JPH09250474A - Fluid machine - Google Patents

Fluid machine

Info

Publication number
JPH09250474A
JPH09250474A JP5769896A JP5769896A JPH09250474A JP H09250474 A JPH09250474 A JP H09250474A JP 5769896 A JP5769896 A JP 5769896A JP 5769896 A JP5769896 A JP 5769896A JP H09250474 A JPH09250474 A JP H09250474A
Authority
JP
Japan
Prior art keywords
expansion mechanism
mechanism section
compression mechanism
expansion
fluid machine
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
JP5769896A
Other languages
Japanese (ja)
Inventor
Hitoshi Hattori
仁司 服部
Akira Morishima
明 森嶋
Toshio Otaka
敏男 大高
Kazuo Saito
和夫 齊藤
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.)
Toshiba Corp
Original Assignee
Toshiba Corp
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 Toshiba Corp filed Critical Toshiba Corp
Priority to JP5769896A priority Critical patent/JPH09250474A/en
Publication of JPH09250474A publication Critical patent/JPH09250474A/en
Pending legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
    • F04C23/003—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle having complementary function
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

PROBLEM TO BE SOLVED: To eliminate electrically driven elements for startup, try to suppress torque variation, and ensure smooth operation state. SOLUTION: This machine incorporates an expansion mechanism part constituting Rankine cycle, and a compression mechanism part 11 constituting a freezing cycle by means of rotational drive force in the same sealing case, the expansion mechanism part 9 is a rotational drive force generation means for generating rotational drive force during startup by means of high-pressure gas while there is provided with a fly wheel 50 for standardize torque variation generated at the expansion mechanism part 9.

Description

【発明の詳細な説明】Detailed Description of the Invention

【０００１】[0001]

【発明の属する技術分野】この発明は、ランキンサイク
ル用の膨張機構部と冷凍サイクル用の圧縮機構部とを一
つの密閉ケース内に配置した流体機械に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a fluid machine in which a Rankine cycle expansion mechanism section and a refrigeration cycle compression mechanism section are arranged in a single sealed case.

【０００２】[0002]

【従来の技術】従来、膨張機構部と圧縮機構部とを一つ
の密閉ケース内に配置した流体機械としては、例えば、
特開昭５９−２５０９７号公報記載のものが知られてい
る。2. Description of the Related Art Conventionally, as a fluid machine in which an expansion mechanism section and a compression mechanism section are arranged in one sealed case, for example,
The one described in JP-A-59-25097 is known.

【０００３】流体機械の概要は、起動時にステータと、
ステータに対して回転可能なロータとから成る電動要素
によって回転動力が与えられる膨張機構部に、高圧の作
動ガスが送り込まれ、ランキンサイクルを繰返すことで
回転動力が発生し、その回転動力は、圧縮機構部に伝達
されるようになる。圧縮機構部では、膨張機構部からの
回転動力により、圧縮室に送り込まれた作動ガスを高圧
として吐出する冷凍サイクルが行なわれる構造となって
いる。An outline of a fluid machine is that a stator is used at the time of start-up.
A high-pressure working gas is sent to the expansion mechanism section that receives rotational power by an electric element that is composed of a rotor that can rotate with respect to the stator, and the Rankine cycle is repeated to generate rotational power, which is compressed. It will be transmitted to the mechanical section. The compression mechanism unit has a structure in which a refrigeration cycle is performed in which the working gas sent to the compression chamber is discharged as high pressure by the rotational power from the expansion mechanism unit.

【０００４】[0004]

【発明が解決しようとする課題】流体機械は、膨張機構
部によって回転動力が発生し、その回転動力は圧縮機構
部に伝達される。膨張機構部は、間欠的に膨張を繰返す
ことで出力トルクを発生する所から膨張機構部からの出
力トルクは、一回転中にムラがあり、圧縮機構部に伝達
する上で、トルク波形に合わさねばならなかったが、従
来は、起動時の電動要素のロータが回転マスとして機能
し、トルク変動を平準化する役目を担っていた。In the fluid machine, rotary power is generated by the expansion mechanism, and the rotary power is transmitted to the compression mechanism. The expansion mechanism section generates output torque by repeating expansion intermittently.Therefore, the output torque from the expansion mechanism section has unevenness during one rotation, and when it is transmitted to the compression mechanism section, it is matched with the torque waveform. Although it had to be done, conventionally, the rotor of the electric element at the time of start-up functioned as a rotating mass and had a role of leveling the torque fluctuation.

【０００５】このために、従来の流体機械にあっては、
トルク変動の平準化が得られる反面、起動時専用の電動
要素が必要となるため、装置全体の大型化、複雑化する
問題を招来していたものである。Therefore, in the conventional fluid machine,
On the other hand, although the torque fluctuation can be leveled, an electric element dedicated for starting is required, which causes a problem that the entire apparatus becomes large and complicated.

【０００６】そこで、この発明は、起動時の電動要素を
なくし、かつ、膨張機構部のトルク変動の平準化が図れ
るようにした流体機械を提供することを目的としてい
る。SUMMARY OF THE INVENTION Therefore, an object of the present invention is to provide a fluid machine which eliminates an electric element at the time of starting and can equalize the torque fluctuation of the expansion mechanism.

【０００７】[0007]

【課題を解決するための手段】前記目的を達成するため
に、この発明は、ランキンサイクルを構成する膨張機構
部と、膨張機構部からの回転動力により冷凍サイクルを
構成する圧縮機構部とを同一密閉ケース内に組込み、前
記膨張機構部を、高圧ガスによって起動時の回転動力を
発生させる回転動力が発生手段とする一方、前記膨張機
構部で発生するトルク変動を平準化するフライホールを
備える。In order to achieve the above-mentioned object, the present invention provides an expansion mechanism part which constitutes a Rankine cycle and a compression mechanism part which constitutes a refrigeration cycle by rotational power from the expansion mechanism part. The expansion mechanism is incorporated in a sealed case, and the expansion mechanism is provided with a flyhole for equalizing torque fluctuations generated in the expansion mechanism, while using rotation power for generating rotation power at the time of startup by high-pressure gas.

【０００８】フライホイールを配置する好ましい実施形
態としては、圧縮機構部の反対側となる膨張機構部の回
転シャフト端部に設ける場合、あるいは、圧縮機構部と
膨張機構部の間で、圧縮機構部と膨張機構部とをつなぐ
回転シャフトに設ける場合、あるいは、膨張機構部の反
対側となる圧縮機構部の回転シャフト端部に設ける場合
がある。As a preferred embodiment of arranging the flywheel, the compression mechanism part is provided at the end of the rotary shaft of the expansion mechanism part opposite to the compression mechanism part, or between the compression mechanism part and the expansion mechanism part. There is a case where it is provided on the rotary shaft that connects the expansion mechanism section and the expansion mechanism section, or a case where it is provided on the rotary shaft end of the compression mechanism section that is on the opposite side of the expansion mechanism section.

【０００９】かかる流体機械によれば、起動時に、高圧
ガスを膨張機構部へ送り込むことで、起動時の回転動力
が発生すると共に、運転中のランキンサイクルにより得
られる膨張機構部からの回転動力は圧縮機構部に伝達さ
れる。圧縮機構部では、膨張機構部からの回転動力によ
り、圧縮室内に取込まれた作動ガスを圧縮して吐出する
冷凍サイクルが行なわれる。According to such a fluid machine, when the high pressure gas is sent to the expansion mechanism at the time of starting, the rotational power at the time of starting is generated and the rotational power from the expansion mechanism obtained by the Rankine cycle in operation is generated. It is transmitted to the compression mechanism section. In the compression mechanism section, a refrigeration cycle is performed in which the rotational power from the expansion mechanism section compresses and discharges the working gas taken into the compression chamber.

【００１０】この運転中において、発生するトルク変動
は、フライホイールにより平準化されて圧縮機構部に伝
達され、安定した運転が行なえるようになる。During this operation, the torque fluctuations generated are leveled by the flywheel and transmitted to the compression mechanism section, so that stable operation can be performed.

【００１１】[0011]

【発明の実施の形態】以下、図１と図２の図面を参照し
ながらこの発明の実施形態を具体的に説明する。BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be specifically described below with reference to the drawings of FIGS.

【００１２】図１において、１は流体機械を示してお
り、ランキンサイクル用の第１の吸込管２及び冷凍サイ
クル用の第２の吸込管３と、吐出管５とを有する密閉ケ
ース７内の右側に膨張機構部９が、左側に圧縮機構部１
１がそれぞれ配置されている。流体機械１は冷凍サイク
ルを構成する圧縮機構部１１の吐出ガスと、ランキンサ
イクルを構成する膨張機構９の吐出ガスが密閉ケース７
内に吐出される１流体方式対応となっている。In FIG. 1, reference numeral 1 denotes a fluid machine, which is provided in a sealed case 7 having a first suction pipe 2 for Rankine cycle, a second suction pipe 3 for refrigeration cycle, and a discharge pipe 5. The expansion mechanism section 9 is on the right side and the compression mechanism section 1 is on the left side.
1 are arranged respectively. In the fluid machine 1, the discharge gas of the compression mechanism section 11 that constitutes the refrigeration cycle and the discharge gas of the expansion mechanism 9 that constitutes the Rankine cycle are sealed case 7
It is compatible with the one-fluid system that is discharged inside.

【００１３】膨張機構部９は、シリンダ１３とシリンダ
１５とからなるツインタイプとなっていて、各シリンダ
１３，１５は、中間仕切板１７によってそれぞれ独立す
るよう仕切られ、両シリンダ１３，１５に第１の回転シ
ャフト１９が貫通している。The expansion mechanism 9 is of a twin type consisting of a cylinder 13 and a cylinder 15. The cylinders 13 and 15 are partitioned by an intermediate partition plate 17 so as to be independent from each other. The rotary shaft 19 of No. 1 penetrates.

【００１４】膨張機構９の第１の回転シャフト１９は、
主軸受部材２１と副軸受部材２３とによって回転自在に
両端支持されている。第１の回転シャフト１９は、後述
するガス吸込通路２５と、前記各シリンダ１３，１５に
対応する部分に、互いに１８０度位相をずらした偏心軸
部２７，２９が設けられ、これら偏心軸部２７，２９に
は前記両シリンダ１３，１５内に配置された第１のロー
ラ３１および第２のローラ３３が嵌合している。The first rotary shaft 19 of the expansion mechanism 9 is
Both ends are rotatably supported by the main bearing member 21 and the sub bearing member 23. The first rotary shaft 19 is provided with eccentric shaft portions 27 and 29, which are 180 degrees out of phase with each other, in a portion corresponding to each of the cylinders 13 and 15 and a gas suction passage 25 described later. , 29 are fitted with a first roller 31 and a second roller 33 arranged in the cylinders 13 and 15, respectively.

【００１５】これにより、各ローラ３１，３３は、偏心
軸部２７，２９の回転により１８０度位相がずれた偏心
回転が与えられるようになる。As a result, the rollers 31 and 33 are given eccentric rotations which are 180 degrees out of phase with each other due to the rotation of the eccentric shaft portions 27 and 29.

【００１６】第１、第２のローラ３１，３３の外周面に
は、図３に示す如く背圧又は、ばね等による付勢手段３
５によって常時接触し合うブレード３７が設けられ、各
ローラ３１，３３及びブレード３７とにより膨張室３９
がそれぞれ作られるようになる。第１の回転シャフト１
９に設けられたガス吸込通路２５は、第１の回転シャフ
ト１９の軸端部から中心軸線に沿って左右の偏心軸部２
７，２９の領域まで延長されている。ガス吸込通路２５
の一方の吸込口２５ａはケーシング４１を介して前記吸
込管２と連通している。On the outer peripheral surfaces of the first and second rollers 31 and 33, as shown in FIG. 3, a back pressure or a biasing means 3 such as a spring is used.
5, a blade 37 that is in constant contact with each other is provided, and the expansion chamber 39 is formed by the rollers 31, 33 and the blade 37.
Will be made respectively. First rotating shaft 1
The gas suction passage 25 provided in the shaft 9 is provided on the left and right eccentric shaft portions 2 along the central axis line from the axial end portion of the first rotary shaft 19.
It extends to the area of 7,29. Gas suction passage 25
One suction port 25a communicates with the suction pipe 2 via the casing 41.

【００１７】ガス吸込通路２５の他方は、各偏心軸部２
７，２９の外周面に１８０度の位相差を有して設けられ
た吸込ポート４７と連通し、吸込ポート４７は、各ロー
ラ３１，３３に設けられた連通ポート４９を介して各膨
張室３９，３９と連通可能となっている。The other of the gas suction passages 25 has the other eccentric shaft portions 2.
7, 29 communicates with a suction port 47 provided with a phase difference of 180 degrees on the outer peripheral surface, and the suction port 47 passes through a communication port 49 provided in each of the rollers 31 and 33 to each expansion chamber 39. , 39 can be communicated with.

【００１８】ケーシング４１は、主軸受部材２１の軸受
部材端部に装着され、ケーシング４１内は、吸込管２か
ら高圧ガスが送り込まれる高圧室となっており、内部に
はフライホイール５０が配置されている。The casing 41 is mounted on the end of the bearing member of the main bearing member 21, the inside of the casing 41 is a high-pressure chamber into which high-pressure gas is fed from the suction pipe 2, and the flywheel 50 is arranged inside. ing.

【００１９】主軸受部材２１の軸受部材の装着面と、前
記ケーシング４１の内部のシャフト外周面及び前記軸受
部材端部内周面との間はシール材４２，４３によりシー
ルされている。Sealing materials 42 and 43 are provided between the bearing member mounting surface of the main bearing member 21 and the outer peripheral surface of the shaft inside the casing 41 and the inner peripheral surface of the end portion of the bearing member.

【００２０】シール材４２は、Ｏリングとなっており、
シール部材４３はリング状に形成され、付勢ばね４５に
より、密着方向の付勢力が与えられ、吸込管２からの高
圧ガスが密閉ケース７の内部又はシリンダ１３へ漏れる
のを防いでいる。The sealing material 42 is an O-ring,
The seal member 43 is formed in a ring shape, and an urging force in the close contact direction is applied by the urging spring 45 to prevent the high-pressure gas from the suction pipe 2 from leaking into the sealed case 7 or the cylinder 13.

【００２１】フライホイール５０は、トルク変動を平準
化して圧縮機構部１１に位置する所定の質量を有する円
板状に形成され、図２に示す如く第１の回転シャフト１
９の軸端部に、ナット５２により固着されている。The flywheel 50 is formed in a disk shape having a predetermined mass and located in the compression mechanism portion 11 for equalizing the torque fluctuation, and as shown in FIG. 2, the first rotating shaft 1
It is fixed to the shaft end of 9 by a nut 52.

【００２２】一方、吸込ポート４７及び連通ポート４９
は、偏心軸部２７，２９が約１８０度回転し、吸込ポー
ト４７と連通ポート４９が連通し合うことで、高圧ガス
が膨張室３９内へ送り込まれる流入タイミング制御手段
５１を構成している。On the other hand, the suction port 47 and the communication port 49
The eccentric shaft portions 27, 29 rotate about 180 degrees, and the suction port 47 and the communication port 49 communicate with each other, thereby forming the inflow timing control means 51 for feeding the high-pressure gas into the expansion chamber 39.

【００２３】各シリンダ１３，１５の吸込ポート４７
は、図５，図６に示す如く吸込ガス流入開口角θが１８
０度以上に設定され、運転停止時にいずれか一方のシリ
ンダ１３，１５側の吸込ポート４７が連通ポート４９と
連通し合う組合せ構造となっている。Suction port 47 of each cylinder 13, 15
And the suction gas inflow opening angle θ is 18 as shown in FIGS.
It is set to 0 degrees or more, and has a combination structure in which the suction port 47 on one of the cylinders 13 and 15 side communicates with the communication port 49 when the operation is stopped.

【００２４】これにより、各吸込ポート４７がいずれの
角度位置で停止しても、吸込ポート４７と連通ポート４
９との連通状態の確保が可能となり、高圧ガスが送り込
まれることで、膨張室３９内において、吸込開始→吸込
終了→膨張開始→膨張終了の起動運転が行なわれるよう
になっている。As a result, even if each suction port 47 stops at any angular position, the suction port 47 and the communication port 4 can be connected.
A communication state with 9 can be secured, and by the high-pressure gas being fed, the start operation of suction start → suction end → expansion start → expansion end is performed in the expansion chamber 39.

【００２５】シリンダ１３，１５には、吐出ポート５５
をそれぞれ有し、一方のシリンダ１３側の吐出ポート５
５にあっては、主軸受部材２１側に、他方のシリンダ１
５の吐出ポート５５にあっては、副軸受部材２３側にそ
れぞれ設けられている。A discharge port 55 is provided in each of the cylinders 13 and 15.
Discharge port 5 on one cylinder 13 side
5, the main bearing member 21 side, the other cylinder 1
The discharge ports 55 of No. 5 are provided on the sub bearing member 23 side.

【００２６】一方のシリンダ１３側の吐出ポート５５
は、マフラ室５７内に臨み、マフラ室５７から密閉ケー
ス７内を通り前記吐出管５と連通している。他方のシリ
ンダ１５側の吐出ポート５５は、シリンダ１５，中間仕
切板１７，シリンダ１３を貫通した貫通孔５５ａを介し
てマフラ室５７に臨み、マフラ室５７から密閉ケース７
内を通り前記吐出管５と連通している。Discharge port 55 on one cylinder 13 side
Faces the muffler chamber 57 and communicates with the discharge pipe 5 from the muffler chamber 57 through the sealed case 7. The discharge port 55 on the other cylinder 15 side faces the muffler chamber 57 through a through hole 55a penetrating the cylinder 15, the intermediate partition plate 17, and the cylinder 13, and then from the muffler chamber 57 to the closed case 7.
It communicates with the discharge pipe 5 through the inside.

【００２７】圧縮機構部１１は、シリンダ６１を有する
シングルタイプとなっていて、シリンダ６１には第２の
回転シャフト６３が貫通している。The compression mechanism 11 is of a single type having a cylinder 61, and a second rotary shaft 63 penetrates through the cylinder 61.

【００２８】圧縮機構部１１の第２の回転シャフト６３
は、継ぎ手６５を介して膨張機構９の第１の回転シャフ
ト１９と一体に結合されると共に、主軸受部材６７及び
副軸受部材６９とによって回転自在に軸支されている。
第２の回転シャフト６３には、前記第２のシリンダ６１
に対応する部分に偏心軸部７１が設けられ、偏心軸部７
１には前記シリンダ６１内に配置されたローラ７３が嵌
合している。これにより、ローラ７３は、偏心軸部７１
の回転により偏心回転が与えられるようになる。The second rotary shaft 63 of the compression mechanism section 11
Is integrally connected to the first rotary shaft 19 of the expansion mechanism 9 via the joint 65, and is rotatably supported by the main bearing member 67 and the sub bearing member 69.
The second rotary shaft 63 includes the second cylinder 61.
The eccentric shaft portion 71 is provided in the portion corresponding to
A roller 73 arranged in the cylinder 61 is fitted into the cylinder 1. As a result, the roller 73 moves the eccentric shaft portion 71.
The eccentric rotation is given by the rotation of.

【００２９】主軸受部材６７には、開閉弁７５を有する
吐出ポート７７が設けられている。吐出ポート７７は、
マフラ室７９から密閉ケース７の内部空間を介して前記
吐出管５と連通している。The main bearing member 67 is provided with a discharge port 77 having an opening / closing valve 75. The discharge port 77 is
The muffler chamber 79 communicates with the discharge pipe 5 through the internal space of the closed case 7.

【００３０】図４に示す如く、シリンダ６１には、前記
した吸込管３と連通し合う吸込ポート８５と、前記ロー
ラ７３の外周面と背圧又はばね等による付勢手段によっ
て常時接触し合うブレード８７とが設けられ、ローラ７
３及びブレード８７とにより圧縮室８９が作られるよう
になっている。As shown in FIG. 4, the cylinder 61 has a suction port 85 communicating with the suction pipe 3 and a blade which constantly contacts the outer peripheral surface of the roller 73 by a back pressure or a biasing means such as a spring. 87 and the roller 7
A compression chamber 89 is formed by 3 and the blade 87.

【００３１】膨張機構部９と圧縮機構部１１は、膨張機
構部９側の副軸受部材２３と圧縮機構部１１側の主軸受
部材６７が接合され、締結ボルト９１によって一体に結
合されている。また、膨張機構部９の第１の回転シャフ
ト１９と、圧縮機構部１１の第２の回転シャフト６３は
継ぎ手６５により同一軸心上に連結されている。The expansion mechanism portion 9 and the compression mechanism portion 11 are joined together by a sub-bearing member 23 on the expansion mechanism portion 9 side and a main bearing member 67 on the compression mechanism portion 11 side, and are integrally connected by a fastening bolt 91. Further, the first rotary shaft 19 of the expansion mechanism section 9 and the second rotary shaft 63 of the compression mechanism section 11 are connected on the same axis center by a joint 65.

【００３２】副軸受部材２３と主軸受部材６７が結合さ
れた結合外周部９３となるフランジ部９５は、前記主軸
受部材６７と一体に形成され、組付けが容易となるよう
分割された密閉ケース７の重ね合せ結合部９７により挾
み込み支持された構造となっている。また、結合外周部
９３となるフランジ部９５の挾み込み位置は、結合され
た膨張機構部９と圧縮機構部１１の重心位置に設定さ
れ、偏荷重による応力の発生が阻止された構造となって
いる。A flange portion 95, which serves as a joint outer peripheral portion 93 in which the sub-bearing member 23 and the main bearing member 67 are joined, is integrally formed with the main bearing member 67, and is a sealed case which is divided for easy assembly. It is structured so as to be sandwiched and supported by the superposing and connecting portion 97 of 7. Further, the sandwiching position of the flange portion 95 that becomes the joint outer peripheral portion 93 is set to the center of gravity position of the jointed expansion mechanism portion 9 and compression mechanism portion 11, and the structure is such that generation of stress due to unbalanced load is prevented. ing.

【００３３】なお、膨張機構部９と圧縮機構部１１の間
となる膨張機構部９の内側に、給油ポンプ１３１が、ま
た圧縮機構部１１の内側と外側とに、回転時の第１・第
２の回転シャフト１９，６３のバランスをとるバランサ
１３３，１３３が設けられている。さらに、圧縮機構部
９の外側となる副軸受部材６９の内部には第２の回転シ
ャフト６３のスラスト力を受けるスラスト受部材１３５
が設けられている。The oil supply pump 131 is provided inside the expansion mechanism section 9 between the expansion mechanism section 9 and the compression mechanism section 11, and is provided inside and outside the compression mechanism section 11 for the first and first rotations. Balancers 133 and 133 for balancing the two rotary shafts 19 and 63 are provided. Further, a thrust receiving member 135 that receives the thrust force of the second rotary shaft 63 is provided inside the auxiliary bearing member 69 that is outside the compression mechanism unit 9.
Is provided.

【００３４】バランサ１３３は、圧縮機構部１１の第２
の回転シャフト６３の端部に、偏心軸部７１と１８０度
反対向きに装着されている。The balancer 133 is the second of the compression mechanism section 11.
The rotary shaft 63 is attached to the end of the rotary shaft 63 opposite to the eccentric shaft 71 by 180 degrees.

【００３５】給油ポンプ１３１は、膨張機構部９の第１
の回転シャフト１９の端部に配置され、吸込側には油溜
め部１３７に延長された給油管（図示されていない）が
接続されている。給油ポンプ１３１の吐出側は、潤滑給
油路（図示していない）を介して一方は、膨張機構部９
側の副軸受部材２３，偏心軸部２７，２９、主軸受部材
２１と連通し、各摺動部に対して潤滑油が供給されるよ
うになっており、ケーシング４１を介して油溜め１３７
に戻るようになっている。The oil supply pump 131 is the first of the expansion mechanism section 9.
An oil supply pipe (not shown) extended to the oil reservoir 137 is connected to the suction side of the rotary shaft 19. The discharge side of the oil supply pump 131 is provided with a lubricating oil supply passage (not shown), and one of them is connected to the expansion mechanism 9
Side sub-bearing member 23, eccentric shaft portions 27 and 29, and main bearing member 21 so that lubricating oil is supplied to each sliding portion, and oil sump 137 is provided via casing 41.
To return to.

【００３６】他方は、圧縮機構部１１側の主軸受部材６
７，偏心軸部７１，副軸受部材６９と連通し、各摺動部
に対して潤滑油が供給されるようになっており、副軸受
部材６９に設けられた戻り通路（図示していない）を介
して油溜め部１３７に戻るようになっている。On the other hand, the main bearing member 6 on the compression mechanism 11 side
7, communicating with the eccentric shaft portion 71 and the auxiliary bearing member 69 so that lubricating oil is supplied to each sliding portion, and a return passage (not shown) provided in the auxiliary bearing member 69. It returns to the oil sump 137 via the.

【００３７】このように構成された流体機械によれば、
運転停止時において、膨張機構部９側の各吸込ポート４
７と、吸込ガス流入開口角θが１８０度以上のずれを有
した組合せとなっているため、いずれの角度位置で吸込
ポート４７が停止しても、吸込ポート４７と膨張室３９
との連通状態が確保される。したがって、運転開始と同
時に高圧ガスは、膨張室３９内へ送り込まれる。According to the fluid machine configured as described above,
Each suction port 4 on the expansion mechanism 9 side when operation is stopped
7 and the suction gas inflow opening angle θ have a deviation of 180 degrees or more. Therefore, even if the suction port 47 stops at any angle position, the suction port 47 and the expansion chamber 39
The communication state with is secured. Therefore, the high-pressure gas is sent into the expansion chamber 39 at the same time when the operation is started.

【００３８】これにより、起動用の電動要素がなくて
も、高圧ガスは、吸込ポート４７から吸込まれ、吸込開
始→吸込終了→膨張開始→膨張終了となり、排気行程を
経て、再び吸込み開始に戻る行程を繰返す起動運転が可
能となる。As a result, the high-pressure gas is sucked in through the suction port 47 even if there is no electric element for start-up, and the suction start-> suction end-> expansion start-> expansion end is completed, and the suction stroke returns again after the exhaust stroke. A start-up operation that repeats the process becomes possible.

【００３９】この時、膨張機構部９側の第１の回転シャ
フト１９に与えられた回転動力は、圧縮機構部１１の第
２の回転シャフト６３を駆動し、ローラ７３に偏心回転
を与える。これにより、吸込ポート８５から送り込まれ
た作動ガスは圧縮され吐出管５から吐出された後、吸込
管３に戻る冷凍サイクルを繰返すようになる。At this time, the rotary power given to the first rotary shaft 19 on the expansion mechanism 9 side drives the second rotary shaft 63 of the compression mechanism 11 to give the roller 73 eccentric rotation. As a result, the working gas sent from the suction port 85 is compressed and discharged from the discharge pipe 5, and then the refrigeration cycle of returning to the suction pipe 3 is repeated.

【００４０】この運転時において発生するトルク変動
は、フライホイール５０により平準化されて圧縮機構部
１１に伝達され、安定した運転状態が得られるようにな
る。The torque fluctuations generated during this operation are leveled by the flywheel 50 and transmitted to the compression mechanism section 11, so that a stable operating state can be obtained.

【００４１】この場合、フライホイール５０の取付位置
は必ずしもケーシング４１内の第１の回転シャフト１９
に特定されない。In this case, the mounting position of the flywheel 50 is not necessarily the first rotating shaft 19 in the casing 41.
Not specified in.

【００４２】例えば、第７図に示す如く、膨張機構部９
と圧縮機構部１１の間で、第１，第２の回転シャフト１
９，６３の接続領域に設けるようにしてもよい。あるい
は、第８図に示す如く、膨張機構部９の反対側となる圧
縮機構部１１の第２の回転シャフト６３の軸端部に設け
ることでもよく、あるいは、図示していないが、図１と
図７と、あるいは図７と図８をそれぞれ組合せた構成と
することも可能である。For example, as shown in FIG. 7, the expansion mechanism section 9
And the compression mechanism section 11 between the first and second rotary shafts 1
You may make it provide in the connection area of 9,63. Alternatively, as shown in FIG. 8, it may be provided at the shaft end portion of the second rotary shaft 63 of the compression mechanism portion 11 on the opposite side of the expansion mechanism portion 9, or, although not shown, as shown in FIG. It is also possible to adopt a configuration in which FIG. 7 or a combination of FIG. 7 and FIG. 8 is combined.

【００４３】[0043]

【発明の効果】以上、説明したように、この発明の流体
機械によれば、起動用の電動要素を構成するロータがな
くても、フライホイールによってトルク変動の平準化が
図れるようになり、安定した運転状態が得られるように
なる。As described above, according to the fluid machine of the present invention, even if there is no rotor constituting the electric starting element, the flywheel can equalize the torque fluctuations and stabilize the torque. The operating condition can be obtained.

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

【図１】この発明に係る流体機械を示した概要切断面。FIG. 1 is a schematic sectional view showing a fluid machine according to the present invention.

【図２】フライホイールの取付状態を示した拡大断面
図。FIG. 2 is an enlarged cross-sectional view showing a mounted state of a flywheel.

【図３】膨張機構部の膨張室、ローラ、ブレードの関係
を示した切断面図。FIG. 3 is a sectional view showing a relationship among an expansion chamber, a roller, and a blade of an expansion mechanism section.

【図４】圧縮機構部の圧縮室、ローラ、ブレードの関係
を示した切断面図。FIG. 4 is a cross-sectional view showing the relationship between a compression chamber of a compression mechanism section, a roller, and a blade.

【図５】ツインに形成された一方のシリンダ側の吸込ポ
ートの説明図。FIG. 5 is an explanatory view of a suction port on one cylinder side formed in a twin shape.

【図６】ツインに形成された他方のシリンダ側の吸込ポ
ートの説明図。FIG. 6 is an explanatory view of a suction port on the other cylinder side formed in a twin shape.

【図７】フライホイールの取付位置を、膨張機構部と圧
縮機構部の間に設けた図１と同様の概要切断面図。FIG. 7 is a schematic cross-sectional view similar to FIG. 1 in which a flywheel mounting position is provided between an expansion mechanism section and a compression mechanism section.

【図８】フライホイールの取付位置を、膨張機構部の反
対側となる圧縮機構部の軸端側に設けた図１と同様の概
要切断面図。FIG. 8 is a schematic sectional view similar to FIG. 1 in which the attachment position of the flywheel is provided on the shaft end side of the compression mechanism portion opposite to the expansion mechanism portion.

【符号の説明】[Explanation of symbols]

７ 密閉ケース ９ 膨張機構部 １１ 圧縮機構部 ５０ フライホイール 7 Airtight case 9 Expansion mechanism 11 Compression mechanism 50 Flywheel

───────────────────────────────────────────────────── フロントページの続き (72)発明者 齊藤 和夫 神奈川県横浜市磯子区新杉田町８番地 株 式会社東芝住空間システム技術研究所内 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Kazuo Saito 8 Shinsugita-cho, Isogo-ku, Yokohama, Kanagawa Prefecture

Claims (4)

【特許請求の範囲】[Claims] 【請求項１】 ランキンサイクルを構成する膨張機構部
と、膨張機構部からの回転動力により冷凍サイクルを構
成する圧縮機構部とを同一密閉ケース内に組込み、前記
膨張機構部を、高圧ガスによって起動時の回転動力を発
生させる回転動力が発生手段とする一方、前記膨張機構
部で発生するトルク変動を平準化するフライホイールを
備えていることを特徴とする流体機械。1. An expansion mechanism section that constitutes a Rankine cycle and a compression mechanism section that constitutes a refrigeration cycle by rotational power from the expansion mechanism section are incorporated in the same sealed case, and the expansion mechanism section is started by high-pressure gas. A fluid machine is provided with a flywheel for equalizing torque fluctuations generated in the expansion mechanism unit, while using a rotational power for generating rotational power as a generating means. 【請求項２】 フライホイールを、圧縮機構部の反対側
となる膨張機構部の回転シャフト端部に設けた配置とす
ることを特徴とする請求項１記載の流体機械。2. The fluid machine according to claim 1, wherein the flywheel is arranged at the end of the rotary shaft of the expansion mechanism opposite to the compression mechanism. 【請求項３】 フライホイールを、圧縮機構部と膨張機
構部の間で、圧縮機構部と膨張機構部とをつなぐ回転シ
ャフトに設けた配置することを特徴とする請求項１記載
の流体機械。3. The fluid machine according to claim 1, wherein the flywheel is arranged on a rotary shaft connecting the compression mechanism section and the expansion mechanism section between the compression mechanism section and the expansion mechanism section. 【請求項４】 フライホイールを、膨張機構部の反対側
となる圧縮機構部の回転シャフト端部に設けた配置する
ことを特徴とする請求項１記載の流体機械。4. The fluid machine according to claim 1, wherein the flywheel is arranged at the end of the rotary shaft of the compression mechanism opposite to the expansion mechanism.
JP5769896A 1996-03-14 1996-03-14 Fluid machine Pending JPH09250474A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP5769896A JPH09250474A (en) 1996-03-14 1996-03-14 Fluid machine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP5769896A JPH09250474A (en) 1996-03-14 1996-03-14 Fluid machine

Publications (1)

Publication Number Publication Date
JPH09250474A true JPH09250474A (en) 1997-09-22

Family

ID=13063166

Family Applications (1)

Application Number Title Priority Date Filing Date
JP5769896A Pending JPH09250474A (en) 1996-03-14 1996-03-14 Fluid machine

Country Status (1)

Country Link
JP (1) JPH09250474A (en)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6338912B1 (en) 1998-11-18 2002-01-15 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Fuel cell system having common scroll type compressor and regenerator
US6361890B1 (en) 1998-11-09 2002-03-26 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Fuel cell system having scroll type compressor and regenerator
US6425746B1 (en) 1999-09-28 2002-07-30 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Compressor and regenerator for fuel cell
US6506512B1 (en) 1999-09-28 2003-01-14 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Compression regenerative machine for fuel cell
US7104061B2 (en) 2003-04-22 2006-09-12 Denso Corporation Fluid machine
JP2007332974A (en) * 2007-09-10 2007-12-27 Daikin Ind Ltd Fluid machinery

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6361890B1 (en) 1998-11-09 2002-03-26 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Fuel cell system having scroll type compressor and regenerator
US6338912B1 (en) 1998-11-18 2002-01-15 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Fuel cell system having common scroll type compressor and regenerator
US6425746B1 (en) 1999-09-28 2002-07-30 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Compressor and regenerator for fuel cell
US6506512B1 (en) 1999-09-28 2003-01-14 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Compression regenerative machine for fuel cell
US7104061B2 (en) 2003-04-22 2006-09-12 Denso Corporation Fluid machine
JP2007332974A (en) * 2007-09-10 2007-12-27 Daikin Ind Ltd Fluid machinery

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