JP2006242173A - Low pressure large capacity scroll fluid machinery - Google Patents
Low pressure large capacity scroll fluid machinery Download PDFInfo
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- JP2006242173A JP2006242173A JP2006001669A JP2006001669A JP2006242173A JP 2006242173 A JP2006242173 A JP 2006242173A JP 2006001669 A JP2006001669 A JP 2006001669A JP 2006001669 A JP2006001669 A JP 2006001669A JP 2006242173 A JP2006242173 A JP 2006242173A
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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
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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
- F04C18/0215—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 where only one member is moving
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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
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
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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
- 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
Abstract
Description
本発明は、比較的低圧で、大容量が得られるようにしたスクロール流体機械に関する。 The present invention relates to a scroll fluid machine capable of obtaining a large capacity at a relatively low pressure.
スクロール圧縮機およびスクロール真空機械を含むスクロール流体機械においては、外周部におけるラップの巻き終わり側から、中心付近におけるラップの巻き始め側までの密閉空間の容積を順次縮小させることにより、外周部から吸入した気体を加圧し、中心部付近から吐出させるか、その逆に、中心部付近から吸気し、外周部から吐出させるようになっている。 In a scroll fluid machine including a scroll compressor and a scroll vacuum machine, the volume of the sealed space from the winding end side of the wrap at the outer peripheral part to the winding start side of the wrap in the vicinity of the center is sequentially reduced to suck from the outer peripheral part. The pressurized gas is pressurized and discharged from the vicinity of the center, or conversely, the air is sucked from the vicinity of the center and discharged from the outer periphery.
このような従来の一般のスクロール流体機械は、いわば中・高圧用のものであって、相当に高圧の圧縮気体を得ることができ、また効果的な減圧作用を行わせることができる。 Such a conventional general scroll fluid machine is, so to speak, for medium and high pressure, and can obtain a compressed gas having a considerably high pressure, and can perform an effective pressure reducing action.
しかし、このような従来型のスクロール流体機械によっては、例えば小麦粉等の粉体を輸送するために、例えば約0.2〜0.3MPa程度の低圧で大容量の圧縮気体を得ることはできない。このような低圧で大容量の圧縮気体を得るためには、ラップ間隔を大として、その巻数を少くしなければならない。 However, according to such a conventional scroll fluid machine, a large volume of compressed gas cannot be obtained at a low pressure of about 0.2 to 0.3 MPa, for example, in order to transport powder such as wheat flour. In order to obtain a large volume of compressed gas at such a low pressure, it is necessary to increase the wrap interval and reduce the number of turns.
ラップ間の間隔を大とすると、当然、旋回スクロールの旋回時の半径が大きくなり、旋回スクロールの外径が大となる。そのため、質量が増加した旋回スクロールを大きく旋回運動させなければならなくなる。また、旋回スクロールの旋回軸受部における荷重も大となり、それに応じて、耐荷重の大きな軸受けが必要となるとともに、重量ならびに寸法は大となり、製造コストも増加する。 When the interval between the laps is increased, the radius of the orbiting scroll is naturally increased, and the outer diameter of the orbiting scroll is increased. For this reason, the orbiting scroll having increased mass must be largely orbited. Further, the load at the orbiting bearing portion of the orbiting scroll is increased, and accordingly, a bearing having a large load resistance is required, and the weight and size are increased, and the manufacturing cost is increased.
このような問題を回避するためには、旋回スクロールの径が極力大とならないように、ラップをなるべく旋回スクロールの中心に近いところまでに亘って形成すればよいが、このようにすると、吐出圧力が高まり、所望の低圧の圧縮気体を得ることはできなくなる。 In order to avoid such a problem, the wrap may be formed as close as possible to the center of the orbiting scroll so that the diameter of the orbiting scroll does not become as large as possible. As a result, the desired low-pressure compressed gas cannot be obtained.
そのため、従来、低圧用のスクロール圧縮機においては、旋回スクロールの中心部付近においては旋回ラップを除去し、中心から離れた部分にのみ、間隔を大としたラップが設けられていた。しかし、このようにしたものでは、旋回スクロールの中心部は、なんら出力には機能せず、非効率的であり、かつ不経済である。 For this reason, conventionally, in the scroll compressor for low pressure, the orbiting wrap is removed in the vicinity of the center portion of the orbiting scroll, and the wrap having a large interval is provided only in the portion away from the center. However, with this arrangement, the center portion of the orbiting scroll does not function at all for output, and is inefficient and uneconomical.
本発明は、ラップ間の間隔を、従来の中・高圧用のものと同様とし、かつ従来利用されていなかった中心部付近にも、外周部におけるラップによる圧縮気体と同等の低圧の圧縮気体を生成しうるラップを設けることにより、全体寸法およびスクロールの回転数を変えることなく、低圧の大風量が得られるようにしたスクロール流体機械を得ることを目的としている。 In the present invention, the interval between the wraps is the same as that for the conventional medium and high pressure, and a compressed gas having a low pressure equivalent to the compressed gas generated by the wraps in the outer peripheral portion is also provided in the vicinity of the central portion which has not been conventionally used. An object of the present invention is to provide a scroll fluid machine in which a low pressure and large air volume can be obtained without changing the overall dimensions and the rotation speed of the scroll by providing a wrap that can be generated.
本発明によると、上記目的は、次のような構成とすることにより達成される。
(1)端板の外周部に、吸気口に連なり、かつ低圧の圧縮気体を得るべく間隔を大とした渦巻状のラップを設けることにより、外側容積変動室を形成し、かつこの外側容積変動室と前記端板の中心部との間に、前記吸気口に連なり、圧縮比を、前記外側容積変動室におけるそれと実質的に同一とした内側容積変動室を設け、前記端板の偏心旋回に伴い、前記内外の容積変動室より、実質的に同一圧力の低圧気体を吐出させるようにする。
According to the present invention, the above object is achieved by adopting the following configuration.
(1) An outer volume fluctuation chamber is formed by providing a spiral wrap that is connected to the air inlet and has a large interval to obtain a low-pressure compressed gas on the outer peripheral portion of the end plate, and this outer volume fluctuation. An inner volume fluctuation chamber is provided between the chamber and the central portion of the end plate, and an inner volume fluctuation chamber is provided with a compression ratio substantially the same as that of the outer volume fluctuation chamber. Accordingly, low-pressure gas having substantially the same pressure is discharged from the inner and outer volume fluctuation chambers.
(2)上記(1)項において、外側容積変動室の外端における外側吸気口と連通する外側始端容積変動室と、外側容積変動室の内端における吐気口と連通する外側終端容積変動室との容積比と、内側容積変動室の外端における内側吸気口と連通する内側始端容積変動室と、内側容積変動室の内端における内側吐気口と連通する内側終端容積変動室との容積比を、実質的に等しくする。 (2) In the above item (1), an outer start volume change chamber communicating with the outer intake port at the outer end of the outer volume change chamber, and an outer end volume change chamber communicating with the air outlet at the inner end of the outer volume change chamber; The volume ratio of the inner start volume change chamber that communicates with the inner intake port at the outer end of the inner volume change chamber and the inner end volume change chamber that communicates with the inner vent at the inner end of the inner volume change chamber. To be substantially equal.
(3)上記(1)または(2)項において、外側容積変動室の吐気口を、内側容積変動室の吸気口と接続する。 (3) In the above item (1) or (2), the air outlet of the outer volume fluctuation chamber is connected to the air inlet of the inner volume fluctuation chamber.
(4)上記(1)〜(3)項のいずれかにおいて、スクロール圧縮機とする。 (4) In any of the above items (1) to (3), a scroll compressor is used.
(5)端板の中心部に、吸気口に連なり、かつ低圧の圧縮気体を得るべく間隔を大とした渦巻状のラップを設けることにより、内側容積変動室を形成し、この内側容積変動室と前記端板の外周部との間に、前記吸気口に連なり、かつ圧縮比を、前記外側容積変動室におけるそれと実質的に同一とした内側容積変動室を設け、前記端板の偏心旋回に伴い、前記内外の容積変動室より、実質的に同一圧力の低圧気体を吐出させるようにする。 (5) An inner volume fluctuation chamber is formed by providing a spiral wrap which is connected to the air inlet and has a large interval in order to obtain a low-pressure compressed gas at the center of the end plate. An inner volume fluctuation chamber that is connected to the air inlet and has a compression ratio substantially the same as that of the outer volume fluctuation chamber is provided between the outer peripheral portion of the end plate and the outer peripheral portion of the end plate. Accordingly, low-pressure gas having substantially the same pressure is discharged from the inner and outer volume fluctuation chambers.
(6)上記(5)項において、外側容積変動室の外端における外側吐気口と連通する外側始端容積変動室と、外側容積変動室の内端における吸気口と連通する外側終端容積変動室との容積比と、内側容積変動室の外端における内側吐気口と連通する内側始端容積変動室と、内側容積変動室の内端における内側吸気口と連通する内側終端容積変動室との容積比を、実質的に等しくする。 (6) In the above item (5), an outer start volume change chamber that communicates with the outer air outlet at the outer end of the outer volume change chamber, and an outer terminal volume change chamber that communicates with the intake port at the inner end of the outer volume change chamber; The volume ratio of the inner start volume change chamber that communicates with the inner vent at the outer end of the inner volume change chamber and the inner end volume change chamber that communicates with the inner intake port at the inner end of the inner volume change chamber. To be substantially equal.
(7)上記(5)または(6)項において、内側容積変動室の吐気口を、外側容積変動室の吸気口と接続する。 (7) In the above item (5) or (6), the air outlet of the inner volume fluctuation chamber is connected to the air inlet of the outer volume fluctuation chamber.
(8)上記(5)〜(7)項のいずれかにおいて、スクロール減圧機とする。 (8) In any one of the above items (5) to (7), a scroll decompressor is used.
請求項1記載の発明:−端板の旋回に伴い、内外の容積変動室内にそれぞれ吸引された気体は、同時に加圧されて、内外の容積変動室より、実質的に同一圧力で吐出するので、全体寸法を大としなくても、両容積変動室からの吐出圧力気体の合計量は、従来の外周部にのみしかラップが設けられていないものに比して大となる。 Invention according to claim 1:-Gases sucked into the inner and outer volume fluctuation chambers as the end plates are swung are simultaneously pressurized and discharged from the inner and outer volume fluctuation chambers at substantially the same pressure. Even if the overall dimensions are not increased, the total amount of the discharge pressure gas from the two volume fluctuation chambers is larger than that in the conventional case where the wrap is provided only on the outer peripheral portion.
請求項2記載の発明:−外側および内側の容積変動室からは、実質的に等圧の大量の圧縮気体が吐出する。 Invention of Claim 2: A large amount of compressed gas of substantially equal pressure is discharged from the outer and inner volume fluctuation chambers.
請求項3記載の発明:−外側容積変動室から吐出した圧縮気体は、内側容積変動室で再圧縮されるので、やや高圧の圧縮気体が大量に得られる。 Invention of Claim 3: Since the compressed gas discharged from the outer volume fluctuation chamber is recompressed in the inner volume fluctuation chamber, a somewhat high pressure compressed gas is obtained.
請求項4記載の発明:−吐出圧力気体量の大きな圧縮機が得られる。 Invention of Claim 4: A compressor with a large discharge pressure gas amount is obtained.
請求項5記載の発明:−端板の旋回に伴い、内外の容積変動室内にそれぞれ吸引された気体は、同時に減圧されて、内外の容積変動室より、実質的に同一圧力で吐出するので、全体寸法を大としなくても、両容積変動室からの吐出気体の合計量は、従来の外周部にのみしかラップが設けられていないものに比して大となり、効果的な減圧が行われる。 The invention according to claim 5:-The gas sucked into the inner and outer volume variation chambers is simultaneously decompressed and discharged from the inner and outer volume variation chambers at substantially the same pressure as the end plate turns. Even if the overall dimensions are not increased, the total amount of gas discharged from both volume change chambers is larger than that of conventional wraps only on the outer periphery, and effective decompression is performed. .
請求項6記載の発明:−内側および外側の容積変動室からは、実質的に等圧の大量の気体が吐出し、効果的な減圧が行われる。 Invention of Claim 6: A large amount of gas of substantially equal pressure is discharged from the inner and outer volume fluctuation chambers, and effective pressure reduction is performed.
請求項7記載の発明:−内側容積変動室へ吸引された圧縮気体は、外側容積変動室で減圧され、効果的な減圧が行われる。 Invention of Claim 7: The compressed gas suck | inhaled to the inner side volume fluctuation | variation chamber is pressure-reduced by an outer side volume fluctuation | variation chamber, and effective pressure reduction is performed.
請求項8記載の発明:−減圧効果の大きな減圧機が得られる。 Invention of Claim 8:-A decompressor with a large decompression effect is obtained.
図1は、請求項1〜4に記載されている本発明、すなわち、スクロール流体機械の一例としてのスクロール圧縮機に、本発明を適用した一実施形態を示す縦断側面図である。 FIG. 1 is a longitudinal side view showing an embodiment in which the present invention is applied to the present invention described in claims 1 to 4, that is, a scroll compressor as an example of a scroll fluid machine.
なお本発明においては、その特徴として、固定ラップと旋回ラップからなる容積変動室を、外周側と内周側とに区分してある。 In the present invention, as a feature thereof, the volume fluctuation chamber composed of a fixed lap and a swirl lap is divided into an outer peripheral side and an inner peripheral side.
図1に示すスクロール圧縮機の基本的な構造は、従来のものと同様であるので、簡単に説明する。なお図1において、左方を前、右方を後とする。 Since the basic structure of the scroll compressor shown in FIG. 1 is the same as that of the conventional one, it will be briefly described. In FIG. 1, the left side is the front and the right side is the rear.
前部、すなわち図1の左端部における固定スクロール(1)の固定端板(2)の外周部適所には、外側吸気口(3a)が、同じく中心部には、内側吐気口(4b)が設けられ、かつそれらの間には、外側吐気口(4a)と内側吸気口(3b)が設けられている。 An outer intake port (3a) is located at a suitable position on the outer periphery of the fixed end plate (2) of the fixed scroll (1) at the front end, that is, the left end of FIG. 1, and an inner exhalation port (4b) is also located at the center. An outer air outlet (4a) and an inner air inlet (3b) are provided between them.
固定端板(2)の後面には、渦巻状の固定ラップ(5)が立設され、同じく前面には、水平方向を向く、緩い波状の等高の冷却フィン(6)が、ほぼ等間隔をもって立設されている。 A spiral fixed wrap (5) is erected on the rear surface of the fixed end plate (2). Similarly, on the front surface, loose, wave-shaped, uniform cooling fins (6) facing the horizontal direction are arranged at almost equal intervals. It is erected with.
固定スクロール(1)の後側に対向して配置されている旋回スクロール(7)は、円形の旋回端板(8)の前面、すなわち固定スクロール(1)と対向する面に、渦巻状の旋回ラップ(9)を立設し、かつ同じく後面に、水平方向を向く多数の波状の等高の冷却フィン(10)を、ほぼ等間隔をもって立設して形成されている。 The orbiting scroll (7) arranged facing the rear side of the fixed scroll (1) has a spiral orbit on the front surface of the circular orbiting end plate (8), that is, the surface facing the fixed scroll (1). The wrap (9) is erected, and a plurality of wavy cooling fins (10) that are horizontally oriented and are erected at substantially equal intervals on the rear surface.
旋回スクロール(7)の後面には、ベアリングプレート(11)が重合され、止着されている。ベアリングプレート(11)の後面の中心部には、駆動軸(12)の偏心軸部(13)をベアリング(14)を介して枢支する筒状ボス(15)が突設されている。 A bearing plate (11) is superposed and secured to the rear surface of the orbiting scroll (7). A cylindrical boss (15) that pivotally supports the eccentric shaft portion (13) of the drive shaft (12) via the bearing (14) projects from the center portion of the rear surface of the bearing plate (11).
ベアリングプレート(11)の後面の外周部の3か所には、例えば公知のクランクピン型式の自転防止機構(16)を組み込んで、旋回スクロール(7)が、それが収容されているハウジング(17)に対し、駆動軸(12)まわりに、偏心的に旋回しうるようにしてある。 For example, a known crankpin type anti-rotation mechanism (16) is incorporated at three locations on the outer peripheral portion of the rear surface of the bearing plate (11), and the orbiting scroll (7) is housed in a housing (17 ) With respect to the drive shaft (12).
固定スクロール(1)の前面にはカバープレート(18)が当接され、適宜の締付けねじ(19)で、締付け固定されている。 A cover plate (18) is brought into contact with the front surface of the fixed scroll (1) and is fastened and fixed by an appropriate fastening screw (19).
旋回スクロール(7)と、その後面に重合されているベアリングプレート(11)とは、締付けねじ(20)で締付けて一体化されている。 The orbiting scroll (7) and the bearing plate (11) superposed on the rear surface are integrated by tightening with a tightening screw (20).
固定スクロール(1)の後面板(21)は、ハウジング(17)の前面に重合され、両者は、ボルト(22)とナット(23)により締着されている。 The rear plate (21) of the fixed scroll (1) is superposed on the front surface of the housing (17), and both are fastened by bolts (22) and nuts (23).
前記固定ラップ(5)および旋回ラップ(9)の先端面には、それぞれ嵌溝(24)(25)が形成され、各嵌溝(24)(25)内には、それぞれ、対向する旋回スクロール(7)の旋回端板(8)、および固定スクロール(1)の固定端板(4)に摺接するシール部材(S)が嵌設されている。 Fitting grooves (24) and (25) are formed on the front end surfaces of the fixed wrap (5) and the orbiting wrap (9), respectively, and the orbiting scrolls facing each other in the fitting grooves (24) and (25), respectively. The revolving end plate (8) of (7) and the seal member (S) that comes into sliding contact with the fixed end plate (4) of the fixed scroll (1) are fitted.
図1におけるII−II線縦断面図である図2および図3に示すように、固定ラップ(5)は、外側吸気口(3a)に連なる外側容積変動室用固定ラップ(5a)と、内側吐出口(4b)に連なる内側容積変動室用固定ラップ(5b)とに区分され、旋回ラップ(9)は、外側容積変動室用旋回ラップ(9a)と、内側容積変動室用旋回ラップ(9b)とに区分されている。 As shown in FIGS. 2 and 3, which are longitudinal sectional views taken along line II-II in FIG. 1, the fixed wrap (5) includes an outer volume fluctuation chamber fixed wrap (5 a) connected to the outer intake port (3 a) and an inner side. The swirl wrap (9) is divided into an inner volume fluctuation chamber swirl wrap (9a) and an inner volume fluctuation chamber swirl wrap (9b). ).
しかして、外側容積変動室用固定ラップ(5a)と外側容積変動室用旋回ラップ(9a)との間隔は大とされ、内側容積変動室用固定ラップ(5b)と内側容積変動室用旋回ラップ(9b)との間隔は、やや小とされている。 Therefore, the distance between the outer volume fluctuation chamber fixed wrap (5a) and the outer volume fluctuation chamber swirl wrap (9a) is increased, and the inner volume fluctuation chamber fixed wrap (5b) and the inner volume fluctuation chamber swirl wrap. The distance from (9b) is a little small.
また、外側吸気口(3a)と連通する外側始端容積変動室(A)と、外側吐気口(4a)と連通する外側終端容積変動室(B)との容積比と、内側吸気口(3b)と連通する内側始端容積変動室(C)と、内側吐気口(4b)と連通する内側終端容積変動室(D)との容積比を、実質的に等しくしてある。 In addition, the volume ratio between the outer start volume change chamber (A) communicating with the outer intake port (3a) and the outer end volume change chamber (B) communicating with the outer exhalation port (4a), and the inner intake port (3b) The volume ratio of the inner start end volume fluctuation chamber (C) communicating with the inner end volume fluctuation chamber (D) communicating with the inner vent (4b) is substantially equal.
従って、外側および内側の両容積変動室内において、ほぼ等圧力の圧縮気体が生成され、スクロールの中心部におけるラップが除去されていた従来のものに比して、大量の低圧圧縮気体が得られる。 Therefore, compressed gas having substantially equal pressure is generated in both the outer and inner volume fluctuation chambers, and a large amount of low-pressure compressed gas is obtained as compared with the conventional one in which the wrap at the center of the scroll is removed.
図4は、請求項5〜8に記載されている本発明、すなわち、スクロール流体機械の一例としてのスクロール減圧機(スクロール真空機械を含む)に、本発明を適用した一実施形態における図2と同様の縦断側面図である。
FIG. 4 shows the present invention described in
図4においては、図2における内側吐気口(4b)を内側吸気口(3b)とし、同じく外側吐気口(4a)を外側吸気口(3a)とし、同じく内側吸気口(3b)を内側吐気口(4b)とし、同じく外側吸気口(3a)を外側吐気口(4a)としたものであり、他は、図1〜図3に示したものと異なるところはない。 In FIG. 4, the inner air outlet (4b) in FIG. 2 is the inner air inlet (3b), the outer air outlet (4a) is the outer air inlet (3a), and the inner air inlet (3b) is the inner air outlet. (4b), and the outer intake port (3a) is also used as the outer exhalation port (4a). Other than that, there is no difference from the one shown in FIGS.
図4に示したものにより、内側吸気口(3b)から吸入された気体は、外側吐気口(4a)から吐出し、減圧されることは明らかである。 As shown in FIG. 4, it is apparent that the gas sucked from the inner air inlet (3b) is discharged from the outer air outlet (4a) and decompressed.
(1)固定スクロール
(2)固定端板
(3a)外側吸気口
(3b)内側吸気口
(4a)外側吐気口
(4b)内側吐気口
(5)固定ラップ
(5a)外側容積変動室用固定ラップ
(5b)内側容積変動室用固定ラップ
(6)冷却フィン
(7)旋回スクロール
(8)旋回端板
(9)旋回ラップ
(9a)外側容積変動室用旋回ラップ
(9b)内側容積変動室用旋回ラップ
(10)冷却フィン
(11)ベアリングプレート
(12)駆動軸
(13)偏心軸部
(14)ベアリング
(15)筒状ボス
(16)自転防止機構
(17)ハウジング
(18)カバープレート
(19)(20)締付けねじ
(21)後面板
(21a)外向フランジ
(22)ボルト
(23)ナット
(24)(25)嵌溝
(S)シール部材
A 外側始端容積変動室
B 外側終端容積変動室
C 内側始端容積変動室
D 内側終端容積変動室
(1) Fixed scroll
(2) Fixed end plate
(3a) Outer air inlet
(3b) Inner air inlet
(4a) Outer vent
(4b) Inside nausea
(5) Fixed wrap
(5a) Outer volume fluctuation chamber fixed wrap
(5b) Inner volume fluctuation chamber fixed wrap
(6) Cooling fin
(7) Orbiting scroll
(8) Revolving end plate
(9) Turning lap
(9a) Swirling wrap for outer volume fluctuation chamber
(9b) Swivel wrap for inner volume fluctuation chamber
(10) Cooling fin
(11) Bearing plate
(12) Drive shaft
(13) Eccentric shaft
(14) Bearing
(15) Cylindrical boss
(16) Anti-rotation mechanism
(17) Housing
(18) Cover plate
(19) (20) Clamping screw
(21) Rear plate
(21a) Outward flange
(22) Bolt
(23) Nut
(24) (25) Fitting groove
(S) Seal member A Outer start volume change chamber B Outer end volume change chamber C Inner start volume change chamber D Inner end volume change chamber
Claims (8)
The scroll fluid machine according to any one of claims 5 to 7, wherein the scroll fluid machine is a scroll decompressor.
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2006001669A JP2006242173A (en) | 2005-02-02 | 2006-01-06 | Low pressure large capacity scroll fluid machinery |
US11/307,082 US20060198746A1 (en) | 2005-02-02 | 2006-01-23 | Scroll fluid machine |
KR1020060008256A KR100732841B1 (en) | 2005-02-02 | 2006-01-26 | Scroll fluid machine |
EP06001710A EP1696127A2 (en) | 2005-02-02 | 2006-01-27 | Scroll compressor |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2005025766 | 2005-02-02 | ||
JP2006001669A JP2006242173A (en) | 2005-02-02 | 2006-01-06 | Low pressure large capacity scroll fluid machinery |
Publications (1)
Publication Number | Publication Date |
---|---|
JP2006242173A true JP2006242173A (en) | 2006-09-14 |
Family
ID=36143180
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP2006001669A Pending JP2006242173A (en) | 2005-02-02 | 2006-01-06 | Low pressure large capacity scroll fluid machinery |
Country Status (4)
Country | Link |
---|---|
US (1) | US20060198746A1 (en) |
EP (1) | EP1696127A2 (en) |
JP (1) | JP2006242173A (en) |
KR (1) | KR100732841B1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR100732841B1 (en) | 2005-02-02 | 2007-06-27 | 아네스토 이와타 가부시키가이샤 | Scroll fluid machine |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR101173826B1 (en) | 2006-02-09 | 2012-08-16 | 알테어 세미콘덕터 엘티디. | Dual-function wireless data terminal |
Family Cites Families (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4141677A (en) * | 1977-08-15 | 1979-02-27 | Ingersoll-Rand Company | Scroll-type two stage positive fluid-displacement apparatus with intercooler |
JP3591101B2 (en) * | 1995-12-19 | 2004-11-17 | ダイキン工業株式会社 | Scroll type fluid machine |
KR100195166B1 (en) * | 1996-12-31 | 1999-06-15 | 신영주 | Scroll compressor |
US6050792A (en) * | 1999-01-11 | 2000-04-18 | Air-Squared, Inc. | Multi-stage scroll compressor |
JP2002130156A (en) * | 2000-10-20 | 2002-05-09 | Anest Iwata Corp | Scroll fluid machine having multistage type fluid compressing part |
JP2002266777A (en) * | 2001-03-07 | 2002-09-18 | Anest Iwata Corp | Scroll fluid machine provided with multi-stage fluid compression part |
JP4031222B2 (en) * | 2001-09-21 | 2008-01-09 | アネスト岩田株式会社 | Scroll type fluid machine |
JP4044311B2 (en) | 2001-09-27 | 2008-02-06 | アネスト岩田株式会社 | Air-cooled scroll fluid machine |
JP4031223B2 (en) * | 2001-09-27 | 2008-01-09 | アネスト岩田株式会社 | Scroll type fluid machine |
US20060099096A1 (en) * | 2004-11-08 | 2006-05-11 | Shaffer Robert W | Scroll pump system |
JP2006242173A (en) | 2005-02-02 | 2006-09-14 | Anest Iwata Corp | Low pressure large capacity scroll fluid machinery |
-
2006
- 2006-01-06 JP JP2006001669A patent/JP2006242173A/en active Pending
- 2006-01-23 US US11/307,082 patent/US20060198746A1/en not_active Abandoned
- 2006-01-26 KR KR1020060008256A patent/KR100732841B1/en not_active IP Right Cessation
- 2006-01-27 EP EP06001710A patent/EP1696127A2/en not_active Withdrawn
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR100732841B1 (en) | 2005-02-02 | 2007-06-27 | 아네스토 이와타 가부시키가이샤 | Scroll fluid machine |
Also Published As
Publication number | Publication date |
---|---|
US20060198746A1 (en) | 2006-09-07 |
EP1696127A2 (en) | 2006-08-30 |
KR20060088824A (en) | 2006-08-07 |
KR100732841B1 (en) | 2007-06-27 |
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