JP4042417B2

JP4042417B2 - Positive displacement machine

Info

Publication number: JP4042417B2
Application number: JP2002017828A
Authority: JP
Inventors: 功早瀬; 弘勝香曽我部; 雅嗣近野; 健司東條; 健一大島
Original assignee: Hitachi Ltd
Current assignee: Hitachi Ltd
Priority date: 2002-01-28
Filing date: 2002-01-28
Publication date: 2008-02-06
Anticipated expiration: 2022-01-28
Also published as: KR20030064637A; ES2245539A1; CN1435568A; CN1256508C; JP2003214104A; KR100540415B1; ES2245539B1

Description

【０００１】
【発明の属する技術分野】
本発明は、容積形機械と容積形機械を用いた冷凍空調機器や燃料電池システムなどの効率向上技術に関する。
【０００２】
【従来の技術】
従来のレシプロ式容積形機械では、特開平９−７２２７５号公報の図７に記載の圧縮機のように作動室空間をその容積の増減に応じて吸入室空間あるいは吐出室空間とを交互に連通させるため、可動部品によって構成されるバルブ機構を使用していた。
また、特開平９−７２２７５号公報の図７に記載の圧縮機における往復動部材はピストン部の中央にアーム部を挿入することにより形成されていた。
【０００３】
【発明が解決しようとする課題】
上記従来技術では、レシプロ式容積形機械を構成する可動部品が多くなり生産性と信頼性を低下させるという問題があった。本発明の第１の目的は部品点数が少なく信頼性の高いレシプロ式容積形機械を提供することである。
また上記従来技術では、組立性からの制約によりピストン部の直径を小さくしたりその直径に対するアーム部の直径の比率を大きくしたりすることが難しく、作動流体の圧力によって摺動部であるアーム部に発生する摺動荷重と摺動面圧の低減に限界があった。このため、特に作動流体が高圧である場合に機械摩擦損失の増大と摺動部の信頼性の低下が発生しやすいという問題があった。本発明の第２の目的は作動流体が高圧であっても機械摩擦損失が小さく摺動部の信頼性が高いレシプロ式容積形機械を提供することである。
【０００４】
さらに高圧の作動流体を適用する容積機械を用いたシステムでは、高圧の作動流体に貯えられたエネルギを絞り機構などの流路抵抗損失によって失わせているので、エネルギ効率の観点から無駄をしているという問題があった。本発明の第３の目的は容積機械を用いたシステムで高圧の作動流体を膨張させて減圧する際にエネルギを回収し、しかも、その回収作業時に発生する機械摩擦損失などのエネルギ損失を小さくして、効率の高いシステムを提供することである。
【０００５】
【課題を解決するための手段】
上記第１の目的を達成するために、往復運動により密閉された作動空間の容積を変化させるピストン部およびそのピストン部の往復運動方向と直角方向であって互いに反対側に伸びる２つのアーム部を有する往復動部材と、作動空間の一部であり前記ピストン部の往復運動を案内する案内部材と、軸方向を同じくして互いに逆方向に回転し、その回転軸から半径方向に偏位した位置でそれぞれアーム部を支持する２つの軸部材と、によりピストン部が往復運動方向の軸線回りに揺動運動しながら往復運動する容積形機械において、バルブ機構のための可動部品を用いずに往復動部材の前記運動を利用して作動空間の容積の増減に応じて、作動流体空間、例えば吸入室空間あるいは吐出室空間と、作動空間とを交互に連通させるための連通経路を構成したものである。
【０００６】
また、上記第２の目的を達成するために、往復運動により密閉された作動空間の容積を変化させるピストン部およびそのピストン部の往復運動方向と直角方向であって互いに反対側に伸びる２つのアーム部を有する往復動部材と、作動空間の一部であり前記ピストン部の往復運動を案内する案内部材と、軸方向を同じくして互いに逆方向に回転し、その回転軸から半径方向に偏位した位置でそれぞれアーム部を支持する２つの軸部材と、によりピストン部が往復運動方向の軸線回りに揺動運動しながら往復運動する容積形機械において、往復動部材を２つのアーム部を持つ部材の中央部にピストン部の形成された部材を挿入することにより形成したものである。
【０００７】
さらに、上記第３の目的を達成するために、往復運動により密閉された作動空間の容積を変化させるピストン部およびそのピストン部の往復運動方向と直角方向であって互いに反対側に伸びる２つのアーム部を有する往復動部材と、作動空間の一部であり前記ピストン部の往復運動を案内する案内部材と、軸方向を同じくして互いに逆方向に回転し、その回転軸から半径方向に偏位した位置でそれぞれアーム部を支持する２つの軸部材と、によりピストン部が往復運動方向の軸線回りに揺動運動しながら往復運動する容積形機械を一構成要素とするシステムとして、圧縮行程と膨張行程を備えたシステムとしたものである。例えば、往復運動部材の両端に設けられたピストン部により作動する２つの作動室の一方を圧縮室、他方を膨張室として構成し、圧縮室で動力を供給して高圧にした作動流体の少なくとも一部を膨張室に導いて動力を回収しながら減圧する容積形機械を一構成要素とし、冷凍空調機器システムにおいては冷凍サイクルの圧縮行程と膨張行程とを行なわせるようにしたものである。
【０００８】
【発明の実施の形態】
以下、本発明の各実施例を図１ないし図１９により説明する。まず第一の実施例を図1乃至図5に基づき説明する。図１乃至図５には本発明の第1の実施例である容積形ポンプを示す。
【０００９】
往復動部材１はその２つのピストン頭部１ａをそれぞれシリンダブロック２の２つの内周円筒面２ａにより案内されて往復運動と該往復運動方向軸線の回りの回転を行なえる様に支持されている。往復動部材１のピストン頭部１ａには、その往復運動方向と直角方向で互いに反対側に突出した２つの円筒状のアーム部１ｂが挿入されてピン１ｃにより固定されている。
２つのアーム部１ｂは、それぞれ球面ブッシュ３の内周円筒面に回転自在に挿入されている。２つの球面ブッシュ３の外周球面部は、それぞれ駆動軸４の駆動アーム部４ａにより駆動軸４の回転軸から半径方向に偏位した位置で球面対偶により支持されている。
【００１０】
その結果、往復動部材の２つのアーム部１ｂと２つの駆動軸４とは相対的な回転と互いの相対的な傾斜方向変化が可能な状態で、駆動軸４の回転軸から偏位した位置で連結されている。駆動軸４の駆動アーム部４ａの径方向反対側には釣合い質量４ｂが形成されている。また２つの駆動軸４はそれぞれ軸受フレーム５の軸受部５ａにより回転支持されている。２つの軸受フレーム５はそれらの軸受部５ａの中心軸が互いに同軸上に配置される様にそれぞれシリンダブロック２にボルトにより固定されている。
シリンダブロック２に形成された２つの内周円筒面２ａ中心軸同士はやはり互いに同軸であり、更に、そのシリンダブロック２に固定された軸受フレーム５の軸受部中心軸とは、互いに直角になっている。
【００１１】
シリンダブロック２に形成された内周円筒面２ａの２つの開口端はそれぞれボルトで固定されたシリンダヘッド６により閉塞されており、往復動部材のピストン頭部１ａとシリンダブロックの内周円筒面２ａとシリンダヘッド６とにより囲まれた作動室７が２つ設けられている。往復動部材のピストン頭部１ａには作動室７への連絡通路１ｄが設けられており、その連絡通路１ｄにはピストン側面の円筒面に２つの開口部を有している。シリンダブロック２には、それぞれ内周円筒面２ａに開口する吸入ポート２ｂおよび吐出ポート２ｃが形成されており、それぞれ内周円筒面２ａの反対側の開口部をシリンダブロック２にボルト等（図示せず）により固定されたカバー８およびカバー９により閉塞されている。吸入ポート２ｂの開口部を閉塞するカバー８にはポンプ外部から挿入された吸入配管１０が連結されており、吐出ポート２ｃの開口部を閉塞するカバー９にはポンプ外部から挿入された吐出配管１１が連結されている。
【００１２】
２つの軸受フレーム５には、それぞれ駆動用モータ１２のステータ部１２ａがボルトで固定され、２つの駆動軸４にはそれぞれ軸受部５ａを挟んで駆動アーム部４ａの反対側に駆動用モータ１２のロータ部１２ｂが固定されている。ロータ部１２ｂには前述の釣合い質量４ｂと逆方向でより小さな遠心力を発生する釣合い質量１３が取付けられている。ステータ部１２ａとロータ部１２ｂとで構成される２つの駆動用モータ１２は同じものであるが、上記の容積形ポンプの全体構成中に互いに対向した姿勢で組込まれており、２つの駆動軸４を互いに逆方向に回転駆動する。本第１の実施例では、図１における右側の駆動用モータ１２と左側の駆動用モータ１２がそれぞれ図の右方向より観て時計方向、反時計方向に回転駆動する構成になっている。なお、２つの軸受フレーム５にはシリンダブロック２への固定ボルトによる共締めでモータカバー１４が固定されている。
【００１３】
以上の構成において２つの駆動軸４が互いに逆方向に回転駆動すると、駆動軸４の回転軸から半径方向に偏位した位置にある２つの球面ブッシュ３の球中心が図１の上下方向には同位相で往復運動し、図１の紙面垂直方向には互いに逆位相で往復運動するため、球面ブッシュ３により２つの円筒状のアーム部１ｂを支持された往復動部材１は、特開平９−７２２７５号公報（図８）にも示す様に往復運動を行ないながらその往復運動方向軸線の回りの揺動を繰り返す。この時、往復動部材１のピストン頭部１ａに形成された連絡通路１ｄのピストン側面開口部は、球面ブッシュ３の中心と駆動軸４の回転軸との偏位量に対して倍のストロークで往復運動行なうが、揺動方向にはピストン外径を２つの球面ブッシュ３の中心間距離で割った比率で揺動運動のストロークが縮小される。すなわち、駆動軸４の回転軸方向から観た時に楕円軌跡１５を描く運動を行なう。
【００１４】
図２ないし図５には、それぞれの断面内に吸入ポート２ｂあるいは吐出ポート２ｃの位置が記載されており、それらに対向した位置にあるピストン頭部１ａの連絡通路１ｄの前記開口部位置を破線にて示し、その楕円軌跡１５を一点鎖線にて示してある。更に、前記の方向に各駆動軸４が回転する時の連絡通路１ｄ開口部の運動方向を矢印にて示す。図２における連絡通路１ｄの開口部とその楕円軌跡１５および吐出ポート２ｃの位置関係は、図１の上部作動室７の容積が減少から増大に転ずる時点でそれまでの連絡通路１ｄによる吐出ポート２ｃと作動室７との導通状態が遮断されたことを示している。図３における連絡通路１ｄの開口部とその楕円軌跡１５および吸入ポート２ｂの位置関係は、上部作動室７の容積が減少から増大に転ずる時点で今後は連絡通路１ｄにより吸入ポート２ｂと作動室７との導通状態が確保されることを示している。図４における連絡通路１ｄの開口部とその楕円軌跡１５および吸入ポート２ｂの位置関係は、図１の下部作動室７の容積が増大から減少に転ずる時点でそれまでの連絡通路１ｄによる吸入ポート２ｂと作動室７との導通状態が遮断されたことを示している。
【００１５】
図５における連絡通路１ｄの開口部とその楕円軌跡１５および吐出ポート２ｃの位置関係は、下部作動室７の容積が増大から減少に転ずる時点で今後は連絡通路１ｄにより吐出ポート２ｃと作動室７との導通状態が確保されることを示している。本第１の実施例においては、吸入配管１０を介して低圧の作動流体（液体）を供給し吸入ポート２ｂを低圧の作動流体空間とし、吐出ポート２ｃを高圧の作動流体空間として吐出配管１１より加圧された作動流体（液体）を排出する構成である。
【００１６】
以上により、本第１の実施例によれば作動室空間の容積が増大している期間に低圧の作動流体空間と該作動室とを連通させ、作動空間の容積が減少している期間に高圧の作動流体空間と該作動室とを連通させることをバルブ機構のための可動部品を用いずに実現できる。したがって、部品点数が少なく生産性と信頼性の高いレシプロ式容積形ポンプを提供することができるという効果がある。また、特開平９−７２２７５号公報に記載されている理由により、レシプロ式容積形ポンプでありながら、駆動トルクの変動や往復質量の慣性力による加振力を極めて小さくすることも可能である。
【００１７】
なお、第１の実施例において吸入配管１０を介して吸入ポート２ｂに高圧の作動液体を供給し、吐出ポート２ｃより吐出配管１１を介して減圧された作動液体を排出する構造変更を行なえば、２つの駆動軸４を出力軸とし実施例１と同様な特長・効果のある液圧モータが得られる。その際に、それらの出力軸で駆動用モータ１２に代わる２つの発電機を駆動して互いに同様な負荷を与えれば、やはり、特開平９−７２２７５号公報に記載されている理由によりレシプロ式容積形液圧モータでありながら、駆動トルクの変動や往復質量の慣性力による加振力を極めて小さくすることが可能である。
【００１８】
次に本発明の第２の実施例を図６乃至図１０に基づき説明する。図６ないし図１０には本発明の第２の実施例である容積形膨張機を示す。各部品の構成は図１ないし図５の第１の実施例とほぼ等しいので、両者の相違点について説明する。シリンダブロック１６にはそれぞれ内周円筒面１６ａに開口する吸入ポート１６ｂおよび吐出ポート１６ｃが形成されているが、吸入ポート１６ｂは吐出ポート１６ｃに比べて小さい。また、カバー１７に連結された吸入配管１８を介して高圧の作動流体（気体）を供給し吸入ポート１６ｂを高圧の作動流体空間とし、吐出ポート１６ｃを低圧の作動流体空間として吐出配管１１より減圧された作動流体（気体）を排出する構成である。以上の構成により、作動室７はその容積が増大する吸入行程の初期期間のみピストン頭部１ａの連絡通路１ｄを介して吸入ポートと導通して高圧の作動流体（気体）を吸入し、吸入行程の後期期間では吸入・吐出の両ポートと遮断された密閉空間となって容積を増大させ内部の作動流体（気体）を膨張させる。吐出ポート１６ｃは十分大きく、作動室７はその容積が減少する吐出行程の全期間でピストン頭部１ａの連絡通路１ｄを介して吐出ポート１６ｃと導通し、膨張して低圧となった作動流体（気体）を吐出する。
【００１９】
往復動部材１は、そのアーム部１ｂが球面ブッシュ３を介して２つの出力軸１９に連結され、それらの出力軸１９のそれぞれにはステータ部２０ａとロータ部２０ｂとで構成される２つの発電機２０のロータ部２０ｂが固定されている。以上の構成により、本実施例２は膨張機として機能して出力軸１８より取出した動力により発電を行なう。
【００２０】
以上により、本第２の実施例によれば作動室空間の容積が増大している期間の初期期間のみ高圧の作動流体空間と該作動室とを連通させ、作動空間の容積が減少している期間に低圧の作動流体空間と該作動室とを連通させることをバルブ機構のための可動部品を用いずに実現できる。したがって、部品点数が少なく生産性と信頼性の高いレシプロ式容積形膨張機を提供することができるという効果がある。また、特開平９−７２２７５号公報に記載されている理由により、レシプロ式容積形膨張機でありながら、駆動トルクの変動や往復質量の慣性力による加振力を極めて小さくすることも可能である。
【００２１】
なお、第２の実施例において吐出配管１１および吐出ポート１６ｃをそれぞれ低圧の作動流体（気体）を吸入するための吸入配管および吸入ポートとして機能させて、吸入ポート１６ｂおよび吸入配管１８をそれぞれ高圧の作動流体（気体）を吐出するための吐出ポートおよび吐出配管として機能させ、更に、出力軸１９を駆動軸として発電機２０に代えて２つの駆動用モータによって図６と逆方向に回転駆動すれば、第２の実施例と同様な特長・効果のある気体圧縮機が得られる。
【００２２】
次に本発明の第３の実施例を図１１及び図１２を用いて説明する。図１１および図１２に本発明の第３の実施例である膨張・圧縮機を示す。第３の実施例は冷媒を作動流体としたものであるが、図１１の全体の側断面図において下部の作動室７は図６と同様な構成の膨張機として機能し、図９および図１０に示した装置と同様に、作動室７は往復動部材２１の連絡通路２１ｆを介してシリンダブロック２２の吸入ポート２２ｃおよび吐出ポート２２ｄと交互に導通する。
【００２３】
一方上部には、往復動部材２１のピストン頭部２１ａとシリンダブロック２２の内周円筒面２２ａとシリンダヘッド２３とにより囲まれた作動室２４が形成されている。このピストン頭部２１ａには吸入ポート２１ｂが形成され、更に、吸入バルブプレート２５がリベット２６により装着されている。リベット２６は吸入バルブプレート２５がピストン頭部２１ａの上端面から浮き上がれるように拘束しており、吸入行程において吸入ポート２１ｂから作動室２４への冷媒ガスの流入を可能にしている。シリンダブロック２２には吸入配管２７が連結されており、本第３の実施例の膨張・圧縮機内部はピストン頭部２１ａの背面に至るまで吸入圧力となって、前記の吸入ポート２１ｂと吸入配管２７とが連絡されている。シリンダヘッド２３には吐出ポート２３ａが形成されており、吐出バルブプレート２８と吐出バルブ押え２９がボルト（図示せず）により固定されている。シリンダヘッド２３は、吐出空間３０を取囲む吐出室カバー３１と共にボルトによりシリンダブロック２２に固定されている。吐出室カバー３１には吐出配管３２が連結されている。この結果、往復動部材２１が往復運動を行なうと作動室２４は圧縮機として機能する。
【００２４】
図１１の容積形機械は、軸動力を発生するエンジンである容積形膨張機部分と駆動軸から供給された動力を消費するマシンである容積形圧縮機部分の両方を有するが、本第３の実施例では圧縮機部分のピストン頭部２１ａの直径は膨張機部分のピストン頭部２１ｂの直径よりも大きく、全体としては動力を消費するマシンとして機能する。したがって駆動軸３３はステータ部３４ａとロータ部３４ｂからなるモータ３４により回転駆動されるが、その理論的な必要動力は上部の容積形圧縮機部分のみを駆動する場合に比べて下部の容積形膨張機部分が発生する動力の分だけ小さくて済む。
【００２５】
図１２に本第３の実施例である膨張・圧縮機を冷凍・空調機器を冷凍サイクルに組込んだ場合のサイクル構成図を示す。中央の膨張・圧縮機３５は図１１の本第３の実施例である膨張・圧縮機である。図中の太線はサイクル配管３６であり太線上の矢印が内部の冷媒の流れ方向を示す。一般的な冷媒および運転条件下では、膨張・圧縮機３５の圧縮機部分で加圧されて高温高圧になった冷媒ガスは吐出配管３２より吐出され、サイクル配管３６を経て凝縮器３７に至りそこで放熱して凝縮し高圧の液冷媒となる。高圧の液冷媒の一部は次にサイクル配管３６を経ての吸入配管１８より膨張・圧縮機３５の膨張機部分に流入し、そこで減圧されながら一部がガス化して全体の容積を増大させ低圧の気液２相状態で吐出配管１１より流出する。その後、サイクル配管３６を経て蒸発器３８に至る。凝縮器３７から出た高圧液冷媒の他の一部は、上記の膨張機を経由する経路とは並列に設けたサイクル配管経路を経由する構成となっているが、その経路に設けられた他の膨張手段３９により減圧されてやはり一部がガス化し低圧の気液２相状態でサイクル配管３６を経て蒸発器３８に至る。なお、膨張手段３９は、従来の冷凍サイクルにおける膨張弁やキャピラリーチューブなどと同様に絞りによるものであり、膨張機のように膨張過程で外部に機械的な仕事をして動力を回収できる構造のものではない。蒸発器３８では前記２つの経路を経由して流入する気液２相の冷媒の液部分が吸熱して蒸発し、全体が低圧ガスになってサイクル配管３６を経て吸入配管２７より膨張・圧縮機３５の内部に流入する。膨張・圧縮機３５の内部に流入した冷媒ガスは圧縮機部分で加圧されて高温高圧になり、再び吐出配管３２より吐出され冷媒の循環の閉ループが構成される。なお、図１２において、凝縮器３７から蒸発器３８に至る2系統の冷媒経路の一方である膨張・圧縮機３５の膨張機部分を経由する経路が無く、冷媒の全量が絞りによる膨張手段３９を通過する場合が、従来技術の冷凍サイクル構成である。
【００２６】
従来技術では、凝縮器から出た高圧液冷媒の全量が膨張手段３９のような絞りを通過する際に圧損としてエネルギーを失い、更にその失われたエネルギーが熱となって冷媒に吸収されるために蒸発器３８において吸熱する能力すなわち冷凍能力を低下させていた。これに対して、本第３の実施例である膨張・圧縮機を組込んだ冷凍サイクルによる冷凍・空調機器では、従来、絞り部の圧損として熱になっていた高圧液冷媒の上記エネルギーの一部を、圧縮機部分と一体となった膨張機部分において機械的なエネルギーとして動力回収でき、圧縮機部分に供給しなければならない動力を低減できるという効果がある。特に本第３の実施例では、圧縮機部分の作動室２４の圧力と膨張機部分の作動室７の圧力は一体となった往復動部材２１のピストン頭部２１ａとピストン頭部２１ｂに作用するため、それらの圧力による往復動部材２１への作用力は一部が荷重の段階で互いに打ち消し合い、往復動部材２１のアーム部２１ｂと球面ブッシュ３との摺動荷重や駆動軸３３と軸受部５ａとの摺動荷重を低減させて機械摩擦損失を低減できるという効果がある。更に、前記のとおり膨張機部分で回収した動力の分だけ冷凍サイクルにおける冷凍能力の低下が回復する（従来技術に対して冷凍能力が増大する）という効果がある。以上の結果、本第３の実施例である膨張・圧縮機を組込んだ冷凍サイクルによる冷凍・空調機器では、より小さな動力でより大きな冷凍能力を得ることができるので冷凍空調機器の効率が向上するという効果がある。なお、本第３の実施例である膨張・圧縮機を組込んだ冷凍・空調機器をヒートポンプとして暖房機器として機能させる場合、暖房能力は通常上記の冷凍能力と膨張・圧縮機３５の消費動力の和であり、上記の冷凍能力の増大分と消費動力の低減分とが打ち消し合ってしまうが、暖房機器としての効率は膨張・圧縮機３５による消費動力の低減分だけ向上する。
【００２７】
図１２のサイクル構成図では、凝縮器３７から蒸発器３８に至る2系統の冷媒経路を構成してある。これを膨張・圧縮機３５の膨張機部分を経由する経路のみとすると、膨張・圧縮機３５における圧縮機作動室２４の吸入容積（最大容積）と膨張機作動室７の吸入容積（吸入ポート２２ｂと導通を遮断された時の容積）との比率が一定値に固定されている場合は、冷凍サイクルのループにおける質量流量の連続性から吸入圧力と吐出圧力との関係が制約され、前記の容積の比率が不適切であったり周囲温度などの運転条件が大きく変化した場合には冷凍サイクルの運転圧力条件が不自然な値になる可能性が懸念される。図１２のサイクル構成図では、凝縮器３７から蒸発器３８に至る他の系統の冷媒経路において膨張手段３９の絞り量を調整して、冷凍サイクルの運転圧力条件を制御できるようにしてある。ただし、前記の各作動室間の吸入容積比率と周囲温度などの運転条件とが良くマッチングしている場合や、膨張・圧縮機３５の各作動室の少なくとも一方における吸入容積が可変であり容量制御が可能である場合などにおいては、上記の膨張・圧縮機３５の膨張機部分を経由する経路以外の経路は必ずしも必要でなく、冷凍サイクルを循環している冷媒の全量から膨張過程での動力を回収できるのでより効率の高い冷凍サイクルを構成できる。また、冷媒の種類や運転圧力によっては凝縮器３７における放熱過程で気体から液体への相変化を伴わないことも起り得るが、その場合の凝縮器３７は放熱器として機能すれば良い。
【００２８】
本発明の第４の実施例を図１３乃至図１７に基づいて説明する。図１３ないし図１６に本発明の第４の実施例である膨張・圧縮機を示す。本第４の実施例は、図１３の全体の側断面図において下部の作動室４１が膨張機として機能し上部の作動室４０が圧縮機として機能する点では図１１の第３の実施例と共通であるが、空気を作動流体としたものであるために膨張・圧縮機全体を容器内に密閉する必要がなく図１１におけるモータカバー１４のような外部ケーシング部材を持たない等の相違点がある。
【００２９】
その他の相違点の１つは、軸受フレーム４２の軸受け部にグリース潤滑方式の玉軸受４３やニードル軸受４４を用いている点である。図１１の第３の実施例における軸受け部がグリースを溶出してしまう冷媒の雰囲気中で使用されるのに対して本第４の実施例では空気雰囲気中での使用となり、グリース密封による潤滑が可能である。
【００３０】
次の相違点は、膨張機として機能する下部作動室４１のピストン頭部４５ｃの直径が圧縮機として機能する上部作動室４０のピストン頭４５ａの直径に近い大きさを持っている点である。図１１の第３の実施例における膨張・圧縮機では、冷凍サイクルに組込まれて使用されるために、膨張機部から排出される冷媒はまだ液冷媒を多量に含んでおりその容積は全量が蒸発してガス化した後に圧縮機に吸入される際の容積に比べて大幅に小さい。したがって、圧縮機部のピストン頭部２１ａの直径に対して膨張機部のピストン頭部２１ｃの直径は大幅に小さい。これに対して空気を作動流体とした本実施例では、圧縮機部で大気圧から加圧した圧縮空気とほぼ同量の気体を膨張機部で大気圧まで膨張させる使い方（図１７）を想定しており、圧縮機部のピストン頭部４５ａの直径に対して膨張機部のピストン頭４５ｃの直径がほぼ同じ大きさになるように設定してある。
【００３１】
これに関連して、往復動部材４５の連絡通路４５ｆの外周円筒面への開口部の楕円軌跡４６が図１４と図１５に示されているが、開口している外周円筒面の半径が大きいために、第１〜第３の実施例における楕円軌跡１５に比べて短軸の長さが大きくなりより膨らんだ楕円となっている。なお、膨張機部分では、高圧ガスは吸入配管４７からシリンダブロック４８に設けられた吸入通路４８ｃと吸入ポート４８ｄおよび連絡通路４５ｆを介して作動室４１へ流入し、その後密閉空間内で膨張して低圧ガスとなり、連絡通路４５ｆからシリンダブロック４８に設けられた吐出ポート４８ｅと吐出通路４８ｆを介して吐出配管４９から流出する。
【００３２】
更に、圧縮機部のピストン頭部４５ａの直径に対して膨張機部のピストン頭４５ｃの直径がほぼ同じ大きさになるように設定してあるので膨張機部における回収動力の大きさが圧縮機部における消費動力の大きさに近くなるため、膨張・圧縮機の全体に供給しなければならない動力が小さくて済み、駆動軸５０を駆動するためのモータ５１は小容量となっている。
【００３３】
次の相違点は、本第４の実施例では圧縮機部の吸入経路が前記第３の実施例と相違しており、外部からの吸入配管から作動室４０までの経路が膨張・圧縮機の駆動機構が収納されて運動する内部空間５２を介さずに構成されている点である。図１３中のＫ−Ｋ断面である図１６に圧縮機部の吸入経路を示す。図１６で左右２つの吸入配管５３からシリンダブロック４８の吸入通路４８ｇに流入した吸入空気は、更に、往復動部材４５のピストン頭部４５aに形成された吸入口４５ｇを通ってピストン頭部４５aの内部空間４５ｈに至り、吸入ポート４５ｂからリベット２６により装着された吸入バルブプレート２５を介して作動室４０に吸入される。シリンダブロック４８の吸入通路４８ｇとピストン頭部４５aの吸入口４５ｇとは、吸入行程の全域にわたり導通している。吸入空気は膨張・圧縮機の内部空間５２を通過しないので、各摺動部の潤滑のために内部空間５２内に封入された潤滑油などが混入することを防止できクリーンな圧縮空気を得ることができる。
【００３４】
更に、本第４の実施例では往復動部材４５のピストン頭部４５ａ、４５ｃとアーム部４５ｄとの結合構造が前記第３の実施例と相違している。本実施例のように作動流体の作動圧力が比較的低い場合には、ピストン頭部４５ａ、４５ｃの直径に対してアーム部４５ｄと球面ブッシュ３の内周との摺動部の直径がかなり小さくても、摺動面圧を実用範囲に抑える設計が可能である。この場合、本実施例のようにピストン頭部４５ａ、４５ｃを貫通してアーム部４５ｄを挿入しナット４５ｅなどにより往復動部材４５として一体に結合する方法が有効である。第１ないし第３の実施例のように２ヵ所のピストン頭部直径の少なくとも一方が、往復動部材のアーム部の摺動部直径に近い場合には、逆に、アーム部の中央部を太くし、これを貫通してピストン頭部を挿入して一体に固定する方法が採用できる。
【００３５】
図１７に本第４の実施例である膨張・圧縮機を燃料電池システムに適用した場合のシステム構成図を示す。右中央部の膨張・圧縮機５６は図１３の本第４の実施例である膨張・圧縮機である。大気中の空気５７は右上のエアクリーナー５８を通過した後に膨張・圧縮機５６の吸入配管５３から流入し、圧縮機部で圧縮された後に吐出配管３２より流出し圧縮空気５９として燃料電池スタック６０のカソード部６０ａに供給される。圧縮空気５９を供給するのは高密度の酸素をカソード部６０ａに供給することで燃料電池スタック６０の高効率化、小型化が図れるためである。一方燃料電池スタック６０のアノード部６０ｂには水素または水素を含有するガスである燃料ガス６１が供給される。カソード部６０ａとアノード部６０ｂの間にはイオン透過膜６０ｃが配されており、アノード部６０ｂに供給された水素または水素を含有するガスから発生した水素イオン（＋イオン）がこのイオン透過膜６０ｃを透過し、カソード部６０ａに供給された酸素から発生する酸素イオン（−イオン）と結合して水分を生成する過程で、燃料電池スタック６０からカソード部６０ａとアノード部６０ｂとを電極として電力６０ｄを取り出すことができる。アノード部６０ｂに供給された燃料ガス６１は、水素を消費された後に排気ガス６２として燃料電池スタック６０から排出され、改質器（図示せず）の熱源などに利用される。カソード部６０ａに供給された圧縮空気５６は酸素の一部を消費されるが新たに生成された水分が追加され、高圧排空気６３として燃料電池スタック６０から排出される。その後、膨張・圧縮機５６に吸入配管４７から再流入し、膨張機部で膨張した後に吐出配管４９より流出して低圧排空気６４として最終的には大気中に放出される。
【００３６】
なお、膨張機部分では、高圧ガスはからシリンダブロック４８に設けられた吸入通路４８ｃと吸入ポート４８ｄおよび連絡通路４５ｆを介して作動室４１へ流入し、その後密閉空間内で膨張して低圧ガスとなり、連絡通路４５ｆからシリンダブロック４８に設けられた吐出ポート４８ｅと吐出通路４８ｆを介して吐出配管４９から流出する。
【００３７】
本第４の実施例の膨張・圧縮機５６を組込んだ燃料電池システムでは、圧縮空気５９を供給するために必要な動力の一部に動力回収機構で回収した動力を利用するので、外部から新規に供給しなければならない正味の動力を低減することができる。また、圧縮機部分と膨張機部分とが独立している通常の動力回収機構では圧縮機部分と膨張機部分のそれぞれで機械摩擦損失が発生して合計の機械摩擦損失が大きくなるのに対して、本第４の実施例では第３の実施例と同様に共通の部品である往復動部材４５に作用する荷重の段階で打消し合わせて各摺動部の摺動荷重を低減し、機械摩擦損失をむしろ低減させている。この事により膨張・圧縮機５６の効率が高くなり、これを用いた燃料電池システム全体の効率荷重が一層高くなるという効果がある。
【００３８】
本発明の第５の実施例を図１８に基づいて説明する。図１８は、本発明の第５の実施例である圧縮機を示す。第５の実施例は図１８の全体の側断面図において中央の上部と下部に形成された２つの作動室６５はいずれも圧縮機の作動室として機能する。すなわち、本第５の実施例は２気筒の圧縮機である。作動流体は二酸化炭素であり、作動室内の圧力は従来のフロン系冷媒に対して４〜５倍と非常に高圧になる。その反面、冷媒の単位体積当たりの冷凍能力も４〜５倍となり、同一の冷凍能力を発生させる圧縮機の行程容積は小さくて良い。図１８の圧縮機では、往復動部材６６における２つのピストント頭部６６ａの直径のみを小さくすることで行程容積を小さくしてあり、駆動アーム部６７ａに装着された球面ブッシュ３の球心が駆動軸６７の回転軸から偏位している量を減少させることにより往復動部材６６の往復運動のストロークを減らすことはしていない。また、従来のフロン系冷媒で同一冷凍能力を持つ２気筒圧縮機に比べて、往復動部材６６のアーム部６６ｂと球面ブッシュ３との摺動部の径や軸方向長さ、および、駆動軸６７と軸受フレーム６８との摺動部の径や軸方向長さなどは同等の大きさを確保しており、摺動部の受圧面積は従来と同等である。このような設計は、本発明で採用している容積形機械の機構では作動室の圧力が直接作用する往復動部材６６の内部に摺動部を持たないために、ピストン部の径と摺動部の大きさなどの寸法諸元とを互いの制約なしにそれぞれ独立して設定できることにより可能になっている。なお、従来のクランクスライダ機構をによるレシプロ機構では、コンロッドの小端部にあるピストンピンが作動室の圧力が直接作用するピストンの内部にあるため、ピストン径を小さくした時にコンロッドとの摺動部の受圧面積を従来と同等に維持するのが困難となる。また、ローリングピストン方式などのロータリ圧縮機では、作動室の圧力が直接作用する面積を低減するために円筒形状ロータ（ピストン）の幅または径を縮小すると、ロータの内部にあるシャフトの偏心ピン部とロータ内周面との摺動部の受圧面積を従来と同等に維持するのが難しい。
【００３９】
作動流体である二酸化炭素は、シリンダブロック６９に取付けられた吸入配管７０より圧縮機の内部空間７１に流入し、往復動部材６６に設けた吸入口６６ｄからピストント頭部６６ａの内部空間６６ｅに至り、吸入ポート６６ｆからリベット７２でピストント頭部６６ａに装着された吸入バルブプレート７３を介して作動室６５に吸入される。作動室６５で圧縮された後に、シリンダヘッド７４に形成された吐出ポート７４ａより吐出バルブプレート７５と吐出バルブ押え７６を介して吐出空間７７に吐出される。吐出バルブプレート７５と吐出バルブ押え７６はボルト（図示せず）によりシリンダヘッド７４に固定されている。シリンダヘッド７４は吐出空間７７を取囲む吐出室カバー７８と共にボルトによりシリンダブロック６９に固定されている。吐出室カバー７８には吐出配管７９が連結されており、高圧の作動流体は最終的にここから圧縮室外へ流出する。
【００４０】
本第５の実施例では、作動流体が二酸化炭素であるため往復動部材６６の２つのピストン頭部６６ａは径がいずれも小さく、それらが挿入されるシリンダブロック６９の２つの内周円筒面６９ａも径が小さい。往復動部材６６のピストン頭部６６ａに内周円筒面６９ａの径より太い部分を形成すると、組立ての際にシリンダブロック６９の内周円筒面６９ａに挿入できなくなる。一方で、内周円筒面６９ａの径に対するアーム部６６ｂの径の比率は従来冷媒の場合に比べて相対的に大きくなっており、往復動部材６６を組立てる際に図１３のようにピストン頭部６６ａに形成した穴にアーム部６６ｂを挿入する構造では強度が確保できない。したがって、本第５の実施例ではアーム部６６ｂの中央に太い部分を形成し、これに設けた穴にピストン頭部６６ａを挿入してピン６６ｃで固定する構造を採用している。
【００４１】
本第５の実施例では、作動流体が二酸化炭素であることと２つの作動室６５にて圧縮仕事を行なう２気筒構造であるために、各作動室６５の行程容積が小さい割には消費動力が大きいので駆動用モータ８０は大きく、これを囲んで密閉空間を形成するモータカバー８１も大きい。
【００４２】
本第５の実施例によれば、まず二酸化炭素などの高圧の作動ガスを用いた場合でも、その圧力をうける部材である往復動部材６６のピストン頭部６６ａの径を縮小する際の制約条件が無いので摺動部の荷重を増大させぬ設計が容易であり、機械摩擦損失を増大させない設計が可能である。また、その際に軸受部などの摺動部の面積を縮小する必要が無いので摺動部の摺動面圧を増大させぬ設計が容易であり、信頼性を低下させない設計が可能である。また、主要部品である往復動部材６６において、ピストン頭部６６ａを縮小してもアーム部６６ｂとの結合部の強度を十分確保することができる。すなわち、二酸化炭素のような非常に高圧であるが自然界の元々存在し環境への負荷の小さい作動ガスを冷媒とした冷凍空調システムの実用化が容易になる。
【００４３】
【発明の効果】
本発明によれば、レシプロ形容積形機械でバルブ機構のための可動部品を不要とできその生産性と信頼性が向上するという効果がある。
また本発明によれば、容積形圧縮機で軸受等の摺動部の大きさや受圧面積を減少させること無しに作動室の受圧面積を低減できるので、２酸化炭素などの超高圧冷媒を作動流体としても摺動部の荷重や摺動面圧を増大させぬことが可能であり信頼性や機械効率の大幅な低下を防止できるという効果がある。
更に本発明によれば、圧縮機と膨張機とを一体化した容積形機械の各摺動部に作用する荷重が低減できるので機械効率が向上し、膨張機による効率的な動力回収が可能になり、動力回収機構を組込んだ冷凍サイクルなどのシステム全体の効率が大きく向上するという効果がある。
【図面の簡単な説明】
【図１】本発明の第1の実施例であるポンプの全体の側断面図。
【図２】図１におけるＡ−Ａ断面図。
【図３】図１におけるＢ−Ｂ断面図。
【図４】図１におけるＣ−Ｃ断面図。
【図５】図１におけるＤ−Ｄ断面図。
【図６】本発明の第２の実施例である膨張機の全体の側断面図。
【図７】図６におけるＥ−Ｅ断面図。
【図８】図６におけるＦ−Ｆ断面図。
【図９】図６におけるＧ−Ｇ断面図。
【図１０】図６におけるＨ−Ｈ断面図。
【図１１】本発明の第３の実施例である冷媒を作動流体とした膨張・圧縮機の全体の側断面図。
【図１２】本発明の第３の実施例である膨張・圧縮機を冷凍・空調機器に適用した場合の冷凍サイクル構成図。
【図１３】本発明の第４の実施例である空気用の膨張・圧縮機の全体の側断面図。
【図１４】図１３におけるＩ−Ｉ断面図。
【図１５】図１３におけるＪ−Ｊ断面図。
【図１６】図１３におけるＫ−Ｋ断面図。
【図１７】本発明の第４の実施例である膨張・圧縮機を燃料電池システムに適用した場合のシステム構成図。
【図１８】は本発明の第５の実施例である圧縮機の全体の側断面図。
【符号の説明】
１…往復動部材、１ａ…ピストン頭部、１ｂ…アーム部、１ｃ…ピン、１ｄ…連絡通路、２…シリンダブロック、２ａ…内周円筒面、２ｂ…吸入ポート、２ｃ…吐出ポート、３…球面ブッシュ、４…駆動軸、４ａ…駆動アーム部、４ｂ…釣合い質量、５…軸受フレーム、５ａ…軸受部、６…シリンダヘッド、７…作動室、８…カバー、９…カバー、１０…吸入配管、１１…吐出配管、１２…駆動用モータ、１２ａ…ステータ部、１２ｂ…ロータ部、１３…釣合い質量、１４…モータカバー、１５…楕円軌跡、１６…シリンダブロック、１６ａ…内周円筒面、１６ｂ…吸入ポート、１６ｃ…吐出ポート、１７…カバー、１８…吸入配管、１９…出力軸、１９ａ…出力アーム部、１９ｂ…釣合い質量、２０…発電機、２０ａ…ステータ部、２０ｂ…ロータ部、２１…往復動部材、２１ａ…ピストン頭部、２１ｂ…吸入ポート、２１ｃ…ピストン頭部、２１ｄ…アーム部、２１ｅ…ピン、２１ｆ…連絡通路、２２…シリンダブロック、２２ａ…内周円筒面、２２ｂ…内周円筒面、２２ｃ…吸入ポート、２２ｄ…吐出ポート、２３…シリンダヘッド、２３ａ…吐出ポート、２４…作動室、２５…吸入バルブプレート、２６…リベット、２７…吸入配管、２８…吐出バルブプレート、２９…吐出バルブ押え、３０…吐出空間、３１…吐出室カバー、３２…吐出配管、３３…駆動軸、３３ａ…駆動アーム部、３３ｂ…釣合い質量、３４…駆動用モータ、３４ａ…ステータ部、３４ｂ…ロータ部、３５…膨張・圧縮機、３６…サイクル配管、３７…凝縮器、３８…蒸発器、３９…膨張手段、４０…作動室、４１…作動室、４２…軸受フレーム、４３…玉軸受、４４…ニードル軸受、４５…往復動部材、４５ａ…ピストン頭部、４５ｂ…吸入ポート、４５ｃ…ピストン頭部、４５ｄ…アーム部、４５ｅ…ナット、４５ｆ…連絡通路、４５ｇ…吸入口、４５ｈ…内部空間、４６…楕円軌跡、４７…吸入配管、４８…シリンダブロック、４８ｃ…吸入通路、４８ｄ…吸入ポート、４８ｅ…吐出ポート、４８ｆ…吐出通路、４８ｇ…吸入通路、４９…吐出配管、５０…駆動軸、５１…モータ、５２…内部空間、５３…吸入配管、５４…シリンダヘッド、５５…釣合い質量、５６…膨張・圧縮機、５７…空気、５８…エアクリーナー、５９…圧縮空気、６０…燃料電池スタック、６０ａ…カソード部、６０ｂ…アノード部、６０ｃ…イオン透過膜、６０ｄ…電力、６１…燃料ガス、６２…排気ガス、６３…高圧排空気、６４…低圧排空気、６５…作動室、６６…往復動部材、６６ａ…ピストント頭部、６６ｂ…アーム部、６６ｃ…ピン、６６ｄ…吸入口、６６ｅ…内部空間、６６ｆ…吸入ポート、６７…駆動軸、６７ａ…駆動アーム部、６７ｂ…釣合い質量、６８…軸受フレーム、６８ａ…軸受部、６９…シリンダブロック、６９ａ…内周円筒面、７０…吸入配管、７１…内部空間、７２…リベット、７３…吸入バルブプレート、７４…シリンダヘッド、７４ａ…吐出ポート、７５…吐出バルブプレート、７６…吐出バルブ押え、７７…吐出空間、７８…吐出室カバー、７９…吐出配管、８０…駆動用モータ、８０ａ…ステータ部、８０ｂ…ロータ部、８１…モータカバー、８２…釣合い質量。[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a volumetric machine and a technology for improving efficiency of a refrigeration air-conditioning apparatus and a fuel cell system using the volumetric machine.
[0002]
[Prior art]
In a conventional reciprocating positive displacement machine, the working chamber space communicates alternately with the suction chamber space or the discharge chamber space in accordance with the increase or decrease of the volume as in the compressor described in FIG. 7 of JP-A-9-72275. Therefore, a valve mechanism composed of movable parts has been used.
Further, the reciprocating member in the compressor described in FIG. 7 of JP-A-9-72275 has been formed by inserting an arm portion at the center of the piston portion.
[0003]
[Problems to be solved by the invention]
In the prior art, there is a problem that the number of moving parts constituting the reciprocating positive displacement machine increases and productivity and reliability are lowered. A first object of the present invention is to provide a reciprocating positive displacement machine having a small number of parts and high reliability.
In the above prior art, it is difficult to reduce the diameter of the piston part or increase the ratio of the diameter of the arm part to the diameter due to restrictions on assembling, and the arm part which is a sliding part by the pressure of the working fluid. There was a limit to the reduction of sliding load and sliding surface pressure. For this reason, there is a problem that an increase in mechanical friction loss and a decrease in the reliability of the sliding portion are likely to occur particularly when the working fluid is at a high pressure. A second object of the present invention is to provide a reciprocating positive displacement machine having a small mechanical friction loss and a high reliability of a sliding portion even when the working fluid is at a high pressure.
[0004]
Furthermore, in a system using a positive displacement working fluid that applies high-pressure working fluid, the energy stored in the high-pressure working fluid is lost due to loss of flow path resistance such as a throttle mechanism, which is wasted from the viewpoint of energy efficiency. There was a problem of being. A third object of the present invention is to recover energy when a high-pressure working fluid is expanded and decompressed in a system using a positive displacement machine, and to reduce energy loss such as mechanical friction loss generated during the recovery operation. It is to provide a highly efficient system.
[0005]
[Means for Solving the Problems]
In order to achieve the first object, a piston part that changes the volume of a working space sealed by a reciprocating motion and two arm parts extending in opposite directions to each other in a direction perpendicular to the reciprocating direction of the piston part are provided. A reciprocating member having a guide member that guides the reciprocating motion of the piston portion that is a part of the working space, and a position that rotates in the opposite directions in the same axial direction and is displaced in the radial direction from the rotating shaft In a positive displacement machine in which the piston part reciprocates while swinging around the axis in the reciprocating direction by two shaft members each supporting the arm part, and reciprocating without using a movable part for the valve mechanism A communication path for alternately connecting the working fluid space, for example, the suction chamber space or the discharge chamber space, and the working space according to the increase or decrease of the volume of the working space using the movement of the member. It is those that you configured.
[0006]
In order to achieve the second object, a piston part that changes the volume of the working space sealed by the reciprocating motion, and two arms that extend in the direction perpendicular to the reciprocating direction of the piston part and opposite to each other A reciprocating member having a portion, a guide member that is part of the working space and guiding the reciprocating motion of the piston portion, and rotating in the opposite directions with the same axial direction, and deviating from the rotating shaft in the radial direction In a positive displacement machine in which the piston part reciprocates while swinging around an axis in the reciprocating direction by means of two shaft members that respectively support the arm part at the position, a member having the reciprocating member as two arm parts It is formed by inserting a member in which a piston portion is formed in the central portion of the.
[0007]
Furthermore, in order to achieve the third object, a piston portion that changes the volume of the working space sealed by the reciprocating motion, and two arms that extend perpendicular to the reciprocating direction of the piston portion and opposite to each other A reciprocating member having a portion, a guide member that is part of the working space and guiding the reciprocating motion of the piston portion, and rotating in the opposite directions with the same axial direction, and deviating from the rotating shaft in the radial direction The compression stroke and expansion as a system consisting of two shaft members that respectively support the arm portion at each position and a positive displacement machine in which the piston portion reciprocates while swinging around the axis in the reciprocating direction. It is a system with a process. For example, one of two working chambers that are operated by piston portions provided at both ends of a reciprocating member is configured as a compression chamber and the other as an expansion chamber, and at least one of the working fluids that are pressurized by supplying power in the compression chamber. One component is a positive displacement machine that guides the part to the expansion chamber and recovers the power, and in the refrigeration air conditioning system, the compression stroke and expansion stroke of the refrigeration cycle are performed.
[0008]
DETAILED DESCRIPTION OF THE INVENTION
Embodiments of the present invention will be described below with reference to FIGS. First, a first embodiment will be described with reference to FIGS. 1 to 5 show a positive displacement pump according to a first embodiment of the present invention.
[0009]
The reciprocating member 1 is supported so that the two piston heads 1a are guided by the two inner peripheral cylindrical surfaces 2a of the cylinder block 2 and can reciprocate and rotate around the reciprocating direction axis. . Two cylindrical arm portions 1b protruding in opposite directions perpendicular to the reciprocating direction are inserted into the piston head 1a of the reciprocating member 1 and fixed by pins 1c.
The two arm portions 1b are rotatably inserted into the inner peripheral cylindrical surface of the spherical bush 3 respectively. The outer spherical surface portions of the two spherical bushes 3 are supported by spherical pairs at positions displaced in the radial direction from the rotation axis of the drive shaft 4 by the drive arm portions 4a of the drive shaft 4, respectively.
[0010]
As a result, the two arm portions 1b of the reciprocating member and the two drive shafts 4 are displaced from the rotation axis of the drive shaft 4 in a state in which the relative rotation and the relative inclination direction change are possible. It is connected with. On the opposite side in the radial direction of the drive arm portion 4a of the drive shaft 4, a balance mass 4b is formed. The two drive shafts 4 are rotatably supported by bearing portions 5a of the bearing frame 5, respectively. The two bearing frames 5 are fixed to the cylinder block 2 with bolts so that the central axes of the bearing portions 5a are arranged coaxially with each other.
The central axes of the two inner peripheral cylindrical surfaces 2a formed in the cylinder block 2 are also coaxial with each other, and are further perpendicular to the central axis of the bearing portion of the bearing frame 5 fixed to the cylinder block 2. Yes.
[0011]
Two open ends of the inner peripheral cylindrical surface 2a formed in the cylinder block 2 are closed by a cylinder head 6 fixed by bolts, respectively, and the piston head 1a of the reciprocating member and the inner peripheral cylindrical surface 2a of the cylinder block. Two working chambers 7 surrounded by the cylinder head 6 are provided. The piston head 1a of the reciprocating member is provided with a communication passage 1d to the working chamber 7, and the communication passage 1d has two openings on the cylindrical surface of the piston side surface. The cylinder block 2 is formed with a suction port 2b and a discharge port 2c that open to the inner peripheral cylindrical surface 2a, respectively, and an opening on the opposite side of the inner peripheral cylindrical surface 2a is connected to the cylinder block 2 with bolts (not shown). The cover 8 and the cover 9 fixed by A suction pipe 10 inserted from the outside of the pump is connected to the cover 8 that closes the opening of the suction port 2b, and a discharge pipe 11 that is inserted from the outside of the pump to the cover 9 that closes the opening of the discharge port 2c. Are connected.
[0012]
The stator parts 12a of the drive motor 12 are fixed to the two bearing frames 5 with bolts, respectively. The two drive shafts 4 have the bearing parts 5a sandwiched between the drive arm parts 4a on the opposite side of the drive arm part 4a. The rotor part 12b is fixed. The rotor portion 12b is provided with a balance mass 13 that generates a smaller centrifugal force in the opposite direction to the balance mass 4b. The two drive motors 12 constituted by the stator portion 12a and the rotor portion 12b are the same, but are incorporated in the overall configuration of the positive displacement pump in a posture facing each other, and the two drive shafts 4 Are rotated in opposite directions. In the first embodiment, the right drive motor 12 and the left drive motor 12 in FIG. 1 are configured to be driven to rotate clockwise and counterclockwise as viewed from the right direction in the drawing. Note that a motor cover 14 is fixed to the two bearing frames 5 by joint fastening to the cylinder block 2 with fixing bolts.
[0013]
In the above configuration, when the two drive shafts 4 are rotationally driven in directions opposite to each other, the spherical centers of the two spherical bushes 3 that are displaced in the radial direction from the rotational shaft of the drive shaft 4 are in the vertical direction in FIG. A reciprocating member 1 in which two cylindrical arm portions 1b are supported by a spherical bush 3 because they reciprocate in the same phase and reciprocate in mutually opposite phases in the direction perpendicular to the paper surface of FIG. As shown in Japanese Patent No. 72275 (FIG. 8), the reciprocating motion is repeated around the axis of the reciprocating motion while reciprocating. At this time, the piston side surface opening of the communication passage 1d formed in the piston head 1a of the reciprocating member 1 has a stroke double the amount of deviation between the center of the spherical bush 3 and the rotation shaft of the drive shaft 4. Although the reciprocating motion is performed, the stroke of the swinging motion is reduced in the swinging direction by a ratio obtained by dividing the piston outer diameter by the distance between the centers of the two spherical bushings 3. That is, a motion of drawing an elliptical locus 15 when viewed from the direction of the rotation axis of the drive shaft 4 is performed.
[0014]
2 to 5, the positions of the suction port 2b or the discharge port 2c are shown in the respective cross sections, and the position of the opening of the communication passage 1d of the piston head 1a at the position facing them is indicated by a broken line. The elliptical locus 15 is indicated by a one-dot chain line. Furthermore, the direction of movement of the opening portion of the communication passage 1d when each drive shaft 4 rotates in the above direction is indicated by an arrow. The positional relationship between the opening of the communication passage 1d in FIG. 2 and its elliptical locus 15 and the discharge port 2c is the discharge port 2c by the communication passage 1d until then when the volume of the upper working chamber 7 in FIG. And the conduction state between the working chamber 7 and the working chamber 7 is interrupted. The positional relationship between the opening of the communication passage 1d in FIG. 3 and its elliptical locus 15 and the suction port 2b is determined so that the suction port 2b and the working chamber 7 will be connected by the communication passage 1d when the volume of the upper working chamber 7 changes from decreasing to increasing. It is shown that a conduction state is secured. The positional relationship between the opening of the communication passage 1d in FIG. 4 and its elliptical locus 15 and the suction port 2b is the same as that of the suction port 2b by the communication passage 1d until then when the volume of the lower working chamber 7 in FIG. And the conduction state between the working chamber 7 and the working chamber 7 is interrupted.
[0015]
The positional relationship between the opening of the communication passage 1d in FIG. 5 and its elliptical locus 15 and the discharge port 2c is as follows. When the volume of the lower working chamber 7 changes from increase to decrease, the discharge port 2c and the operation chamber 7 are now connected by the communication passage 1d. It is shown that a conduction state is secured. In the first embodiment, a low-pressure working fluid (liquid) is supplied through the suction pipe 10, the suction port 2b is used as a low-pressure working fluid space, and the discharge port 2c is used as a high-pressure working fluid space from the discharge pipe 11. It is the structure which discharges the pressurized working fluid (liquid).
[0016]
As described above, according to the first embodiment, the low-pressure working fluid space and the working chamber communicate with each other while the volume of the working chamber space is increasing, and the high pressure is generated when the volume of the working space is decreasing. It is possible to establish communication between the working fluid space and the working chamber without using a movable part for the valve mechanism. Therefore, there is an effect that it is possible to provide a reciprocating positive displacement pump with a small number of parts and high productivity and reliability. Further, for the reason described in Japanese Patent Laid-Open No. 9-72275, it is possible to extremely reduce the excitation force due to fluctuations in driving torque and inertial force of reciprocating mass, even though it is a reciprocating positive displacement pump.
[0017]
In the first embodiment, if a structural change is made such that a high-pressure working liquid is supplied to the suction port 2b via the suction pipe 10 and the decompressed working liquid is discharged from the discharge port 2c via the discharge pipe 11, A hydraulic motor having the same features and effects as in the first embodiment can be obtained by using the two drive shafts 4 as output shafts. At that time, if two generators instead of the drive motor 12 are driven by these output shafts and the same load is applied to each other, the reciprocating volume is also described for the reason described in Japanese Patent Laid-Open No. 9-72275. Even though it is a type hydraulic motor, it is possible to extremely reduce the excitation force due to the fluctuation of the driving torque and the inertial force of the reciprocating mass.
[0018]
Next, a second embodiment of the present invention will be described with reference to FIGS. 6 to 10 show a positive displacement expander according to a second embodiment of the present invention. Since the configuration of each component is almost the same as that of the first embodiment shown in FIGS. 1 to 5, the difference between them will be described. The cylinder block 16 is formed with a suction port 16b and a discharge port 16c that open to the inner peripheral cylindrical surface 16a. The suction port 16b is smaller than the discharge port 16c. Further, a high-pressure working fluid (gas) is supplied through a suction pipe 18 connected to the cover 17, the suction port 16 b is used as a high-pressure working fluid space, and the discharge port 16 c is used as a low-pressure working fluid space, and the pressure is reduced from the discharge pipe 11. The discharged working fluid (gas) is discharged. With the above configuration, the working chamber 7 is connected to the suction port through the communication passage 1d of the piston head 1a only during the initial period of the suction stroke in which the volume increases, and sucks the high-pressure working fluid (gas). In the latter period, the internal working fluid (gas) is expanded by increasing the volume by forming a sealed space that is blocked from both the suction and discharge ports. The discharge port 16c is sufficiently large, and the working chamber 7 is electrically connected to the discharge port 16c through the communication passage 1d of the piston head 1a during the entire discharge stroke in which the volume of the working chamber 7 is reduced. Gas).
[0019]
The reciprocating member 1 has an arm portion 1b connected to two output shafts 19 via a spherical bush 3, and each of the output shafts 19 includes two power generation units each including a stator portion 20a and a rotor portion 20b. The rotor part 20b of the machine 20 is fixed. With the above configuration, the second embodiment functions as an expander and generates power using the power extracted from the output shaft 18.
[0020]
As described above, according to the second embodiment, the high-pressure working fluid space is communicated with the working chamber only in the initial period in which the working chamber space is increasing, and the working space volume is reduced. The low-pressure working fluid space and the working chamber can be communicated with each other without using a movable part for the valve mechanism. Therefore, there is an effect that it is possible to provide a reciprocating positive displacement expander with a small number of parts and high productivity and reliability. Further, for the reason described in Japanese Patent Laid-Open No. 9-72275, it is possible to extremely reduce the excitation force due to fluctuations in driving torque and inertial force of reciprocating mass, even though it is a reciprocating positive displacement expander. .
[0021]
In the second embodiment, the discharge pipe 11 and the discharge port 16c function as a suction pipe and a suction port for sucking low-pressure working fluid (gas), respectively. If it functions as a discharge port and a discharge pipe for discharging the working fluid (gas), and is driven to rotate in the opposite direction to FIG. 6 by two drive motors instead of the generator 20 with the output shaft 19 as a drive shaft. A gas compressor having the same features and effects as those of the second embodiment can be obtained.
[0022]
Next, a third embodiment of the present invention will be described with reference to FIGS. 11 and 12 show an expander / compressor according to a third embodiment of the present invention. In the third embodiment, a refrigerant is used as a working fluid. In the entire side sectional view of FIG. 11, the lower working chamber 7 functions as an expander having the same configuration as in FIG. Similarly to the apparatus shown in FIG. 1, the working chamber 7 is alternately connected to the suction port 22c and the discharge port 22d of the cylinder block 22 through the communication passage 21f of the reciprocating member 21.
[0023]
On the other hand, a working chamber 24 surrounded by a piston head 21 a of the reciprocating member 21, an inner peripheral cylindrical surface 22 a of the cylinder block 22, and a cylinder head 23 is formed. A suction port 21b is formed in the piston head 21a, and a suction valve plate 25 is mounted by a rivet 26. The rivet 26 is constrained so that the suction valve plate 25 is lifted from the upper end surface of the piston head 21a, and allows refrigerant gas to flow from the suction port 21b to the working chamber 24 in the suction stroke. A suction pipe 27 is connected to the cylinder block 22, and the inside of the expansion / compressor of the third embodiment becomes a suction pressure up to the back surface of the piston head 21a, so that the suction port 21b and the suction pipe are connected. 27 is contacted. A discharge port 23a is formed in the cylinder head 23, and a discharge valve plate 28 and a discharge valve presser 29 are fixed by bolts (not shown). The cylinder head 23 is fixed to the cylinder block 22 with bolts together with a discharge chamber cover 31 that surrounds the discharge space 30. A discharge pipe 32 is connected to the discharge chamber cover 31. As a result, when the reciprocating member 21 reciprocates, the working chamber 24 functions as a compressor.
[0024]
The positive displacement machine of FIG. 11 has both a positive displacement expander portion that is an engine that generates shaft power and a positive displacement compressor portion that is a machine that consumes power supplied from a drive shaft. In the embodiment, the diameter of the piston head portion 21a of the compressor portion is larger than the diameter of the piston head portion 21b of the expander portion, and functions as a machine that consumes power as a whole. Therefore, the drive shaft 33 is rotationally driven by the motor 34 composed of the stator portion 34a and the rotor portion 34b, but the theoretical required power thereof is lower volumetric expansion compared to the case where only the upper volumetric compressor portion is driven. The power can be reduced by the amount of power generated by the machine part.
[0025]
FIG. 12 shows a cycle configuration diagram in the case where the expansion / compressor according to the third embodiment is incorporated in the refrigeration / air conditioning apparatus in the refrigeration cycle. A central expansion / compression machine 35 is the expansion / compression machine according to the third embodiment of FIG. The thick line in the figure is the cycle piping 36, and the arrow on the thick line indicates the flow direction of the internal refrigerant. Under general refrigerant and operating conditions, the refrigerant gas that has been pressurized at the compressor portion of the expansion / compressor 35 to become high temperature and high pressure is discharged from the discharge pipe 32 and reaches the condenser 37 through the cycle pipe 36. Dissipates heat and condenses to form a high-pressure liquid refrigerant. Next, a part of the high-pressure liquid refrigerant flows into the expander portion of the expansion / compressor 35 from the suction pipe 18 through the cycle pipe 36, and a part of the high-pressure liquid refrigerant is gasified while being decompressed there. Out of the discharge pipe 11 in a gas-liquid two-phase state. Then, it reaches the evaporator 38 through the cycle pipe 36. The other part of the high-pressure liquid refrigerant that has come out of the condenser 37 is configured to pass through a cycle piping path provided in parallel with the path that passes through the expander. The gas is partially decompressed by the expansion means 39 and is partially gasified to reach the evaporator 38 via the cycle pipe 36 in a low-pressure gas-liquid two-phase state. The expansion means 39 is based on a throttle like an expansion valve or a capillary tube in a conventional refrigeration cycle, and has a structure capable of recovering power by performing mechanical work outside in the expansion process like an expander. It is not a thing. In the evaporator 38, the liquid part of the gas-liquid two-phase refrigerant that flows in through the two paths absorbs heat and evaporates, and the whole becomes low-pressure gas, passes through the cycle pipe 36, and expands and compresses from the suction pipe 27. 35 flows into the interior. Refrigerant gas that has flowed into the expansion / compressor 35 is pressurized at the compressor portion to become high temperature and pressure, and is discharged again from the discharge pipe 32 to form a closed loop of refrigerant circulation. In FIG. 12, there is no path through the expander portion of the expansion / compressor 35, which is one of the two refrigerant paths from the condenser 37 to the evaporator 38, and the expansion means 39 is configured so that the entire amount of refrigerant is reduced. The case of passing is the prior art refrigeration cycle configuration.
[0026]
In the prior art, when the entire amount of high-pressure liquid refrigerant that has come out of the condenser passes through a throttle such as the expansion means 39, it loses energy as pressure loss, and the lost energy is further absorbed by the refrigerant as heat. In addition, the ability to absorb heat in the evaporator 38, that is, the refrigerating capacity, was reduced. On the other hand, in the refrigeration / air-conditioning equipment using the refrigeration cycle incorporating the expansion / compressor according to the third embodiment, the energy of the high-pressure liquid refrigerant that has conventionally been heated as the pressure loss of the throttle portion is as follows. As a result, power can be recovered as mechanical energy in the expander portion integrated with the compressor portion, and power that must be supplied to the compressor portion can be reduced. In particular, in the third embodiment, the pressure in the working chamber 24 in the compressor portion and the pressure in the working chamber 7 in the expander portion act on the piston head portion 21a and the piston head portion 21b of the reciprocating member 21 integrated. Therefore, part of the acting force on the reciprocating member 21 caused by these pressures cancels each other out at the stage of the load, and the sliding load between the arm portion 21b of the reciprocating member 21 and the spherical bush 3 or the drive shaft 33 and the bearing portion. There is an effect that the mechanical friction loss can be reduced by reducing the sliding load with 5a. Furthermore, as described above, there is an effect that the decrease in the refrigeration capacity in the refrigeration cycle is recovered by the amount of power recovered in the expander portion (the refrigeration capacity is increased as compared with the prior art). As a result of the above, the refrigeration / air-conditioning equipment using the refrigeration cycle incorporating the expansion / compressor according to the third embodiment can increase the refrigeration / air-conditioning equipment efficiency by obtaining a larger refrigeration capacity with less power. There is an effect of doing. When the refrigeration / air-conditioning apparatus incorporating the expansion / compressor according to the third embodiment is caused to function as a heating device as a heat pump, the heating capacity is usually the above-described refrigeration capacity and the power consumption of the expansion / compressor 35. The increase in the refrigerating capacity and the reduction in power consumption cancel each other out, but the efficiency as a heating device is improved by the reduction in power consumption due to the expansion / compressor 35.
[0027]
In the cycle configuration diagram of FIG. 12, two refrigerant paths from the condenser 37 to the evaporator 38 are configured. If this is only the path through the expander portion of the expander / compressor 35, the suction volume (maximum volume) of the compressor working chamber 24 in the expander / compressor 35 and the suction volume (suction port 22b) of the expander working chamber 7 are used. And the volume when the continuity is interrupted) is fixed at a constant value, the relationship between the suction pressure and the discharge pressure is restricted due to the continuity of the mass flow rate in the loop of the refrigeration cycle, and the above volume There is a concern that the operating pressure condition of the refrigeration cycle may become an unnatural value when the ratio of the above is inappropriate or the operating conditions such as the ambient temperature change greatly. In the cycle configuration diagram of FIG. 12, the operating pressure condition of the refrigeration cycle can be controlled by adjusting the throttle amount of the expansion means 39 in the refrigerant path of another system from the condenser 37 to the evaporator 38. However, when the suction volume ratio between the working chambers and the operating conditions such as the ambient temperature are well matched, the suction volume in at least one of the working chambers of the expansion / compressor 35 is variable and the volume control is performed. However, a route other than the route passing through the expander portion of the expansion / compressor 35 is not always necessary, and power in the expansion process is obtained from the total amount of refrigerant circulating in the refrigeration cycle. Since it can collect | recover, a more efficient refrigerating cycle can be comprised. In addition, depending on the type of refrigerant and the operating pressure, there may be no phase change from gas to liquid during the heat dissipation process in the condenser 37. In this case, the condenser 37 may function as a heat radiator.
[0028]
A fourth embodiment of the present invention will be described with reference to FIGS. 13 to 16 show an expansion / compression machine according to a fourth embodiment of the present invention. The fourth embodiment is different from the third embodiment of FIG. 11 in that the lower working chamber 41 functions as an expander and the upper working chamber 40 functions as a compressor in the entire side sectional view of FIG. Although common, since air is used as the working fluid, it is not necessary to seal the entire expansion / compression device in the container, and there is a difference such as not having an external casing member like the motor cover 14 in FIG. is there.
[0029]
One of the other differences is that a grease lubricated ball bearing 43 or a needle bearing 44 is used for the bearing portion of the bearing frame 42. The bearing portion in the third embodiment shown in FIG. 11 is used in an atmosphere of a refrigerant that elutes grease. In the fourth embodiment, the bearing portion is used in an air atmosphere, and lubrication by grease sealing is performed. Is possible.
[0030]
The next difference is that the diameter of the piston head 45c of the lower working chamber 41 functioning as an expander is close to the diameter of the piston head 45a of the upper working chamber 40 functioning as a compressor. In the expansion / compression machine in the third embodiment of FIG. 11, since the refrigerant discharged from the expansion unit still contains a large amount of liquid refrigerant because it is used in the refrigeration cycle, the volume of the refrigerant is entirely It is much smaller than the volume when it is sucked into the compressor after evaporating and gasifying. Therefore, the diameter of the piston head 21c of the expander part is significantly smaller than the diameter of the piston head 21a of the compressor part. On the other hand, in this embodiment in which air is used as the working fluid, it is assumed that the compressed air pressurized from the atmospheric pressure in the compressor section is expanded to the atmospheric pressure in the expander section (FIG. 17). The diameter of the piston head 45c of the expander unit is set to be approximately the same as the diameter of the piston head 45a of the compressor unit.
[0031]
In this connection, an elliptical locus 46 of the opening to the outer peripheral cylindrical surface of the communication passage 45f of the reciprocating member 45 is shown in FIG. 14 and FIG. 15, but the radius of the opened outer peripheral cylindrical surface is large. Therefore, the length of the short axis is larger than the elliptical locus 15 in the first to third embodiments, and the ellipse is more swollen. In the expander portion, the high-pressure gas flows into the working chamber 41 from the suction pipe 47 through the suction passage 48c provided in the cylinder block 48, the suction port 48d, and the communication passage 45f, and then expands in the sealed space. It becomes low-pressure gas and flows out from the discharge pipe 49 through the discharge port 48e and the discharge passage 48f provided in the cylinder block 48 from the communication passage 45f.
[0032]
Furthermore, since the diameter of the piston head 45c of the expander unit is set to be approximately the same as the diameter of the piston head 45a of the compressor unit, the magnitude of the recovered power in the expander unit is the compressor. Therefore, the power required to be supplied to the entire expansion / compressor is small, and the motor 51 for driving the drive shaft 50 has a small capacity.
[0033]
The following difference is that the suction path of the compressor portion in the fourth embodiment is different from that in the third embodiment, and the path from the external suction pipe to the working chamber 40 is the same as that of the expansion / compressor. The drive mechanism is housed in an internal space 52 that moves. FIG. 16 which is a KK cross section in FIG. 13 shows a suction path of the compressor section. In FIG. 16, the intake air that has flowed into the suction passage 48g of the cylinder block 48 from the two left and right suction pipes 53 passes through the suction port 45g formed in the piston head 45a of the reciprocating member 45, and reaches the piston head 45a. It reaches the internal space 45h and is sucked into the working chamber 40 from the suction port 45b through the suction valve plate 25 attached by the rivet 26. The suction passage 48g of the cylinder block 48 and the suction port 45g of the piston head 45a are electrically connected over the entire suction stroke. Since the intake air does not pass through the internal space 52 of the expansion / compressor, it is possible to prevent the lubricating oil sealed in the internal space 52 from being mixed for lubrication of each sliding portion and to obtain clean compressed air. Can do.
[0034]
Further, in the fourth embodiment, the coupling structure between the piston heads 45a and 45c of the reciprocating member 45 and the arm portion 45d is different from that of the third embodiment. When the working pressure of the working fluid is relatively low as in this embodiment, the diameter of the sliding portion between the arm portion 45d and the inner periphery of the spherical bush 3 is considerably smaller than the diameter of the piston head portions 45a and 45c. However, it is possible to design the sliding surface pressure within the practical range. In this case, as in this embodiment, a method of penetrating the piston heads 45a and 45c and inserting the arm portion 45d and integrally connecting as the reciprocating member 45 with a nut 45e or the like is effective. When at least one of the two piston head diameters is close to the sliding part diameter of the arm part of the reciprocating member as in the first to third embodiments, conversely, the central part of the arm part is thickened. And the method of penetrating this and inserting a piston head and fixing integrally can be employ | adopted.
[0035]
FIG. 17 shows a system configuration diagram when the expansion / compressor according to the fourth embodiment is applied to a fuel cell system. The expander / compressor 56 in the right center portion is the expander / compressor according to the fourth embodiment of FIG. The atmospheric air 57 passes through the upper right air cleaner 58 and then flows in from the suction pipe 53 of the expansion / compression machine 56, and after being compressed by the compressor section, flows out from the discharge pipe 32 and becomes compressed air 59 as the fuel cell stack 60. To the cathode portion 60a. The reason why the compressed air 59 is supplied is that high-density oxygen can be supplied to the cathode portion 60a to increase the efficiency and size of the fuel cell stack 60. On the other hand, a fuel gas 61 that is hydrogen or a gas containing hydrogen is supplied to the anode portion 60 b of the fuel cell stack 60. An ion permeable membrane 60c is disposed between the cathode portion 60a and the anode portion 60b, and hydrogen ions (+ ions) generated from hydrogen or a gas containing hydrogen supplied to the anode portion 60b are the ion permeable membrane 60c. In the process of generating moisture by combining with oxygen ions (− ions) generated from oxygen supplied to the cathode part 60a, the fuel cell stack 60 uses the cathode part 60a and the anode part 60b as electrodes to generate electric power 60d. Can be taken out. The fuel gas 61 supplied to the anode part 60b is exhausted from the fuel cell stack 60 as exhaust gas 62 after consuming hydrogen, and used as a heat source for a reformer (not shown). The compressed air 56 supplied to the cathode portion 60 a consumes a part of oxygen, but newly generated moisture is added and is discharged from the fuel cell stack 60 as high-pressure exhaust air 63. Thereafter, the air flows again into the expansion / compression machine 56 from the suction pipe 47, expands in the expander section, flows out from the discharge pipe 49, and is finally discharged into the atmosphere as low-pressure exhaust air 64.
[0036]
In the expander portion, the high pressure gas flows into the working chamber 41 via the suction passage 48c, the suction port 48d and the communication passage 45f provided in the cylinder block 48, and then expands in the sealed space to become low pressure gas. Then, the fluid flows out from the discharge pipe 49 through the discharge port 48e and the discharge passage 48f provided in the cylinder block 48 from the communication passage 45f.
[0037]
In the fuel cell system incorporating the expansion / compressor 56 of the fourth embodiment, the power recovered by the power recovery mechanism is used as a part of the power required to supply the compressed air 59, so that it is externally applied. The net power that must be supplied anew can be reduced. In addition, in a normal power recovery mechanism in which the compressor part and the expander part are independent, mechanical friction loss occurs in each of the compressor part and the expander part, and the total mechanical friction loss increases. In the fourth embodiment, similar to the third embodiment, the sliding load of each sliding portion is reduced by canceling at the stage of the load acting on the reciprocating member 45 which is a common part, and the mechanical friction is reduced. The loss is rather reduced. As a result, the efficiency of the expansion / compression device 56 is increased, and the efficiency load of the entire fuel cell system using the same is further increased.
[0038]
A fifth embodiment of the present invention will be described with reference to FIG. FIG. 18 shows a compressor according to a fifth embodiment of the present invention. In the fifth embodiment, the two working chambers 65 formed in the upper part and the lower part of the center in the entire side sectional view of FIG. 18 function as working rooms of the compressor. That is, the fifth embodiment is a two-cylinder compressor. The working fluid is carbon dioxide, and the pressure in the working chamber is as high as 4 to 5 times that of the conventional chlorofluorocarbon refrigerant. On the other hand, the refrigerating capacity per unit volume of the refrigerant is 4 to 5 times, and the stroke volume of the compressor generating the same refrigerating capacity may be small. In the compressor of FIG. 18, the stroke volume is reduced by reducing only the diameter of the two piston heads 66a in the reciprocating member 66, and the spherical center of the spherical bush 3 attached to the drive arm portion 67a is driven. The stroke of the reciprocating motion of the reciprocating member 66 is not reduced by reducing the amount of displacement of the shaft 67 from the rotating shaft. Further, compared to a conventional two-cylinder compressor having the same refrigeration capacity with a chlorofluorocarbon refrigerant, the diameter and axial length of the sliding portion between the arm portion 66b of the reciprocating member 66 and the spherical bush 3, and the drive shaft The diameter and axial length of the sliding portion between 67 and the bearing frame 68 have the same size, and the pressure receiving area of the sliding portion is equivalent to the conventional one. Such a design does not have a sliding portion inside the reciprocating member 66 in which the pressure of the working chamber directly acts in the mechanism of the positive displacement machine employed in the present invention. This is possible because dimensional specifications such as the size of the part can be set independently of each other without any restrictions. In the reciprocating mechanism using the conventional crank slider mechanism, the piston pin at the small end of the connecting rod is inside the piston directly acting on the working chamber pressure, so when the piston diameter is reduced, the sliding portion with the connecting rod It is difficult to maintain the pressure receiving area of the same as the conventional one. Further, in a rotary compressor such as a rolling piston type, when the width or diameter of the cylindrical rotor (piston) is reduced in order to reduce the area in which the pressure of the working chamber directly acts, the eccentric pin portion of the shaft inside the rotor It is difficult to maintain the pressure receiving area of the sliding portion between the rotor and the inner peripheral surface of the rotor at the same level as the conventional one.
[0039]
Carbon dioxide, which is a working fluid, flows into the internal space 71 of the compressor from a suction pipe 70 attached to the cylinder block 69, and reaches an internal space 66e of the piston head 66a from a suction port 66d provided in the reciprocating member 66. Then, the air is sucked into the working chamber 65 from the suction port 66f through the suction valve plate 73 mounted on the piston head 66a by the rivet 72. After being compressed in the working chamber 65, it is discharged from the discharge port 74 a formed in the cylinder head 74 to the discharge space 77 through the discharge valve plate 75 and the discharge valve presser 76. The discharge valve plate 75 and the discharge valve retainer 76 are fixed to the cylinder head 74 by bolts (not shown). The cylinder head 74 is fixed to the cylinder block 69 with bolts together with a discharge chamber cover 78 surrounding the discharge space 77. A discharge pipe 79 is connected to the discharge chamber cover 78 so that the high-pressure working fluid finally flows out of the compression chamber.
[0040]
In the fifth embodiment, since the working fluid is carbon dioxide, the two piston heads 66a of the reciprocating member 66 are both small in diameter, and the two inner peripheral cylindrical surfaces 69a of the cylinder block 69 into which they are inserted. The diameter is small. If a portion thicker than the diameter of the inner peripheral cylindrical surface 69a is formed in the piston head 66a of the reciprocating member 66, it cannot be inserted into the inner peripheral cylindrical surface 69a of the cylinder block 69 during assembly. On the other hand, the ratio of the diameter of the arm portion 66b to the diameter of the inner peripheral cylindrical surface 69a is relatively larger than that of the conventional refrigerant, and when the reciprocating member 66 is assembled, as shown in FIG. The structure in which the arm portion 66b is inserted into the hole formed in the 66a cannot secure strength. Therefore, the fifth embodiment employs a structure in which a thick portion is formed at the center of the arm portion 66b, and the piston head portion 66a is inserted into a hole provided in the arm portion 66b and fixed by the pin 66c.
[0041]
In the fifth embodiment, since the working fluid is carbon dioxide and the two-cylinder structure performs the compression work in the two working chambers 65, the power consumption is small for the stroke volume of each working chamber 65 being small. Therefore, the drive motor 80 is large, and the motor cover 81 that surrounds the motor 80 and forms a sealed space is also large.
[0042]
According to the fifth embodiment, even when a high-pressure working gas such as carbon dioxide is used, there are restrictions on reducing the diameter of the piston head 66a of the reciprocating member 66 that is a member that receives the pressure. Therefore, it is easy to design without increasing the load of the sliding portion, and it is possible to design without increasing the mechanical friction loss. In addition, since it is not necessary to reduce the area of the sliding portion such as the bearing portion at that time, the design without increasing the sliding surface pressure of the sliding portion is easy, and the design without reducing the reliability is possible. Further, in the reciprocating member 66 which is a main part, the strength of the coupling portion with the arm portion 66b can be sufficiently ensured even if the piston head portion 66a is reduced. That is, it becomes easy to put into practical use a refrigerating and air-conditioning system that uses a working gas that has a very high pressure, such as carbon dioxide, but exists naturally in the natural world and has a low environmental load.
[0043]
【The invention's effect】
According to the present invention, it is possible to eliminate the need for moving parts for the valve mechanism in the reciprocating positive displacement type machine, and the productivity and reliability are improved.
Further, according to the present invention, since the pressure receiving area of the working chamber can be reduced without reducing the size and pressure receiving area of the sliding portion such as the bearing in the positive displacement compressor, an ultrahigh pressure refrigerant such as carbon dioxide is used as the working fluid. However, it is possible to prevent an increase in the load of the sliding portion and the sliding surface pressure, and it is possible to prevent a significant decrease in reliability and mechanical efficiency.
Furthermore, according to the present invention, since the load acting on each sliding portion of the displacement type machine in which the compressor and the expander are integrated can be reduced, the mechanical efficiency is improved, and efficient power recovery by the expander is enabled. Thus, the efficiency of the entire system such as a refrigeration cycle incorporating a power recovery mechanism is greatly improved.
[Brief description of the drawings]
FIG. 1 is a side sectional view of an entire pump according to a first embodiment of the present invention.
FIG. 2 is a cross-sectional view taken along the line AA in FIG.
3 is a cross-sectional view taken along the line BB in FIG.
4 is a cross-sectional view taken along the line CC in FIG. 1. FIG.
5 is a cross-sectional view taken along the line DD in FIG. 1. FIG.
FIG. 6 is a side sectional view of an entire expander according to a second embodiment of the present invention.
7 is a cross-sectional view taken along the line E-E in FIG. 6;
8 is a cross-sectional view taken along line FF in FIG.
9 is a cross-sectional view taken along line GG in FIG.
10 is a cross-sectional view taken along line HH in FIG.
FIG. 11 is a side sectional view of an entire expansion / compression machine using a refrigerant as a working fluid according to a third embodiment of the present invention.
FIG. 12 is a configuration diagram of a refrigeration cycle when an expansion / compressor according to a third embodiment of the present invention is applied to a refrigeration / air conditioning apparatus.
FIG. 13 is an overall side sectional view of an air expansion / compression machine according to a fourth embodiment of the present invention.
14 is a cross-sectional view taken along the line II in FIG.
15 is a cross-sectional view taken along line JJ in FIG.
16 is a cross-sectional view taken along the line KK in FIG.
FIG. 17 is a system configuration diagram when an expansion / compressor according to a fourth embodiment of the present invention is applied to a fuel cell system;
FIG. 18 is a side sectional view of the entirety of a compressor according to a fifth embodiment of the present invention.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 ... Reciprocating member, 1a ... Piston head, 1b ... Arm part, 1c ... Pin, 1d ... Communication path, 2 ... Cylinder block, 2a ... Inner peripheral cylindrical surface, 2b ... Suction port, 2c ... Discharge port, 3 ... Spherical bush, 4 ... drive shaft, 4a ... drive arm portion, 4b ... balance mass, 5 ... bearing frame, 5a ... bearing portion, 6 ... cylinder head, 7 ... work chamber, 8 ... cover, 9 ... cover, 10 ... suction Pipe, 11 ... Discharge pipe, 12 ... Motor for driving, 12a ... Stator part, 12b ... Rotor part, 13 ... Balance mass, 14 ... Motor cover, 15 ... Ellipse locus, 16 ... Cylinder block, 16a ... Inner peripheral cylindrical surface, 16b ... Suction port, 16c ... Discharge port, 17 ... Cover, 18 ... Suction pipe, 19 ... Output shaft, 19a ... Output arm part, 19b ... Balance mass, 20 ... Generator, 20a ... Stator part, 20b Rotor part, 21 ... reciprocating member, 21a ... piston head, 21b ... suction port, 21c ... piston head, 21d ... arm part, 21e ... pin, 21f ... communication passage, 22 ... cylinder block, 22a ... inner cylinder Surface, 22b ... inner peripheral cylindrical surface, 22c ... suction port, 22d ... discharge port, 23 ... cylinder head, 23a ... discharge port, 24 ... working chamber, 25 ... suction valve plate, 26 ... rivet, 27 ... suction pipe, 28 DESCRIPTION OF SYMBOLS ... Discharge valve plate, 29 ... Discharge valve retainer, 30 ... Discharge space, 31 ... Discharge chamber cover, 32 ... Discharge piping, 33 ... Drive shaft, 33a ... Drive arm part, 33b ... Balance mass, 34 ... Drive motor, 34a ... Stator part, 34b ... Rotor part, 35 ... Expansion / compressor, 36 ... Cycle piping, 37 ... Condenser, 38 ... Evaporator, 39 ... Expansion means, 40 ... Moving chamber, 41 ... Working chamber, 42 ... Bearing frame, 43 ... Ball bearing, 44 ... Needle bearing, 45 ... Reciprocating member, 45a ... Piston head, 45b ... Suction port, 45c ... Piston head, 45d ... Arm portion 45e ... Nut, 45f ... Communication passage, 45g ... Suction port, 45h ... Internal space, 46 ... Elliptic locus, 47 ... Suction piping, 48 ... Cylinder block, 48c ... Suction passage, 48d ... Suction port, 48e ... Discharge port, 48f ... discharge passage, 48g ... suction passage, 49 ... discharge pipe, 50 ... drive shaft, 51 ... motor, 52 ... internal space, 53 ... suction pipe, 54 ... cylinder head, 55 ... balance mass, 56 ... expansion / compression machine 57 ... Air, 58 ... Air cleaner, 59 ... Compressed air, 60 ... Fuel cell stack, 60a ... Cathode part, 60b ... Anode part, 60c ... Ion permeable membrane, 6 0d ... Electric power, 61 ... Fuel gas, 62 ... Exhaust gas, 63 ... High pressure exhaust air, 64 ... Low pressure exhaust air, 65 ... Working chamber, 66 ... Reciprocating member, 66a ... Piston head, 66b ... Arm part, 66c ... Pin 66d ... Suction port 66e ... Internal space 66f ... Suction port 67 ... Drive shaft 67a ... Drive arm portion 67b ... Balance mass 68 ... Bearing frame 68a ... Bearing portion 69 ... Cylinder block 69a ... Inner circumferential cylindrical surface, 70 ... suction pipe, 71 ... inner space, 72 ... rivet, 73 ... suction valve plate, 74 ... cylinder head, 74a ... discharge port, 75 ... discharge valve plate, 76 ... discharge valve presser, 77 ... discharge Space 78: Discharge chamber cover 79 ... Discharge piping 80 ... Drive motor 80a ... Stator part 80b Rotor part 81 ... Motor cover 82 ... Balance quality .

Claims

A reciprocating member having a piston part that changes the volume of the working space sealed by the reciprocating movement, and two arm parts extending in opposite directions to each other in a direction perpendicular to the reciprocating direction of the piston part; A guide member that guides the reciprocating motion of the piston portion, and two shafts that rotate in opposite directions in the same axial direction, and respectively support the arm portions at positions displaced in the radial direction from the rotation shaft In the compressor in which the piston part reciprocates while swinging around the axis of the reciprocating direction by the member,
The piston portion has a communication passage that communicates the working space and the low-pressure working fluid space, and a communication passage that communicates the working space and the high-pressure working fluid space,
Communicating the low-pressure working fluid space and the working space through a communication passage during a period in which the volume of the working space is increased by reciprocating motion accompanied by a swinging motion of the piston portion;
The high-pressure working fluid space and the working space are shut off at the beginning of a period in which the volume of the working space is reduced by a reciprocating motion accompanied by a swinging motion of the piston portion, and via a communication passage at a later stage of the period. compressor, characterized in that communicated the high pressure working fluid space and the working space Te.

A reciprocating member having a piston portion that changes the volume of the working space sealed by reciprocating motion, and two arm portions extending in opposite directions to each other in a direction perpendicular to the reciprocating motion direction of the piston portion; A guide member that guides the reciprocating motion of the piston portion, and two shafts that rotate in opposite directions in the same axial direction and respectively support the arm portion at a position displaced in the radial direction from the rotation axis In the expander in which the piston part reciprocates while swinging around the axis in the reciprocating direction by the member,
The piston portion has a communication passage that communicates the working space and the low-pressure working fluid space, and a communication passage that communicates the working space and the high-pressure working fluid space,
The volume of the working space by the reciprocating movement with the rocking movement of the piston portion via the initially walkway period has increased communicates the working fluid space and the working space of the high pressure, late of the period Shutting off the high-pressure working fluid space and the working space,
An expander in which the low-pressure working fluid space and the working space are communicated with each other through a communication passage during a period in which the volume of the working space is reduced by a reciprocating motion accompanied by a swinging motion of the piston portion.

A reciprocating motion comprising two piston portions that are guided by other members to perform a reciprocating motion and a swinging motion about an axis in the reciprocating motion direction, and two arm portions that protrude in opposite directions perpendicular to the reciprocating motion direction. A reciprocating member and a guide member, which is another member for guiding the piston portion of the reciprocating member, and the reciprocating member at positions displaced radially from the rotating shaft while rotating in opposite directions around a coaxial rotating shaft. The component has two shaft members that support one of the arm portions of the moving member so as to allow relative rotation and change in the direction of the rotation axis, and a bearing member that supports rotation of the two shaft members. A closed space is formed adjacent to each of the two piston portions of the reciprocating member to form two working spaces, and one working space is operated by changing the volume by rotating the two shaft members in opposite directions. Fluid transfer Functions as positive-displacement machine for performing compression, the other working space acts as a positive displacement engine driven to rotate in opposite directions the two shaft members to change the volume by pressure of the working fluid,
The piston portion of the other working space has a communication passage that communicates the other working space and the low-pressure working fluid space, and a communication passage that communicates the other working space and the high-pressure working fluid space. ,
The high-pressure working fluid space and the other working space are communicated with each other via a communication passage at an initial stage of a period in which the volume of the other working space is increased by a reciprocating motion accompanied by a swinging motion of the piston portion; Shutting off the high-pressure working fluid space and the working space at a later stage of the period;
A volume type in which the low-pressure working fluid space and the other working space are communicated with each other via a communication passage during a period in which the volume of the other working space is reduced due to reciprocating motion accompanied by swinging motion of the piston portion. machine.

In claim 3,
Each of the two shaft members is rotationally driven by an electric motor, the positive displacement machine portion is a compressor that uses gas as a working fluid, and the positive displacement engine portion uses at least a portion of the gas compressed in the compressor as a working fluid. A positive displacement machine characterized by being an expander.

Compressing means for compressing low-pressure refrigerant gas, cooling means for radiating heat from the compressed and high-temperature and high-pressure refrigerant gas, expansion means for decompressing the cooled high-pressure refrigerant, and liquid refrigerant after being decompressed In a refrigeration cycle having heating means for evaporating parts and piping that connects them to form a closed cycle as components,
A refrigeration cycle and a refrigeration / air-conditioning apparatus using the positive displacement machine part of the positive displacement machine of claim 4 as the compression means and the positive displacement engine part of the positive displacement machine of claim 4 as the expansion means. .

Compressing means for compressing low-pressure refrigerant gas, cooling means for radiating heat from the compressed and high-temperature and high-pressure refrigerant gas, expansion means for decompressing the cooled high-pressure refrigerant, and liquid refrigerant after being decompressed In a refrigeration cycle having heating means for evaporating parts and piping that connects them to form a closed cycle as components,
The positive displacement machine portion of the positive displacement machine of claim 4 is used as the compression means, and the positive displacement engine portion of the positive displacement machine of claim 4 and another expansion means such as a throttle are used in combination as the expansion means. Refrigeration cycle and refrigeration / air conditioning equipment.

In a fuel cell system for supplying compressed air to a fuel cell stack,
The volume of the positive displacement machine of claim 4 wherein the compressed air is produced in the positive displacement machine portion of the positive displacement machine of claim 4 and at least a portion of the compressed air after consumption of oxygen through the fuel cell stack. A fuel cell system, wherein the fuel cell system is opened to the atmosphere after being introduced to a large engine portion and expanded.