JP2014109243A - Scroll liquid pump - Google Patents

Scroll liquid pump Download PDF

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Publication number
JP2014109243A
JP2014109243A JP2012264815A JP2012264815A JP2014109243A JP 2014109243 A JP2014109243 A JP 2014109243A JP 2012264815 A JP2012264815 A JP 2012264815A JP 2012264815 A JP2012264815 A JP 2012264815A JP 2014109243 A JP2014109243 A JP 2014109243A
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Prior art keywords
scroll
orbiting
crankshaft
wrap
fixed
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JP2012264815A
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JP5540192B2 (en
Inventor
Fuseki Ko
富石 黄
Kwangseon Hwang
光宣 黄
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RICCHISUTOON KK
RichStone Ltd Japan
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RICCHISUTOON KK
RichStone Ltd Japan
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Priority to JP2012264815A priority Critical patent/JP5540192B2/en
Priority to KR1020130136672A priority patent/KR20140071229A/en
Priority to GB1320556.2A priority patent/GB2511597A/en
Priority to US14/088,346 priority patent/US20140170009A1/en
Priority to CN201310645664.9A priority patent/CN103850936A/en
Publication of JP2014109243A publication Critical patent/JP2014109243A/en
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Publication of JP5540192B2 publication Critical patent/JP5540192B2/en
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    • 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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
    • F04C18/0269—Details concerning the involute wraps
    • 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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • 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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/02—Rotary-piston machines or pumps of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C2/025—Rotary-piston machines or pumps of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents the moving and the stationary member having co-operating elements in spiral form
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0007—Radial sealings for working fluid
    • 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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/02—Rotary-piston machines or pumps of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • 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
    • F04C2240/00—Components
    • F04C2240/50—Bearings

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

PROBLEM TO BE SOLVED: To provide a scroll liquid pump for increasing a pressure of liquid refrigerant or oil for its delivery.SOLUTION: A fixed scroll 2 integrated with a frame 1 and having three pairs of laps 3a is faced to and combined with a revolving scroll 3 having three pairs of laps. A discharge pressure is applied to a part of a back surface of the revolving scroll to bring the revolving scroll in tight contact with the fixed scroll. The revolving scroll is allowed to move in a radial direction in a tiny amount, and the laps of both of the scrolls are brought into contact with each other.

Description

本発明は液冷媒や油のような液体用のスクロール液ポンプに関する。   The present invention relates to a scroll liquid pump for liquids such as liquid refrigerant and oil.

特許文献１に示すように、従来のスクロール液ポンプは、固定スクロールおよび旋回スクロールにそれぞれ複数組の旋回ラップと固定ラップを設ける。旋回スクロールは背面が旋回軸に固定されて旋回駆動する。固定スクロールは軸方向に移動可能に設置される。ポンプ室の圧力による荷重と背面の吐出圧力による荷重の差により、固定スクロールを旋回スクロールに押し付け、旋回ラップの先端と固定ラップ溝底および固定ラップの先端と旋回ラップ溝底それぞれのシールを行う。流体が最初に流入する吸入室（固定体）と外側のシールは、旋回スクロール外周壁（移動体）で行う。流体のシールを固定体と移動体の間で行うから、流体の漏れは０にならない。外側が外気のとき、シール部から漏れた流体は外部に流出される。スクロール液ポンプを油で潤滑し、外側が駆動部空間のとき、シール部から漏れた流体は駆動部空間へ流入し、潤滑油を希釈するから軸受の潤滑不良を起こす。また、旋回スクロールは、旋回軸に固定されるから、旋回軸の旋回半径からずれた位置に移動できない。したがって旋回ラップと固定ラップの径方向隙間を０にできなく、ポンプ室の密閉は十分ではない。   As shown in Patent Document 1, a conventional scroll liquid pump is provided with a plurality of sets of orbiting wraps and fixed wraps on a fixed scroll and a turning scroll, respectively. The orbiting scroll is pivotally driven with its back surface fixed to the orbiting shaft. The fixed scroll is installed so as to be movable in the axial direction. Due to the difference between the load due to the pressure in the pump chamber and the load due to the discharge pressure on the back surface, the fixed scroll is pressed against the orbiting scroll, and the tip of the orbiting wrap and the bottom of the fixed wrap groove and the tip of the fixed wrap and the orbiting lap groove bottom are sealed. The suction chamber (fixed body) into which the fluid first flows and the outer seal are formed on the outer peripheral wall (moving body) of the orbiting scroll. Since the fluid is sealed between the fixed body and the movable body, the fluid leakage does not become zero. When the outside is outside air, the fluid leaking from the seal portion flows out to the outside. When the scroll liquid pump is lubricated with oil and the outside is the drive unit space, the fluid leaking from the seal portion flows into the drive unit space and dilutes the lubricating oil, causing poor lubrication of the bearing. Further, since the orbiting scroll is fixed to the orbiting shaft, it cannot move to a position deviated from the orbiting radius of the orbiting shaft. Therefore, the radial gap between the swirl wrap and the fixed wrap cannot be made zero, and the pump chamber is not sufficiently sealed.

国際公開ＷＯ２０１０／０１３３５１International Publication WO2010 / 013351

課題は旋回ラップと固定ラップの隙間から漏れた液体が外部や駆動部に漏れないようにし、旋回ランプと固定ラップの径方向隙間をほぼ０にし、ポンプ室の密閉性の良いスクロール液ポンプ（以下“本ポンプ”と言う）を提供することである。   The problem is that the liquid leaking from the gap between the swirl wrap and the fixed wrap does not leak to the outside or the drive unit, the radial gap between the swirl ramp and the fixed wrap is almost zero, and the scroll liquid pump (hereinafter referred to as the pump chamber) has good sealing performance. "This pump").

フレームと一体であり、３組の固定ラップを持つ固定スクロールに、３組の旋回ラップを持つ旋回スクロールを向かい合わせて組み合わせる。各ラップ部によりポンプ室を形成する。固定スクロールの中心部に主軸受を設ける。固定スクロールと一体の軸受ハウジングに副軸受を設ける。主軸受と副軸受に支持されるクランク軸を有する回転軸を設ける。旋回スクロールの中心部に旋回ラップ先端側の面に開口する軸受ハウジングを設ける。軸受ハウジングに旋回軸受を設ける。旋回軸受がクランク軸の回転部と嵌合する。   The orbiting scroll with three sets of orbiting wraps is combined with a fixed scroll that is integral with the frame and has three sets of fixed wraps. A pump chamber is formed by each lap portion. A main bearing is provided at the center of the fixed scroll. A secondary bearing is provided in a bearing housing integrated with the fixed scroll. A rotating shaft having a crankshaft supported by a main bearing and a sub-bearing is provided. A bearing housing is provided at the center of the orbiting scroll so as to open to the surface on the leading end side of the orbiting wrap. A slewing bearing is provided in the bearing housing. A slewing bearing engages with the rotating part of the crankshaft.

クランク軸の回転部は回転リングである。回転リングは長穴を有する。クランク軸は長穴と隙間嵌めで嵌合する扁平部を有する。回転リングは扁平部に対し、長穴の中心軸方向へ微小量移動できる。回転リングの長穴および扁平部の中心線は回転方向に対して後退角を持つ。   The rotating part of the crankshaft is a rotating ring. The rotating ring has a slot. The crankshaft has a flat portion that fits into the long hole by a clearance fit. The rotating ring can move by a minute amount in the direction of the central axis of the elongated hole with respect to the flat portion. The elongated hole of the rotating ring and the center line of the flat part have a receding angle with respect to the rotating direction.

旋回スクロールの中心部に吐出ポートを設ける。旋回ラップと反対側の面に各旋回ラップの外周径と同程度の径の位置にシール部材を設ける。シール部材の内部空間に吐出ポートから吐出された流体の圧力を作用させる。   A discharge port is provided at the center of the orbiting scroll. A seal member is provided on a surface opposite to the swirl wrap at a position having a diameter approximately equal to the outer diameter of each swirl wrap. The pressure of the fluid discharged from the discharge port is applied to the internal space of the seal member.

吸入室１ａは吸入ポート４と連通するのみであり、他の部分とは遮蔽される。従って、吸入室から外部や駆動部空間へ流体が漏れない。旋回スクロール３は径方向にも軸方向にも隙間がほぼ０になるように小さい力で固定スクロール２に押し付けられるので、密閉性が向上し、体積効率が上がる。この時、押し付け力は小さい力なので機械損失は少なく摩耗も小さい。 The suction chamber 1a only communicates with the suction port 4 and is shielded from other parts. Therefore, fluid does not leak from the suction chamber to the outside or the drive unit space. Since the orbiting scroll 3 is pressed against the fixed scroll 2 with a small force so that the gap is almost zero in both the radial direction and the axial direction, the sealing performance is improved and the volume efficiency is increased. At this time, since the pressing force is small, mechanical loss is small and wear is small.

本ポンプの断面図。Sectional drawing of this pump. 本ポンプの固定スクロールを示す平面図。The top view which shows the fixed scroll of this pump. 本ポンプの旋回スクロールを示す平面図。The top view which shows the turning scroll of this pump. 本ポンプの固定ラップと旋回ラップが重ね合わされた状態の断面図。Sectional drawing of the state with which the fixed lap and the turning wrap of this pump were piled up. 本ポンプの旋回軸受部の断面図。Sectional drawing of the rotation bearing part of this pump. 本ポンプの内カバーの平面図。The top view of the inner cover of this pump. クランク軸の後退角θが１２°の荷重シミュレーション結果。The load simulation result when the receding angle θ of the crankshaft is 12 °. クランク軸の後退角θが１４°の荷重シミュレーション結果。The load simulation result when the receding angle θ of the crankshaft is 14 °. クランク軸の後退角θが２０°の荷重シミュレーション結果。The load simulation result when the receding angle θ of the crankshaft is 20 °.

図１のように、フレーム１と一体に固定スクロール２が設けられる。フレーム１の後部にハウジング１０が取付けられる。フレーム１に主軸受１１が設けられる。ハウジング１０に副軸受１２が設けられる。主軸受１１と副軸受１２に支持されて回転軸１３が回転自在に設置される。回転軸１３の先端に軸中心が偏心したクランク軸１３ａが一体に設けられる。図5のように、クランク軸１３ａは扁平部１３ｂを有し、長穴７ａと隙間嵌めで嵌合される。長穴７aの長径は扁平部１３ｂの長径よりわずかに大きい。従って回転リング７は扁平部１３ｂと相対回転しないが、長穴７ａの長径方向にわずかに移動できる。中心線１３ｃは長穴７ａおよび扁平部１３ｂの中心線である。中心線１３ｃは回転軸１３の中心と扁平部１３ｂの中心を結ぶ線から回転方向１３ｄに対して所定角度だけ後退角θを持つように傾斜する。図1のように、内カバー８の外側に外カバー１４が装着される。外カバー１４は連通ポート８ａから流出した流体が滞留する吐出室１４ａを有する。外カバー１４は流体を外部へ排出する排出ポート１４ｂを有する。偏心質量との回転バランスを取るために、主バランスウェイト１５および副バランスウェイト１６が回転軸１３に装着される。   As shown in FIG. 1, a fixed scroll 2 is provided integrally with the frame 1. A housing 10 is attached to the rear portion of the frame 1. A main bearing 11 is provided on the frame 1. A secondary bearing 12 is provided in the housing 10. The rotary shaft 13 is rotatably supported by being supported by the main bearing 11 and the sub bearing 12. A crankshaft 13 a whose shaft center is eccentric is integrally provided at the tip of the rotating shaft 13. As shown in FIG. 5, the crankshaft 13a has a flat portion 13b and is fitted to the long hole 7a with a clearance fit. The long diameter of the long hole 7a is slightly larger than the long diameter of the flat portion 13b. Therefore, the rotating ring 7 does not rotate relative to the flat portion 13b, but can move slightly in the major axis direction of the long hole 7a. The center line 13c is the center line of the long hole 7a and the flat portion 13b. The center line 13c is inclined from the line connecting the center of the rotation shaft 13 and the center of the flat portion 13b so as to have a receding angle θ with respect to the rotation direction 13d by a predetermined angle. As shown in FIG. 1, the outer cover 14 is attached to the outside of the inner cover 8. The outer cover 14 has a discharge chamber 14a in which the fluid flowing out from the communication port 8a stays. The outer cover 14 has a discharge port 14b for discharging the fluid to the outside. In order to balance the rotation with the eccentric mass, the main balance weight 15 and the sub balance weight 16 are attached to the rotation shaft 13.

図２のように固定スクロール２に３つの固定ラップ２ａが立つ。隣接する固定ラップ２ａは配置角度を１２０度間隔にし、互いの位相は１２０度ずつずれる。固定スクロール２の外周部にシール壁２ｂが設けられる。固定スクロール２に吸入ポート４が設けられる。図１のフレーム１の内部には吸入ポート４に連通する吸入室１ａが設けられる。 As shown in FIG. 2, three fixed wraps 2 a stand on the fixed scroll 2. Adjacent fixed wraps 2a are arranged at intervals of 120 degrees, and their phases are shifted by 120 degrees. A seal wall 2 b is provided on the outer periphery of the fixed scroll 2. A suction port 4 is provided in the fixed scroll 2. A suction chamber 1 a communicating with the suction port 4 is provided inside the frame 1 of FIG.

図３の旋回スクロール３が、図２の固定スクロール２と向い合せに設けられる。旋回スクロール３に３つの旋回ラップ３ａが立つ。隣接する二つの旋回ラップ３a、３aの配置間隔は120度であり、互いの位相は１２０度ずつずれる。旋回ラップ３ａの中心部に吐出ポート３ｂが設けられる。 The orbiting scroll 3 of FIG. 3 is provided to face the fixed scroll 2 of FIG. Three orbiting laps 3a stand on the orbiting scroll 3. The arrangement interval between two adjacent swirl wraps 3a and 3a is 120 degrees, and the phases are shifted by 120 degrees. A discharge port 3b is provided at the center of the swirl wrap 3a.

固定ラップ２ａと旋回ラップ３ａは図４のように組み合わせられてポンプ室５を形成する。旋回スクロール３の中心に旋回軸受６が設けられる。旋回軸受６に回転リング７が嵌合される。 The fixed wrap 2a and the swivel wrap 3a are combined as shown in FIG. A orbiting bearing 6 is provided at the center of the orbiting scroll 3. A rotating ring 7 is fitted to the slewing bearing 6.

図５のように、回転リング７に長円形の長穴７ａが設けられる。 As shown in FIG. 5, the rotating ring 7 is provided with an oval long hole 7 a.

図６の内カバー８が旋回スクロール３の背面に設けられる。旋回スクロール３の吐出ポート３ｂと連通する連通ポート８ａが内カバー８に設けられる。連通ポート８ａの周囲にシール溝８ｂが設けられる。シール溝８ｂにリング上のシール部材９（図1）が装着される。シール部材９は旋回スクロール３の背面に密着して、内外の圧力差をシールする。 An inner cover 8 in FIG. 6 is provided on the back surface of the orbiting scroll 3. A communication port 8 a that communicates with the discharge port 3 b of the orbiting scroll 3 is provided in the inner cover 8. A seal groove 8b is provided around the communication port 8a. A seal member 9 (FIG. 1) on the ring is mounted in the seal groove 8b. The seal member 9 is in close contact with the back surface of the orbiting scroll 3 to seal the pressure difference between inside and outside.

動作を説明する。回転軸１３が電動機により駆動されて回転する。それに伴いクランク軸１３ａが回転する。クランク軸１３ａは回転リング７を回転させる。回転リング７は旋回軸受６を駆動して旋回スクロール３を偏心運動させる。偏心運動によりポンプ室５は外周側から体積を減少しながら中心側へ移動する。流体は吸入ポート４から吸引され、吸入室１ａを経由し、ポンプ室５の内周側へ押し込まれる。その時、流体力が旋回スクロール３に旋回方向の向かい側から作用する。図５のように流体力は旋回軸受６及び回転リング７の接線流体力Ｆｔとして作用する。クランク軸１３ａは扁平部１３ｂを有する。クランク軸１３aは扁平部１３ｂの中心線１３ｃが回転方向１３ｄに対して後退角θを持つように傾斜する。回転リング７は中心線１３ｃに沿って移動できるから回転リング７に接線力Ｆｔの分力として半径力Ｆｔｒが生じる。半径力Ｆｔｒは旋回スクロール３を旋回半径が大きくなる方向へ押す。   The operation will be described. The rotating shaft 13 is driven by an electric motor to rotate. Accordingly, the crankshaft 13a rotates. The crankshaft 13a rotates the rotating ring 7. The rotating ring 7 drives the orbiting bearing 6 to cause the orbiting scroll 3 to move eccentrically. The pump chamber 5 moves toward the center side while decreasing the volume from the outer peripheral side by the eccentric motion. The fluid is sucked from the suction port 4 and pushed into the inner peripheral side of the pump chamber 5 via the suction chamber 1a. At that time, fluid force acts on the orbiting scroll 3 from the opposite side of the orbiting direction. As shown in FIG. 5, the fluid force acts as a tangential fluid force Ft of the slewing bearing 6 and the rotating ring 7. The crankshaft 13a has a flat portion 13b. The crankshaft 13a is inclined so that the center line 13c of the flat portion 13b has a receding angle θ with respect to the rotational direction 13d. Since the rotating ring 7 can move along the center line 13c, a radial force Ftr is generated in the rotating ring 7 as a component of the tangential force Ft. The radial force Ftr pushes the orbiting scroll 3 in the direction in which the orbiting radius increases.

本ポンプを運転時に旋回スクロール３の半径方向内側向きに半径方向流体力Ｆｒが作用する。旋回スクロール３には遠心力Ｆｃが半径方向外側向きに発生する。低速回転時には半径方向流体力Ｆｒが遠心力Ｆｃより大きくなることがある。このとき半径力Ｆｔｒが半径方向流体力Ｆｒと遠心力Ｆｃの差よりもわずかに大きくなるように後退角θを設定すると、合力により旋回スクロール３は半径方向外側へ小さい力で押される。このため、旋回ラップ３ａは固定ラップ２ａに接するまで移動し、径方向の隙間がほぼ０になる。従ってポンプ室５の密閉性が向上する。   A radial fluid force Fr acts radially inward of the orbiting scroll 3 during operation of the pump. A centrifugal force Fc is generated in the orbiting scroll 3 outward in the radial direction. When rotating at a low speed, the radial fluid force Fr may be larger than the centrifugal force Fc. At this time, when the receding angle θ is set so that the radial force Ftr is slightly larger than the difference between the radial fluid force Fr and the centrifugal force Fc, the orbiting scroll 3 is pushed radially outward by the resultant force. For this reason, the turning wrap 3a moves until it contacts the fixed wrap 2a, and the radial gap becomes substantially zero. Therefore, the sealing property of the pump chamber 5 is improved.

図７は後退角θを１２°に設定した時の半径力Ｆｔｒと半径方向流体力Ｆｒのシミュレーション結果である。３つのポンプ室５の個々の半径方向流体力（図示せず）は旋回ラップ３ａおよび固定ラップ２ａの位相にかかわらずほぼ一定なので3組のポンプ室を総合した半径方向流体力Ｆｒはほぼ一定値になる。これに対し、ポンプ室５の個々の半径力（図示せず）は一周期内で変動するので、3組のポンプ室を総合した半径力Ｆｔｒは固定ラップ２ａおよび旋回ラップ３ａの位相差の周期で変動する。実施例１では位相差が１２０°なので半径力Ｆｔｒは１２０°周期で変動する。後退角θが１２°の時は１周期中、半径力Ｆｔｒが半径方向流体力Ｆｒを僅かに下回る時期があるが、平均的には半径力Ｆｔｒが半径方向流体力Ｆｒを上回る。従って後退角θの１２°は下限値である。 FIG. 7 shows simulation results of the radial force Ftr and the radial fluid force Fr when the receding angle θ is set to 12 °. Since the individual radial fluid forces (not shown) of the three pump chambers 5 are substantially constant regardless of the phases of the swirl wrap 3a and the fixed wrap 2a, the total radial fluid force Fr of the three sets of pump chambers is substantially constant. become. On the other hand, since each radial force (not shown) of the pump chamber 5 varies within one cycle, the total radial force Ftr of the three sets of pump chambers is a phase difference cycle between the fixed wrap 2a and the swirl wrap 3a. It fluctuates with. In the first embodiment, since the phase difference is 120 °, the radial force Ftr varies in a cycle of 120 °. When the receding angle θ is 12 °, there is a time when the radial force Ftr is slightly lower than the radial fluid force Fr in one cycle, but on average, the radial force Ftr exceeds the radial fluid force Fr. Therefore, 12 ° of the receding angle θ is a lower limit value.

図８は後退角θを１４°に設定した時の半径力Ｆｔｒと半径方向流体力Ｆｒのシミュレーション結果である。１周期中、半径力Ｆｔｒが半径方向流体力Ｆｒを常に上回るから、後退角θの１４°は適正値である。 FIG. 8 shows the simulation results of the radial force Ftr and the radial fluid force Fr when the receding angle θ is set to 14 °. Since the radial force Ftr always exceeds the radial fluid force Fr during one cycle, the receding angle θ of 14 ° is an appropriate value.

図９は後退角θを２０°に設定した時の半径力Ｆｔｒと半径方向流体力Ｆｒのシミュレーション結果である。１周期中、半径力Ｆｔｒの平均値が半径方向流体力Ｆｒの約２倍なので、十分安定的に旋回ラップ３ａを固定ラップ２ａに密着できる。一方、これ以上の半径力Ｆｔｒで押し戻せば、半径方向流体力Ｆｒよりも大きい力で旋回ラップ３ａを固定ラップ２ａに押し付け、接触面圧が過大になり、摩擦損失や摩耗の増大を招くので好ましくない。従って、後退角θの２０°は上限値である。 FIG. 9 shows the simulation results of the radial force Ftr and the radial fluid force Fr when the receding angle θ is set to 20 °. Since the average value of the radial force Ftr is approximately twice the radial fluid force Fr during one cycle, the swirl wrap 3a can be brought into close contact with the fixed wrap 2a sufficiently stably. On the other hand, if it is pushed back with a radial force Ftr larger than this, the swirl wrap 3a is pressed against the fixed lap 2a with a force larger than the radial fluid force Fr, and the contact surface pressure becomes excessive, resulting in increased friction loss and wear. It is not preferable. Accordingly, the receding angle θ of 20 ° is an upper limit value.

以上の検討から後退角θは１２°乃至２０°の範囲に設定することが望ましい。 From the above examination, it is desirable to set the receding angle θ in the range of 12 ° to 20 °.

ポンプ室５内の圧力は吐出圧力に等しい。ポンプ室５の平面方向断面積は吸入開始時に最大で、吐出終了時に最低となる。この断面積に比例してポンプ室５内の吐出圧力は旋回スクロール３を固定スクロール２から引き離そうとする力を発生する。旋回スクロール背面３ｂの圧力は吐出圧力である。この吐出圧力が作用する面積はシール部材９の内側の面積である。この内側の面積はポンプ室５が吸入開始時の最大の水平方向断面積よりわずかに大きくなるようにシール部材９の径を決める。それにより、旋回スクロール３は圧力差により、小さい力で固定スクロール２に押し付けられる。従って、軸方向の隙間がほぼ０になり、ポンプ室５の密閉性が向上する。 The pressure in the pump chamber 5 is equal to the discharge pressure. The cross-sectional area in the plane direction of the pump chamber 5 is maximum at the start of inhalation and minimum at the end of discharge. In proportion to this cross-sectional area, the discharge pressure in the pump chamber 5 generates a force for pulling the orbiting scroll 3 away from the fixed scroll 2. The pressure on the orbiting scroll back surface 3b is the discharge pressure. The area where the discharge pressure acts is the area inside the seal member 9. The inner area determines the diameter of the seal member 9 so that the pump chamber 5 is slightly larger than the maximum horizontal sectional area at the start of suction. Thereby, the orbiting scroll 3 is pressed against the fixed scroll 2 with a small force due to the pressure difference. Therefore, the axial gap becomes almost zero, and the sealing performance of the pump chamber 5 is improved.

ポンプ室で内周側へ押し込まれた流体は吐出ポート３ｂ、連通ポート８ａ、吐出室１４ａを経由して排出ポート１４ｂから外部へ排出される。旋回スクロール３には流体力により回転軸１３の回転方向１３ｄと同一方向に自転トルクが発生する。しかし、固定ラップ２ａと旋回ラップ３ａが１２０度間隔で３組あり、旋回スクロール３の自転力は３組の固定ラップ２ａと旋回ラップ３ａのいずれかのラップ接触部で受けるので、旋回スクロール３の自転は防止される。従って、本ポンプに専用の自転防止機構は必要ない。   The fluid pushed inward in the pump chamber is discharged from the discharge port 14b to the outside through the discharge port 3b, the communication port 8a, and the discharge chamber 14a. A rotating torque is generated in the orbiting scroll 3 by the fluid force in the same direction as the rotational direction 13 d of the rotary shaft 13. However, there are three sets of fixed wrap 2a and orbiting wrap 3a at intervals of 120 degrees, and the rotating force of the orbiting scroll 3 is received by any one of the lap contact portions of the three sets of fixed wrap 2a and orbiting wrap 3a. Rotation is prevented. Therefore, a dedicated rotation prevention mechanism is not necessary for this pump.

課題は旋回ラップと固定ラップの隙間から漏れた液体が外部や駆動部に漏れないようにし、旋回ラップと固定ラップの径方向隙間をほぼ０にし、ポンプ室の密閉性の良いスクロール液ポンプ（以下“本ポンプ”と言う）を提供することである。The problem is that the liquid leaking from the gap between the swirl wrap and the fixed wrap does not leak to the outside and the drive unit, the radial gap between the swirl wrap and the fixed wrap is almost zero, and the scroll liquid pump (hereinafter referred to as the pump chamber) has good sealing performance. "This pump").

図６の内カバー８が旋回スクロール３の背面に設けられる。旋回スクロール３の吐出ポート３ｂと連通する連通ポート８ａが内カバー８に設けられる。連通ポート８ａの周囲にシール溝８ｂが設けられる。シール溝８ｂにリング状のシール部材９（図１）が装着される。シール部材９は旋回スクロール３の背面に密着して、内外の圧力差をシールする。An inner cover 8 in FIG. 6 is provided on the back surface of the orbiting scroll 3. A communication port 8 a that communicates with the discharge port 3 b of the orbiting scroll 3 is provided in the inner cover 8. A seal groove 8b is provided around the communication port 8a. A ring- shaped seal member 9 (FIG. 1) is mounted in the seal groove 8b. The seal member 9 is in close contact with the back surface of the orbiting scroll 3 to seal the pressure difference between inside and outside.

ポンプ室５内の圧力は吐出圧力に等しい。ポンプ室５の平面方向断面積は吸入開始時に最大で、吐出終了時に最低となる。この断面積に比例してポンプ室５内の吐出圧力は旋回スクロール３を固定スクロール２から引き離そうとする力を発生する。旋回スクロール背面の圧力は吐出圧力である。この吐出圧力が作用する面積はシール部材９の内側の面積である。この内側の面積はポンプ室５が吸入開始時の最大の水平方向断面積よりわずかに大きくなるようにシール部材９の径を決める。それにより、旋回スクロール３は圧力差により、小さい力で固定スクロール２に押し付けられる。従って、軸方向の隙間がほぼ０になり、ポンプ室５の密閉性が向上する。The pressure in the pump chamber 5 is equal to the discharge pressure. The cross-sectional area in the plane direction of the pump chamber 5 is maximum at the start of inhalation and minimum at the end of discharge. In proportion to this cross-sectional area, the discharge pressure in the pump chamber 5 generates a force for pulling the orbiting scroll 3 away from the fixed scroll 2. The pressure on the back of the orbiting scroll is the discharge pressure. The area where the discharge pressure acts is the area inside the seal member 9. The inner area determines the diameter of the seal member 9 so that the pump chamber 5 is slightly larger than the maximum horizontal sectional area at the start of suction. Thereby, the orbiting scroll 3 is pressed against the fixed scroll 2 with a small force due to the pressure difference. Therefore, the axial gap becomes almost zero, and the sealing performance of the pump chamber 5 is improved.

Claims (3)

３組の固定ラップを持つ固定スクロールに、３組の旋回ラップを持つ旋回スクロールを向かい合わせて組み合わせ、各ラップ部によりポンプ室を形成し、
固定スクロールの中心部に主軸受を設け、
固定スクロールと一体化した軸受ハウジングに副軸受を設け、
主軸受と副軸受に支持されるクランク軸を有する回転軸を設け、
旋回スクロールの中心部に旋回ラップ先端側の面に開口する旋回軸受ハウジングを設け、
旋回軸受ハウジングに旋回軸受を設け、
旋回軸受がクランク軸と嵌合するスクロール液ポンプ。 Combining fixed scrolls with three sets of fixed wraps with orbiting scrolls with three sets of orbiting laps facing each other, each wrap part forms a pump chamber,
A main bearing is provided at the center of the fixed scroll.
A secondary bearing is provided in the bearing housing integrated with the fixed scroll.
A rotating shaft having a crankshaft supported by the main bearing and the sub-bearing is provided,
A pivot bearing housing is provided at the center of the orbiting scroll and opens to the surface on the orbiting lap tip side.
The slewing bearing housing is provided with a slewing bearing,
A scroll fluid pump in which a slewing bearing is fitted to a crankshaft. 請求項１のスクロール液ポンプにおいて、
クランク軸に回転リングを装着し、
回転リングは長穴を有し、
クランク軸は長穴と隙間嵌めで嵌合する扁平部を有し、
回転リングはクランク軸に対し、長穴の中心軸方向へ微小量移動でき、
回転リングの長穴およびクランク軸の扁平部は回転方向に対して後退角を持つ。 The scroll liquid pump according to claim 1,
Attach a rotating ring to the crankshaft
The rotating ring has a slot,
The crankshaft has a flat part that fits into the long hole with a gap fit,
The rotating ring can move a small amount in the direction of the central axis of the long hole with respect to the crankshaft,
The elongated hole of the rotating ring and the flat part of the crankshaft have a receding angle with respect to the rotation direction. 請求項１のスクロール液ポンプにおいて、
旋回スクロールに設けた旋回ラップの中心部に吐出ポートを設け、
旋回ラップと反対側の面に旋回ラップの外周径と同程度の径の位置にシール部材を設け、
シール部材の内部空間に吐出ポートから吐出された流体の圧力を作用させる。 The scroll liquid pump according to claim 1,
A discharge port is provided at the center of the orbiting wrap provided on the orbiting scroll,
A seal member is provided on the surface opposite to the swirl wrap at a position having a diameter similar to the outer diameter of the swirl wrap,
The pressure of the fluid discharged from the discharge port is applied to the internal space of the seal member.
JP2012264815A 2012-12-03 2012-12-03 Scroll liquid pump Active JP5540192B2 (en)

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