JP2020148177A - Scroll expander - Google Patents

Scroll expander Download PDF

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JP2020148177A
JP2020148177A JP2019048617A JP2019048617A JP2020148177A JP 2020148177 A JP2020148177 A JP 2020148177A JP 2019048617 A JP2019048617 A JP 2019048617A JP 2019048617 A JP2019048617 A JP 2019048617A JP 2020148177 A JP2020148177 A JP 2020148177A
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scroll
pressure
communication hole
expansion
expansion chamber
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JP7287022B2 (en
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賢哲 安嶋
Kentetsu Yasujima
賢哲 安嶋
時空 吉田
Tokiaki Yoshida
時空 吉田
岩崎　正道
Masamichi Iwasaki
正道 岩崎
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Fuji Electric Co Ltd
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Fuji Electric Co Ltd
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Abstract

To provide a scroll expander capable of varying the expansion ratio of the scroll expander to suppress a decrease in recovery power due to a decrease in expansion efficiency.SOLUTION: A scroll expander includes: an expansion mechanism that meshes a fixed scroll 11 and an orbital scroll 12 with each other to form expansion chambers; a main suction port 20 through which a high-pressure working fluid is sucked in with orbiting of the orbital scroll 12; an inner communication port 31i and an outer communication port 31o, which are separated from the main suction port 20 and work as auxiliary suction ports communicating with the insides of the expansion chambers; an inner shutoff valve 41i and an outer shutoff valve 41o, which open and close the inner communication port 31i and the outer communication port 31o, respectively. When the expansion mechanism is operated, the inner communication port 31i communicates with the inner expansion chamber that is formed first in the inner periphery of the orbital scroll 12, and the outer communication port 31o communicates with the outer expansion chamber that is formed first in the outer periphery of the orbital scroll 12.SELECTED DRAWING: Figure 1

Description

本発明は、スクロール膨張機の膨張比を可変にして膨張効率の低下による回収動力の低下を抑えるスクロール膨張機に関する。 The present invention relates to a scroll expander in which the expansion ratio of the scroll expander is made variable to suppress a decrease in recovery power due to a decrease in expansion efficiency.

容積型膨張機の一つとしてスクロール膨張機がある。スクロール膨張機は、固定スクロールの板状渦巻歯が旋回スクロールの板状渦巻歯に互いに噛み合った状態で、旋回スクロールが固定スクロールの中心に対して旋回することによって、固定スクロールの中心の吸入口から吸入された冷媒や蒸気などの作動流体を膨張させ、外周側の吐出口から吐出する。スクロール膨張機は、中心部の吸入容積と外側の吐出容積との容積比が幾何的に一つに決定される。 There is a scroll expander as one of the positive displacement expanders. The scroll expander is a state in which the plate-shaped spiral teeth of the fixed scroll mesh with each other with the plate-shaped spiral teeth of the swivel scroll, and the swivel scroll swivels with respect to the center of the fixed scroll from the suction port at the center of the fixed scroll. The working fluid such as the sucked refrigerant and steam is expanded and discharged from the discharge port on the outer peripheral side. In the scroll expander, the volume ratio of the suction volume at the center and the discharge volume at the outside is geometrically determined to be one.

なお、特許文献１には、スクロール膨張機の膨張室に連通するサブ吸入ポートを設け、このサブ吸入ポートの開度を調整することによって、スクロール膨張機に吸入される冷媒の圧力が目標圧力となるように制御する膨張機が記載されている。 In Patent Document 1, a sub suction port communicating with the expansion chamber of the scroll expander is provided, and by adjusting the opening degree of the sub suction port, the pressure of the refrigerant sucked into the scroll expander becomes the target pressure. An inflator controlled to be is described.

特開２０１３−１４２３５５号公報Japanese Unexamined Patent Publication No. 2013-142355

ところで、スクロール膨張機では、容積比が幾何的に一つに決定されるため、膨張比も一定となる。この膨張比が一定であることから、スクロール膨張機では、設定された運転条件以外の膨張処理が行われた場合、膨張不足や過膨張が発生し、膨張効率の低下により作動流体から回収する動力が低下してしまうという問題があった。 By the way, in the scroll expander, since the volume ratio is geometrically determined to be one, the expansion ratio is also constant. Since this expansion ratio is constant, in the scroll expander, when expansion processing other than the set operating conditions is performed, insufficient expansion or overexpansion occurs, and the power recovered from the working fluid due to a decrease in expansion efficiency. There was a problem that

本発明は、上記に鑑みてなされたものであって、スクロール膨張機の膨張比を可変にして膨張効率の低下による回収動力の低下を抑えることができるスクロール膨張機を提供することを目的とする。 The present invention has been made in view of the above, and an object of the present invention is to provide a scroll expander capable of varying the expansion ratio of the scroll expander to suppress a decrease in recovery power due to a decrease in expansion efficiency. ..

上述した課題を解決し、目的を達成するために、本発明にかかるスクロール膨張機は、吸入した高圧作動流体を膨張して低圧作動流体を吐出するスクロール膨張機であって、固定スクロールと旋回スクロールとを噛み合わせて膨張室を形成する膨張機構と、前記旋回スクロールの旋回に伴って前記高圧作動流体が吸入される主吸入口と、前記主吸入口から隔離され、前記高圧作動流体を前記膨張室内に吸入する副吸入口と、前記副吸入口を開閉する開閉弁と、前記開閉弁を制御する制御部と、を備え、前記副吸入口は、前記膨張機構作動時に、前記旋回スクロールの内周に最初に形成される内側膨張室に前記高圧作動流体を吸入する内側連通孔と、前記旋回スクロールの外周に最初に形成される外側膨張室に前記高圧作動流体を吸入する外側連通孔と、で一対となるように形成されることを特徴とする。 In order to solve the above-mentioned problems and achieve the object, the scroll expander according to the present invention is a scroll expander that expands the sucked high-pressure working fluid and discharges the low-pressure working fluid, and is a fixed scroll and a swivel scroll. The expansion mechanism that forms an expansion chamber by meshing with the main suction port, the main suction port into which the high-pressure working fluid is sucked as the swivel scroll swivels, and the main suction port are separated from the main suction port, and the high-pressure working fluid is expanded. A sub-suction port for sucking into a room, an on-off valve for opening and closing the sub-suction port, and a control unit for controlling the on-off valve are provided, and the sub-suction port is inside the swivel scroll when the expansion mechanism is operated. An inner communication hole for sucking the high-pressure working fluid into the inner expansion chamber first formed on the circumference, and an outer communication hole for sucking the high-pressure working fluid into the outer expansion chamber first formed on the outer periphery of the swivel scroll. It is characterized in that it is formed so as to form a pair.

また、本発明にかかるスクロール膨張機は、上記の発明において、一対の前記副吸入口は、前記主吸入口を中心として互いに対称となる位置に配置されていることを特徴とする。 Further, the scroll expander according to the present invention is characterized in that, in the above invention, the pair of the sub suction ports are arranged at positions symmetrical with each other about the main suction port.

また、本発明にかかるスクロール膨張機は、上記の発明において、前記高圧作動流体の吸入圧力を検出する高圧圧力検出部と、前記低圧作動流体の吐出圧力を検出する低圧圧力検出部と、をさらに備え、前記吐出圧力に対する前記吸入圧力の圧力比に応じて、対となる前記開閉弁を同時に開閉制御することを特徴とする。 Further, in the above invention, the scroll expander according to the present invention further includes a high pressure pressure detecting unit for detecting the suction pressure of the high pressure working fluid and a low pressure pressure detecting unit for detecting the discharge pressure of the low pressure working fluid. It is characterized in that the paired on-off valve is simultaneously opened and closed according to the pressure ratio of the suction pressure to the discharge pressure.

また、本発明にかかるスクロール膨張機は、上記の発明において、前記内側連通孔は、前記固定スクロールに形成された板状渦巻歯の外側に形成され、前記外側連通孔は、前記固定スクロールに形成された板状渦巻歯の内側に形成されることを特徴とする。 Further, in the scroll expander according to the present invention, in the above invention, the inner communication hole is formed on the outside of the plate-shaped spiral tooth formed on the fixed scroll, and the outer communication hole is formed on the fixed scroll. It is characterized in that it is formed inside the plate-shaped spiral tooth.

また、本発明にかかるスクロール膨張機は、上記の発明において、前記副吸入口の径は、前記旋回スクロールに形成された板状渦巻歯の厚さよりも小さいことを特徴とする。 Further, the scroll expander according to the present invention is characterized in that, in the above invention, the diameter of the sub suction port is smaller than the thickness of the plate-shaped spiral teeth formed on the swirl scroll.

また、本発明にかかるスクロール膨張機は、上記の発明において、前記副吸入口の形成位置から前記旋回スクロールの旋回角が進んだ位置に、さらに一対以上の前記副吸入口が形成されていることを特徴とする。 Further, in the scroll expander according to the present invention, in the above invention, a pair or more of the sub suction ports are further formed at a position where the swivel angle of the swivel scroll is advanced from the formation position of the sub suction port. It is characterized by.

また、本発明にかかるスクロール膨張機は、上記の発明において、複数対の前記副吸入口は、それぞれ前記旋回角が１８０°進む毎に設けられることを特徴とする。 Further, the scroll expander according to the present invention is characterized in that, in the above invention, a plurality of pairs of the sub suction ports are provided every time the turning angle advances by 180 °.

また、本発明にかかるスクロール膨張機は、上記の発明において、前記制御部は、前記圧力比の所定値を一つ以上設定し、前記所定値に達するに応じて、一対または複数対の前記開閉弁を段階的に制御することを特徴とする。 Further, in the scroll expander according to the present invention, in the above invention, the control unit sets one or more predetermined values of the pressure ratio, and depending on reaching the predetermined value, a pair or a plurality of pairs of the opening / closing It is characterized by controlling the valve step by step.

また、本発明にかかるスクロール膨張機は、上記の発明において、前記旋回スクロールの旋回軸に連結した動力回収機を備えたことを特徴とする。 Further, the scroll expander according to the present invention is characterized in that, in the above invention, the power recovery machine connected to the swivel shaft of the swivel scroll is provided.

本発明によれば、スクロール膨張機の膨張比を可変にして膨張効率の低下による回収動力の低下を抑えることができる。 According to the present invention, the expansion ratio of the scroll expander can be made variable to suppress a decrease in recovery power due to a decrease in expansion efficiency.

図１は、本発明の実施の形態であるスクロール膨張機の構成を示す断面図である。FIG. 1 is a cross-sectional view showing the configuration of a scroll expander according to an embodiment of the present invention. 図２は、図１に示したスクロール膨張機本体のＡ−Ａ線断面図である。FIG. 2 is a cross-sectional view taken along the line AA of the scroll expander main body shown in FIG. 図３は、内側連通孔、外側連通孔、追加内側連通孔及び追加外側連通孔を開にした状態における旋回スクロールが０°のときのスクロール膨張機本体の膨張行程を示す図である。FIG. 3 is a diagram showing an expansion stroke of the scroll expander main body when the swivel scroll is 0 ° in a state where the inner communication hole, the outer communication hole, the additional inner communication hole and the additional outer communication hole are opened. 図４は、内側連通孔、外側連通孔、追加内側連通孔及び追加外側連通孔を開にした状態における旋回スクロールが９０°のときのスクロール膨張機本体の膨張行程を示す図である。FIG. 4 is a diagram showing an expansion stroke of the scroll expander main body when the swivel scroll is 90 ° in a state where the inner communication hole, the outer communication hole, the additional inner communication hole and the additional outer communication hole are opened. 図５は、内側連通孔、外側連通孔、追加内側連通孔及び追加外側連通孔を開にした状態における旋回スクロールが１８０°のときのスクロール膨張機本体の膨張行程を示す図である。FIG. 5 is a diagram showing an expansion stroke of the scroll expander main body when the swivel scroll is 180 ° in a state where the inner communication hole, the outer communication hole, the additional inner communication hole, and the additional outer communication hole are opened. 図６は、内側連通孔、外側連通孔、追加内側連通孔及び追加外側連通孔を開にした状態における旋回スクロールが２７０°のときのスクロール膨張機本体の膨張行程を示す図である。FIG. 6 is a diagram showing an expansion stroke of the scroll expander main body when the swivel scroll is 270 ° in a state where the inner communication hole, the outer communication hole, the additional inner communication hole and the additional outer communication hole are opened. 図７は、内側連通孔、外側連通孔、追加内側連通孔及び追加外側連通孔を開にした状態における旋回スクロールが３６０°（０°）のときのスクロール膨張機本体の膨張行程を示す図である。FIG. 7 is a diagram showing an expansion stroke of the scroll expander main body when the swivel scroll is 360 ° (0 °) with the inner communication hole, the outer communication hole, the additional inner communication hole, and the additional outer communication hole open. is there. 図８は、制御部による内側開閉弁、外側開閉弁、追加内側開閉弁及び追加外側開閉弁の開閉制御処理手順を示すフローチャートである。FIG. 8 is a flowchart showing an opening / closing control processing procedure of the inner on-off valve, the outer on-off valve, the additional inner on-off valve, and the additional outer on-off valve by the control unit. 図９は、本実施の形態による膨張損失の低減を説明する説明図である。FIG. 9 is an explanatory diagram illustrating reduction of expansion loss according to the present embodiment. 図１０は、追加内側連通孔及び追加外側連通孔の設置の変形例を示す図である。FIG. 10 is a diagram showing a modified example of the installation of the additional inner communication hole and the additional outer communication hole. 図１１は、追加外側連通孔などの連通孔の径と旋回スクロールの板状渦巻歯の厚さとの関係を示す図である。FIG. 11 is a diagram showing the relationship between the diameter of the communication hole such as the additional outer communication hole and the thickness of the plate-shaped spiral tooth of the swivel scroll. 図１２は、図１１における連通孔が長穴である場合における、連通孔の径と旋回スクロールの板状渦巻歯の厚さとの関係を示す図である。FIG. 12 is a diagram showing the relationship between the diameter of the communication hole and the thickness of the plate-shaped spiral tooth of the swivel scroll when the communication hole in FIG. 11 is a long hole.

以下、添付図面を参照してこの発明を実施するための形態について説明する。 Hereinafter, embodiments for carrying out the present invention will be described with reference to the accompanying drawings.

＜スクロール膨張機の構成＞
図１は、本発明の実施の形態であるスクロール膨張機１の構成を示す断面図である。また、図２は、図１に示したスクロール膨張機本体２のＡ−Ａ線断面図である。 <Structure of scroll expander>
FIG. 1 is a cross-sectional view showing the configuration of the scroll expander 1 according to the embodiment of the present invention. Further, FIG. 2 is a cross-sectional view taken along the line AA of the scroll expander main body 2 shown in FIG.

図１に示すように、スクロール膨張機１は、スクロール膨張機本体２、発電機３、制御部４及び表示操作部５を有する。スクロール膨張機本体２は、配管Ｌ１から高圧室１７を介して吸入される作動流体の一例である高圧蒸気ＨＷを膨張して、配管Ｌ２から低圧蒸気ＬＷを吐出する。スクロール膨張機本体２は、固定スクロール１１と旋回スクロール１２とを有した膨張機構である。固定スクロール１１と旋回スクロール１２とは、それぞれ板状渦巻歯が互いに噛み合わされた状態で、旋回スクロール１２が固定スクロール１１の中心２０ａを旋回し、この旋回に伴って主吸入口２０から吸入される高圧蒸気ＨＷを、固定スクロール１１と旋回スクロール１２との間に形成される膨張室によって膨張させて低圧蒸気ＬＷを生成する。なお、固定スクロール１１および旋回スクロール１２の各内壁及び各外壁は、インボリュート曲線ＬＩを形成している。 As shown in FIG. 1, the scroll expander 1 includes a scroll expander main body 2, a generator 3, a control unit 4, and a display operation unit 5. The scroll expander main body 2 expands the high-pressure steam HW, which is an example of the working fluid sucked from the pipe L1 through the high-pressure chamber 17, and discharges the low-pressure steam LW from the pipe L2. The scroll expander main body 2 is an expansion mechanism having a fixed scroll 11 and a swivel scroll 12. The fixed scroll 11 and the swivel scroll 12 are in a state where the plate-shaped spiral teeth are meshed with each other, and the swivel scroll 12 swivels around the center 20a of the fixed scroll 11 and is sucked from the main suction port 20 with this swivel. The high-pressure steam HW is expanded by an expansion chamber formed between the fixed scroll 11 and the swirl scroll 12 to generate a low-pressure steam LW. The inner wall and the outer wall of the fixed scroll 11 and the swivel scroll 12 form an involute curve LI.

固定スクロール１１および旋回スクロール１２は、筐体１０ａ，１０ｂによって形成された筐体１０内に設けられる。高圧蒸気ＨＷの膨張は、旋回スクロール１２が固定スクロール１１に対して回転方向ＡＬで公転運動することによって行われる。クランクシャフト１３は、旋回スクロール１２の旋回に伴って回転する軸であり、軸回転は発電機３に伝達される。スラスト軸受１４は、旋回スクロール１２の回転に対してスラスト方向に軸支する。クランクシャフト１３には、旋回スクロール１２の公転運動に対する回転バランスをとるためのバランスウェイト１５が設けられている。 The fixed scroll 11 and the swivel scroll 12 are provided in the housing 10 formed by the housings 10a and 10b. The expansion of the high-pressure steam HW is performed by the swivel scroll 12 revolving with respect to the fixed scroll 11 in the rotation direction AL. The crankshaft 13 is a shaft that rotates as the swivel scroll 12 turns, and the shaft rotation is transmitted to the generator 3. The thrust bearing 14 pivotally supports the rotation of the swivel scroll 12 in the thrust direction. The crankshaft 13 is provided with a balance weight 15 for balancing the rotation of the swivel scroll 12 with respect to the revolutionary motion.

配管Ｌ１には、高圧蒸気ＨＷの吸入圧力Ｐｓを検出して制御部４に出力する高圧圧力検出部２２が設けられる。また、配管Ｌ１には、高圧蒸気ＨＷの吸入温度Ｔｐを検出して制御部４に出力する高圧温度検出部２３を有する。また、配管Ｌ２には、低圧蒸気ＬＷの吐出圧力Ｐｄを検出して制御部４に出力する低圧圧力検出部２４を有する。また、配管Ｌ２には、低圧蒸気ＬＷの吐出温度Ｔｄを検出して制御部４に出力する低圧温度検出部２５を有する。 The pipe L1 is provided with a high pressure pressure detecting unit 22 that detects the suction pressure Ps of the high pressure steam HW and outputs it to the control unit 4. Further, the pipe L1 has a high-pressure temperature detection unit 23 that detects the suction temperature Tp of the high-pressure steam HW and outputs it to the control unit 4. Further, the pipe L2 has a low pressure pressure detecting unit 24 that detects the discharge pressure Pd of the low pressure steam LW and outputs it to the control unit 4. Further, the pipe L2 has a low pressure temperature detecting unit 25 that detects the discharge temperature Td of the low pressure steam LW and outputs it to the control unit 4.

図１及び図２に示すように、固定スクロール１１には、旋回スクロール１２の旋回に伴って高圧蒸気ＨＷが吸入される主吸入口２０から隔離されて旋回スクロール１２と固定スクロール１１との間であって旋回スクロール１２の内側に最初に形成される初段内側膨張室Ｒｉ１に連通して高圧蒸気ＨＷを高圧室１７から流入させる内側連通孔３１ｉと、旋回スクロール１２の旋回に伴って主吸入口２０から隔離されて旋回スクロール１２と固定スクロール１１との間であって旋回スクロール１２の外側に最初に形成された初段外側膨張室Ｒｏ１に連通して高圧蒸気ＨＷを高圧室１７から流入させる外側連通孔３１ｏとが形成される。 As shown in FIGS. 1 and 2, the fixed scroll 11 is isolated between the swivel scroll 12 and the fixed scroll 11 so as to be isolated from the main suction port 20 into which the high-pressure steam HW is sucked as the swivel scroll 12 turns. There is an inner communication hole 31i that communicates with the first stage inner expansion chamber Ri1 formed inside the swivel scroll 12 to allow high-pressure steam HW to flow in from the high-pressure chamber 17, and a main suction port 20 as the swivel scroll 12 swivels. An outer communication hole that allows high-pressure steam HW to flow in from the high-pressure chamber 17 between the swivel scroll 12 and the fixed scroll 11 and communicates with the first-stage outer expansion chamber Ro1 initially formed on the outside of the swivel scroll 12. 31o and are formed.

また、内側連通孔３１ｉの位置から旋回スクロール１２の旋回角が１８０°進んだ位置に設けられて初段内側膨張室Ｒｉ１に連通する追加内側連通孔３２ｉと、外側連通孔３１ｏの位置から旋回スクロール１２の旋回角が１８０°進んだ位置に設けられて初段外側膨張室Ｒｏ１に連通する追加外側連通孔３２ｏとが形成される。内側連通孔３１ｉ、外側連通孔３１ｏ、追加内側連通孔３２ｉ及び追加外側連通孔３２ｏは、副吸入口の一例である。 Further, an additional inner communication hole 32i that is provided at a position where the turning angle of the swivel scroll 12 is 180 ° advanced from the position of the inner communication hole 31i and communicates with the first stage inner expansion chamber Ri1, and a swivel scroll 12 from the position of the outer communication hole 31o. An additional outer communication hole 32o that is provided at a position where the turning angle of the above is advanced by 180 ° and communicates with the first stage outer expansion chamber Ro1 is formed. The inner communication hole 31i, the outer communication hole 31o, the additional inner communication hole 32i, and the additional outer communication hole 32o are examples of the auxiliary suction port.

なお、内側連通孔３１ｉ及び追加内側連通孔３２ｉは、固定スクロール１１の板状渦巻歯の外側に沿って形成され、外側連通孔３１ｏ及び追加外側連通孔３２ｏは、固定スクロール１１の板状渦巻歯の内側に沿って形成される。また、内側連通孔３１ｉと外側連通孔３１ｏとは、固定スクロール１１の中心２０ａを通る直線上に配置される。また、追加内側連通孔３２ｉと追加外側連通孔３２ｏとは、固定スクロール１１の中心２０ａを通る直線上に配置される。 The inner communication hole 31i and the additional inner communication hole 32i are formed along the outside of the plate-shaped spiral tooth of the fixed scroll 11, and the outer communication hole 31o and the additional outer communication hole 32o are the plate-shaped spiral tooth of the fixed scroll 11. Formed along the inside of the. Further, the inner communication hole 31i and the outer communication hole 31o are arranged on a straight line passing through the center 20a of the fixed scroll 11. Further, the additional inner communication hole 32i and the additional outer communication hole 32o are arranged on a straight line passing through the center 20a of the fixed scroll 11.

内側連通孔３１ｉ、外側連通孔３１ｏ、追加内側連通孔３２ｉ及び追加外側連通孔３２ｏの高圧室１７側には、それぞれ、内側開閉弁４１ｉ、外側開閉弁４１ｏ、追加内側開閉弁４２ｉ及び追加外側開閉弁４２ｏが設けられる。内側開閉弁４１ｉ、外側開閉弁４１ｏ、追加内側開閉弁４２ｉ及び追加外側開閉弁４２ｏは、制御部４によって、内側開閉弁４１ｉと外側開閉弁４１ｏとの対、及び、追加内側開閉弁４２ｉと追加外側開閉弁４２ｏとの対をそれぞれ同時に開閉制御される。 On the high-pressure chamber 17 side of the inner communication hole 31i, the outer communication hole 31o, the additional inner communication hole 32i and the additional outer communication hole 32o, the inner on-off valve 41i, the outer on-off valve 41o, the additional inner on-off valve 42i and the additional outer on-off valve 42i, respectively. A valve 42o is provided. The inner on-off valve 41i, the outer on-off valve 41o, the additional inner on-off valve 42i, and the additional outer on-off valve 42o are added by the control unit 4 to the pair of the inner on-off valve 41i and the outer on-off valve 41o, and the additional inner on-off valve 42i. The opening and closing of each pair with the outer on-off valve 42o is controlled at the same time.

なお、発電機３は、旋回スクロール１２の旋回軸であるクランクシャフト１３に連結して高圧蒸気ＨＷの膨張に伴う軸動力を回収する動力回収機として機能し、発電された電気エネルギーを外部出力する。 The generator 3 functions as a power recovery machine connected to the crankshaft 13 which is the swing shaft of the swivel scroll 12 to recover the shaft power accompanying the expansion of the high-pressure steam HW, and outputs the generated electric energy to the outside. ..

また、表示操作部５は、例えばタッチパネルであり、制御部４に対する各種操作入力及び各種表示出力を行う入出力デバイスである。 Further, the display operation unit 5 is, for example, a touch panel, and is an input / output device that performs various operation inputs and various display outputs to the control unit 4.

図２に示すように、スクロール膨張機本体２では、主吸入口２０近傍に形成された初段内側膨張室Ｒｉ１及び初段外側膨張室Ｒｏ１は、旋回スクロール１２が回転方向ＡＬに旋回することによって、順次周方向に沿って外側に移動しつつ膨張する。周方向外側の初段内側膨張室Ｒｉ１´及び初段外側膨張室Ｒｏ１´は、旋回スクロール１２が３回転した状態を示している。初段内側膨張室Ｒｉ１と初段外側膨張室Ｒｏ１とを加えた容積Ｖ１は、初段内側膨張室Ｒｉ１´と初段外側膨張室Ｒｏ１´とを加えた容積Ｖ２（＞容積Ｖ１）となり、高圧蒸気ＨＷは、旋回スクロール１２の旋回によって膨張される。 As shown in FIG. 2, in the scroll expander main body 2, the first-stage inner expansion chamber Ri1 and the first-stage outer expansion chamber Ro1 formed in the vicinity of the main suction port 20 are sequentially rotated by the swivel scroll 12 in the rotation direction AL. It expands while moving outward along the circumferential direction. The first stage inner expansion chamber Ri1'and the first stage outer expansion chamber Ro1' on the outer side in the circumferential direction show a state in which the swivel scroll 12 has rotated three times. The volume V1 including the first-stage inner expansion chamber Ri1 and the first-stage outer expansion chamber Ro1 becomes the volume V2 (> volume V1) including the first-stage inner expansion chamber Ri1'and the first-stage outer expansion chamber Ro1', and the high-pressure steam HW is It is expanded by the turning of the turning scroll 12.

＜膨張行程＞
次に、内側連通孔３１ｉ、外側連通孔３１ｏ、追加内側連通孔３２ｉ及び追加外側連通孔３２ｏを開にした状態におけるスクロール膨張機本体２の膨張行程について説明する。図３〜図７は、内側連通孔３１ｉ、外側連通孔３１ｏ、追加内側連通孔３２ｉ及び追加外側連通孔３２ｏを開にした状態におけるスクロール膨張機本体２の膨張行程を示す図である。 <Expansion stroke>
Next, the expansion stroke of the scroll expander main body 2 in a state where the inner communication hole 31i, the outer communication hole 31o, the additional inner communication hole 32i, and the additional outer communication hole 32o are opened will be described. 3 to 7 are views showing an expansion stroke of the scroll expander main body 2 in a state where the inner communication hole 31i, the outer communication hole 31o, the additional inner communication hole 32i, and the additional outer communication hole 32o are opened.

図３に示すように、まず旋回スクロール１２の旋回角０°において、固定スクロール１１と旋回スクロール１２とによって主吸入口２０近傍に初段内側膨張室Ｒｉ１及び初段外側膨張室Ｒｏ１が形成される。初段内側膨張室Ｒｉ１は、内側連通孔３１ｉによって高圧室１７に連通して高圧蒸気ＨＷが流入可能となる。また、初段外側膨張室Ｒｏ１は、外側連通孔３１ｏによって高圧室１７に連通して高圧蒸気ＨＷが流入可能となる。一方、主吸入口２０周辺の領域ＲＣも、主吸入口２０を介して高圧室１７に連通して高圧蒸気ＨＷが流入される。したがって、初段内側膨張室Ｒｉ１及び初段外側膨張室Ｒｏ１は、領域ＲＣの高圧蒸気ＨＷと同じ高圧状態となり、このまま旋回スクロール１２が旋回しても膨張を開始せず、高圧蒸気ＲＷと同じ高圧状態が維持される。 As shown in FIG. 3, first, at a turning angle of 0 ° of the turning scroll 12, the first stage inner expansion chamber Ri1 and the first stage outer expansion chamber Ro1 are formed in the vicinity of the main suction port 20 by the fixed scroll 11 and the turning scroll 12. The first stage inner expansion chamber Ri1 communicates with the high pressure chamber 17 through the inner communication hole 31i so that the high pressure steam HW can flow in. Further, the first stage outer expansion chamber Ro1 communicates with the high pressure chamber 17 through the outer communication hole 31o so that the high pressure steam HW can flow in. On the other hand, the region RC around the main suction port 20 also communicates with the high pressure chamber 17 via the main suction port 20 and the high pressure steam HW flows in. Therefore, the first-stage inner expansion chamber Ri1 and the first-stage outer expansion chamber Ro1 are in the same high-pressure state as the high-pressure steam HW in the region RC, and even if the swivel scroll 12 is swiveled as it is, expansion does not start, and the same high-pressure state as the high-pressure steam RW is maintained. Be maintained.

その後、図４に示すように、旋回スクロール１２が旋回角９０°になると、初段内側膨張室Ｒｉ１は、さらに追加内側連通孔３２ｉを介して高圧室１７に連通して高圧蒸気ＨＷと同じ高圧状態が維持され、膨張は行われない。同様に、初段外側膨張室Ｒｏ１も、さらに追加外側連通孔３２ｏを介して高圧室１７に連通して高圧蒸気ＨＷと同じ高圧状態が維持され、膨張は行われない。 After that, as shown in FIG. 4, when the swivel scroll 12 reaches a swivel angle of 90 °, the first stage inner expansion chamber Ri1 further communicates with the high pressure chamber 17 through the additional inner communication hole 32i, and is in the same high pressure state as the high pressure steam HW. Is maintained and no expansion occurs. Similarly, the first-stage outer expansion chamber Ro1 is further communicated with the high-pressure chamber 17 via the additional outer communication hole 32o to maintain the same high-pressure state as the high-pressure steam HW, and is not expanded.

その後、図５に示すように、旋回スクロール１２が旋回角１８０°になると、初段内側膨張室Ｒｉ１は、追加内側連通孔３２ｉのみを介して高圧室１７に連通して高圧蒸気ＨＷと同じ高圧状態が維持され、膨張は行われない。同様に、初段外側膨張室Ｒｏ１も、追加外側連通孔３２ｏのみを介して高圧室１７に連通して高圧蒸気ＨＷと同じ高圧状態が維持され、膨張は行われない。なお、この旋回スクロール１２が旋回角１８０°のとき、内側連通孔３１ｉ及び外側連通孔３１ｏは、旋回スクロール１２の板状渦巻歯によって塞がれる。 After that, as shown in FIG. 5, when the swivel scroll 12 reaches a swivel angle of 180 °, the first stage inner expansion chamber Ri1 communicates with the high pressure chamber 17 only through the additional inner communication hole 32i, and is in the same high pressure state as the high pressure steam HW. Is maintained and no expansion occurs. Similarly, the first-stage outer expansion chamber Ro1 also communicates with the high-pressure chamber 17 only through the additional outer communication hole 32o to maintain the same high-pressure state as the high-pressure steam HW, and is not expanded. When the swivel scroll 12 has a swivel angle of 180 °, the inner communication hole 31i and the outer communication hole 31o are closed by the plate-shaped spiral teeth of the swirl scroll 12.

その後、図６に示すように、旋回スクロール１２が旋回角２７０°になると、この場合も、図３（ｃ）と同様に、初段内側膨張室Ｒｉ１は、追加内側連通孔３２ｉのみを介して高圧室１７に連通して高圧蒸気ＲＷと同じ高圧状態が維持され、膨張は行われない。同様に、初段外側膨張室Ｒｏ１も、追加外側連通孔３２ｏのみを介して高圧室１７に連通して高圧蒸気ＲＷと同じ高圧状態が維持され、膨張は行われない。一方、この段階では、次段の内側膨張室及び外側膨張室は形成されておらず、内側連通孔３１ｉ及び外側連通孔３１ｏは、主吸入口２０周辺の領域ＲＣに連通し、主吸入口２０とともに、主吸入口２０周辺の領域ＲＣと高圧室１７との間を連通して高圧蒸気ＨＷと同じ高圧状態に維持する。したがって、主吸入口２０から初段内側膨張室Ｒｉ１及び初段外側膨張室Ｒｏ１までの領域は、すべて高圧蒸気ＨＷと同じ高圧状態となり、膨張が行われない。 After that, as shown in FIG. 6, when the turning scroll 12 reaches the turning angle of 270 °, the first stage inner expansion chamber Ri1 also has a high pressure through only the additional inner communication hole 32i, as in FIG. 3C. It communicates with the chamber 17 and maintains the same high pressure state as the high pressure steam RW, and expansion is not performed. Similarly, the first-stage outer expansion chamber Ro1 also communicates with the high-pressure chamber 17 only through the additional outer communication hole 32o to maintain the same high-pressure state as the high-pressure steam RW, and is not expanded. On the other hand, at this stage, the inner expansion chamber and the outer expansion chamber of the next stage are not formed, and the inner communication hole 31i and the outer communication hole 31o communicate with the region RC around the main suction port 20 and the main suction port 20. At the same time, the region RC around the main suction port 20 and the high pressure chamber 17 are communicated with each other to maintain the same high pressure state as the high pressure steam HW. Therefore, the regions from the main suction port 20 to the first stage inner expansion chamber Ri1 and the first stage outer expansion chamber Ro1 are all in the same high pressure state as the high pressure steam HW, and expansion is not performed.

その後、図７に示すように、旋回スクロールが旋回角３６０°（０°）になると、追加内側連通孔３２ｉ及び追加外側連通孔３２ｏは、旋回スクロール１２の板状渦巻歯によって塞がれる。一方、主吸入口２０近傍には、次段内側膨張室Ｒｉ２及び次段外側膨張室Ｒｏ２が形成され、次段内側膨張室Ｒｉ２及び次段外側膨張室Ｒｏ２は、それぞれ内側連通孔３１ｉ及び外側連通孔３１ｏを介して高圧室１７に連通し、高圧蒸気ＨＷと同じ高圧状態となる。また、主吸入口２０の周辺の領域ＲＣも、主吸入口２０を介して高圧室１７に連通し、高圧蒸気ＨＷと同じ高圧状態となる。したがって、この時点まで、初段内側膨張室Ｒｉ１、初段外側膨張室Ｒｏ１、次段内側膨張室Ｒｉ２、次段外側膨張室Ｒｏ２及び領域ＲＣは、すべて高圧蒸気ＨＷと同じ高圧状態となり、膨張されていない。 After that, as shown in FIG. 7, when the turning scroll reaches a turning angle of 360 ° (0 °), the additional inner communication hole 32i and the additional outer communication hole 32o are closed by the plate-shaped spiral teeth of the turning scroll 12. On the other hand, the next-stage inner expansion chamber Ri2 and the next-stage outer expansion chamber Ro2 are formed in the vicinity of the main suction port 20, and the next-stage inner expansion chamber Ri2 and the next-stage outer expansion chamber Ro2 are connected to the inner communication hole 31i and the outer communication, respectively. It communicates with the high pressure chamber 17 through the hole 31o and becomes the same high pressure state as the high pressure steam HW. Further, the region RC around the main suction port 20 also communicates with the high pressure chamber 17 via the main suction port 20 and becomes the same high pressure state as the high pressure steam HW. Therefore, up to this point, the first stage inner expansion chamber Ri1, the first stage outer expansion chamber Ro1, the next stage inner expansion chamber Ri2, the next stage outer expansion chamber Ro2, and the region RC are all in the same high pressure state as the high pressure steam HW and are not expanded. ..

この旋回角３６０°を過ぎると、初段内側膨張室Ｒｉ１及び初段外側膨張室Ｒｏ１は、高圧室１７と連通することがないので、旋回スクロール１２の旋回に伴って膨張することになる。すなわち、内側開閉弁４１ｉ、外側開閉弁４１ｏ、追加内側開閉弁４２ｉ及び追加外側開閉弁４２ｏをすべて開として、内側連通孔３１ｉ、外側連通孔３１ｏ、追加内側連通孔３２ｉ及び追加外側連通孔３２ｏをすべて高圧室と連通状態とすることによって、旋回スクロール１２が１回転するまでの間、膨張を行わず、１回転後に膨張開始を行うようにしている。すなわち、膨張開始時点を３６０°遅らせるようにしている。この結果、膨張比を小さくできる。 After this turning angle of 360 °, the first-stage inner expansion chamber Ri1 and the first-stage outer expansion chamber Ro1 do not communicate with the high-pressure chamber 17, so that the first-stage inner expansion chamber Ri1 expands with the rotation of the swivel scroll 12. That is, the inner on-off valve 41i, the outer on-off valve 41o, the additional inner on-off valve 42i, and the additional outer on-off valve 42o are all opened, and the inner communication hole 31i, the outer communication hole 31o, the additional inner communication hole 32i, and the additional outer communication hole 32o are opened. By communicating with the high-pressure chamber, expansion is not performed until the swivel scroll 12 makes one rotation, and expansion starts after one rotation. That is, the expansion start time is delayed by 360 °. As a result, the expansion ratio can be reduced.

なお、追加内側開閉弁４２ｉ及び追加外側開閉弁４２ｏを閉じたままにした場合、追加内側連通孔３２ｉ及び追加外側連通孔３２ｏは高圧室１７とは連通しない。この場合、図５に示したように、旋回スクロール１２が旋回角１８０°になるまで、初段内側膨張室Ｒｉ１、初段外側膨張室Ｒｏ１及び領域ＲＣは、高圧蒸気ＨＷと同じ高圧状態になって膨張が行われない。旋回角１８０°からさらに旋回スクロール１２が旋回すると、初段内側膨張室Ｒｉ１及び初段外側膨張室Ｒｏ１はその後、膨張を開始する。すなわち、この場合は、膨張開始点を１８０°まで遅らせることができる。この場合の膨張比は、内側連通孔３１ｉ、外側連通孔３１ｏ、追加内側連通孔３２ｉ及び追加外側連通孔３２ｏをすべて開にした場合に比べて、大きくなるが、内側連通孔３１ｉ、外側連通孔３１ｏ、追加内側連通孔３２ｉ及び追加外側連通孔３２ｏをすべて閉にした場合に比べて小さくなる。 When the additional inner on-off valve 42i and the additional outer on-off valve 42o are left closed, the additional inner communication hole 32i and the additional outer communication hole 32o do not communicate with the high pressure chamber 17. In this case, as shown in FIG. 5, the first stage inner expansion chamber Ri1, the first stage outer expansion chamber Ro1 and the region RC are expanded in the same high pressure state as the high pressure steam HW until the turning scroll 12 has a turning angle of 180 °. Is not done. When the swivel scroll 12 further swivels from the swivel angle of 180 °, the first-stage inner expansion chamber Ri1 and the first-stage outer expansion chamber Ro1 then start expanding. That is, in this case, the expansion start point can be delayed up to 180 °. In this case, the expansion ratio is larger than that when the inner communication hole 31i, the outer communication hole 31o, the additional inner communication hole 32i, and the additional outer communication hole 32o are all opened, but the inner communication hole 31i and the outer communication hole are open. It is smaller than the case where the 31o, the additional inner communication hole 32i and the additional outer communication hole 32o are all closed.

また、内側連通孔３１ｉと外側連通孔３１ｏとは、固定スクロール１１の中心２０ａを通る直線上に対として配置される。さらに、追加内側連通孔３２ｉと追加外側連通孔３２ｏとは、固定スクロール１１の中心２０ａを通る直線上に対として配置される。これにより、初段内側膨張室Ｒｉ１と初段外側膨張室Ｒｏ１とは、等圧状態となり、初段内側膨張室Ｒｉ１と初段外側膨張室Ｒｏ１との間の旋回スクロール１２の板状渦巻歯の壁面の変形を抑えることができる。 Further, the inner communication hole 31i and the outer communication hole 31o are arranged as a pair on a straight line passing through the center 20a of the fixed scroll 11. Further, the additional inner communication hole 32i and the additional outer communication hole 32o are arranged as a pair on a straight line passing through the center 20a of the fixed scroll 11. As a result, the first-stage inner expansion chamber Ri1 and the first-stage outer expansion chamber Ro1 are in an isobaric state, and the wall surface of the plate-shaped spiral tooth of the swirl scroll 12 between the first-stage inner expansion chamber Ri1 and the first-stage outer expansion chamber Ro1 is deformed. It can be suppressed.

＜制御部による開閉弁制御処理＞
次に、制御部４による内側開閉弁４１ｉ、外側開閉弁４１ｏ、追加内側開閉弁４２ｉ及び追加外側開閉弁４２ｏの開閉制御処理手順について説明する。この開閉制御処理は、膨張比（圧力比）を調整するためのものである。図８は、制御部４による内側開閉弁４１ｉ、外側開閉弁４１ｏ、追加内側開閉弁４２ｉ及び追加外側開閉弁４２ｏの開閉制御処理手順を示すフローチャートである。 <On-off valve control process by the control unit>
Next, the opening / closing control processing procedure of the inner on-off valve 41i, the outer on-off valve 41o, the additional inner on-off valve 42i, and the additional outer on-off valve 42o by the control unit 4 will be described. This opening / closing control process is for adjusting the expansion ratio (pressure ratio). FIG. 8 is a flowchart showing an opening / closing control processing procedure of the inner on-off valve 41i, the outer on-off valve 41o, the additional inner on-off valve 42i, and the additional outer on-off valve 42o by the control unit 4.

図８に示すように、まず制御部４は、内側開閉弁４１ｉ、外側開閉弁４１ｏ、追加内側開閉弁４２ｉ及び追加外側開閉弁４２ｏのすべてを閉にしておく（ステップＳ１０１）。その後、制御部４は、吸入圧力Ｐｓ及び吐出圧力Ｐｄを取得し、吐出圧力Ｐｄに対する吸入圧力Ｐｓの比である圧力比ΔＰを求め、圧力比ΔＰが所定値Ｐａ以下であるか否かを判定する（ステップＳ１０２）。この所定値Ｐａは、内側開閉弁４１ｉ、外側開閉弁４１ｏ、追加内側開閉弁４２ｉ及び追加外側開閉弁４２ｏのすべてを閉にした状態における圧力比ΔＰである設定値よりも小さい値である。 As shown in FIG. 8, first, the control unit 4 closes all of the inner on-off valve 41i, the outer on-off valve 41o, the additional inner on-off valve 42i, and the additional outer on-off valve 42o (step S101). After that, the control unit 4 acquires the suction pressure Ps and the discharge pressure Pd, obtains the pressure ratio ΔP which is the ratio of the suction pressure Ps to the discharge pressure Pd, and determines whether or not the pressure ratio ΔP is a predetermined value Pa or less. (Step S102). This predetermined value Pa is a value smaller than the set value which is the pressure ratio ΔP when all of the inner on-off valve 41i, the outer on-off valve 41o, the additional inner on-off valve 42i, and the additional outer on-off valve 42o are closed.

圧力比ΔＰが所定値Ｐａ以下である場合（ステップＳ１０２，Ｙｅｓ）には、内側開閉弁４１ｉ及び外側開閉弁４１ｏを同時に開にするとともに、追加内側開閉弁４２ｉ及び追加外側開閉弁４２ｏを閉のままにする（ステップＳ１０３）。一方、圧力比ΔＰが所定値Ｐａ以下でない場合（ステップＳ１０２，Ｎｏ）には、ステップＳ１０２の判定処理を繰り返す。 When the pressure ratio ΔP is equal to or less than the predetermined value Pa (steps S102, Yes), the inner on-off valve 41i and the outer on-off valve 41o are opened at the same time, and the additional inner on-off valve 42i and the additional outer on-off valve 42o are closed. Leave (step S103). On the other hand, when the pressure ratio ΔP is not equal to or less than the predetermined value Pa (steps S102, No), the determination process of step S102 is repeated.

その後、圧力比ΔＰが所定値Ｐａを超えたか否かを判定する（ステップＳ１０４）。圧力比ΔＰが所定値Ｐａを超える場合（ステップＳ１０４，Ｙｅｓ）には、ステップＳ１０１に移行して、内側開閉弁４１ｉ、外側開閉弁４１ｏ、追加内側開閉弁４２ｉ及び追加外側開閉弁４２ｏのすべてを閉にする。一方、圧力比ΔＰが所定値Ｐａを超えない場合（ステップＳ１０４，Ｎｏ）には、さらに圧力比ΔＰが所定値Ｐｂ以下であるか否かを判定する（ステップＳ１０５）。この所定値Ｐｂは、所定値Ｐａよりも小さい値である。圧力比ΔＰが所定値Ｐｂ以下でない場合（ステップＳ１０５，Ｎｏ）には、ステップＳ１０３に移行して、内側開閉弁４１ｉ及び外側開閉弁４１ｏを開にし、追加内側開閉弁４２ｉ及び追加外側開閉弁４２ｏを閉のままとする現在の状態を維持する。 After that, it is determined whether or not the pressure ratio ΔP exceeds the predetermined value Pa (step S104). When the pressure ratio ΔP exceeds the predetermined value Pa (step S104, Yes), the process proceeds to step S101, and all of the inner on-off valve 41i, the outer on-off valve 41o, the additional inner on-off valve 42i, and the additional outer on-off valve 42o are used. Close it. On the other hand, when the pressure ratio ΔP does not exceed the predetermined value Pa (steps S104, No), it is further determined whether or not the pressure ratio ΔP is equal to or less than the predetermined value Pb (step S105). This predetermined value Pb is a value smaller than the predetermined value Pa. When the pressure ratio ΔP is not equal to or less than the predetermined value Pb (steps S105 and No), the process proceeds to step S103 to open the inner on-off valve 41i and the outer on-off valve 41o, and the additional inner on-off valve 42i and the additional outer on-off valve 42o. Keep the current state.

一方、圧力比ΔＰが所定値Ｐｂ以下である場合（ステップＳ１０５，Ｙｅｓ）には、内側開閉弁４１ｉ及び外側開閉弁４１ｏを開のままで、追加内側開閉弁４２ｉ及び追加外側開閉弁４２ｏを同時に閉にする（ステップＳ１０６）。その後、圧力比ΔＰが所定値Ｐｂを超えたか否かを判定する（ステップＳ１０７）。圧力比ΔＰが所定値Ｐｂを超えた場合（ステップＳ１０７，Ｙｅｓ）には、ステップＳ１０３に移行して、追加内側開閉弁４２ｉ及び追加外側開閉弁４２ｏを同時に閉にする。一方、圧力比ΔＰが所定値Ｐｂを超えない場合（ステップＳ１０７，Ｎｏ）には、膨張処理の終了指示があったか否かを判定する（ステップＳ１０８）。膨張処理の終了指示がない場合（ステップＳ１０８，Ｎｏ）には、ステップＳ１０６に移行して現在の状態を維持する。一方、膨張処理の終了指示があった場合（ステップＳ１０８，Ｙｅｓ）には、本処理を終了する。 On the other hand, when the pressure ratio ΔP is equal to or less than the predetermined value Pb (steps S105, Yes), the inner on-off valve 41i and the outer on-off valve 41o are left open, and the additional inner on-off valve 42i and the additional outer on-off valve 42o are simultaneously opened. Close (step S106). After that, it is determined whether or not the pressure ratio ΔP exceeds the predetermined value Pb (step S107). When the pressure ratio ΔP exceeds the predetermined value Pb (steps S107, Yes), the process proceeds to step S103, and the additional inner on-off valve 42i and the additional outer on-off valve 42o are closed at the same time. On the other hand, when the pressure ratio ΔP does not exceed the predetermined value Pb (steps S107 and No), it is determined whether or not there is an instruction to end the expansion process (step S108). If there is no instruction to end the expansion process (steps S108, No), the process proceeds to step S106 to maintain the current state. On the other hand, when there is an instruction to end the expansion process (step S108, Yes), this process ends.

＜膨張損失の低減＞
次に、本実施の形態による膨張損失の低減について説明する。図９は、本実施の形態による膨張損失の低減を説明する説明図である。図９（ａ）は、膨張行程に伴う初段内側膨張室Ｒｉ１の容積と初段外側膨張室Ｒｏ１の容積とを加算した膨張室容積Ｖの変化に対する膨張行程に伴う初段内側膨張室Ｒｉ１及び初段外側膨張室Ｒｏ１の圧力Ｐの変化を示す図である。図９（ａ）は、内側連通孔３１ｉ、外側連通孔３１ｏ、追加内側連通孔３２ｉ及び追加外側連通孔３２ｏを設けない従来の膨張室容積Ｖの変化に対する圧力Ｐの変化を示している。圧力変化ｄＰは、吸入圧力Ｐｓと吐出圧力Ｐｄとの差であり、圧力変化ｄＰは、設定値である。 <Reduction of expansion loss>
Next, reduction of expansion loss according to the present embodiment will be described. FIG. 9 is an explanatory diagram illustrating reduction of expansion loss according to the present embodiment. FIG. 9A shows the first-stage inner expansion chamber Ri1 and the first-stage outer expansion associated with the expansion stroke with respect to the change in the expansion chamber volume V, which is the sum of the volume of the first-stage inner expansion chamber Ri1 and the volume of the first-stage outer expansion chamber Ro1 accompanying the expansion stroke. It is a figure which shows the change of the pressure P of the chamber Ro1. FIG. 9A shows a change in pressure P with respect to a change in the conventional expansion chamber volume V without the inner communication hole 31i, the outer communication hole 31o, the additional inner communication hole 32i, and the additional outer communication hole 32o. The pressure change dP is the difference between the suction pressure Ps and the discharge pressure Pd, and the pressure change dP is a set value.

ここで、内側連通孔３１ｉ、外側連通孔３１ｏ、追加内側連通孔３２ｉ及び追加外側連通孔３２ｏを設けない場合、スクロール膨張機本体２の中心部の吸入容積Ｖ１と吐出容積Ｖ２との容積比（Ｖ２／Ｖ１）が幾何的に一つに決定されるため、次式に示すように、圧力比ΔＰ（＝Ｐｓ／Ｐｄ）も一定となる。
Ｐｓ／Ｐｄ＝（Ｖ２／Ｖ１）＾κ
なお、Ｐｓは吸入圧力、Ｐｄは吐出圧力、Ｖ２は吐出容積、Ｖ２は吸入容積、κは断熱指数である。 Here, when the inner communication hole 31i, the outer communication hole 31o, the additional inner communication hole 32i, and the additional outer communication hole 32o are not provided, the volume ratio of the suction volume V1 and the discharge volume V2 at the center of the scroll expander main body 2 ( Since V2 / V1) is geometrically determined to be one, the pressure ratio ΔP (= Ps / Pd) is also constant as shown in the following equation.
Ps / Pd = (V2 / V1) ^ κ
Ps is the suction pressure, Pd is the discharge pressure, V2 is the discharge volume, V2 is the suction volume, and κ is the adiabatic index.

ここで、図９（ｂ）に示すように、吐出圧力Ｐｄが設定値よりも大きい吐出圧力Ｐｄ´に上昇した場合、膨張行程では、吐出圧力Ｐｄとなるまで減圧する膨張を行うため、過膨張損失Ｓａが発生する。これに対し、本実施の形態では、図９（ｃ）に示すように、内側連通孔３１ｉ、外側連通孔３１ｏ、追加内側連通孔３２ｉ及び追加外側連通孔３２ｏにより高圧室１７に連通して初段内側膨張室Ｒｉ１の圧力及び初段外側膨張室Ｒｏ１の圧力を吸入圧力Ｐｓに維持し、膨張開始点を膨張室容積Ｖが膨張室容積Ｖ´になるまで遅らせて膨張行程を短縮している。すなわち、圧力変化ｄＰを圧力変化ｄＰ´に小さくし、圧力比ΔＰを小さくしている。この結果、無駄な過膨張損失Ｓａが発生せず、膨張効率の低下を抑止することができる。 Here, as shown in FIG. 9B, when the discharge pressure Pd rises to a discharge pressure Pd ′ larger than the set value, in the expansion stroke, the pressure is reduced until the discharge pressure Pd is reached. Loss Sa occurs. On the other hand, in the present embodiment, as shown in FIG. 9C, the inner communication hole 31i, the outer communication hole 31o, the additional inner communication hole 32i, and the additional outer communication hole 32o communicate with the high pressure chamber 17 in the first stage. The pressure of the inner expansion chamber Ri1 and the pressure of the first stage outer expansion chamber Ro1 are maintained at the suction pressure Ps, and the expansion start point is delayed until the expansion chamber volume V becomes the expansion chamber volume V', and the expansion stroke is shortened. That is, the pressure change dP is reduced to the pressure change dP', and the pressure ratio ΔP is reduced. As a result, unnecessary hyperexpansion loss Sa does not occur, and a decrease in expansion efficiency can be suppressed.

また、図９（ｄ）に示すように、吸入圧力Ｐｓが設定値よりも小さい吸入圧力Ｐｓ´に上昇した場合、膨張行程では、圧力変化ｄＰとなるまで膨張行程を行って減圧するため、過膨張損失Ｓｂが発生する。これに対し、本実施の形態では、図９（ｅ）に示すように、内側連通孔３１ｉ、外側連通孔３１ｏ、追加内側連通孔３２ｉ及び追加外側連通孔３２ｏにより高圧室１７に連通して初段内側膨張室Ｒｉ１の圧力及び初段外側膨張室Ｒｏ１の圧力を吸入圧力Ｐｓ´に維持し、膨張開始点を膨張室容積Ｖが膨張室容積Ｖ´になるまで遅らせて膨張行程を短縮している。すなわち、圧力変化ｄＰを圧力変化ｄＰ´´に小さくし、圧力比ΔＰを小さくしている。この結果、無駄な過膨張損失Ｓｂが発生せず、膨張効率の低下を抑止することができる。 Further, as shown in FIG. 9D, when the suction pressure Ps rises to a suction pressure Ps'smaller than the set value, the expansion stroke is performed until the pressure changes dP, and the pressure is reduced. Expansion loss Sb occurs. On the other hand, in the present embodiment, as shown in FIG. 9E, the inner communication hole 31i, the outer communication hole 31o, the additional inner communication hole 32i, and the additional outer communication hole 32o communicate with the high pressure chamber 17 in the first stage. The pressure of the inner expansion chamber Ri1 and the pressure of the first stage outer expansion chamber Ro1 are maintained at the suction pressure Ps', and the expansion start point is delayed until the expansion chamber volume V becomes the expansion chamber volume V'to shorten the expansion stroke. That is, the pressure change dP is reduced to the pressure change dP ″, and the pressure ratio ΔP is reduced. As a result, unnecessary hyperexpansion loss Sb does not occur, and a decrease in expansion efficiency can be suppressed.

ここで、膨張開始点は、内側連通孔３１ｉ及び外側連通孔３１ｏの連通、さらに内側連通孔３１ｉ、外側連通孔３１ｏ、追加内側連通孔３２ｉ及び追加外側連通孔３２ｏのすべての連通という多段階の制御によって圧力変化ｄＰ（圧力比ΔＰ）を変化することができる。具体的には、圧力変化ｄＰの変化に応じて、図９（ｃ）及び図９（ｅ）の膨張室容積Ｖ´の位置を多段階に変化することができる。 Here, the expansion start point is a multi-stage communication of the inner communication hole 31i and the outer communication hole 31o, and all the communication of the inner communication hole 31i, the outer communication hole 31o, the additional inner communication hole 32i, and the additional outer communication hole 32o. The pressure change dP (pressure ratio ΔP) can be changed by control. Specifically, the position of the expansion chamber volume V'in FIGS. 9 (c) and 9 (e) can be changed in multiple stages according to the change in the pressure change dP.

なお、上述した実施の形態では、内側連通孔３１ｉ及び外側連通孔３１ｏの対と、追加内側連通孔３２ｉ及び追加外側連通孔３２ｏの対からなる２対の連通孔を設けていたが、さらに複数対の連通孔を設けて、さらに多段階に圧力比を可変にしてもよい。 In the above-described embodiment, two pairs of communication holes including a pair of the inner communication hole 31i and the outer communication hole 31o and a pair of the additional inner communication hole 32i and the additional outer communication hole 32o are provided. A pair of communication holes may be provided to further change the pressure ratio in multiple stages.

すなわち、内側連通孔３１ｉの位置から固定スクロール１１に沿って旋回スクロール１２の旋回角が進んだ位置に、初段内側膨張室Ｒｉ１に連通する１以上の追加内側連通孔を設けるとともに、外側連通孔３１ｏの位置から固定スクロール１１に沿って旋回スクロールの旋回角が進んだ位置に、初段外側膨張室Ｒｏ１に連通する１以上の追加外側連通孔を設けるようにしてもよい。上記の追加内側連通孔３２ｉ及び追加外側連通孔３２ｏは旋回角が１８０°進んだ一例である。なお、各追加内側連通孔及び各追加外側連通孔には、それぞれ開閉する１以上の追加内側開閉弁及び１以上の追加外側開閉弁が設けられ、制御部４によって開閉制御される。 That is, one or more additional inner communication holes communicating with the first stage inner expansion chamber Ri1 are provided at a position where the turning angle of the turning scroll 12 advances along the fixed scroll 11 from the position of the inner communication hole 31i, and the outer communication hole 31o is provided. One or more additional outer communication holes communicating with the first stage outer expansion chamber Ro1 may be provided at a position where the turning angle of the turning scroll advances along the fixed scroll 11 from the position of. The additional inner communication hole 32i and the additional outer communication hole 32o are examples in which the turning angle is advanced by 180 °. Each additional inner communication hole and each additional outer communication hole is provided with one or more additional inner on-off valves and one or more additional outer on-off valves that open and close, respectively, and is controlled by the control unit 4.

具体的には、図１０に示すように、内側連通孔３１ｉの位置から旋回スクロール１２の旋回角が９０°進んだ位置に追加内側連通孔３３ｉ、及び、外側連通孔３１ｏの位置から旋回スクロールの旋回角が９０°進んだ位置に追加外側連通孔３３ｏを対として設ける。内側連通孔３１ｉ、外側連通孔３１ｏ、追加内側連通孔３３ｉ及び追加外側連通孔３３ｏが閉になっている場合、旋回スクロールの旋回角が１８０°（半回転）になるまで、圧縮開始点を遅らせることができる。 Specifically, as shown in FIG. 10, the swivel scroll 12 is added to a position where the swivel angle of the swivel scroll 12 is advanced by 90 ° from the position of the inner communication hole 31i, and the swivel scroll is swiveled from the position of the inner communication hole 33i and the outer communication hole 31o. An additional outer communication hole 33o is provided as a pair at a position where the turning angle is advanced by 90 °. When the inner communication hole 31i, the outer communication hole 31o, the additional inner communication hole 33i, and the additional outer communication hole 33o are closed, the compression start point is delayed until the turning angle of the turning scroll becomes 180 ° (half rotation). be able to.

また、図１０に示すように、内側連通孔３１ｉの位置から旋回スクロール１２の旋回角が２７０°進んだ位置に追加内側連通孔３４ｉ、及び、外側連通孔３１ｏの位置から旋回スクロールの旋回角が２７０°進んだ位置に追加外側連通孔３４ｏを対として設ける。内側連通孔３１ｉ、外側連通孔３１ｏ、追加内側連通孔３３ｉ、追加外側連通孔３３ｏ、追加内側連通孔３２ｉ、追加外側連通孔３２ｏ、追加内側連通孔３４ｉ及び追加外側連通孔３４ｏが閉になっている場合、旋回スクロールの旋回角が５４０°（１回転半）になるまで、圧縮開始点を遅らせることができる。 Further, as shown in FIG. 10, the turning angle of the turning scroll 12 is added to a position advanced by 270 ° from the position of the inner communication hole 31i, and the turning angle of the turning scroll is increased from the position of the inner communication hole 34i and the outer communication hole 31o. An additional outer communication hole 34o is provided as a pair at a position advanced by 270 °. The inner communication hole 31i, the outer communication hole 31o, the additional inner communication hole 33i, the additional outer communication hole 33o, the additional inner communication hole 32i, the additional outer communication hole 32o, the additional inner communication hole 34i, and the additional outer communication hole 34o are closed. If so, the compression start point can be delayed until the turning angle of the turning scroll reaches 540 ° (one and a half turns).

なお、上記の実施の形態では、各連通孔が設けられる位置の旋回角の進み角は、１８０°単位、あるいは９０°単位としていたが、これに限らずの任意の進み角の位置に設けてもよい。 In the above embodiment, the advancing angle of the turning angle at the position where each communication hole is provided is in units of 180 ° or 90 °, but the advancing angle is not limited to this and is provided at any advancing angle. May be good.

また、連通孔の径は、旋回スクロール１２の板状渦巻歯の厚さよりも小さくする。例えば、図１１に示すように、外側連通孔３１ｏの径Ｗ２は、旋回スクロール１２の板状渦巻歯の厚さＷ１よりも小さくする。これにより、外側連通孔３１ｏを介して旋回スクロール１２を跨いだ蒸気の圧力漏れが回避される。 Further, the diameter of the communication hole is made smaller than the thickness of the plate-shaped spiral teeth of the swirl scroll 12. For example, as shown in FIG. 11, the diameter W2 of the outer communication hole 31o is made smaller than the thickness W1 of the plate-shaped spiral teeth of the swirl scroll 12. As a result, pressure leakage of steam straddling the swirl scroll 12 through the outer communication hole 31o is avoided.

なお、図１２に示すように、外側連通孔３１ｏ´が長穴である場合、短手方向の径Ｗ２´は旋回スクロール１２の板状渦巻場の厚さＷ１よりも小さくする。 As shown in FIG. 12, when the outer communication hole 31o'is a long hole, the diameter W2'in the lateral direction is made smaller than the thickness W1 of the plate-shaped spiral field of the swirl scroll 12.

さらに、上記の実施の形態及び変形例で図示した各構成は機能概略的なものであり、必ずしも物理的に図示の構成をされていることを要しない。すなわち、各装置及び構成要素の分散・統合の形態は図示のものに限られず、その全部又は一部を各種の使用状況などに応じて、任意の単位で機能的又は物理的に分散・統合して構成することができる。 Further, each configuration shown in the above-described embodiment and modification is a schematic function, and does not necessarily have to be physically illustrated. That is, the form of distribution / integration of each device and component is not limited to the one shown in the figure, and all or part of the device and components are functionally or physically distributed / integrated in arbitrary units according to various usage conditions. Can be configured.

１ スクロール膨張機
２ スクロール膨張機本体
３ 発電機
４ 制御部
５ 表示操作部
１０ 筐体
１０ａ，１０ｂ 筐体
１１ 固定スクロール
１２ 旋回スクロール
１３ クランクシャフト
１４ スラスト軸受
１５ バランスウェイト
１７ 高圧室
２０ 主吸入口
２０ａ 中心
２２ 高圧圧力検出部
２３ 高圧温度検出部
２４ 低圧圧力検出部
２５ 低圧温度検出部
３１ｏ 外側連通孔
３１ｉ 内側連通孔
３２ｏ，３３ｏ，３４ｏ 追加外側連通孔
３２ｉ，３３ｉ，３４ｉ 追加内側連通孔
４１ｏ 外側開閉弁
４１ｉ 内側開閉弁
４２ｏ 追加外側開閉弁
４２ｉ 追加内側開閉弁
ＡＬ 回転方向
ｄＰ 圧力変化
ＨＷ 高圧蒸気
Ｌ１，Ｌ２ 配管
ＬＷ 低圧蒸気
Ｐａ，Ｐｂ 所定値
Ｐｄ 吐出圧力
Ｐｓ 吸入圧力
ＲＣ 領域
Ｒｉ１ 初段内側膨張室
Ｒｉ２ 次段内側膨張室
Ｒｏ１ 初段外側膨張室
Ｒｏ２ 次段外側膨張室
ＲＷ 高圧蒸気
Ｓａ，Ｓｂ 過膨張損失
Ｖ 膨張室容積
Ｖ１ 吸入容積
Ｖ２ 吐出容積
ΔＰ 圧力比 1 Scroll inflator 2 Scroll inflator body 3 Generator 4 Control unit 5 Display operation unit 10 Housing 10a, 10b Housing 11 Fixed scroll 12 Swing scroll 13 Crank shaft 14 Thrust bearing 15 Balance weight 17 High pressure chamber 20 Main suction port 20a Center 22 High pressure pressure detector 23 High pressure temperature detector 24 Low pressure pressure detector 25 Low pressure temperature detector 31o Outer communication hole 31i Inner communication hole 32o, 33o, 34o Additional outer communication hole 32i, 33i, 34i Additional inner communication hole 41o Outer opening and closing Valve 41i Inner on-off valve 42o Additional outer on-off valve 42i Additional inner on-off valve AL Rotation direction dP Pressure change HW High pressure steam L1, L2 Piping LW Low pressure steam Pa, Pb Predetermined value Pd Discharge pressure Ps Intake pressure RC region Ri1 First stage inner expansion chamber Ri2 Next stage inner expansion chamber Ro1 First stage outer expansion chamber Ro2 Second stage outer expansion chamber RW High pressure steam Sa, Sb Overexpansion loss V Expansion chamber volume V1 Suction volume V2 Discharge volume ΔP Pressure ratio

Claims (9)

吸入した高圧作動流体を膨張して低圧作動流体を吐出するスクロール膨張機であって、
固定スクロールと旋回スクロールとを噛み合わせて膨張室を形成する膨張機構と、
前記旋回スクロールの旋回に伴って前記高圧作動流体が吸入される主吸入口と、
前記主吸入口から隔離され、前記高圧作動流体を前記膨張室内に吸入する副吸入口と、
前記副吸入口を開閉する開閉弁と、
前記開閉弁を制御する制御部と、
を備え、
前記副吸入口は、前記膨張機構作動時に、前記旋回スクロールの内周に最初に形成される内側膨張室に前記高圧作動流体を吸入する内側連通孔と、前記旋回スクロールの外周に最初に形成される外側膨張室に前記高圧作動流体を吸入する外側連通孔と、で一対となるように形成されることを特徴とするスクロール膨張機。 A scroll expander that expands the sucked high-pressure working fluid and discharges the low-pressure working fluid.
An expansion mechanism that meshes a fixed scroll and a swivel scroll to form an expansion chamber,
A main suction port into which the high-pressure working fluid is sucked as the swivel scroll swivels,
An auxiliary suction port that is isolated from the main suction port and sucks the high-pressure working fluid into the expansion chamber.
An on-off valve that opens and closes the sub suction port,
A control unit that controls the on-off valve and
With
The sub-suction port is first formed on the outer periphery of the swivel scroll and the inner communication hole for sucking the high-pressure working fluid into the inner expansion chamber first formed on the inner circumference of the swivel scroll when the expansion mechanism is operated. A scroll expander characterized in that it is formed in a pair with an outer communication hole for sucking the high-pressure working fluid in the outer expansion chamber. 一対の前記副吸入口は、前記主吸入口を中心として互いに対称となる位置に配置されていることを特徴とする請求項１に記載のスクロール膨張機。 The scroll expander according to claim 1, wherein the pair of the sub suction ports are arranged symmetrically with respect to the main suction port. 前記高圧作動流体の吸入圧力を検出する高圧圧力検出部と、
前記低圧作動流体の吐出圧力を検出する低圧圧力検出部と、
をさらに備え、
前記吐出圧力に対する前記吸入圧力の圧力比に応じて、対となる前記開閉弁を同時に開閉制御することを特徴とする請求項２に記載のスクロール膨張機。 A high-pressure pressure detection unit that detects the suction pressure of the high-pressure working fluid, and
A low-pressure pressure detection unit that detects the discharge pressure of the low-pressure working fluid,
With more
The scroll expander according to claim 2, further comprising controlling the opening and closing of the paired on-off valves at the same time according to the pressure ratio of the suction pressure to the discharge pressure. 前記内側連通孔は、前記固定スクロールに形成された板状渦巻歯の外側に形成され、
前記外側連通孔は、前記固定スクロールに形成された板状渦巻歯の内側に形成されることを特徴とする請求項１に記載のスクロール膨張機。 The inner communication hole is formed on the outside of the plate-shaped spiral tooth formed on the fixed scroll.
The scroll expander according to claim 1, wherein the outer communication hole is formed inside a plate-shaped spiral tooth formed in the fixed scroll. 前記副吸入口の径は、前記旋回スクロールに形成された板状渦巻歯の厚さよりも小さいことを特徴とする請求項１〜４のいずれか一つに記載のスクロール膨張機。 The scroll expander according to any one of claims 1 to 4, wherein the diameter of the sub suction port is smaller than the thickness of the plate-shaped spiral teeth formed on the swivel scroll. 前記副吸入口の形成位置から前記旋回スクロールの旋回角が進んだ位置に、さらに一対以上の前記副吸入口が形成されていることを特徴とする請求項１〜５のいずれか一つに記載のスクロール膨張機。 The invention according to any one of claims 1 to 5, wherein a pair or more of the auxiliary suction ports are further formed at a position where the turning angle of the turning scroll is advanced from the formation position of the secondary suction port. Scroll expander. 複数対の前記副吸入口は、それぞれ前記旋回角が１８０°進む毎に設けられることを特徴とする請求項６に記載のスクロール膨張機。 The scroll expander according to claim 6, wherein the plurality of pairs of the sub suction ports are provided every time the turning angle advances by 180 °. 前記制御部は、前記圧力比の所定値を一つ以上設定し、前記所定値に達するに応じて、一対または複数対の前記開閉弁を段階的に制御することを特徴とする請求項３〜７に記載のスクロール膨張機。 3. The control unit is characterized in that one or more predetermined values of the pressure ratio are set, and one or a plurality of pairs of the on-off valves are controlled stepwise according to reaching the predetermined value. 7. The scroll expander according to 7. 前記旋回スクロールの旋回軸に連結した動力回収機を備えたことを特徴とする請求項１〜８のいずれか一つに記載のスクロール膨張機。 The scroll expander according to any one of claims 1 to 8, further comprising a power recovery machine connected to the swivel shaft of the swivel scroll.
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Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000227080A (en) * 1999-02-05 2000-08-15 Nippon Soken Inc Scroll type expansion machine
JP2003269103A (en) * 2002-03-14 2003-09-25 Matsushita Electric Ind Co Ltd Scroll expansion machine and its driving method
JP2006046223A (en) * 2004-08-05 2006-02-16 Daikin Ind Ltd Scroll type expander
JP2007255327A (en) * 2006-03-23 2007-10-04 Nippon Soken Inc Expander controlling device
WO2008072575A1 (en) * 2006-12-08 2008-06-19 Daikin Industries, Ltd. Freezing apparatus, and expander
JP2013142355A (en) * 2012-01-12 2013-07-22 Toyota Industries Corp Expander
US20140219844A1 (en) * 2013-02-06 2014-08-07 Daimler Ag Expansion device for use in a working medium circuit and method for operating an expansion device
JP2016164381A (en) * 2015-03-06 2016-09-08 ヤンマー株式会社 Power generation device

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000227080A (en) * 1999-02-05 2000-08-15 Nippon Soken Inc Scroll type expansion machine
JP2003269103A (en) * 2002-03-14 2003-09-25 Matsushita Electric Ind Co Ltd Scroll expansion machine and its driving method
JP2006046223A (en) * 2004-08-05 2006-02-16 Daikin Ind Ltd Scroll type expander
JP2007255327A (en) * 2006-03-23 2007-10-04 Nippon Soken Inc Expander controlling device
WO2008072575A1 (en) * 2006-12-08 2008-06-19 Daikin Industries, Ltd. Freezing apparatus, and expander
JP2013142355A (en) * 2012-01-12 2013-07-22 Toyota Industries Corp Expander
US20140219844A1 (en) * 2013-02-06 2014-08-07 Daimler Ag Expansion device for use in a working medium circuit and method for operating an expansion device
JP2016164381A (en) * 2015-03-06 2016-09-08 ヤンマー株式会社 Power generation device

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