JP5525371B2 - External combustion type closed cycle heat engine - Google Patents

External combustion type closed cycle heat engine Download PDF

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JP5525371B2
JP5525371B2 JP2010173278A JP2010173278A JP5525371B2 JP 5525371 B2 JP5525371 B2 JP 5525371B2 JP 2010173278 A JP2010173278 A JP 2010173278A JP 2010173278 A JP2010173278 A JP 2010173278A JP 5525371 B2 JP5525371 B2 JP 5525371B2
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heater
cooler
air chamber
flow path
external combustion
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JP2012031804A (en
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俊光 海法
省三 鶴野
幾夫 小井田
宗平 関根
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Yokohama Seiki Co Ltd
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Yokohama Seiki Co Ltd
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    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K27/00—Plants for converting heat or fluid energy into mechanical energy, not otherwise provided for

Description

本発明は、簡易構造にして操作、維持容易な外燃式クローズドサイクル熱機関に関するものである。   The present invention relates to an external combustion type closed cycle heat engine that has a simple structure and is easy to operate and maintain.

スターリングエンジンは、熱源の種類を問わず、現在、無駄となっているエネルギーの有効利用が可能であり、静粛で低公害であるので、各種のタイプが研究開発され、重要な将来熱機関の一つと目されている外燃式熱機関である。   Stirling engines, regardless of the type of heat source, can effectively use energy that is currently wasted, and are quiet and low-pollution, so various types have been researched and developed, and are one of the important future heat engines. It is an external combustion type heat engine that is regarded as one of the most important.

スターリングエンジンは、気室内に封入した作動ガスを加熱及び冷却して該作動ガスを膨張及び収縮させ、動力を得る外燃式熱機関である。
従来のディスプレーサ型スターリングエンジンは、ディスプレーサの往復動により、該作動ガスを加熱部と冷却部との間で往復させて該作動ガスを加熱及び冷却、即ち膨張及び収縮させて、パワーピストンを作用させることにより動力を得るものである。ディスプレーサは、パワーピストンと位相をもって連動するように構成されている（特許文献１）。 A Stirling engine is an external combustion heat engine that obtains power by heating and cooling a working gas sealed in an air chamber to expand and contract the working gas.
In a conventional displacer type Stirling engine, the working gas is reciprocated between a heating part and a cooling part by reciprocating the displacer to heat and cool the working gas, that is, expand and contract, thereby operating a power piston. To gain power. The displacer is configured to interlock with the power piston in phase (Patent Document 1).

しかしながら、従来のスターリングエンジンでは、気室、加熱器及び冷却器内の作動ガスが同時に加圧、減圧され、このため加熱時において、気室を加圧するために冷却器内の作動ガスも加圧しなければならず、また冷却時において、気室を減圧するために加熱器内の作動ガスも減圧しなければならない。このため、気室容積に比して加熱器又は冷却器の容積が大きくなるとエンジン効率が低下する。従って、エンジン効率を上げるために加熱器及び冷却器を小型化する必要がある。   However, in the conventional Stirling engine, the working gas in the air chamber, the heater and the cooler is pressurized and depressurized at the same time. Therefore, during heating, the working gas in the cooler is also pressurized to pressurize the air chamber. Also, during cooling, the working gas in the heater must be depressurized in order to depressurize the air chamber. For this reason, when the volume of the heater or the cooler is larger than the air chamber volume, the engine efficiency is lowered. Therefore, it is necessary to reduce the size of the heater and the cooler in order to increase the engine efficiency.

しかし、エンジンを作動させるには必要な熱量を取り込み、また排出する必要があり、加熱器及び冷却器は十分な能力を持たなければならない。加熱器を小型かつ充分な能力を持たせるには、伝熱面の肉厚を薄くし、また加熱温度を上げて面積当りの伝熱量を増やす手段があるが、精密な工作を要し、高価な耐熱金属を使用する必要があり、また高温により加熱器の腐蝕が促進されるといった弊害がある。
また、冷却期間中、加熱器は利用されず、全期間を通じた加熱器の効率は低下し、加熱器に加えられる外部熱量は無駄に消費され利用効率が低下している。加熱期間の冷却器も同様である。 However, to operate the engine, it is necessary to take in and discharge the necessary amount of heat, and the heater and cooler must have sufficient capacity. In order to make the heater small and have sufficient capacity, there are means to reduce the thickness of the heat transfer surface and increase the heat transfer amount per area by raising the heating temperature, but it requires precise work and is expensive. It is necessary to use a new refractory metal, and the high temperature promotes corrosion of the heater.
In addition, the heater is not used during the cooling period, and the efficiency of the heater throughout the entire period is reduced, and the amount of external heat applied to the heater is wasted and the utilization efficiency is reduced. The same applies to the cooler during the heating period.

上述するような従来技術に鑑み、加熱器又は冷却器の容積がエンジンの効率に関係せず、多気筒化、大型化、高出力化が可能で、低温熱源を有効に利用することができ、種々の条件下で設計、製作できる外燃式クローズドサイクル熱機関を、本発明の発明者らは開発し、先に出願した（特許文献２）（特許文献３）（特許文献４）（以下、「本発明者の先願発明」という）。   In view of the prior art as described above, the volume of the heater or cooler is not related to the efficiency of the engine, can be multi-cylinder, large, and high output, and can effectively use a low-temperature heat source, The inventors of the present invention have developed an external combustion type closed cycle heat engine that can be designed and manufactured under various conditions, and have previously filed an application (Patent Document 2) (Patent Document 3) (Patent Document 4) "Inventor's prior invention").

即ち、密閉された気室と加熱器及び冷却器を設け、該気室と該加熱器の入り口側及び出口側と導通する流路を設け、該気室と冷却器の入り口側及び出口側と導通する流路を設け、それぞれ入り口側及び出口側の流路に開閉弁を設け、作動ガスの移動手段を設け、冷却器入り口側及び出口側の開閉弁を閉として冷却器を密閉し、加熱器入り口側及び出口側の開閉弁は開として気室内の作動ガスを加熱器を通じて循環させ、気室内の作動ガスを加熱し、また加熱器入り口側及び出口側の開閉弁を閉として加熱器を密閉し、一方、冷却器入り口側及び出口側の開閉弁は開として気室内の作動ガスを冷却器を通じて循環させて気室内の作動ガスを冷却し、気室内の作動ガスを膨張、収縮させて気室下部に連接した作用体を駆動する外燃式クローズドサイクル熱機関で、加熱器又は冷却器の容積がエンジンの効率に関係せず、種々の条件下で設計、製作でき、また加熱器、冷却器各１台に複数の気室、作用体を設けることができる外燃式クローズドサイクル熱機関を提案した（特許文献２）。   That is, a sealed air chamber, a heater and a cooler are provided, and a flow path is provided to communicate with the air chamber and the inlet side and the outlet side of the heater, and the air chamber and the inlet side and the outlet side of the cooler are provided. Provide a flow path that conducts, provide an open / close valve in the flow path on the inlet side and the outlet side, provide a means for moving the working gas, close the open / close valve on the cooler inlet side and the outlet side, seal the cooler, and heat Open / close valves on the inlet side and outlet side are opened and the working gas in the air chamber is circulated through the heater to heat the working gas in the air chamber, and the on / off valves on the inlet and outlet sides of the heater are closed. On the other hand, the opening and closing valves on the inlet side and outlet side of the cooler are opened and the working gas in the air chamber is circulated through the cooler to cool the working gas in the air chamber, and the working gas in the air chamber is expanded and contracted. An external combustion closed sensor that drives an action body connected to the lower part of the air chamber In the Kul heat engine, the volume of the heater or cooler is not related to the efficiency of the engine, and can be designed and manufactured under various conditions, and a plurality of air chambers and working bodies are provided in each heater and cooler. An external combustion type closed cycle heat engine that can be used has been proposed (Patent Document 2).

さらに特許文献２の外燃式クローズドサイクル熱機関に対し、作用体から冷却器に向かう流路、および気室から冷却器に向かう流路を高温部とし、気室から加熱器に向かう流路を低温部として、高温部と低温部の間に熱交換器を設けて加熱器に流入する作動ガスを加熱することにより冷却器から本来外部に流出する熱量の一部を効率よく回収し、再利用できるために、熱効率を向上することができる熱回収装置付多気筒外燃式クローズドサイクル熱機関を提案した（特許文献３）。   Furthermore, with respect to the external combustion closed cycle heat engine of Patent Document 2, the flow path from the operating body to the cooler and the flow path from the air chamber to the cooler are set as high-temperature portions, and the flow path from the air chamber to the heater is As a low-temperature part, a heat exchanger is installed between the high-temperature part and the low-temperature part to heat the working gas that flows into the heater, thereby efficiently recovering and reusing part of the heat that originally flows out of the cooler Therefore, a multi-cylinder external combustion type closed cycle heat engine with a heat recovery device capable of improving thermal efficiency has been proposed (Patent Document 3).

また気室と作用体を分離することによりの複数の作用体が一つの気室を共有できるため構造を簡易にすることができ、また作用体に対する作動ガスの流れは一方向であるため各作用体に対する開閉弁は２個、または三方弁１個ですみ、作用体周りの構造を簡易にすることができ、特に多気筒の場合は弁の総数を少なくでき、また作用体の温度は一定となるため作用体の熱設計が容易になる外燃式クローズドサイクル熱機関を提案した（特許文献４）。   In addition, by separating the air chamber and the working body, a plurality of working bodies can share one air chamber, so that the structure can be simplified, and the flow of the working gas to the working body is unidirectional, so that each action Only two or three on-off valves for the body are required, and the structure around the working body can be simplified. Especially in the case of multiple cylinders, the total number of valves can be reduced, and the temperature of the working body is constant. Therefore, an external combustion type closed cycle heat engine that facilitates the thermal design of the working body has been proposed (Patent Document 4).

しかしながら、上記従来の気室内から加熱器、または冷却器を通じて循環する作動ガス移動手段は、原理的には等圧下で行われるためファンや送風機等としていたが、大容量の作動ガス移動流量を回転数に対し一定にすることが困難で、熱効率低下の一因となっていた。作動ガス移動流量が回転数に対し一定の大容量の作動ガスを移動する手段として、ルーツブロア等容積形の送風機を使用することができるが、高温、高圧環境下で使用するため容積形送風機側面の機密性や潤滑油による熱交換器に与える伝熱効率低下等の技術的課題を解決しなければならない問題があった。   However, since the working gas moving means circulating from the conventional air chamber through a heater or a cooler is theoretically performed under equal pressure, it has been used as a fan or a blower. However, the working gas moving means rotates a large capacity working gas moving flow rate. It was difficult to keep constant with respect to the number, which was a cause of a decrease in thermal efficiency. As a means of moving a large volume of working gas whose working gas transfer flow rate is constant with respect to the rotation speed, a volumetric blower such as a Roots blower can be used. There were problems that had to be solved for technical issues such as confidentiality and lowering of heat transfer efficiency given to heat exchangers due to lubricating oil.

特開２００６−２７５０１８号公報JP 2006-275018 A 特願２００９−００８５７０号Japanese Patent Application No. 2009-008570 特願２００９−２１５１１５号Japanese Patent Application No. 2009-215115 特願２００９−２７７３２９号Japanese Patent Application No. 2009-277329

上述するような本発明者の先願発明に鑑み、本発明では、作動ガス移動手段を改良し、加熱器又は冷却器の容積がエンジンの効率に関係せず、種々の条件下で設計、製作でき、簡易構造にして、より効率が高く、操作、維持容易な外燃式クローズドサイクル熱機関を提供することを課題とする。   In view of the inventor's prior application as described above, the present invention improves the working gas moving means, and the volume of the heater or cooler is not related to the efficiency of the engine, and is designed and manufactured under various conditions. It is an object of the present invention to provide an external combustion type closed-cycle heat engine that can be made simple and has a higher efficiency and is easier to operate and maintain.

本発明の発明者らは、上記課題を解決すべく鋭意検討を重ねた結果、以下の構成を有する発明を完成するに至った。
請求項１の発明は、密閉された気室と加熱器及び冷却器を設け、該気室と該加熱器の入り口部及び出口部と導通する流路を設け、該気室と冷却器の入り口部及び出口部と導通する流路を設け、それぞれ入り口部側及び出口部側の流路に開閉弁を設け、更に、加熱器と導通する流路と該流路に開閉弁を設け、冷却器と導通する流路と該流路に開閉弁を設けて、加熱器と冷却器それぞれと導通する作用体を設けた外燃式クローズドサイクル熱機関であって、気室と冷却器間及び気室と加熱器間の開閉弁と連動するディスプレーサを少なくとも１個気室内に設けたことを特徴とするものである。ディスプレーサとは、前記気室内の作動ガスを移動させるピストンと定義する。 The inventors of the present invention have intensively studied to solve the above problems, and as a result, have completed the invention having the following configuration.
The invention of claim 1 is provided with a sealed air chamber, a heater, and a cooler, and provided with a flow path that communicates with the air chamber and an inlet portion and an outlet portion of the heater, and the air chamber and the inlet of the cooler. A flow path that communicates with the outlet portion and the outlet portion, an open / close valve is provided for the flow channel on the inlet portion side and the outlet portion side, respectively, a flow passage that communicates with the heater, and an open / close valve is provided on the flow passage, An external combustion type closed cycle heat engine provided with an opening and closing valve in the flow path, and an operating body connected to the heater and the cooler, respectively, between the air chamber and the cooler, and the air chamber And at least one displacer that interlocks with an on-off valve between the heater and the heater. The displacer is defined as a piston that moves the working gas in the air chamber.

請求項２の発明は、請求項１記載の外燃式クローズドサイクル熱機関であって、開閉弁の流路が３分岐あり、１分岐から入り込む流体を、他の２分岐流路のいずれかを選択的に流路とする、又は２分岐流路のいずれかを選択し、他の１分岐を流路とする三方弁としたことを特徴とするものである。三方弁は全閉とする機能を含むものとする。   The invention according to claim 2 is the external combustion type closed cycle heat engine according to claim 1, wherein the flow path of the on-off valve has three branches, and the fluid entering from one branch is changed to one of the other two branch paths. A three-way valve having a selective flow path or a two-branch flow path and another one branch as a flow path is provided. The three-way valve shall include a fully closed function.

請求項３の発明は、請求項１又は２に記載の外燃式クローズドサイクル熱機関であって、作用体が、ピストンであることを特徴とするものである。   The invention of claim 3 is the external combustion type closed cycle heat engine according to claim 1 or 2, wherein the operating body is a piston.

請求項４の発明は、請求項１又は２に記載の外燃式クローズドサイクル熱機関であって、作用体がタービン等であることを特徴とするものである。   A fourth aspect of the invention is the external combustion type closed cycle heat engine according to the first or second aspect, wherein the operating body is a turbine or the like.

請求項５の発明は、請求項１〜４のいずれかに記載の外燃式クローズドサイクル熱機関であって、作用体を複数設け、加熱器および冷却器を共有することを特徴とするものである。   The invention of claim 5 is the external combustion type closed cycle heat engine according to any one of claims 1 to 4, wherein a plurality of operating bodies are provided, and a heater and a cooler are shared. is there.

請求項６の発明は、請求項１〜５のいずれかに記載の外燃式クローズドサイクル熱機関であって、複数設けた作用体の駆動軸を共有することを特徴とするものである。   A sixth aspect of the present invention is the external combustion type closed cycle heat engine according to any one of the first to fifth aspects of the present invention, and is characterized by sharing a plurality of actuating drive shafts.

請求項７の発明は、請求項１〜３、５、又は６のいずれかに記載の外燃式クローズドサイクル熱機関であって、複数設けたピストンのクランク室を共有したことを特徴とするものである。   The invention according to claim 7 is the external combustion type closed cycle heat engine according to any one of claims 1 to 3, 5, or 6, wherein a plurality of piston crank chambers are shared. It is.

請求項８の発明は、請求項１〜３、又は５〜７のいずれかに記載の外燃式クローズドサイクル熱機関であって、複数設けたピストンが、クランクシャフトを介して総和が３６０°、またはその倍数となる位相差をもって共有する駆動軸に連接することを特徴とするものである。   Invention of Claim 8 is the external combustion type closed cycle heat engine in any one of Claims 1-3, or 5-7, Comprising: The piston provided in multiple is 360 degrees through a crankshaft, Alternatively, the drive shafts are connected to a common drive shaft with a phase difference that is a multiple thereof.

請求項９の発明は、請求項１〜８のいずれかに記載の外燃式クローズドサイクル熱機関であって、加熱器入り口部側及び冷却器入り口部側の流路間、又は開閉弁を設けた流路に熱交換器を設けたことを特徴とするものである。   Invention of Claim 9 is an external combustion type closed cycle heat engine in any one of Claims 1-8, Comprising: Between the flow paths of a heater inlet part side and a cooler inlet part side, or an on-off valve is provided. A heat exchanger is provided in the flow path.

請求項１０の発明は、請求項１〜９のいずれかに記載の外燃式クローズドサイクル熱機関であって、気室を加熱器と冷却器に並列して２個を１組として、１組または複数組設けたことを特徴とするものである。   The invention of claim 10 is the external combustion type closed cycle heat engine according to any one of claims 1 to 9, wherein the air chamber is parallel to the heater and the cooler, and two of them are set as one set. Alternatively, a plurality of sets are provided.

請求項１１の発明は、請求項１〜１０のいずれかに記載の外燃式クローズドサイクル熱機関であって、内部にディスプレーサを設けた気室に替えて内部にピストンを設けた気筒（シリンダー）の２個を一組として、１組または複数組設け、該１組のピストンが１８０°の位相差とするクランク機構を設け、それぞれのシリンダーヘッドと加熱器及び冷却器と導通する流路を設け、該流路に開閉弁を設けたことを特徴とするものである。   The invention of claim 11 is the external combustion type closed cycle heat engine according to any one of claims 1 to 10, wherein the cylinder is provided with a piston inside instead of an air chamber provided with a displacer inside. 1 set or two or more sets are provided as a set, a crank mechanism in which the one set of pistons has a phase difference of 180 ° is provided, and a flow path is provided to connect each cylinder head, heater and cooler. The on-off valve is provided in the flow path.

本発明の外燃式クローズドサイクル熱機関は、本発明者の先願発明が流路に作動ガスの移動手段を設けたのに対し、気室と作動ガス移動手段を一体化させたので構造をさらに簡易化でき、該作動ガス移動手段をディスプレーサ（ピストン）としたため気室内の作動ガスを確実に循環させ、さらに過循環等を生じないために、安定的に熱量を回収し、再利用して熱効率を向上させ、高温、高圧環境下で潤滑に問題も無く運転することができる。 ディスプレーサを用いて作動ガスの移動を行うことは従来のスターリングエンジンと同様であるが、従来のスターリングエンジンは、気室と加熱器及び冷却器は連結されているため、気室、加熱器及び冷却器内の作動ガスが同時に加圧、減圧されてエネルギーの損失が生じるのに対し、本発明の外燃式クローズドサイクル熱機関は、気室と加熱器及び冷却器は開閉弁により遮断されており、気室と冷却器、及び気室と加熱器間の開閉弁と連動させてディスプレーサが移動することにより、加熱器及び冷却器内の圧力は大きく変化することなく、下記する本発明者の先願発明の利点を保っている。
即ち、気室加熱時、冷却器は開閉弁により加熱器から密閉分離されているので冷却器内の作動ガスは加圧されず、低温・低圧のままで、気室冷却時、加熱器は開閉弁により冷却器から密閉分離されているので加熱器内の作動ガスは減圧されず、高温・高圧のままで、温度・圧力の変化は気室内の作動ガスにのみ生じ、スターリングエンジンが従来生じさせていた加熱器、冷却器内の作動ガスを加圧、減圧するための無駄なエネルギー消費は加熱器、冷却器の大きさにかかわりなく生じない。 The external combustion type closed cycle heat engine of the present invention has a structure that is integrated with the air chamber and the working gas moving means, whereas the prior invention of the present inventor provided the working gas moving means in the flow path. Furthermore, since the working gas moving means is a displacer (piston), the working gas in the air chamber can be circulated reliably, and in order not to cause over-circulation, the amount of heat can be stably recovered and reused. It improves thermal efficiency and can operate without problems in lubrication under high temperature and high pressure environment. The movement of the working gas using the displacer is the same as that of the conventional Stirling engine. However, the conventional Stirling engine is connected to the air chamber, the heater, and the cooler. While the working gas in the chamber is pressurized and depressurized at the same time, energy loss occurs, whereas in the external combustion closed cycle heat engine of the present invention, the air chamber, the heater and the cooler are shut off by an on-off valve The displacer moves in conjunction with the air chamber and the cooler and the on-off valve between the air chamber and the heater, so that the pressure in the heater and the cooler does not change greatly, and The advantages of the claimed invention are maintained.
That is, when the air chamber is heated, the cooler is hermetically separated from the heater by an on-off valve, so the working gas in the cooler is not pressurized, and the heater opens and closes when the air chamber is cooled at low temperature and low pressure. Since the valve is hermetically separated from the cooler by the valve, the working gas in the heater is not depressurized and remains at high temperature and pressure, and the change in temperature and pressure occurs only in the working gas in the air chamber. The wasteful energy consumption for pressurizing and depressurizing the working gas in the heater and cooler that has been used does not occur regardless of the size of the heater or cooler.

従って、加熱器、冷却器を大きくすることが可能である。加熱器、冷却器を大きくできるため伝熱面積を大きくでき、温度差が小さくても十分な伝熱量が得られ、廃熱等の低温熱源も有効に利用できるとともに、加熱器の設計条件が緩やかになり、加熱器の材料、構造、工作等に関し、目的に合う最適なものを選択できる。作動ガスとして稀少なヘリウムを使う必要がなく、作動ガスは窒素、空気等でよい。
また、気室加熱時、冷却器は開閉弁により加熱器から密閉分離されているので、冷却器内の作動ガスを有効に冷却し続けることができ、気室冷却時、加熱器は開閉弁により冷却器から密閉分離されているので加熱器内の作動ガスを有効に加熱し続けることができ、加熱器・冷却器内を全期間有効に作用させることができるとともに、熱源、冷熱源の利用効率を高めることができる。このため加熱、冷却の効率が向上し、従来のスターリングエンジンに比し高いエンジン効率を得ることができる。 Therefore, it is possible to enlarge the heater and the cooler. The heater and cooler can be enlarged, so the heat transfer area can be increased, a sufficient amount of heat transfer can be obtained even if the temperature difference is small, low-temperature heat sources such as waste heat can be used effectively, and the design conditions of the heater are gradual Therefore, it is possible to select the most suitable material for the purpose regarding the material, structure, work, etc. of the heater. There is no need to use rare helium as the working gas, and the working gas may be nitrogen, air or the like.
In addition, since the cooler is hermetically separated from the heater by an on-off valve when the air chamber is heated, the working gas in the cooler can continue to be effectively cooled. Since it is hermetically separated from the cooler, the working gas in the heater can continue to be heated effectively, the heater / cooler can be effectively operated for the entire period, and the utilization efficiency of the heat source and cold source Can be increased. For this reason, the efficiency of heating and cooling is improved, and higher engine efficiency can be obtained as compared with the conventional Stirling engine.

また、作用体に対する作動ガスの流れは一方向であるため各作用体に対する開閉弁は２個、または三方弁１個ですみ、作用体周りの構造を簡易にすることができ、特に、多気筒の場合は弁の総数を少なくできる。   In addition, since the working gas flow with respect to the working body is unidirectional, only two on-off valves or one three-way valve is required for each working body, and the structure around the working body can be simplified. In this case, the total number of valves can be reduced.

また、作用体を通過する作動ガスの流れが一方向（従来のスターリングエンジンの作動ガスの流れは、往復方向）であるので、ピストンの他、タービン、ローター（回転子）を使用できる。タービン形式に対しては、二酸化炭素、キセノン等の重比重のガスを使用することが可能で、発生圧力差を仕事量に効率よく変換することができると同時にタービンを小型化できる。   Further, since the flow of the working gas passing through the working body is one direction (the working gas flow of the conventional Stirling engine is the reciprocating direction), a turbine and a rotor (rotor) can be used in addition to the piston. For the turbine type, a gas having a heavy specific gravity such as carbon dioxide or xenon can be used, and the generated pressure difference can be efficiently converted into a work amount, and at the same time, the turbine can be downsized.

また、流路を含めた加熱器、及び冷却器の容積が効率に影響しなくなるために、加熱器、冷却器及び気室と作用体間の流路を長くでき、加熱器、冷却器及び気室を作用体本体と離れて設置することができるため機器配置にも自由度が生じ、作用体本体の設置しにくい場所の既存廃熱源なども有効に利用でき、ひとつの加熱器と冷却器及び気室を複数の作用体が共有することができ、構造を簡易にすることができ、作用体の多用途化が図れる。   Further, since the volume of the heater and the cooler including the flow path does not affect the efficiency, the flow path between the heater, the cooler and the air chamber and the working body can be lengthened, and the heater, the cooler and the air Since the chamber can be set apart from the main body of the operation body, the arrangement of the equipment is also free, and the existing waste heat source in the place where it is difficult to install the main body of the operation body can be used effectively. A plurality of operating bodies can share the air chamber, the structure can be simplified, and the operating bodies can be used in many ways.

また、複数の作用体を同一場所に設け、該作用体の駆動軸を共有することによって、装置のコンパクト化が図れると同時に大きな動力（出力）を得ることができ、複数設けたピストン（作用体）のクランク室を共有し、複数設けたピストンの位相差総和を３６０度、又は３６０度の倍数とすることにより、クランク室及びピストン裏側の体積を一定として背圧の変化を無くし、ピストン動作を円滑に行わせることができる。   In addition, by providing a plurality of operating bodies in the same place and sharing the drive shaft of the operating bodies, the apparatus can be made compact and at the same time a large power (output) can be obtained. ), And the phase difference sum of the plurality of pistons is set to 360 degrees or multiples of 360 degrees, so that the volume of the crank chamber and the back side of the piston is kept constant, the back pressure is not changed, and the piston operation is performed. It can be performed smoothly.

また、加熱器入り口側及び冷却器入り口部側の流路間、又は開閉弁を設けた流路に熱交換器を設けたので、冷却器に供給される加熱終了後の高温作動ガスにより、加熱器に供給される冷却終了後の低温作動ガスへ熱を移動するので、冷却器から本来外部に流出する熱量の一部を効率よく回収し、再利用できるために熱効率を高めることができる。   In addition, since a heat exchanger is provided between the flow paths on the heater inlet side and the cooler inlet side, or on the flow path provided with the open / close valve, heating is performed by the high-temperature working gas after heating is supplied to the cooler. Since heat is transferred to the low-temperature working gas after completion of the cooling supplied to the cooler, a part of the heat amount originally flowing out from the cooler can be efficiently recovered and reused, so that the heat efficiency can be improved.

また、気室を加熱器と冷却器に並列して２個を１組として、１組または複数組設けたので、気室と加熱器間の循環、気室と冷却器間の循環が並行して行われ、加熱器及び冷却器は全サイクルを通じて作動しているため作動効率、及び熱効率を向上できるとともに、設置場所等の設計条件に応じ装置のコンパクト化が図れると同時に、大容量の作動ガスを移動することができる。   In addition, the air chamber is arranged in parallel with the heater and the cooler, and one set or two or more sets are provided, so that the circulation between the air chamber and the heater and the circulation between the air chamber and the cooler are performed in parallel. Since the heater and cooler are operated throughout the entire cycle, the operating efficiency and thermal efficiency can be improved, and the equipment can be made compact in accordance with the design conditions such as the installation location. Can be moved.

また、内部にディスプレーサを設けた気室に替えて内部にピストンを設けた気筒（シリンダー）２個を設け、該ピストンを１８０°の位相差とするクランク機構を設け、それぞれのシリンダーヘッドと加熱器及び冷却器と導通する流路を設け、該流路に開閉弁を設けたので、気室即ち気筒高さを低くコンパクト化することができ、開閉弁をシリンダーヘッド同一端へ設置することができるため、構造を簡略化することができメンテナンスを容易にすることができる。   Also, in place of the air chamber provided with a displacer inside, two cylinders (cylinders) provided with pistons inside are provided, and a crank mechanism is provided with a phase difference of 180 ° for each piston, and each cylinder head and heater In addition, since a flow path that communicates with the cooler is provided, and an open / close valve is provided in the flow path, the air chamber, that is, the cylinder height can be reduced and the open / close valve can be installed at the same end of the cylinder head. Therefore, the structure can be simplified and maintenance can be facilitated.

上記するように、本発明の外燃式クローズドサイクル熱機関は、多くの効果を有するものである。   As described above, the external combustion type closed cycle heat engine of the present invention has many effects.

本発明の外燃式クローズドサイクル熱機関の実施例を示す概念図The conceptual diagram which shows the Example of the external combustion type closed cycle heat engine of this invention 本発明の外燃式クローズドサイクル熱機関の実施例を示す概念図The conceptual diagram which shows the Example of the external combustion type closed cycle heat engine of this invention 本発明の異なる種類の作用体を用いた要部断面図Cross-sectional view of main parts using different types of working bodies of the present invention 本発明の外燃式クローズドサイクル熱機関の実施例を示す概念図The conceptual diagram which shows the Example of the external combustion type closed cycle heat engine of this invention 本発明の外燃式クローズドサイクル熱機関の実施例を示す概念図The conceptual diagram which shows the Example of the external combustion type closed cycle heat engine of this invention 本発明の外燃式クローズドサイクル熱機関の実施例を示す概念図The conceptual diagram which shows the Example of the external combustion type closed cycle heat engine of this invention 本発明の外燃式クローズドサイクル熱機関の実施例を示す概念図The conceptual diagram which shows the Example of the external combustion type closed cycle heat engine of this invention 本発明の外燃式クローズドサイクル熱機関の実施例を示す概念図The conceptual diagram which shows the Example of the external combustion type closed cycle heat engine of this invention

以下、本発明を実施するための具体的な形態について、図１〜７を参照しながら詳細に説明する。図１以降と共通する構成部品に同一符号を付与し、詳述を省略する。   Hereinafter, specific modes for carrying out the present invention will be described in detail with reference to FIGS. The same reference numerals are given to components common to those in FIG.

図１は、本発明の外燃式クローズドサイクル熱機関の実施例を示す概念図である。
同図において、加熱器１０、冷却器２０、密閉された気室３０、作用体４０を設け、該気室３０の上部に設けた出入り口部３１及び下部に設けた出入り口部３２と該加熱器１０の出口部１１及び入り口部１２と導通する流路１３、１４をそれぞれ設け、該気室３０の出入り口部３１及び出入り口部３２と冷却器２０の入り口部２１及び出口部２２と導通する流路２３、２４をそれぞれ設け、それぞれの流路１３、１４、２３、２４に開閉弁１５、１６、２５、２６を設け、気室３０の内部へ作動ガスの移動手段であるディスプレーサ（ピストン）３３を設けている。 FIG. 1 is a conceptual diagram showing an embodiment of an external combustion type closed cycle heat engine of the present invention.
In the figure, a heater 10, a cooler 20, a sealed air chamber 30, and an action body 40 are provided, and an entrance / exit portion 31 provided at the upper portion of the air chamber 30, an entrance / exit portion 32 provided at the lower portion, and the heater 10. The flow passages 13 and 14 are respectively provided to communicate with the outlet portion 11 and the inlet portion 12 of the gas chamber 30, and the flow passages 23 are electrically connected to the inlet / outlet portion 31 and the inlet / outlet portion 32 of the air chamber 30 and the inlet portion 21 and the outlet portion 22 of the cooler 20. , 24 are provided, on-off valves 15, 16, 25, 26 are provided in the respective flow paths 13, 14, 23, 24, and a displacer (piston) 33 that is a means for moving the working gas is provided inside the air chamber 30. ing.

該ディスプレーサ３３は、気室３０の上部又は下部に軸封装置を設けた貫通部３４が設けられ、ディスプレーサ３３と連接するディスプレーサロッド３５が貫通して気室３０の外部へ位置する。外部へ位置したディスプレーサロッド３５は、ディスプレーサ３３が気室３０内部で上下方向に前記開閉弁１５、１６、２５、２６と連動して駆動する駆動装置（図示せず）が設けられている。   The displacer 33 is provided with a penetrating portion 34 provided with a shaft seal device at the upper or lower portion of the air chamber 30, and a displacer rod 35 connected to the displacer 33 passes through and is positioned outside the air chamber 30. The displacer rod 35 located outside is provided with a driving device (not shown) that is driven by the displacer 33 in the vertical direction inside the air chamber 30 in conjunction with the on-off valves 15, 16, 25, 26.

作用体４０は、公知のピストンシリンダー４１、該ピストンシリンダー４１内を上下に摺動するピストン４２、駆動軸４４に固設されたフライホイール４３、ピストン４２とフライホイール４３を連接するクランク４５、クランク室４６で構成されている。駆動軸４４は、クランク室４６外へ軸封装置（図示せず）を介して外部へ出力する。ピストンシリンダー４１トップへ作動ガスの出入り口部４７を設け、加熱器１０の出口部１７及び冷却器２０入り口部２７と導通する流路１８、２８をそれぞれ設け、該流路１８、２８にそれぞれ開閉弁１９、２９が設けられている。作動ガスは、窒素ガス等が封入されている。   The working body 40 includes a known piston cylinder 41, a piston 42 that slides up and down in the piston cylinder 41, a flywheel 43 fixed to the drive shaft 44, a crank 45 that connects the piston 42 and the flywheel 43, The chamber 46 is configured. The drive shaft 44 outputs outside the crank chamber 46 via a shaft seal device (not shown). A working gas inlet / outlet portion 47 is provided at the top of the piston cylinder 41, and flow paths 18 and 28 are provided to communicate with the outlet portion 17 of the heater 10 and the inlet portion 27 of the cooler 20, respectively. 19 and 29 are provided. The working gas is sealed with nitrogen gas or the like.

上記作用について詳述する。
図１で示す気室３０内の実線で示すディスプレーサ３３の位置は下死点にあり、開閉弁１５、１６、２５、２６は破線の位置で、加熱過程が終了した状態である。
即ち、冷却器２０入り口部２１側及び出口部２２側の開閉弁２５、２６を破線で示すように閉として冷却器２０を気室３０及び加熱器１０から密閉分離し、加熱器１０入り口部１２側及び出口部１１側の開閉弁１６、１５を破線で示すように開とし、ディスプレーサ３３は下死点の位置で加熱過程が終了した状態において、加熱器１０入り口部１２側及び出口部１１側の開閉弁１６、１５を実線で示すように閉とし、加熱器１０を冷却器２０及び気室３０から密閉分離し、冷却器２０入り口部２１側及び出口部２２側の開閉弁２５、２６を実線で示すように開とすればディスプレーサ３３上下の圧力は等しくなり、該ディスプレーサ３３を上方に移動すれば、ディスプレーサ３３上方空間３６（図１の気室３０中央部に位置する破線ディスプレーサ３３上部側）の作動ガスは、実線矢印で示すように開閉弁２５→流路２３→冷却器２０の経路により冷却器２０内に移動し冷却され、冷却器２０内の作動ガスは、流路２４→開閉弁２６の経路によりディスプレーサ３３下方空間３７（図１の気室３０中央部に位置する破線ディスプレーサ３３下部側）に移動し、冷却過程を行い、気室３０最上部の破線で示すディスプレーサ３３は上死点に至り冷却過程を終了する。 The above operation will be described in detail.
The position of the displacer 33 indicated by the solid line in the air chamber 30 shown in FIG. 1 is at the bottom dead center, and the on-off valves 15, 16, 25, and 26 are in the positions indicated by the broken lines, and the heating process has been completed.
That is, the open / close valves 25 and 26 on the cooler 20 inlet portion 21 side and the outlet portion 22 side are closed as indicated by broken lines, and the cooler 20 is hermetically separated from the air chamber 30 and the heater 10, and the heater 10 inlet portion 12 is closed. In the state where the opening and closing valves 16 and 15 on the side and the outlet portion 11 side are opened as indicated by broken lines and the heating process is completed at the position of the bottom dead center, the displacer 33 is on the inlet portion 12 side and the outlet portion 11 side. The on-off valves 16 and 15 are closed as indicated by solid lines, the heater 10 is hermetically separated from the cooler 20 and the air chamber 30, and the on-off valves 25 and 26 on the inlet side 21 and outlet side 22 side of the cooler 20 are connected. When the displacer 33 is opened as shown by the solid line, the pressure above and below the displacer 33 becomes equal. When the displacer 33 is moved upward, the displacer 33 upper space 36 (a broken line displacer located at the center of the air chamber 30 in FIG. 1). The working gas on the upper side of the sensor 33 is moved into the cooler 20 through the path of the on-off valve 25 → the flow path 23 → the cooler 20 as indicated by the solid line arrow, and is cooled, and the working gas in the cooler 20 is It moves to the space 37 below the displacer 33 (the lower side of the broken line displacer 33 located at the center of the air chamber 30 in FIG. 1) by the path of the flow path 24 → the on-off valve 26, and performs the cooling process. The displacer 33 shown reaches top dead center and finishes the cooling process.

ディスプレーサ３３は、図１の気室３０最上部の破線で示す上死点の位置に至るまで移動した後、冷却過程を終了する。
次に開閉弁２５、２６を破線で示す閉とし、開閉弁１５，１６を破線で示す開とすれば、ディスプレーサ上下の圧力は等しくなり、該ディスプレーサを下方に移動すれば、ディスプレーサ３３下方空間３７（図１の気室３０中央部に位置する破線ディスプレーサ３３下部側）の作動ガスは、破線矢印で示すように開閉弁１６→流路１４→加熱器１０の経路により加熱器１０内に移動し加熱され、加熱器１０内の作動ガスは、流路１３→開閉弁１５の経路によりディスプレーサ３３上方空間３６に移動し、加熱過程を行い、ディスプレーサ３３は下死点に至り加熱過程を終了する。 The displacer 33 moves to the position of the top dead center indicated by the broken line at the top of the air chamber 30 in FIG. 1, and then ends the cooling process.
Next, when the open / close valves 25 and 26 are closed as indicated by broken lines and the open / close valves 15 and 16 are opened as indicated by broken lines, the pressure above and below the displacer becomes equal, and when the displacer is moved downward, the space 37 below the displacer 33. The working gas in the lower part of the broken line displacer 33 located at the center of the air chamber 30 in FIG. 1 moves into the heater 10 through the path of the on-off valve 16 → the flow path 14 → the heater 10 as indicated by the broken line arrow. When heated, the working gas in the heater 10 moves to the upper space 36 of the displacer 33 through the path 13 → the on-off valve 15 and performs a heating process. The displacer 33 reaches the bottom dead center and ends the heating process.

上記過程において、冷却器２０はｍHのガス量を取り込みｍLのガス量を放出する。従ってｍL＞ｍHであれば冷却器２０内のガス量は減少し圧力は低下する。一方、加熱器１０はｍHのガス量を放出し、ｍLのガス量を取り込む。従って加熱器１０内のガス量は増加し圧力は上昇する。この過程において、サイクルあたり「ｍL−ｍH」のガス量が冷却器２０から加熱器１０に移動する。この過程はｍL＝ｍHとなった時点で平衡に達するが、ボイル・シャルルの法則によれば平衡条件は「加熱器１０内圧力／冷却器２０内圧力＝加熱内温度／冷却内温度」である。即ち「加熱内温度／冷却内温度」で規定される、平衡条件以下の「加熱器１０内圧力／冷却器２０内圧力」の比以下であれば上記サイクルにより冷却器２０内のガスは加熱器１０に移動し続ける。   In the above process, the cooler 20 takes in the mH gas amount and releases the mL gas amount. Therefore, if mL> mH, the amount of gas in the cooler 20 decreases and the pressure decreases. On the other hand, the heater 10 releases the mH gas amount and takes in the mL gas amount. Accordingly, the amount of gas in the heater 10 increases and the pressure rises. In this process, a gas amount of “mL−mH” per cycle moves from the cooler 20 to the heater 10. This process reaches equilibrium when ml = mH, but according to Boyle-Charle's law, the equilibrium condition is “pressure in heater 10 / pressure in cooler 20 = temperature in heating / temperature in cooling”. . That is, the gas in the cooler 20 is heated by the above cycle if the ratio is equal to or less than the ratio of “pressure in the heater 10 / pressure in the cooler 20”, which is defined by “temperature in heating / temperature in cooling”, which is equal to or less than the equilibrium condition. Continue to move to 10.

一方、加熱器１０の出口部１７と作用体４０の出入り口部４７と導通する流路１８に設けた開閉弁１９を実線で示すように閉とし、冷却器２０の入り口部２７と作用体４０の出入り口部４７と導通する流路２８に設けた開閉弁２９を実線で示すように開とすれば、シリンダー４１は冷却器２０と導通されて低温・低圧になりピストン４２は上昇する。尚、図中ピストン４２は、上死点に位置している。   On the other hand, the on-off valve 19 provided in the flow path 18 connected to the outlet portion 17 of the heater 10 and the inlet / outlet portion 47 of the operating body 40 is closed as shown by a solid line, and the inlet portion 27 of the cooler 20 and the operating body 40 are connected. If the opening / closing valve 29 provided in the flow path 28 connected to the inlet / outlet portion 47 is opened as shown by a solid line, the cylinder 41 is connected to the cooler 20 to become low temperature / low pressure, and the piston 42 rises. In the figure, the piston 42 is located at the top dead center.

また、冷却器２０の入り口部２７と作用体４０の出入り口部４７と導通する流路２８に設けた開閉弁２９を破線で示すように閉とし、加熱器１０の出口部１７と作用体４０の出入り口部４７と導通する流路１８に設けた開閉弁１９を破線で示すように開とすれば、シリンダー４１は、加熱器１０と導通されて高温・高圧になりピストン４２は下降する。
この過程において、ピストン４２を介し、「ｍP」のガス量が加熱器１０から冷却器２０に移動する。従って、「ｍP＝ｍL−ｍH」、即ち気室３０を介した冷却器２０から加熱器１０への作動ガス量が、ピストンシリンダー４１を介した加熱器１０から冷却器２０への移動に等しい圧力差で、本発明の外燃式クローズドサイクル熱機関は作動する。 Moreover, the on-off valve 29 provided in the flow path 28 connected to the inlet portion 27 of the cooler 20 and the inlet / outlet portion 47 of the operating body 40 is closed as indicated by a broken line, and the outlet portion 17 of the heater 10 and the operating body 40 are closed. If the opening / closing valve 19 provided in the flow path 18 connected to the inlet / outlet portion 47 is opened as indicated by a broken line, the cylinder 41 is connected to the heater 10 to become high temperature / high pressure, and the piston 42 is lowered.
In this process, the amount of “mP” gas moves from the heater 10 to the cooler 20 via the piston 42. Therefore, “mP = mL−mH”, that is, the amount of working gas from the cooler 20 to the heater 10 via the air chamber 30 is equal to the movement from the heater 10 to the cooler 20 via the piston cylinder 41. With the difference, the external combustion closed cycle heat engine of the present invention operates.

上記加熱過程において開閉弁２５、２６を破線で示す閉とし、開閉弁１５，１６を破線で示す開とすれば、ディスプレーサ３３上下の圧力は等しくなり、ディスプレーサ３３を下方に移動すれば、ディスプレーサ３３下方空間３７（図１の気室３０中央部に位置する破線ディスプレーサ３３下部側）の作動ガスは、破線矢印で示すように開閉弁１６→流路１４→加熱器１０の経路により加熱器１０内に移動し加熱され、加熱器１０内の作動ガスは、流路１３→開閉弁１５の経路によりディスプレーサ３３上方空間３６に移動し、加熱過程を行い、ディスプレーサ３３は下死点に至り加熱過程を終了するが、ディスプレーサ３３が下死点に至る以前に開閉弁１５を実線で示す閉とすれば、ディスプレーサ３３上方空間３６の作動ガスは加熱過程を終了まで断熱過程となる。
また、冷却器２０の入り口部２７と作用体４０の出入り口部４７と導通する流路２８に設けた開閉弁２９を破線で示すように閉とし、加熱器１０の出口部１７と作用体４０の出入り口部４７と導通する流路１８に設けた開閉弁１９を破線で示すように開とすれば、シリンダー４１は、加熱器１０と導通されて高温・高圧になりピストン４２は下降するが、ピストン４２が下死点に至る以前に開閉弁１９を実線で示す閉とすれば、シリンダー４１内の作動ガスはピストン４２が下死点に至るまで断熱過程となる。この結果、出力は低下するが、加熱器１０から冷却器２０に移動する高温作動ガス量、即ち消費熱量も減少し、開閉弁２９及び開閉弁１９を閉とするタイミング時期を選ぶことにより熱効率を向上することができる。 If the on-off valves 25 and 26 are closed as indicated by broken lines in the heating process, and the on-off valves 15 and 16 are opened as indicated by broken lines, the pressure above and below the displacer 33 becomes equal, and if the displacer 33 is moved downward, the displacer 33 The working gas in the lower space 37 (on the lower side of the broken line displacer 33 located in the central portion of the air chamber 30 in FIG. 1) passes through the path of the on-off valve 16 → the flow path 14 → the heater 10 as indicated by the broken line arrow. The working gas in the heater 10 moves to the upper space 36 of the displacer 33 through the flow path 13 → the on-off valve 15 and performs a heating process. The displacer 33 reaches the bottom dead center and performs the heating process. If the on-off valve 15 is closed as indicated by a solid line before the displacer 33 reaches bottom dead center, the working gas in the upper space 36 of the displacer 33 is heated. An adiabatic process until the end.
Moreover, the on-off valve 29 provided in the flow path 28 connected to the inlet portion 27 of the cooler 20 and the inlet / outlet portion 47 of the operating body 40 is closed as indicated by a broken line, and the outlet portion 17 of the heater 10 and the operating body 40 are closed. If the opening / closing valve 19 provided in the flow path 18 connected to the inlet / outlet portion 47 is opened as shown by a broken line, the cylinder 41 is connected to the heater 10 to become high temperature / high pressure and the piston 42 is lowered. If the on-off valve 19 is closed as indicated by a solid line before 42 reaches the bottom dead center, the working gas in the cylinder 41 becomes an adiabatic process until the piston 42 reaches the bottom dead center. As a result, although the output is reduced, the amount of high-temperature working gas that moves from the heater 10 to the cooler 20, that is, the amount of heat consumed is also reduced, and the thermal efficiency is improved by selecting the timing when the on-off valve 29 and the on-off valve 19 are closed. Can be improved.

周知の如く内燃式エンジン（内燃式熱機関）は、シリンダー内で霧化したガソリン等に点火爆発させて高圧を発生し、ピストンの上下駆動をさせて動力を発生させているが、本発明の外燃式クローズドサイクル熱機関は、気室３０を介しての熱力学サイクル過程において、加熱器１０は自動的に高圧になり、冷却器２０は自動的に低圧になることを特徴とするものである。   As is well known, an internal combustion engine (internal combustion heat engine) generates high pressure by igniting and exploding gasoline or the like atomized in a cylinder, and generating power by driving the piston up and down. The external combustion type closed cycle heat engine is characterized in that the heater 10 automatically becomes a high pressure and the cooler 20 automatically becomes a low pressure in a thermodynamic cycle process through the air chamber 30. is there.

図２は、本発明の外燃式クローズドサイクル熱機関の実施例を示す概念図である。
同図において、５０、５１、５２は、流路が３分岐あり、１分岐から入り込む流体を、他の２分岐流路のいずれかを選択的に流路とする（２分岐流路のいずれも選択しないことも含む（後述））、又は２分岐流路のいずれかを選択し（２分岐流路のいずれも選択しないことも含む（後述））、他の１分岐を流路とする三方弁である。即ち、図１における開閉弁１５と２５を三方弁５０に置き換え、開閉弁１６と２６を三方弁５１に置き換え、開閉弁１９と２９を三方弁５２に置き換え、これに従って配管を変更したものである。
なお、上記括弧内意味は、図１の開閉弁１５と２５、開閉弁１６と２６、開閉弁１９と２９が、それぞれ同時に開又は閉となる状態に作用させることができることに呼応するものである。例えば、作用体４０への作動ガス導通を、加熱器１０と冷却器２０から一時的に遮断する場合や、加熱器１０と冷却器２０から気室３０への作動ガス導通を一時的に遮断する場合等である。即ち、上記三方弁５０、５１、５２は、図１の開閉弁１５と２５、１６と２６、１９と２９と等機能を有するものである。 FIG. 2 is a conceptual diagram showing an embodiment of the external combustion type closed cycle heat engine of the present invention.
In the figure, reference numerals 50, 51, and 52 indicate that the flow path is divided into three branches, and the fluid entering from one branch is selectively set to one of the other two branch paths (both of the two branch paths). A three-way valve that includes a non-selection (described later)) or a two-branch channel (including the selection of none of the two-branch channels (described later)) and uses the other one branch as a channel. It is. That is, the on-off valves 15 and 25 in FIG. 1 are replaced with the three-way valve 50, the on-off valves 16 and 26 are replaced with the three-way valve 51, the on-off valves 19 and 29 are replaced with the three-way valve 52, and the piping is changed accordingly. .
The meaning in the parenthesis corresponds to the fact that the on-off valves 15 and 25, the on-off valves 16 and 26, and the on-off valves 19 and 29 in FIG. . For example, the working gas conduction to the working body 40 is temporarily interrupted from the heater 10 and the cooler 20, or the working gas conduction from the heater 10 and the cooler 20 to the air chamber 30 is temporarily interrupted. This is the case. That is, the three-way valves 50, 51 and 52 have the same functions as the on-off valves 15 and 25, 16 and 26, 19 and 29 in FIG.

上記図２の作用について詳述する。
図２で示す気室３０内の実線で示すディスプレーサ３３の位置は下死点にあり、三方弁５０、５１は破線の位置で、加熱過程が終了した状態である。
即ち、三方弁５０、５１を破線で示す位置として、冷却器２０を気室３０及び加熱器１０から密閉分離し、ディスプレーサ３３は下死点の位置で加熱過程が終了した状態において、三方弁５０、５１を実線で示す位置とし、加熱器１０を冷却器２０及び気室３０から密閉分離すればディスプレーサ３３上下の圧力は等しくなり、該ディスプレーサ３３を上方に移動すれば、ディスプレーサ３３上方空間３６の作動ガスは、実線矢印で示すように三方弁５０→流路２３→冷却器２０の経路により冷却器２０内に移動し冷却され、冷却器２０内の作動ガスは、流路２４→三方弁５１の経路によりディスプレーサ３３下方空間３７に移動し、冷却過程を行う。 The operation of FIG. 2 will be described in detail.
The position of the displacer 33 indicated by the solid line in the air chamber 30 shown in FIG. 2 is at the bottom dead center, and the three-way valves 50 and 51 are at the positions indicated by the broken line, and the heating process has been completed.
That is, with the three-way valves 50 and 51 as indicated by broken lines, the cooler 20 is hermetically separated from the air chamber 30 and the heater 10, and the displacer 33 is in a state where the heating process is completed at the bottom dead center position. , 51 is a position indicated by a solid line, and when the heater 10 is hermetically separated from the cooler 20 and the air chamber 30, the pressure above and below the displacer 33 becomes equal, and when the displacer 33 is moved upward, the displacer 33 upper space 36 The working gas moves into the cooler 20 through the path of the three-way valve 50 → the flow path 23 → the cooler 20 as indicated by the solid line arrow, and is cooled, and the working gas in the cooler 20 is changed to the flow path 24 → the three-way valve 51. Then, it moves to the space 37 below the displacer 33 and performs a cooling process.

ディスプレーサ３３は、図２の気室３０最上部の破線で示す上死点の位置に至るまで移動した後、冷却過程を終了する。次に三方弁５０、５１を破線で示す位置とすれば、ディスプレーサ上下の圧力は等しくなり、該ディスプレーサを下方に移動すれば、ディスプレーサ３３下方空間３７の作動ガスは、破線矢印で示すように三方弁５１→流路１４→加熱器１０の経路により加熱器１０内に移動し加熱され、加熱器１０内の作動ガスは、流路１３→三方弁５０の経路によりディスプレーサ３３上方空間３６に移動し、加熱過程を行い、ディスプレーサ３３は下死点に至り加熱過程を終了する。   The displacer 33 moves to the position of the top dead center indicated by the broken line at the top of the air chamber 30 in FIG. 2 and then ends the cooling process. Next, when the three-way valves 50 and 51 are set to the positions indicated by broken lines, the pressures above and below the displacer become equal, and when the displacer is moved downward, the working gas in the space 37 below the displacer 33 is three-way as shown by the broken line arrows. The working gas in the heater 10 moves to the space 36 above the displacer 33 through the path of the flow path 13 → the three-way valve 50 through the path of the valve 51 → the flow path 14 → the heater 10. Then, the heating process is performed, and the displacer 33 reaches the bottom dead center and ends the heating process.

一方、三方弁５２を実線の位置とすれば、シリンダー４１は冷却器２０と導通されて低温・低圧になりピストン４２は上昇する。尚、図中ピストン４２は、下死点に位置しており加熱器１０の加熱過程終了状態にある。また、三方弁５２を破線の位置とすれば、シリンダー４１は、加熱器１０と導通されて高温・高圧になりピストン４２は下降する。
この過程において、ピストン４２を介し、ガス量が加熱器１０から冷却器２０に移動する。従って、気室３０を介した冷却器２０から加熱器１０への作動ガス量が、ピストン４２を介した加熱器１０から冷却器２０への移動に等しい圧力差で、本発明の外燃式クローズドサイクル熱機関は作動する。
上記作用は、図１で詳述した作用と等価で、機能も等価であり、構造を簡略化することができ、故障などを少なくすることができる。 On the other hand, if the three-way valve 52 is set to the position of the solid line, the cylinder 41 is connected to the cooler 20 to become low temperature and low pressure, and the piston 42 is raised. In the figure, the piston 42 is located at the bottom dead center and is in a state where the heating process of the heater 10 is completed. If the three-way valve 52 is positioned at the broken line, the cylinder 41 is electrically connected to the heater 10 and becomes high temperature and high pressure, and the piston 42 is lowered.
In this process, the amount of gas moves from the heater 10 to the cooler 20 via the piston 42. Accordingly, the amount of working gas from the cooler 20 to the heater 10 via the air chamber 30 is equal to the movement from the heater 10 to the cooler 20 via the piston 42, and the external combustion closed loop of the present invention. The cycle heat engine operates.
The above-described operation is equivalent to the operation described in detail with reference to FIG. 1, and the functions are also equivalent, so that the structure can be simplified and failure and the like can be reduced.

図３は、本発明の異なる種類の作用体を用いた要部断面図である。
図３（ａ）は、作用体４０を図１におけるピストン４２に替えて往復流型タービン６０とし、高圧の加熱器１０と低圧の冷却器２０間に生じる作動ガス流が、三方弁５２の切り替えにより上部気室６１と下部気室６２を移動することで回転トルクを発生させ、軸封装置６４を介して回転軸６３を外部に出し、回転動力を得るように構成したものである。
図３（ｂ）は、作用体４０をタービン５９とし、高圧の加熱器１０と低圧の冷却器２０間に生じる作動ガス流により回転トルクを発生させ、軸封装置６４を介して回転軸６３を外部に出し、回転動力を得るように構成したものである。作動ガス流の流れ方向は、一方向の定常流であるため加熱器１０→流路１８→タービン５９→流路２８→冷却器２０間の作動ガス流路には開閉弁を必要としない。また、本エンジンでは発生圧力差が大きい反面、ガス流量が少ないため特殊なタービンが必要になるが、重比重ガスの使用により発生圧力差を運動量に効率よく変換することができる。
図３（ｃ）は、作用体４０として２個のローター（回転子）６５をケーシング６６内に設け、高圧の加熱器１０と低圧の冷却器２０間に生じる作動ガス流により回転トルクを発生させ、軸封装置（図示せず）を介して回転軸（図示せず）をケーシング６６外部に出し、回転動力を得るように構成したものである。 FIG. 3 is a cross-sectional view of a main part using different types of working bodies of the present invention.
FIG. 3A shows a reciprocating turbine 60 instead of the piston 42 in FIG. 1, and the working gas flow generated between the high-pressure heater 10 and the low-pressure cooler 20 switches the three-way valve 52. Thus, rotational torque is generated by moving the upper air chamber 61 and the lower air chamber 62, and the rotary shaft 63 is taken out via the shaft seal device 64 to obtain rotational power.
In FIG. 3 (b), the working body 40 is a turbine 59, rotational torque is generated by the working gas flow generated between the high-pressure heater 10 and the low-pressure cooler 20, and the rotary shaft 63 is connected via the shaft seal device 64. It is configured to take out and obtain rotational power. Since the flow direction of the working gas flow is a unidirectional steady flow, an open / close valve is not required in the working gas flow path between the heater 10 → the flow path 18 → the turbine 59 → the flow path 28 → the cooler 20. In addition, although the generated pressure difference is large in this engine, a special turbine is required because the gas flow rate is small, but the generated pressure difference can be efficiently converted into momentum by using heavy specific gravity gas.
In FIG. 3C, two rotors (rotors) 65 are provided in the casing 66 as the working body 40, and rotational torque is generated by the working gas flow generated between the high-pressure heater 10 and the low-pressure cooler 20. The rotary shaft (not shown) is taken out of the casing 66 through a shaft seal device (not shown) to obtain rotational power.

図４及び図５は、本発明の外燃式クローズドサイクル熱機関の実施例を示す概念図である。
図４は、図１の作用体４０を流路１８と２８に並列に２台設けたもので、複数の作用体４０を設け、一台の加熱器１０及び冷却器２０を共有する構成である。
上部側の作用体４０（１）のピストン４２は下死点に位置し、下部側の作用体４０（２）のピストン４２は上死点に位置し、ピストントップ４８が上下死点中間の位置になるように、駆動軸４４を共有している。更に作用体４０の数を増加させた多気筒とする場合は各ピストンの位相差が同じで、該位相差の総和を３６０度、又は３６０度の倍数とすれば、スムーズに稼動させることができる。
尚、気筒は偶数でなくてもピストンシリンダー４１容積を勘案すれば奇数でもよい。
図５は、図４の実施例に加えて、気室３０を流路１３、１４と２３、２４に並列に２台設け、一台の加熱器１０及び冷却器２０を共有する構成である。
作用体４０の駆動軸４４とクランク室４６を複数の作用体４０で共有しているため駆動軸４４は大きな動力を得ることができ、作用体４０を複数台の群に分けて複数の動力を得ることもできる。 4 and 5 are conceptual diagrams showing an embodiment of the external combustion type closed cycle heat engine of the present invention.
FIG. 4 is a configuration in which two working bodies 40 of FIG. 1 are provided in parallel to the flow paths 18 and 28, and a plurality of working bodies 40 are provided to share one heater 10 and cooler 20. .
The piston 42 of the upper acting body 40 (1) is located at the bottom dead center, the piston 42 of the lower acting body 40 (2) is located at the top dead center, and the piston top 48 is located between the upper and lower dead centers. Thus, the drive shaft 44 is shared. Further, in the case of a multi-cylinder with the number of acting members 40 increased, the phase difference of each piston is the same, and if the sum of the phase differences is 360 degrees or a multiple of 360 degrees, it can be operated smoothly. .
The number of cylinders is not limited to an even number, but may be an odd number as long as the volume of the piston cylinder 41 is taken into consideration.
FIG. 5 shows a configuration in which two air chambers 30 are provided in parallel with the flow paths 13, 14, 23, and 24 in addition to the embodiment of FIG. 4, and one heater 10 and cooler 20 are shared.
Since the drive shaft 44 and the crank chamber 46 of the operating body 40 are shared by the plurality of operating bodies 40, the driving shaft 44 can obtain a large amount of power, and the operating body 40 is divided into a plurality of groups to generate a plurality of power. It can also be obtained.

また、クランク室４６を複数の作用体４０が共有し、ピストン４２の位相差の総和を３６０度又は３６０度の倍数とすることにより、ピストンシリンダー４１のピストン下部、及びクランク室４６の容積の総和を一定とすることができ、ピストン４２の背圧が定常となるためピストン４２の作動を円滑にすることができる。
ピストンシリンダー４１（１）と４１（２）のいずれかが上昇過程にあるため流路２８にはピストンシリンダー４１から冷却器２０に向かう高温作動ガスが常時流れる。
気室３０（１）内のディスプレーサ３３（１）と気室３０（２）内のディスプレーサ３３（２）の位相差を１８０度とすることにより、気室３０（１）または気室３０（２）のいずれかが必ず加熱過程にあり、他は冷却過程にある。従って気室３０を介した冷却器２０から加熱器１０への作動ガスの移動が連続して行われるので、加熱器１０及び冷却器２０は全サイクルを通じて作動するため作動効率、及び熱効率を向上できるとともに、冷却器２０内及び加熱器１０内の圧力変動が少なくなる。 Further, the crank chamber 46 is shared by the plurality of operating bodies 40, and the sum of the phase differences of the piston 42 is set to 360 degrees or a multiple of 360 degrees, so that the total volume of the piston lower portion of the piston cylinder 41 and the volume of the crank chamber 46 is increased. Since the back pressure of the piston 42 becomes steady, the operation of the piston 42 can be made smooth.
Since one of the piston cylinders 41 (1) and 41 (2) is in the ascending process, the high-temperature working gas from the piston cylinder 41 toward the cooler 20 always flows through the flow path 28.
By setting the phase difference between the displacer 33 (1) in the air chamber 30 (1) and the displacer 33 (2) in the air chamber 30 (2) to 180 degrees, the air chamber 30 (1) or the air chamber 30 (2 ) Is always in the heating process, and the other is in the cooling process. Therefore, since the working gas is continuously transferred from the cooler 20 to the heater 10 through the air chamber 30, the heater 10 and the cooler 20 operate throughout the entire cycle, so that the operation efficiency and the heat efficiency can be improved. At the same time, pressure fluctuations in the cooler 20 and the heater 10 are reduced.

気室３０内のディスプレーサ３３は、ディスプレーサクランク室（図示せず）内に設けられたディスプレーサクランク（図示せず）、ディスプレーサ駆動軸（図示せず）等のディスプレーサクランク機構により駆動されており、ディスプレーサ駆動軸はピストン４２の駆動軸４４に直結されている。このため気室３０とピストンシリンダー４１、クランク室４６、及びディスプレーサクランク室を一体構造として構成できるので、別動力源、または動力伝達装置を必要とせずコンパクトな構造とすることができる。
また、ディスプレーサ３３をピストン４２と同一サイクル数で駆動する必要はなく、ディスプレーサ３３を別動力源、または増速装置を介して高サイクル数で駆動すれば気室３０を小型化することが可能である。 The displacer 33 in the air chamber 30 is driven by a displacer crank mechanism such as a displacer crank (not shown) and a displacer drive shaft (not shown) provided in a displacer crank chamber (not shown). The drive shaft is directly connected to the drive shaft 44 of the piston 42. For this reason, since the air chamber 30, the piston cylinder 41, the crank chamber 46, and the displacer crank chamber can be configured as an integral structure, a separate power source or power transmission device is not required, and a compact structure can be achieved.
Further, it is not necessary to drive the displacer 33 with the same number of cycles as the piston 42. If the displacer 33 is driven with a high number of cycles via a separate power source or a speed increasing device, the air chamber 30 can be reduced in size. is there.

図６は、本発明の外燃式クローズドサイクル熱機関の実施例を示す概念図である。
図６（ａ）は、図５の流路２３へ高温部である熱交換器７０を設け、流路１４へ低温部である熱交換器７１を設け、同図では分離設置に見えるが、一体構成で形成されて熱回収装置としたものである。
本実施例では２気室であるため気室３０（１）または気室３０（２）のいずれかが必ず加熱過程にあり、他は冷却過程にある。従って流路２３には冷却過程の時、ディスプレーサ上方空間３６の加熱過程を終了した加熱された高温作動ガスが常時通過し、流路１４には加熱過程の時、ディスプレーサ３３によりディスプレーサ下方空間３７の冷却過程を終了した冷却された低温作動ガスが常時通過している。従って流路１４、及び流路２３にまたがる熱交換器７０、７１により、流路２３に流れる高温作動ガスにより流路１４に流れる低温作動ガスを加熱し、加熱過程の一部とすることにより熱回収を行うものである。
本方式では気体間の伝熱を利用したもので、伝熱効率が悪く、大型化する必要があり、また複数の気室が必要である。 FIG. 6 is a conceptual diagram showing an embodiment of the external combustion type closed cycle heat engine of the present invention.
6A, a heat exchanger 70 that is a high-temperature part is provided in the flow path 23 of FIG. 5, and a heat exchanger 71 that is a low-temperature part is provided in the flow path 14. In FIG. The heat recovery device is formed by the configuration.
In this embodiment, since there are two air chambers, either the air chamber 30 (1) or the air chamber 30 (2) is always in the heating process, and the other is in the cooling process. Therefore, the heated high-temperature working gas that has finished the heating process of the displacer upper space 36 always passes through the flow path 23 during the cooling process, and the displacer 33 lowers the displacer lower space 37 during the heating process. The cooled low-temperature working gas that has finished the cooling process always passes. Therefore, the heat exchangers 70 and 71 spanning the flow path 14 and the flow path 23 heat the low-temperature working gas flowing in the flow path 14 with the high-temperature working gas flowing in the flow path 23, and make it a part of the heating process. The collection is performed.
In this method, heat transfer between gases is utilized, heat transfer efficiency is poor, the size needs to be increased, and a plurality of air chambers are required.

図６（ｂ）は、図１に図６（ｂ）破線で囲む蓄熱器７５と開閉弁７６，７７を付加したものである。即ち、図１に示す開閉弁２５と導通する流路２３へ蓄熱器７５、開閉弁７７、流路２３、冷却器入り口部２１の流路と、開閉弁２５と導通する流路２３へ開閉弁７６、流路１４、加熱器入り口部１２の流路を構成し、また、図１に示す開閉弁１６と導通する流路１４へ蓄熱器７５、開閉弁７６、流路１４、加熱器入り口部１２の流路を構成したものである。
冷却過程の時は開閉弁の切り替えにより、ディスプレーサ上方空間３６の加熱過程を終了した加熱された高温作動ガスは、図中実線矢印で示すディスプレーサ上方空間３６→開閉弁２５→流路２３→蓄熱器７５→開閉弁７７→流路２３→冷却器入り口部２１の流れで蓄熱器７５を加熱する。加熱過程の時は弁の切り替えにより、ディスプレーサ下方空間３７の冷却過程を終了した冷却された低温作動ガスは、図中破線矢印で示すディスプレーサ下方空間３７→開閉弁１６→流路１４→蓄熱器７５→開閉弁７６→流路１４→加熱器入り口部１２の流れで、加熱器１０に入る前に蓄熱器７５により加熱される。本方式では気体と蓄熱材間の伝熱を利用したもので、伝熱効率が高く、一個の気室にも応用できる。 FIG. 6B is obtained by adding a heat accumulator 75 and on-off valves 76 and 77 surrounded by broken lines in FIG. That is, the heat accumulator 75, the on-off valve 77, the flow path 23, the flow path of the cooler inlet 21 to the flow path 23 connected to the on-off valve 25 shown in FIG. 76, the flow path 14, the flow path of the heater inlet 12, and the heat accumulator 75, the open / close valve 76, the flow path 14, the heater inlet to the flow path 14 connected to the open / close valve 16 shown in FIG. 1. 12 channels are configured.
During the cooling process, the heated high-temperature working gas that has finished the heating process of the displacer upper space 36 by switching the on / off valve is the displacer upper space 36 → open / close valve 25 → flow path 23 → heat accumulator indicated by the solid line arrow in the figure. The heat accumulator 75 is heated by the flow of 75 → open / close valve 77 → flow path 23 → cooler inlet 21. During the heating process, the cooled low-temperature working gas that has finished the cooling process of the displacer lower space 37 by switching the valve is the displacer lower space 37 → opening / closing valve 16 → channel 14 → heat accumulator 75 indicated by the broken line arrow in the figure. It is heated by the heat accumulator 75 before entering the heater 10 in the flow of the on-off valve 76 → the flow path 14 → the heater inlet 12. This method uses heat transfer between gas and heat storage material, has high heat transfer efficiency, and can be applied to a single air chamber.

図７は、本発明の外燃式クローズドサイクル熱機関の実施例を示す概念図である。
同図は、図１の内部にディスプレーサ３３を設けた気室３０に替えて内部にピストン８１、８６を設けたシリンダー８０、８５の２個を使用し、各シリンダートップにはそれぞれ作動ガスの出入り口８３、８８が設けられ、ピストンロッド８２、８７を介してピストン８１、８６を１８０°の位相をもってクランクシャフト９０で連動する構成としたものである。図１の内部にディスプレーサ３３を設けた気室３０と同等の作用を行わせるものである。 FIG. 7 is a conceptual diagram showing an embodiment of the external combustion type closed cycle heat engine of the present invention.
In this figure, instead of the air chamber 30 provided with the displacer 33 in FIG. 1, two cylinders 80 and 85 provided with pistons 81 and 86 inside are used. 83 and 88 are provided, and the pistons 81 and 86 are interlocked with the crankshaft 90 with a phase of 180 ° via the piston rods 82 and 87. The operation equivalent to that of the air chamber 30 in which the displacer 33 is provided in FIG. 1 is performed.

同図の開閉弁及び加熱器、冷却器に対する流路を含む気室Ａは、図１のディスプレーサ３３を設けた気室３０のディスプレーサ３３及び開閉弁１６、２６、加熱器１０、冷却器２０に対する流路１４、２４を含む下部に相当し、開閉弁及び加熱器、冷却器に対する流路を含む気室Ｂは、図１のディスプレーサ３３を設けた気室３０のディスプレーサ３３及び開閉弁１５、２５、加熱器１０、冷却器２０に対する流路１３、２３を含む上部に相当する。気室Ａ及び気室Ｂは、ピストン８１、８６を１８０°の位相をもって移動させることにより、図１のディスプレーサ３３を設けた気室３０と同等に作動ガスの移動を行う。従って、本発明の作用は、ディスプレーサ３３を設けた気室３０と同等であるが、気室３０の高さ寸法を小さくできること、また開閉弁１５、２５、１６、２６を気室３０の同一端に設置できるため構造を簡略化できる利点がある。   The air chamber A including the opening / closing valve, the heater, and the flow path for the cooler shown in FIG. 1 corresponds to the displacer 33 and the open / close valves 16 and 26 of the air chamber 30 provided with the displacer 33 of FIG. The air chamber B corresponding to the lower part including the flow paths 14 and 24 and including the flow paths for the opening / closing valve, the heater and the cooler is the displacer 33 and the opening / closing valves 15 and 25 of the air chamber 30 provided with the displacer 33 of FIG. This corresponds to the upper part including the flow paths 13 and 23 for the heater 10 and the cooler 20. The air chamber A and the air chamber B move the working gas in the same manner as the air chamber 30 provided with the displacer 33 in FIG. 1 by moving the pistons 81 and 86 with a phase of 180 °. Accordingly, the operation of the present invention is equivalent to that of the air chamber 30 provided with the displacer 33, but the height dimension of the air chamber 30 can be reduced, and the on-off valves 15, 25, 16, and 26 are connected to the same end of the air chamber 30. There is an advantage that the structure can be simplified.

また、加熱過程の始まりにおいて、気室Ｂのピストン８１が上死点にあり、気室Ａのピストン８６が下死点にあり、気室Ａに低温低圧の作動ガスが充満している状態において、気室Ａの加熱器１０側及び冷却器２０側の開閉弁を閉とし、気室Ｂの冷却器２０側の開閉弁を閉とし加熱器１０側の開閉弁を開とすれば、気室Ｂのピストン８１には加熱器１０内の高圧が加わり、気室Ａのピストン８６には低圧が加わっているので、気室Ｂのピストン８１に加わる力は、気室Ａのピストン８６に加わる力より大きく、動力が発生する。   At the beginning of the heating process, the piston 81 of the air chamber B is at the top dead center, the piston 86 of the air chamber A is at the bottom dead center, and the air chamber A is filled with the low-temperature and low-pressure working gas. If the on-off valve on the heater 10 side and the cooler 20 side of the air chamber A is closed, the on-off valve on the cooler 20 side of the air chamber B is closed, and the on-off valve on the heater 10 side is opened, the air chamber Since the high pressure in the heater 10 is applied to the piston 81 of B and the low pressure is applied to the piston 86 of the air chamber A, the force applied to the piston 81 of the air chamber B is the force applied to the piston 86 of the air chamber A. Larger and more power is generated.

気室Ａのピストン８６が上昇するに従って、気室Ａ内の作動ガスは高圧になる。気室Ａ内の作動ガス圧が、加熱器１０内の圧力と等しくなった時点で、気室Ａの加熱器１０側の開閉弁を開とすれば、気室Ｂのピストン８１に加わる力は、気室Ａのピストン８６に加わる力と等しくなる。サイクルの他の部分でも気室Ｂのピストン８１に加わる力は、気室Ａのピストン８６に加わる力とバランスしており、ピストン８１、８６の駆動に動力を要しない。
従って図７の方式によれば、作動ガスの循環のみならず動力を発生できる利点がある。 As the piston 86 of the air chamber A rises, the working gas in the air chamber A becomes high pressure. When the working gas pressure in the air chamber A becomes equal to the pressure in the heater 10, if the on-off valve on the heater 10 side of the air chamber A is opened, the force applied to the piston 81 of the air chamber B is It becomes equal to the force applied to the piston 86 of the air chamber A. The force applied to the piston 81 in the air chamber B in the other parts of the cycle is balanced with the force applied to the piston 86 in the air chamber A, and no power is required to drive the pistons 81 and 86.
Therefore, according to the method of FIG. 7, there is an advantage that not only the working gas is circulated but also power can be generated.

１０ 加熱器
１１ 加熱器出口部
１２ 加熱器入り口部
１３、１４、１８、２３、２４、２８ 流路
１７ 出口部
１５、１６、１９、２５、２６、２９ 開閉弁
２０ 冷却器
２１ 冷却器入り口部
２２ 冷却器出口部
２７ 入り口部
３０ 気室
３１、３２ 気室の出入り口部
３３ ディスプレーサ
３４ 貫通部
３５ ディスプレーサロッド
３６ ディスプレーサ上方空間
３７ ディスプレーサ下方空間
４０ 作用体
４１ ピストンシリンダー
４２ ピストン
４３ フライホイール
４４ 駆動軸
４５ クランク
４６ クランク室
４７ 出入り口部
４８ ピストントップ
５０、５１、５２ 三方弁
５９ タービン
６０ 往復流型タービン
６１ 上部気室
６２ 下部気室
６３ 回転軸
６４ 軸封装置
６５ ローター（回転子）
６６ ケーシング
７０、７１ 熱交換器
７５ 蓄熱器
７６、７７ 開閉弁
８０、８５ シリンダー
８１、８６ ピストン
８２、８７ ピストンロッド
８３、８８ 出入り口
９０ クランクシャフト DESCRIPTION OF SYMBOLS 10 Heater 11 Heater outlet part 12 Heater inlet part 13, 14, 18, 23, 24, 28 Channel 17 Outlet part 15, 16, 19, 25, 26, 29 On-off valve 20 Cooler 21 Cooler inlet part 22 Cooler outlet portion 27 Entrance portion 30 Air chambers 31, 32 Air chamber inlet / outlet portion 33 Displacer 34 Penetration portion 35 Displacer rod 36 Displacer upper space 37 Displacer lower space 40 Acting body 41 Piston cylinder 42 Piston 43 Flywheel 44 Drive shaft 45 Crank 46 Crank chamber 47 Entrance / exit port 48 Piston top 50, 51, 52 Three-way valve 59 Turbine 60 Reciprocating turbine 61 Upper air chamber 62 Lower air chamber 63 Rotating shaft 64 Shaft seal device 65 Rotor (rotor)
66 Casing 70, 71 Heat exchanger 75 Heat storage 76, 77 On-off valve 80, 85 Cylinder 81, 86 Piston 82, 87 Piston rod 83, 88 Entrance / exit 90 Crankshaft

Claims (11)

密閉された気室と加熱器及び冷却器を設け、該気室と該加熱器の入り口部及び出口部と導通する流路を設け、該気室と冷却器の入り口部及び出口部と導通する流路を設け、それぞれ入り口部側及び出口部側の流路に開閉弁を設け、更に、加熱器と導通する流路と該流路に開閉弁を設け、冷却器と導通する流路と該流路に開閉弁を設けて、加熱器と冷却器それぞれと導通する作用体を設けた外燃式クローズドサイクル熱機関であって、気室と冷却器間及び気室と加熱器間の開閉弁と連動するディスプレーサを少なくとも１個気室内に設けたことを特徴とする外燃式クローズドサイクル熱機関。   A sealed air chamber, a heater and a cooler are provided, and a flow path is provided to communicate with the air chamber and the inlet and outlet of the heater, and the air chamber and the inlet and outlet of the cooler are electrically connected. A flow path is provided, and an open / close valve is provided in each of the flow path on the inlet side and the outlet side, and a flow path that is connected to the heater, an open / close valve is provided in the flow path, and a flow path that is connected to the cooler is An external combustion type closed cycle heat engine provided with an opening / closing valve in a flow path and an operating body that is electrically connected to each of a heater and a cooler, and between the air chamber and the cooler and between the air chamber and the heater An external combustion type closed cycle heat engine characterized in that at least one displacer that is linked to the engine is provided in the air chamber. 開閉弁の流路が３分岐あり、１分岐から入り込む流体を、他の２分岐流路のいずれかを選択的に流路とする、又は２分岐流路のいずれかを選択し、他の１分岐を流路とする三方弁としたことを特徴とする請求項１記載の外燃式クローズドサイクル熱機関。   The flow path of the on-off valve has three branches, and the fluid entering from one branch is selectively set to one of the other two branch paths, or one of the two branch paths is selected and the other 1 The external combustion type closed cycle heat engine according to claim 1, wherein the three-way valve has a branch as a flow path. 作用体が、ピストンであることを特徴とする請求項１又は２に記載の外燃式クローズドサイクル熱機関。   The external combustion type closed cycle heat engine according to claim 1 or 2, wherein the operating body is a piston. 作用体が、タービン等であることを特徴とする請求項１又は２に記載の外燃式クローズドサイクル熱機関。   The external combustion type closed cycle heat engine according to claim 1 or 2, wherein the operating body is a turbine or the like. 作用体を複数設け、加熱器および冷却器を共有することを特徴とする請求項１〜４のいずれかに記載の外燃式クローズドサイクル熱機関。   The external combustion type closed cycle heat engine according to any one of claims 1 to 4, wherein a plurality of operating bodies are provided and a heater and a cooler are shared. 複数設けた作用体の駆動軸を共有することを特徴とする請求項１〜５のいずれかに記載の外燃式クローズドサイクル熱機関。   The external combustion type closed cycle heat engine according to any one of claims 1 to 5, wherein a plurality of actuating body drive shafts are shared. 複数設けたピストンのクランク室を共有したことを特徴とする請求項１〜３、５、又は６のいずれかに記載の外燃式クローズドサイクル熱機関。   The external combustion type closed cycle heat engine according to any one of claims 1 to 3, wherein a plurality of piston crank chambers are shared. 複数設けたピストンが、クランクシャフトを介して総和が３６０度又は３６０度の倍数となる位相差をもって共有する駆動軸に連接することを特徴とする請求項１〜３、又は５〜７のいずれかに記載の外燃式クローズドサイクル熱機関。   The plurality of pistons are connected to a common drive shaft via a crankshaft with a phase difference whose sum is a multiple of 360 degrees or 360 degrees. External combustion type closed cycle heat engine described in 1. 加熱器入り口部側及び冷却器入り口部側の流路間、又は開閉弁を設けた流路に熱交換器を設けたことを特徴とする請求項１〜８のいずれかに記載の外燃式クローズドサイクル熱機関。   The external combustion type according to any one of claims 1 to 8, wherein a heat exchanger is provided between the flow paths on the heater inlet side and the cooler inlet side or on the flow path provided with the on-off valve. Closed cycle heat engine. 気室を加熱器と冷却器に並列して２個を１組として、１組又は複数組設けたことを特徴とする請求項１〜９のいずれかに記載の外燃式クローズドサイクル熱機関。   The external combustion type closed cycle heat engine according to any one of claims 1 to 9, wherein the air chamber is provided in parallel with a heater and a cooler, and one set or two sets are provided. 内部にディスプレーサを設けた気室に替えて内部にピストンを設けた気筒（シリンダー）の２個を一組として、１組または複数組設け、該１組のピストンが１８０°の位相差とするクランク機構を設け、それぞれのシリンダーヘッドと加熱器及び冷却器と導通する流路を設け、該流路に開閉弁を設けたことを特徴とする請求項１〜１０のいずれかに記載の外燃式クローズドサイクル熱機関。   A crank that has two or more cylinders (cylinders) with pistons inside instead of an air chamber with a displacer inside, and the one piston has a phase difference of 180 °. The external combustion type according to any one of claims 1 to 10, wherein a mechanism is provided, a flow path is provided to communicate with each cylinder head, a heater, and a cooler, and an open / close valve is provided in the flow path. Closed cycle heat engine.
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