WO2016194156A1 - スクロール式流体機械 - Google Patents
スクロール式流体機械 Download PDFInfo
- Publication number
- WO2016194156A1 WO2016194156A1 PCT/JP2015/065974 JP2015065974W WO2016194156A1 WO 2016194156 A1 WO2016194156 A1 WO 2016194156A1 JP 2015065974 W JP2015065974 W JP 2015065974W WO 2016194156 A1 WO2016194156 A1 WO 2016194156A1
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- WIPO (PCT)
- Prior art keywords
- scroll
- wrap
- lap
- fluid machine
- fixed scroll
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Classifications
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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
- 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
- F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
- F04C18/0269—Details concerning the involute wraps
Definitions
- the present invention relates to a scroll fluid machine that is suitably used as a compressor such as air or refrigerant, or as a vacuum pump.
- Japanese Patent Laid-Open No. 2004-26883 discloses that a portion where the temperature increase on the tooth tip side of the wrap portion of the fixed scroll or the orbiting scroll is larger than the temperature increase on the tooth bottom side during the compression operation is the lap portion of the fixed scroll or the orbiting scroll. A configuration is described in which the clearance in the closest state between the scroll lap portions facing radially outward is larger than the portion where the temperature rise on the tooth bottom side is larger than the temperature rise on the tooth tip side. ing.
- Scroll-type fluid machines are designed to increase compression efficiency by reducing the lap clearance between the fixed scroll and the orbiting scroll as much as possible during compression operation and suppressing leakage of compressed fluid from the compression chamber.
- the lap is heated by the compressed air that has been compressed to a high temperature, and the lap gap changes due to thermal deformation. Due to the change in the lap gap, there is a possibility that the lap may come into contact with the portion where the gap becomes small, and the leak performance of the compressed fluid deteriorates at the portion where the gap becomes large.
- the temperature increase on the tooth tip side of the wrap portion is greater than the temperature increase on the tooth bottom side.
- the clearance in the closest state between the lap parts of the scroll which are opposed to each other on the outer side in the radial direction is made large, and the contact of the lap due to thermal deformation is prevented.
- the present invention includes a plurality of means for solving the above-described problems.
- a fixed scroll having a spiral wrap portion, and a wrap portion of the fixed scroll provided to face the fixed scroll.
- a orbiting scroll in which a spiral wrap portion revolves so as to form a plurality of compression chambers between the fixed scroll and the orbiting scroll.
- a scroll fluid machine is provided in which a concave portion is provided on one side surface and a convex portion is provided on the other side surface.
- FIG. 1 is a cross-sectional view of a scroll compressor according to Embodiment 1 of the present invention. It is sectional drawing of the scroll compressor which concerns on Example 1 of this invention. It is sectional drawing of the scroll compressor which concerns on Example 1 of this invention. It is sectional drawing of the scroll compressor which shows the subject of this invention. It is sectional drawing of the scroll compressor which shows the subject of this invention. It is sectional drawing of the lap
- Embodiment 1 of the present invention will be described in detail with reference to FIGS.
- FIG. 1 is an external view of a scroll compressor main body according to the present invention, in which (A) is a front view, (B) is a right side view, (C) is a left side view, (D) is a top view, E) shows a rear view.
- reference numeral 70 denotes a casing that constitutes the outer shell of the compressor body, and is formed as a bottomed cylindrical body that is closed on one side in the axial direction and opened on the other side in the axial direction. An orbiting scroll described later is accommodated in the cylindrical portion of the casing 70.
- the compressor main body has a fixed scroll as one scroll member fixedly provided on the opening end side of the casing 70.
- a pulley 72 is provided at one end of a drive shaft (not shown) and is connected to an output side of an electric motor as a drive source via a belt (none of which is shown) to drive the drive shaft. .
- the drive shaft causes the orbiting scroll to orbit with respect to the fixed scroll.
- a motor-integrated scroll air compressor in which the rotation shaft of the motor is integrated with the drive shaft, and the pulley 72 and the belt may be omitted.
- Reference numeral 80 denotes a suction port provided on the outer peripheral side of the fixed scroll. The suction port 80 sucks air from the outside through the suction filter 81, and this air is continuously generated in each compression chamber as the orbiting scroll rotates. Compressed.
- the orbiting scroll is driven via a drive shaft by an electric motor (not shown) or the like, and performs an orbiting motion with respect to the fixed scroll.
- the compression chamber on the outer diameter side among the plurality of compression chambers sucks air from the suction port 80 of the fixed scroll, and this air is continuously compressed in each compression chamber.
- compressed air is discharged toward the exterior from the discharge port 42 located in the center side from the compression chamber of the innermost diameter side.
- Reference numeral 73 denotes a discharge pipe provided in connection with the discharge port 42 of the fixed scroll.
- the discharge pipe 73 constitutes a discharge flow path for communicating between a storage tank (not shown) and the discharge port 42. .
- Reference numeral 74 denotes a fan duct that guides cooling air generated by rotation of a cooling fan described later to the fixed cooling fin 75 of the fixed scroll and the orbiting cooling fin 76 of the orbiting scroll.
- Reference numeral 77 denotes a fin cover that covers the fixed cooling fin 75.
- FIG. 2 shows a cross-sectional view of the scroll portion of the scroll compressor of the present invention.
- the orbiting scroll 1 and the fixed scroll 2 are respectively provided in a spiral shape on the end plate and overlap each other. Due to the orbiting motion of the orbiting scroll 1, the compression chamber 5 defined between the lap portion 3 of the orbiting scroll 1 and the lap portion 4 of the fixed scroll 2 is continuously reduced. As a result, each compression chamber sequentially compresses the air sucked from the suction port 6 and discharges the compressed air from the discharge port 7 to the external air tank (not shown) via the discharge port 42.
- the ab line is called an outside line
- the ac line is called an extension line
- the distance between d and e is called an outside line
- the distance between d and f is called an extension.
- compression chambers 5 on the outer peripheral side are referred to as a compression chamber Pd (5d), a compression chamber Pe (5e), and a compression chamber Pf (5f), respectively.
- the pressure in each compression chamber increases as it approaches the discharge port 6. That is, the height of the pressure is 5c> 5b> 5a in order. Similarly, 5f> 5e> 5d.
- FIG. 3 shows a cross-sectional view of the scroll compressor after the orbiting scroll 1 has moved half a turn from the state of FIG.
- each compression chamber approaches the discharge port 6 by a half circumference
- the compression chamber Pa (5a) is in the compression chamber Pa ′ (5a ′)
- the compression chamber Pb (5b) is in the compression chamber Pb ′ (5b ′).
- the compression chamber Pc (5c) is changed to a compression chamber Pc ′ (5c ′).
- the compression chamber Pd (5d) is the compression chamber Pd ′ (5d ′)
- the compression chamber Pe (5e) is the compression chamber Pe ′ (5e ′)
- the compression chamber Pf (5f) is the compression chamber Pf ′ ( 5f ').
- the inner compression chamber Pc '(5c') and the compression chamber Pf '(5f') communicate with the discharge port 6 and discharge compressed air to an air tank (not shown).
- Figure 4 shows the lap gap.
- the orbiting scroll 1 and the fixed scroll 2 have a compressed air from each compression chamber by reducing the radial gap ⁇ (referred to as a lap gap) formed in the lap portions 3 and 4 as much as possible. Is suppressed and the efficiency as an air compressor is increased.
- Compressed air is hot, causing the orbiting scroll 1 and the fixed scroll 2 to undergo thermal deformation. Further, deformation is caused by receiving the pressure of compressed air. Further, the wrap portions 3 and 4 are similarly deformed. Therefore, if the lap gap ⁇ is reduced, the wrap portions 3 and 4 may come into contact when the lap portions 3 and 4 are deformed due to the influence of the heat of the compressed air or the like.
- FIG. 5 and 6 are cross-sectional views of a scroll compressor showing the problem of the present invention.
- FIG. 5 shows the compressor during operation when the lap gap ⁇ is small.
- the wrap portion is deformed by the influence of heat or the like. 4 has contacted the lap part 3. In this case, the scroll compressor is damaged.
- the lap gap ⁇ is made large so that the lap portion 3 and the lap portion 4 do not contact each other.
- the lap gap ⁇ passes from the pressure difference, and the compression chamber Pc (5c) to the compression chamber Pb ( 5b), the compressed air flows out from the compression chamber Pb (5b) to the compression chamber Pa (5a), and the efficiency of the compressor is lowered.
- FIG. 6 is the moment when the orbiting scroll 1 has moved half a turn from the state of FIG.
- FIG. 6 shows an AA cross section at the same position as in FIG.
- the AA cross section of FIG. 6 defines a compression chamber Pf ′ (5f ′) and a compression chamber Pe ′ (5e ′), and a compression chamber Pd ′ (5d ′) and a compression chamber Pe ′ (5e ′). Yes.
- the wrap portion 4 that has been deformed so as to fall in the contact direction due to the influence of heat or the like at the moment of FIG. It is shaped to leave, creating a gap.
- Patent Document 1 Patent No. 4988805 shown in the background art
- contact with the lap portion 3 is prevented by shaving the lap portions 3 and 4 at a portion where the lap gap ⁇ is reduced by deformation, thereby preventing the lap gap ⁇ .
- the portion where the lap gap ⁇ becomes large as shown in FIG. 6 has the gap as it is and the efficiency as the compressor is lowered.
- FIG. 7 shows the shape of the lap portion 4 in the present embodiment.
- a concave portion 8 is provided on the side surface of the lap portion 4 where the lap gap is reduced due to deformation due to the influence of heat or the like, and the lap portions 3 and 4 come into contact (galling). It is preventing.
- a convex portion 9 is provided on the opposite side surface provided with the concave portion 8 in order to prevent the lap gap from becoming large. By providing the convex part 9, even after the wrap part 3 and the wrap part 4 are deformed, the enlargement of the lap gap can be prevented and the leakage of compressed air is prevented.
- FIG. 8 shows a cross-sectional view of the wrap portion 4 of the fixed scroll 2 in this embodiment.
- FIG. 7 shows the concave portion 8 and the convex portion 9 only for a part for explanation, but in this embodiment, the concave portion 8 and the convex portion 9 are provided over the entire circumference of the wrap portion 4 as shown in FIG. 8. .
- the wrap portion 3 of the orbiting scroll 1 may be similarly provided with the concave portion 8 and the convex portion 9 over the entire circumference.
- FIG. 9 shows the deformation amount of the wrap portions 3 and 4 during the compressor operation.
- the vertical axis shows the amount of wrap deformation, and shows the amount of deformation outward in the circumferential direction.
- the horizontal axis is the extension angle from the center of the wrap. As shown in FIG.
- the positions where the concave portions 8 and the convex portions 9 are provided are, for example, the amount of deformation of the extension on the tooth tip side of the wrap portion 4 of the fixed scroll 2 and the tooth base side of the wrap portion 3 of the orbiting scroll 1 opposed thereto. It is calculated
- the deformation amount of the outer line on the tooth tip side of the wrap portion 4 of the fixed scroll 2 is compared with the deformation amount of the inner line on the tooth root side of the wrap portion 3 of the orbiting scroll 1 that is opposite to the deformation amount.
- the position where the convex portion and the concave portion are provided is specified.
- the deformation amount of the inner side and the outer line of the lap portion 4 of the fixed scroll 2 is compared with the deformation amount of the inner side and the outer line of the tooth tip side of the wrap portion 3 of the orbiting scroll 1 relative to the wrap portion 4;
- the position where the convex part and the concave part are provided can be specified.
- the size of the convex portion and the concave portion may be adjusted according to the deformation amount. For example, in a region where the difference between the deformation amount of the tooth tip side inner line of the wrap portion 4 of the fixed scroll 2 and the deformation amount of the tooth base side outer line of the wrap portion 3 of the orbiting scroll 1 shown in FIG. A convex part is formed large.
- the fixed scroll 2 is provided with convex portions and concave portions.
- the orbiting scroll 2 may be provided with convex portions and concave portions based on the deformation shown in FIG. You may provide in both.
- the sizes of the concave portion 8 and the convex portion 9 in the present embodiment are calculated in advance based on the amount of thermal deformation during operation, and are formed by adjusting the amount of cutting during cutting as necessary. When the concave portion 8 is formed, the amount of shaving is increased, and when the convex portion 9 is formed, the concave portion 8 and the convex portion 9 are formed by reducing the amount of shaving.
- the concave portion 8 and the convex portion 9 may be formed by punching by adjusting the mold of the material of the lap portions 3 and 4 in advance without using the cutting process.
- the concave portion 8 and the convex portion 9 may be configured by adjusting the film thickness of the coating agent. .
- the concave or convex portion is a portion processed in a direction in which the tooth thickness of the wrap portion becomes relatively small with respect to the wrap portion of another region (radially outward if it is an inner line, radially inner if it is an outer line).
- a portion processed as a concave portion and processed in a direction in which the tooth thickness is relatively increased (inner diameter is radially inward and outer wire is radially outer) can be considered as a convex portion.
- FIG. 10 shows the shape of the lap portion in the present embodiment.
- the concave portion 8 is provided on the side surface of the lap portion 4 where the lap gap is reduced by deformation of the lap to prevent the lap portion 3 and the lap portion 4 from contacting each other.
- the convex part 9a is provided in the side surface of the lap
- FIG. 11 shows the shape of the lap portion in the present embodiment. Similar to the first and second embodiments, the concave portion 8a is provided on the side surface of the lap portion 4 where the lap gap is reduced by deformation of the lap. The range was only a part on the tooth tip side in the direction (tooth height direction) from the tooth root (g) of the wrap portion 4 toward the tooth tip (g ′).
- the convex portion 9b is formed only on the inner tooth tip (i ′) side of the i-i ′ portion. As a result, even when the lap gap between i and j ′ on the tooth base side is small or unchanged, it is possible to appropriately prevent the lap gap on the tooth tip (i ′) side from widening.
- the concave portion 8b is provided on the side surface of the lap portion 4 where the lap gap is reduced by deformation of the lap. Similar to the third embodiment, a range in which the concave portion 8b and the convex portion 9 are provided is a part in the tooth height direction. However, the shape is not limited to a straight line but is also a curved line. The shape of this curve is determined by the lap gap between the side surfaces h-h ′ of the opposite lap portions 3. Therefore, if necessary, the recess 8b may be provided not only in a part but also in all of g-g '.
- a more optimal wrap gap can be formed by making the concave portion 8b in a curved shape.
- the size and shape of the convex portion 9c are determined by the lap gap between j-j 'on the side surfaces of the opposing wrap portion 3. Accordingly, the size and shape of the concave portion 8b between g-g 'and the size and shape of the convex portion 9c between i-i' do not necessarily match. Further, by forming the convex portion 8b in a curved shape, it is possible to suppress the enlargement of the lap gap as much as possible.
- the concave portions 8b and 8c and the convex portion 9c are curved for the sake of explanation, but of course, the shape may be prioritized and only a straight line may be used.
- Example 5 will be described with reference to FIG.
- FIG. 13 shows the shape of the lap portion in the present embodiment.
- the fifth embodiment is characterized in that the concave portion 8 and the convex portion 9 are provided on the side surface of the wrap provided with the labyrinth (protrusion 10).
- the labyrinth is a protrusion 10 provided on the side surface of the wrap.
- the labyrinth (projection 10)
- the lap gap ⁇ can be reduced, and the efficiency as a compressor can be increased. Since the labyrinth (protrusion 10) is provided in order to prevent the wrap portion 3 and the wrap portion 4 from coming into contact with each other, the range protruding from the side surface of the wrap is very small in the circumferential direction.
- the convex portion 9 is provided on the opposite wrap side surface provided with the concave portion 8. Since the convex portion 9 is intended to prevent the lap gap ⁇ from expanding due to the deformation of the lap portion 4, the range protruding from the side surface of the lap is relatively large in the circumferential direction. Further, in the present embodiment, the wrap portion 4 is deformed in a direction away from the side surface of the opposite wrap portion 3 (the wrap gap becomes larger) in a range where the convex portion 9 is provided. Therefore, the possibility of contact with the wrap portion 3 is low.
- the protruding amount of the protrusion 9 is formed larger than that of the protrusion 10. For this reason, the labyrinth protrusion 10 is eliminated in the range where the protrusions 9 are provided. Moreover, since the convex part 9 is provided higher than the front-end
- the projection 10 is provided in the region where the convex portion is not provided.
- the protrusion 10 may be provided with the protrusion 10 as in the shape 2 of FIG. In that case, although the performance as a compressor is deteriorated, even if it comes in contact with the wrap part 3 in the range where the convex part 9 is provided, the reliability is maintained without being damaged. Can be improved.
- the scroll fluid machine is used as an air compressor
- the present invention is not limited to this, and may be applied to other scroll type fluid machines including, for example, a refrigerant compressor that compresses refrigerant, a vacuum pump, and the like.
Abstract
Description
2 固定スクロール
3 旋回スクロールラップ部
4 固定スクロールラップ部
5,5a,5b,5c,5a',5b',5c',5d,5e,5f,5d',5e',5f' 圧縮室
6 吸込ポート
7 吐出ポート
8,8a,8b,8c 凹部
9,9a,9b,9c 凸部
10,10a,10b 突起
Claims (13)
- 渦巻状のラップ部を有する固定スクロールと、該固定スクロールに対向して設けられ、該固定スクロールのラップ部との間で複数の圧縮室を形成するように渦巻状のラップ部が旋回する旋回スクロールと、を備えるスクロール式流体機械において、
前記固定スクロールと前記旋回スクロールのうち少なくとも一方のラップ部は、所定の領域において、一方の側面に凹部が設けられ、他方の側面には凸部が設けられることを特徴とするスクロール式流体機械。 - 前記凹部又は凸部は、前記固定スクロールまたは前記旋回スクロールのラップ部の高さ方向の一部にのみ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式流体機械。
- 前記固定スクロールと前記旋回スクロールのうち少なくとも一方のラップ部は、所定の領域において、一方の側面に歯底から歯先の間に凹部及び凸部が設けられることを特徴とする請求項1に記載のスクロール式流体機械。
- 前記凸部又は前記凹部は、前記ラップ部を削り加工を行うことにより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式流体機械。
- 前記凹部又は前記凸部は、歯底から歯先の間で凹となる量又は凸となる量が変化することを特徴とする請求項1に記載のスクロール式流体機械。
- 前記ラップ部には、前記凸部の設けられた領域を除いて複数の突起が設けられることを特徴とする請求項1に記載のスクロール式流体機械。
- 前記ラップ部には、前記凸部の設けられた領域を含め複数の突起が設けられることを特徴とする請求項1に記載のスクロール式流体機械。
- 前記凸部は、圧縮運転時に前記固定スクロール又は前記旋回スクロールの一方のスクロールのラップ部の外線の外周方向への変形量より、外側に対向する他方のスクロール部のラップ部の内線の外周方向への変形量が大きくなる領域に設けられることを特徴とする請求項1に記載のスクロール式流体機械。
- 前記凸部及び凹部は、ラップ部の複数の領域に設けられることを特徴とする請求項1に記載のスクロール式流体機械。
- 前記凸部は、前記固定スクロールと前記旋回スクロールとの運転時の変形量に応じて、領域により異なる大きさで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式流体機械。
- 渦巻状のラップ部を有する固定スクロールと、該固定スクロールに対向して設けられ、該固定スクロールのラップ部との間で複数の圧縮室を形成するように渦巻状のラップ部が旋回する旋回スクロールと、を備えるスクロール式流体機械において、
前記固定スクロールと前記旋回スクロールのうち少なくとも一方のラップ部は、所定の領域において、一方の側面に凹部が設けられ、当該領域のラップの他方の側面に対向するスクロールのラップ部の側面には凸部が設けられることを特徴とするスクロール式流体機械。 - 前記凸部及び前記凹部は、前記固定スクロール及び前記旋回スクロールの内線又は外線の一方の側にのみ設けられることを特徴とする請求項11に記載のスクロール式流体機械。
- 前記凸部は、圧縮運転時に前記固定スクロール又は前記旋回スクロールの一方のスクロールのラップ部の外線の外周方向への変形量より、外側に対向する他方のスクロール部のラップ部の内線の外周方向への変形量が大きくなる領域に設けられることを特徴とする請求項11に記載のスクロール式流体機械。
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KR1020207028959A KR102254871B1 (ko) | 2015-06-03 | 2015-06-03 | 스크롤식 유체 기계 |
EP15894189.8A EP3306096B1 (en) | 2015-06-03 | 2015-06-03 | Scroll-type fluid machine |
PCT/JP2015/065974 WO2016194156A1 (ja) | 2015-06-03 | 2015-06-03 | スクロール式流体機械 |
US15/578,093 US11118583B2 (en) | 2015-06-03 | 2015-06-03 | Scroll fluid machine with concave and convex portions in the spiral laps |
KR1020177037189A KR20180012306A (ko) | 2015-06-03 | 2015-06-03 | 스크롤식 유체 기계 |
JP2017521409A JP6531173B2 (ja) | 2015-06-03 | 2015-06-03 | スクロール式流体機械 |
CN201580081251.XA CN107683372B (zh) | 2015-06-03 | 2015-06-03 | 涡旋式流体机械 |
CN202010709199.0A CN111828314B (zh) | 2015-06-03 | 2015-06-03 | 涡旋式流体机械 |
KR1020197015272A KR102194689B1 (ko) | 2015-06-03 | 2015-06-03 | 스크롤식 유체 기계 |
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US20180202441A1 (en) | 2018-07-19 |
CN111828314B (zh) | 2022-09-27 |
KR20190061103A (ko) | 2019-06-04 |
CN111828314A (zh) | 2020-10-27 |
EP3306096A4 (en) | 2018-10-31 |
KR102254871B1 (ko) | 2021-05-21 |
KR20200121371A (ko) | 2020-10-23 |
JPWO2016194156A1 (ja) | 2018-03-22 |
EP3306096A1 (en) | 2018-04-11 |
JP6531173B2 (ja) | 2019-06-12 |
CN107683372A (zh) | 2018-02-09 |
KR20180012306A (ko) | 2018-02-05 |
KR102194689B1 (ko) | 2020-12-23 |
EP3306096B1 (en) | 2024-03-13 |
CN107683372B (zh) | 2020-08-21 |
US11118583B2 (en) | 2021-09-14 |
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