JPS5925061A - Sterling engine for driving heat pump - Google Patents

Sterling engine for driving heat pump

Info

Publication number
JPS5925061A
JPS5925061A JP13425682A JP13425682A JPS5925061A JP S5925061 A JPS5925061 A JP S5925061A JP 13425682 A JP13425682 A JP 13425682A JP 13425682 A JP13425682 A JP 13425682A JP S5925061 A JPS5925061 A JP S5925061A
Authority
JP
Japan
Prior art keywords
piston
heat pump
pistons
guide
compressor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
JP13425682A
Other languages
Japanese (ja)
Inventor
Kazuaki Yamaguchi
和明 山口
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Aisin Corp
Original Assignee
Aisin Seiki Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Aisin Seiki Co Ltd filed Critical Aisin Seiki Co Ltd
Priority to JP13425682A priority Critical patent/JPS5925061A/en
Publication of JPS5925061A publication Critical patent/JPS5925061A/en
Pending legal-status Critical Current

Links

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
    • F02G1/044—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 having at least two working members, e.g. pistons, delivering power output
    • 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
    • F02G2270/00—Constructional features
    • F02G2270/20—Plural piston swash plates

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Abstract

PURPOSE:To obtain efficient work by arranging operation pistons and guide pistons to keep the phase difference at 120 deg. and providing Freon compressor pistons for a heat pump between guide pistons for operating a freon compressor in accordance with the change of thermal load of the heat pump. CONSTITUTION:Guide pins 10 are arranged to keep the phase different at 120 deg., and compressor pistons 19 are provided between them. The first, the second, and the third pistons are kept at the position phase difference of 120 deg., and the capacity phase difference between a compression space and an expansion space is kept at 60 deg.. Consequently, the pressure ratio can be increased up to 2.3, and the average pressure of operation gas can be increased to a line C from a line B for sufficiently corresponding to the torque change of a Freon compressor between numbers of revolutions n1 and n2.

Description

【発明の詳細な説明】 この発明は、ヒートポンプ駆動用スターリングエンジン
に関する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a Stirling engine for driving a heat pump.

ヒートポンプは、放熱器および膨張弁を有する回路およ
び吸熱器および膨張弁を有する回路を、中間熱交換器お
よび切換弁を介してフレオンコンプレッサーに接続する
構成となっている。、このフレオンコンプレッサーは、
定速電動モータで駆動する。即ち、フレオンコンプレッ
サーは一定トルクで駆動される。The heat pump has a configuration in which a circuit having a heat radiator and an expansion valve and a circuit having a heat absorber and an expansion valve are connected to a Freon compressor via an intermediate heat exchanger and a switching valve. , this freon compressor is
Driven by a constant speed electric motor. That is, the Freon compressor is driven with constant torque.

ところで、本発明者らの実験によれば、ヒートポンプの
熱負荷変動に応じて、フレオンコンプレッサーのトルク
変動範囲は、第４図の斜線で示される如く変化させる方
が望ましいことが分った。By the way, according to experiments conducted by the present inventors, it has been found that it is preferable to change the torque fluctuation range of the Freon compressor as shown by diagonal lines in FIG. 4 in accordance with the heat load fluctuation of the heat pump.

一方、フレオンコンプレッサーの動力源として、電動モ
ータに代えて、熱効率のよいスターリングエンジンが用
いられるようになっている。スターリングエンジンは、
作動ピストンにより区画されるシリンダ室内の高温部と
なる膨張室と、低温部となる圧縮室との間を、作動ガス
を等温膨張、等容置化、等温圧縮および等容置化させな
がら往復させて外部に出力を取シ出しており、その出力
は閉回路中の作動ガスの平均圧力にはソ比例する。この
ような作用をなすスターリングエンジンは、作動ガス最
高圧力と掃気容積を同じにした場合出力が比較的大であ
ｐ１又、クランク式ダブルアクティングによシ構造が容
易となることから圧縮空間と膨張空間の変化の位相差を
９０°（角度）にとった４気筒のものが用いられる。さ
らに、作動ガスの平均圧力は、作動空間の最高圧力回路
と最低圧力回路とを選択的に作動ガスタンクに連通させ
制御させている。このような従来の方式では、作動ガス
の平均圧力を、作動空間の最高圧力と最低圧力の比即ち
圧力比以上の中白で変化するが、従来の４気筒ダブルア
クテイングスターリングエンジンでは、この圧力比を２
程度しか取れない。On the other hand, as a power source for Freon compressors, Stirling engines with good thermal efficiency are being used instead of electric motors. The Stirling engine is
The working gas is reciprocated between the expansion chamber, which is a high-temperature part, and the compression chamber, which is a low-temperature part, in the cylinder chamber, which is divided by the working piston, while isothermal expansion, isovolume, isothermal compression, and isovolume. The output is taken out to the outside, and the output is proportional to the average pressure of the working gas in the closed circuit. The Stirling engine, which operates in this way, has a relatively large output when the maximum working gas pressure and scavenging volume are the same, and since the engine structure is easy due to the crank type double acting, the compression space and A 4-cylinder engine with a phase difference of 90 degrees (angle) in changes in the expansion space is used. Further, the average pressure of the working gas is controlled by selectively communicating the highest pressure circuit and the lowest pressure circuit of the working space with the working gas tank. In such a conventional system, the average pressure of the working gas is changed by the ratio of the highest pressure to the lowest pressure in the working space, that is, the pressure ratio or higher, but in the conventional 4-cylinder double-acting Stirling engine, this pressure ratio to 2
I can only take it to a certain extent.

このような従来のスターリングエンジンを、ヒートポン
プの７シオンコンプレツサーの駆動源として用い、その
回転数を変え、ヒートポンプの熱負荷の変動に応じてそ
のトルクを制御した場合、第４図のＢで表示される作動
ガス平均圧力しか得られず、ヒートポンプの熱負荷に応
じたトルク変動が充分に確保できない。さらに、ヒート
ポンプの別個のフレオンコンプレッサーを必要としてい
た。If such a conventional Stirling engine is used as a drive source for a heat pump's 7-ion compressor, and its rotational speed is varied and its torque is controlled in response to fluctuations in the heat load of the heat pump, B in Figure 4. Only the average pressure of the working gas that is displayed can be obtained, and it is not possible to ensure sufficient torque fluctuation according to the heat load of the heat pump. Additionally, the heat pump required a separate Freon compressor.

それ故、この発明は、従来の圧力比２より高い圧力比を
得るようにし、スターリングエンジンの出力に関連する
作動ガスの平均圧力をこの高い圧力比の中白で変化させ
、ヒートポンプのフレオンコンプレッサーをヒートポン
プの熱負荷の変動に応じて充分に対応させるようにし、
且つヒートポンプのコンプレッサーをスターリング機関
に組込むようにしたもので、このために、この発明は、
作動ピストンおよびガイドピストンを１２０度の位置位
相差となるように配し、該ガイドピストン間ニヒートポ
ンプ用フレオンコンプレッサーのピストンを組込む技術
手段を用いる。Therefore, this invention makes it possible to obtain a pressure ratio higher than the conventional pressure ratio 2, and to change the average pressure of the working gas related to the output of the Stirling engine in the middle of this high pressure ratio, and to change the Freon compressor of the heat pump. Make sure to adequately respond to fluctuations in the heat load of the heat pump.
In addition, the heat pump compressor is incorporated into the Stirling engine, and for this reason, this invention has the following features:
A technical means is used in which the working piston and the guide piston are arranged to have a positional phase difference of 120 degrees, and a piston of a Freon compressor for a heat pump is installed between the guide pistons.

この発明によれば、圧力比が２，３と高くなるので、ヒ
ートポンプの熱負荷に応じた回転数をフレオンコンプレ
ッサーに与えることができ又、該コンプレッサーをスタ
ーリングエンジンに組込み効率のよい作業が可能となる
。According to this invention, since the pressure ratio is as high as 2.3, it is possible to give the Freon compressor a rotational speed corresponding to the heat load of the heat pump, and it is also possible to incorporate the compressor into a Stirling engine for efficient work. Become.

この発明の実施例を添付図面を参照して説明する。Embodiments of the invention will be described with reference to the accompanying drawings.

スターリングエンジン１は、作動ピストン２により区画
される膨張室３と圧縮室４とをシリンダ５内に有し、膨
張室３がヒータ６、畜熱器７およびクーラ８を介して隣
り合・うシリンダの圧縮室４に連通ずる。この発明では
、３個のシリンダ５が等間隔に、即ち、１２０度（角度
）のピストン位置位相差で配置される（第２図参照）。The Stirling engine 1 has an expansion chamber 3 and a compression chamber 4 in a cylinder 5, which are partitioned by an operating piston 2. It communicates with the compression chamber 4 of. In this invention, three cylinders 5 are arranged at equal intervals, that is, with a piston position phase difference of 120 degrees (angle) (see FIG. 2).

作動ピストン２は、ロッド９を介してガイドピストン１
０に連結される。ガイドピストン１０は、斜板１１と協
働し、作動ピストン２の往復動を斜板１１により回転運
動に変換する。作動空間、好ましくは、圧縮室４が作動
ガスタンク１２に、加速弁１３および一方向弁１４を有
する回路１５と減速弁１６および一方向弁１７を有する
回路１８とを介して連結される。The working piston 2 is connected to the guide piston 1 via a rod 9.
Concatenated to 0. The guide piston 10 cooperates with a swash plate 11 to convert the reciprocating motion of the working piston 2 into rotational motion by the swash plate 11. The working space, preferably the compression chamber 4, is connected to the working gas tank 12 via a circuit 15 with an acceleration valve 13 and a one-way valve 14 and a circuit 18 with a deceleration valve 16 and a one-way valve 17.

第２図に示すようにガイドピストン１０をその位置位相
差が１２０度となるように配するか、その間にコンプレ
ッサー用ピストン１９が配設される。ピストン１９は斜
板により上下動し、その上下の空間２０内に弁２１を介
して供給されたフレオンガスを圧縮させ弁２２を介して
吐出させる。２３は回転軸を示す。As shown in FIG. 2, the guide pistons 10 are arranged so that their positional phase difference is 120 degrees, or the compressor piston 19 is arranged between them. The piston 19 is moved up and down by a swash plate, compresses Freon gas supplied through a valve 21 into a space 20 above and below it, and discharges it through a valve 22. 23 indicates a rotation axis.

前述した如く３気筒としたスターリングエンジン１は、
第３図に示す如く、第１ピストン、第２ピストンおよび
第３ピストンが１２０度の位置位相差で配され、圧縮空
間と膨張空間との容積位相差が６０度となる。この結果
、くして、第４図に示される如く、作動ガスの平均圧力
はＣで表示される線までＢから上げることかでき、回転
数がｎｌからｎ、において、クレオンコンブレッサーの
トルク変動に充分対応させることができる。同、第４図
のＡで表示される線は作動ガスの平均圧力が圧力比と同
じ場合を示す。As mentioned above, the Stirling engine 1 with three cylinders is
As shown in FIG. 3, the first piston, second piston, and third piston are arranged with a positional phase difference of 120 degrees, and the volume phase difference between the compression space and the expansion space is 60 degrees. As a result, as shown in Fig. 4, the average pressure of the working gas can be increased from B to the line indicated by C, and when the rotational speed is from nl to n, the torque fluctuation of the Creon compressor is It can be fully adapted. The line indicated by A in FIG. 4 shows the case where the average pressure of the working gas is the same as the pressure ratio.

コンプレッサーピストン１９のガイドピストン１０間へ
の設置は、斜板１１部分の空間の有効利用となる。この
コンプレッサービストン１＋の設置は、ガイドピストン
１０の径を小さくさせる必要がなく、最適径をとること
ができる。The installation of the compressor piston 19 between the guide pistons 10 makes effective use of the space in the swash plate 11 portion. This installation of the compressor service ton 1+ eliminates the need to reduce the diameter of the guide piston 10, and allows an optimum diameter to be taken.

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

第１図はこの発明の一例のスターリングエンジンの断面
図、第２図は第１図の矢視■−■よりみた断面図、第３
図は位相角とピストン位置との関係を示す図、第４図は
スターリングエンジンの回転数とトルクの関係を示す図
である。 図中：　１・・・スターリングエンジン、２・・・作動
ピストン、３・・・膨張室、４・・・圧縮室、９・・・
ロッド、１０・・・ガイドピストン、１１・・・斜板、
１２・・・作動ガスタンク、１３・・・増速弁、１６・
・・減速弁、１９・・・コンプレッサーピストン。 代理人　弁理士　桑　原　英　明Fig. 1 is a cross-sectional view of a Stirling engine as an example of the present invention, Fig. 2 is a cross-sectional view taken from the arrow direction ■-■ in Fig. 1, and Fig.
The figure shows the relationship between the phase angle and the piston position, and FIG. 4 shows the relationship between the rotation speed and torque of the Stirling engine. In the diagram: 1... Stirling engine, 2... Working piston, 3... Expansion chamber, 4... Compression chamber, 9...
Rod, 10... Guide piston, 11... Swash plate,
12... Working gas tank, 13... Speed increase valve, 16...
...Reduction valve, 19...Compressor piston. Agent Patent Attorney Hideaki Kuwahara

Claims (1)

【特許請求の範囲】[Claims] シリンダ内の作動ピストンにより膨張室と圧縮室とに区
画し、前記膨張室を隣り合うシリンダ内の圧縮室にヒー
タ、蓄熱器およびクーラを介して連通させ且つ前記作動
ピストンの往復動をロッドおよびガイドピストンを介し
て斜板を回転運動させるスターリングエンジンにおいて
、その作動空間を増速弁および減速弁を介して作動ガス
タンクに連結し、前記作動ピストンおよび前記ガイドピ
ストンを１２０度の位置位相差となるように配し且つ前
記ガイドピストン間にヒートポンプ用フレオンコンプレ
ッサーのピストンを配したことを特徴とするヒートポン
プ駆動用スターリングエンジン。The cylinder is divided into an expansion chamber and a compression chamber by a working piston, and the expansion chamber is communicated with the compression chamber in an adjacent cylinder via a heater, a heat storage device, and a cooler, and the reciprocating movement of the working piston is controlled by a rod and a guide. In a Stirling engine that rotates a swash plate through a piston, its working space is connected to a working gas tank through a speed increasing valve and a decelerating valve, and the working piston and the guide piston are arranged to have a positional phase difference of 120 degrees. A Stirling engine for driving a heat pump, characterized in that the piston of a Freon compressor for a heat pump is arranged between the guide pistons.
JP13425682A 1982-07-31 1982-07-31 Sterling engine for driving heat pump Pending JPS5925061A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP13425682A JPS5925061A (en) 1982-07-31 1982-07-31 Sterling engine for driving heat pump

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP13425682A JPS5925061A (en) 1982-07-31 1982-07-31 Sterling engine for driving heat pump

Publications (1)

Publication Number Publication Date
JPS5925061A true JPS5925061A (en) 1984-02-08

Family

ID=15124042

Family Applications (1)

Application Number Title Priority Date Filing Date
JP13425682A Pending JPS5925061A (en) 1982-07-31 1982-07-31 Sterling engine for driving heat pump

Country Status (1)

Country Link
JP (1) JPS5925061A (en)

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