ら効率の向上、振動、騒音の低減をすることができる。(E) Effect of the Invention Since the multi-cylinder Stirling engine according to the present invention is configured as described above, it is possible to improve efficiency, reduce vibration, and reduce noise while suppressing output reduction to a minimum.
第１図は本発明による多気筒スターリングエンジンのガ
ス回路の線図的説明図、 第２図は第１図に含まれる精密流量調整弁の概念を示す
断面正面図、 第３図は第２図に含まれるステッピングモータを制御す
るための制御回路のブロック図、 第４図は第２図に示される調整弁の実験データを示すグ
ラフである。 １……加熱室 ２……再生室 ３……冷却室 ４……熱交換室 ５……ピストン ６……シリンダ ７……コンプレッサ ８……タンク ９……低圧ガス配管 9a……逆止弁 10……高圧ガス配管 10a……逆止弁 11a〜11c……電磁弁 12……ロッドシール 13……精密流量調整弁 14……ギヤ 15……ステッピングモータFIG. 1 is a diagrammatic explanatory view of a gas circuit of a multi-cylinder Stirling engine according to the present invention, FIG. 2 is a sectional front view showing the concept of a precise flow rate control valve included in FIG. 1, and FIG. 3 is FIG. FIG. 4 is a block diagram of a control circuit for controlling the stepping motor included in FIG. 4, and FIG. 4 is a graph showing experimental data of the regulating valve shown in FIG. 1 ... Heating chamber 2 ... Regeneration chamber 3 ... Cooling chamber 4 ... Heat exchange chamber 5 ... Piston 6 ... Cylinder 7 ... Compressor 8 ... Tank 9 ... Low-pressure gas piping 9a ... Check valve 10 ...... High-pressure gas piping 10a ...... Check valve 11a to 11c ...... Solenoid valve 12 ...... Rod seal 13 ...... Precision flow control valve 14 ...... Gear 15 ...... Stepping motor
───────────────────────────────────────────────────── フロントページの続き (56)参考文献 特開 昭58−210345（ＪＰ，Ａ) 特開 昭58−77146（ＪＰ，Ａ) 実開 昭56−167760（ＪＰ，Ｕ) ─────────────────────────────────────────────────── ─── Continuation of the front page (56) References JP-A-58-210345 (JP, A) JP-A-58-77146 (JP, A) Actually developed JP-A-56-167760 (JP, U)
Claims (1)
室とピストンを有するシリンダとを交互に複数個環状に
継続接続し、前記熱交換室と前記シリンダとの各中間接
続点をそれぞれ逆止弁を介して作動ガス供給用の低圧ガ
ス配管と作動ガス回収用の高圧ガス配管とに接続してな
る多気筒スターリングエンジンにおいて、 前記高圧ガス配管と前記低圧ガス配管との間に介装され
た微量流量弁と、 前記微量流量弁の弁開度を調整するアクチュエータと、 前記アクチュエータに弁開度信号を与える制御装置とを
備え、 前記制御装置は前記高圧ガス配管及び前記低圧ガス配管
のガス圧力をそれぞれ検出する圧力センサとエンジン回
転数を検出する回転数センサとを有し、前記両圧力セン
サにて検出されたガス圧力の平均値及び前記回転数セン
サにて検出された回転数と予め記憶されたデータとを比
較して弁開度信号を発するものとしたことを特徴とする
多気筒スターリングエンジン。1. A plurality of heat exchange chambers comprising a heating chamber, a regeneration chamber and a cooling chamber and a cylinder having a piston are continuously connected alternately in a ring shape, and each intermediate connection point between the heat exchange chamber and the cylinder is connected. In a multi-cylinder Stirling engine connected to a low-pressure gas pipe for supplying a working gas and a high-pressure gas pipe for collecting a working gas via a check valve, an interposition between the high-pressure gas pipe and the low-pressure gas pipe. A minute flow rate valve, an actuator for adjusting the valve opening degree of the minute flow rate valve, and a control device for giving a valve opening signal to the actuator, the control device of the high pressure gas pipe and the low pressure gas pipe It has a pressure sensor for detecting the gas pressure and a rotation speed sensor for detecting the engine rotation speed, and the average value of the gas pressure detected by the pressure sensors and the rotation speed sensor. A multi-cylinder Stirling engine characterized in that a valve opening signal is generated by comparing the rotational speed detected by the engine with data stored in advance.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3829486A JPH0718381B2 (en) | 1986-02-25 | 1986-02-25 | Multi-cylinder Stirling engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3829486A JPH0718381B2 (en) | 1986-02-25 | 1986-02-25 | Multi-cylinder Stirling engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS62197662A JPS62197662A (en) | 1987-09-01 |
| JPH0718381B2 true JPH0718381B2 (en) | 1995-03-06 |
Family
ID=12521289
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP3829486A Expired - Fee Related JPH0718381B2 (en) | 1986-02-25 | 1986-02-25 | Multi-cylinder Stirling engine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0718381B2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009504980A (en) * | 2005-08-16 | 2009-02-05 | アンドレアス ギムザ | 4-cycle Stirling engine with two double piston units |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2513649Y2 (en) * | 1991-07-01 | 1996-10-09 | 船井電機株式会社 | Tape deck |
| JP2513648Y2 (en) * | 1991-07-01 | 1996-10-09 | 船井電機株式会社 | Tape deck |
| JP2008510933A (en) * | 2004-08-24 | 2008-04-10 | インフィニア コーポレイション | Double-acting thermodynamic resonance-free piston multi-cylinder Stirling system and method |
-
1986
- 1986-02-25 JP JP3829486A patent/JPH0718381B2/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009504980A (en) * | 2005-08-16 | 2009-02-05 | アンドレアス ギムザ | 4-cycle Stirling engine with two double piston units |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS62197662A (en) | 1987-09-01 |
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