US20060198746A1 - Scroll fluid machine - Google Patents
Scroll fluid machine Download PDFInfo
- Publication number
- US20060198746A1 US20060198746A1 US11/307,082 US30708206A US2006198746A1 US 20060198746 A1 US20060198746 A1 US 20060198746A1 US 30708206 A US30708206 A US 30708206A US 2006198746 A1 US2006198746 A1 US 2006198746A1
- Authority
- US
- United States
- Prior art keywords
- volume
- variable chamber
- scroll
- stationary
- orbiting
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- 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
- 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
-
- 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
-
- 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
Definitions
- the present invention relates to a scroll fluid machine by which a high volume of gases are produced under relatively low pressure.
- volume of a sealed chamber is gradually reduced from the beginning end of a wrap winding at the circumference to the terminating end near the center, so that a gas sucked from the circumference is compressed and discharged near the center or a gas sucked from the center is decompressed and discharged from the circumference.
- Such a known scroll fluid machine is used for middle or high pressure to make relatively high-pressure compressed gas or achieve effective decompressing.
- Expanded spaces between the wraps make a radius of a revolving orbiting scroll larger to increase an external diameter of the orbiting scroll. So it is necessary for the heavy orbiting scroll to revolve with a larger diameter. Load adapted to a support for an orbiting shaft of the orbiting scroll increases to make it necessary to provide a high load-resistant bearing thereby resulting in increase in weight and size requiring high manufacturing cost.
- the wraps must be made as close as possible to the center of the orbiting scroll not to increase a diameter of the orbiting scroll. But it involves high discharge pressure to make it impossible to obtain a desired low-pressure compressed gas.
- FIG. 1 is a vertical sectional view of one embodiment of a scroll fluid machine according to the present invention
- FIG. 2 is a vertical sectional view taken along the line II-II in FIG. 1 ;
- FIG. 3 is a vertical sectional view similar to FIG. 2 and showing that engagement of wraps varies.
- FIG. 4 is a vertical sectional view similar to FIG. 2 and showing another embodiment of the present invention.
- FIG. 1 is a vertical sectional side view of a scroll compressor as one embodiment of the present invention.
- this invention there are outer and inner volume-variable chambers defined by stationary and orbiting wraps.
- FIG. 1 The scroll compressor in FIG. 1 is basically similar to a known device and will be simply described.
- left and rights sides are deemed front and rear respectively.
- an outer intake port 3 a is formed on the circumference of a stationary end plate 2 of a stationary scroll 1 , and an inner discharge port 4 b is formed at the center. Between them, an outer discharge port 4 a and an inner intake port 3 b are formed.
- a spiral stationary wrap 5 is provided on the rear surface of the stationary end plate 2 .
- On the front surface there are a plurality of horizontal equal-height gently-corrugated cooling fins 6 equally spaced.
- An orbiting scroll 7 behind the stationary scroll 1 has a spiral orbiting wrap 9 on the front surface of a circular orbiting end plate 3 or opposing surface to the stationary scroll 1 , and a plurality of horizontal equal-height corrugated cooling fins 10 equally spaced on the rear surface.
- a bearing plate 11 is mounted on the rear surface of the orbiting scroll 7 .
- a tubular boss 15 pivotally supporting an eccentric axial portion 13 of a driving shaft 12 via a bearing 14 .
- crank-pin-type self-rotation preventing device 16 At three points of the circumference on the rear surface of the bearing plate 11 , there is a known crank-pin-type self-rotation preventing device 16 , so that the orbiting scroll 7 is eccentrically revolved around the driving shaft 12 with respect to a housing 17 .
- a cover plate 18 is fixed to the front surface of the stationary scroll 1 with a screw 19 .
- the orbiting scroll 7 is fixed to the bearing plate 11 with a screw 20 .
- a rear portion 21 of the stationary scroll 1 is fixed to the housing 17 with a bolt 22 and a nut 23 .
- Engagement grooves 24 , 25 are formed on the tip ends of the stationary and orbiting wraps 5 , 9 respectively. Sealing members “S” are fitted in the engagement grooves 24 , 25 in sliding contact between the orbiting end plate 8 of the orbiting scroll 7 and the stationary end plate 4 of the stationary scroll 1 .
- the stationary wrap 5 is separated to an outer volume-variable chamber stationary wrap 5 a communicating with the outer intake port 3 a and an inner volume-variable chamber stationary wrap 5 b communicating with the inner discharge port 4 b
- the orbiting wrap 9 is separated to an outer volume-variable chamber orbiting wrap 9 a and an inner volume-variable chamber orbiting wrap 9 b.
- a gap between the outer volume-variable chamber stationary wrap 5 a and the outer volume-variable chamber orbiting wrap 9 a is large, and a gap between the inner volume-variable chamber stationary wrap 5 b and the inner volume-variable chamber orbiting wrap 9 b is somewhat small.
- a volume ratio of an outer beginning-end volume-variable chamber “B” communicating with the outer discharger port 4 a to an outer terminating-end volume-variable chamber “A” communicating with the outer intake port 3 a is substantially the same as a volume ratio of an inner terminating-end volume-variable chamber “D” communicating with the inner discharge port 4 b to an inner beginning-end volume-variable chamber “C” communicating with the inner intake port 3 b.
- FIG. 4 is a vertical sectional side view of a scroll decompressor according to the present invention and similar to FIG. 2 .
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
A scroll fluid machine comprises a stationary scroll fixed to a housing and an orbiting scroll that turns with a driving shaft. The stationary scroll comprises a stationary end plate having inner and outer stationary wraps and the orbiting scroll comprises an orbiting end plate having inner and outer orbiting wraps. Rotation of the orbiting scroll allows the inner and outer stationary wraps to engage with the inner and outer orbiting wraps respectively to form inner and outer volume-variable chambers. The two chambers have substantially the same compression ratio, so that substantially-equal low pressure gases are produced.
Description
- The present invention relates to a scroll fluid machine by which a high volume of gases are produced under relatively low pressure.
- In a scroll fluid machine including a scroll compressor and a scroll decompressor, volume of a sealed chamber is gradually reduced from the beginning end of a wrap winding at the circumference to the terminating end near the center, so that a gas sucked from the circumference is compressed and discharged near the center or a gas sucked from the center is decompressed and discharged from the circumference.
- Such a known scroll fluid machine is used for middle or high pressure to make relatively high-pressure compressed gas or achieve effective decompressing.
- However, in the scroll fluid machine, to transport powders such as flour, it is impossible to obtain a high volume of compressed gases under low pressure such as about 0.2 to 0.3 MPa. To obtain a high volume of compressed gases under such low pressure, it is necessary to expand spaces between wraps and to reduce the number of windings.
- Expanded spaces between the wraps make a radius of a revolving orbiting scroll larger to increase an external diameter of the orbiting scroll. So it is necessary for the heavy orbiting scroll to revolve with a larger diameter. Load adapted to a support for an orbiting shaft of the orbiting scroll increases to make it necessary to provide a high load-resistant bearing thereby resulting in increase in weight and size requiring high manufacturing cost.
- To avoid such problems, the wraps must be made as close as possible to the center of the orbiting scroll not to increase a diameter of the orbiting scroll. But it involves high discharge pressure to make it impossible to obtain a desired low-pressure compressed gas.
- Thus, conventionally, in a scroll compressor for low pressure, an orbiting wrap is partially removed near the center of an orbiting scroll and large-spaced wraps are provided only in parts remote from the center. However, the center of the orbiting scroll does not play a role of output, which is inefficient and uneconomical.
- In view of the disadvantages in the prior art, it is an object of the present invention to provide a scroll fluid machine in which a space between wraps is the same as a known middle or high pressure machine, wraps—being provided to produce a low-pressure compressed gas almost equal to a compressed gas in the circumference to make it possible to obtain a high volume of low-pressure gases without change in the whole size or the number of revolutions of the scroll.
- The features and advantages of the invention will become more apparent from the following description with respect to embodiments as shown in accompanying drawings wherein:
-
FIG. 1 is a vertical sectional view of one embodiment of a scroll fluid machine according to the present invention; -
FIG. 2 is a vertical sectional view taken along the line II-II inFIG. 1 ; -
FIG. 3 is a vertical sectional view similar toFIG. 2 and showing that engagement of wraps varies; and -
FIG. 4 is a vertical sectional view similar toFIG. 2 and showing another embodiment of the present invention. -
FIG. 1 is a vertical sectional side view of a scroll compressor as one embodiment of the present invention. In this invention, there are outer and inner volume-variable chambers defined by stationary and orbiting wraps. - The scroll compressor in
FIG. 1 is basically similar to a known device and will be simply described. InFIG. 1 , left and rights sides are deemed front and rear respectively. - In the front or left side in
FIG. 1 , anouter intake port 3 a is formed on the circumference of astationary end plate 2 of astationary scroll 1, and aninner discharge port 4 b is formed at the center. Between them, anouter discharge port 4 a and aninner intake port 3 b are formed. - A spiral
stationary wrap 5 is provided on the rear surface of thestationary end plate 2. On the front surface, there are a plurality of horizontal equal-height gently-corrugated cooling fins 6 equally spaced. Anorbiting scroll 7 behind thestationary scroll 1 has a spiral orbitingwrap 9 on the front surface of a circular orbiting end plate 3 or opposing surface to thestationary scroll 1, and a plurality of horizontal equal-height corrugated cooling fins 10 equally spaced on the rear surface. - On the rear surface of the orbiting
scroll 7, abearing plate 11 is mounted. At the center of the rear surface of thebearing plate 11, there is atubular boss 15 pivotally supporting an eccentricaxial portion 13 of adriving shaft 12 via abearing 14. - At three points of the circumference on the rear surface of the
bearing plate 11, there is a known crank-pin-type self-rotation preventing device 16, so that theorbiting scroll 7 is eccentrically revolved around the drivingshaft 12 with respect to ahousing 17. - A
cover plate 18 is fixed to the front surface of thestationary scroll 1 with ascrew 19. The orbitingscroll 7 is fixed to thebearing plate 11 with ascrew 20. Arear portion 21 of thestationary scroll 1 is fixed to thehousing 17 with abolt 22 and anut 23. - Engagement grooves 24,25 are formed on the tip ends of the stationary and orbiting
wraps end plate 8 of the orbitingscroll 7 and thestationary end plate 4 of thestationary scroll 1. - As shown in
FIGS. 2 and 3 sectioned along the line II-II inFIG. 1 , thestationary wrap 5 is separated to an outer volume-variable chamberstationary wrap 5 a communicating with theouter intake port 3 a and an inner volume-variable chamberstationary wrap 5 b communicating with theinner discharge port 4 b, while the orbitingwrap 9 is separated to an outer volume-variablechamber orbiting wrap 9 a and an inner volume-variablechamber orbiting wrap 9 b. - A gap between the outer volume-variable chamber
stationary wrap 5 a and the outer volume-variablechamber orbiting wrap 9 a is large, and a gap between the inner volume-variable chamberstationary wrap 5 b and the inner volume-variablechamber orbiting wrap 9 b is somewhat small. - A volume ratio of an outer beginning-end volume-variable chamber “B” communicating with the
outer discharger port 4 a to an outer terminating-end volume-variable chamber “A” communicating with theouter intake port 3 a is substantially the same as a volume ratio of an inner terminating-end volume-variable chamber “D” communicating with theinner discharge port 4 b to an inner beginning-end volume-variable chamber “C” communicating with theinner intake port 3 b. - Accordingly, compressed gases having almost equal pressure are produced in the outer and inner volume-variable chambers, so that a large quantity of low-pressure compressed gas is obtained compared with a conventional device in which a central wrap is removed in a scroll.
-
FIG. 4 is a vertical sectional side view of a scroll decompressor according to the present invention and similar toFIG. 2 . - In
FIG. 4 , theinner discharge port 4 b inFIG. 2 is changed to aninner intake port 3 b and theouter discharge port 4 a is changed to anouter intake port 3 a. Similarly, theinner intake port 3 b is changed to aninner discharge port 4 b, and theouter intake port 3 a is changed to anouter discharge port 4 a. The others are the same as those in FIGS. 1 to 3. InFIG. 4 , a gas sucked from theinner intake port 3 b is decompressed and discharged from theouter discharge port 4 a. - The foregoing merely relates to embodiments of the present invention. Various changes and modifications may be made by a person skilled in the art without departing from the scope of claims wherein.
Claims (8)
1. A scroll fluid machine comprising:
a housing;
a driving shaft having an eccentric axial portion;
a stationary scroll fixed to and in the housing and having an inner stationary wrap and an outer stationary wrap on an stationary end plate; and
an orbiting scroll having an inner orbiting wrap and an outer orbiting wrap on an orbiting end plate, the orbiting scroll being revolved with the eccentric axial portion of the driving shaft with respect to the stationary scroll to allow the inner stationary wrap to engage with the inner orbiting wrap to form an inner volume-variable chamber within the inner stationary wrap and to allow the outer stationary wrap to engage with the outer orbiting wrap to form an outer volume-variable chamber between the inner and outer stationary wraps, the stationary end plate having an outer intake port at a circumference and an outer discharge port radially far from the circumference within the outer volume variable chamber and having an inner intake port radially far from a center and an inner discharge port at the center in the inner volume-variable chamber, the inner volume-variable chamber having substantially the same compression ratio as that of the outer volume-variable chamber, a gas introduced from the outer intake port being compressed in the outer volume-variable chamber with revolution of the orbiting scroll and discharged from the outer discharge port, a gas introduced from the inner intake port being compressed in the inner volume-variable chamber with the revolution of the orbiting scroll and discharged from the inner discharge port under substantially the same low-pressure as what is discharged from the outer discharge port.
2. A scroll fluid machine as claimed in claim 1 wherein the outer volume-variable chamber comprises an outer beginning-end volume-variable chamber communicating with the outer intake port and an outer terminating-end volume-variable chamber communicating with the outer discharger port, the inner volume-variable chamber comprising an inner beginning-end volume-variable chamber communicating with the inner intake port and an inner terminating-end volume-variable chamber communicating with the inner discharger port, a volume ratio of the outer terminating-end volume-variable chamber to the outer beginning-end volume-variable chamber being substantially equal to that of the inner terminating-end volume variable chamber to the inner beginning-end volume-variable chamber.
3. A scroll fluid machine as claimed in claim I wherein the outer discharge port of the outer volume-variable chamber is connected to the inner intake port of the inner volume-variable chamber.
4. A scroll fluid machine as claimed in claim 1 wherein the scroll fluid machine is a scroll compressor.
5. A scroll fluid machine comprising:
a housing;
a driving shaft having an eccentric axial portion;
a stationary scroll fixed to and in the housing and having an inner stationary wrap and an outer stationary wrap on an stationary end plate; and
an orbiting scroll having an inner orbiting wrap and an outer orbiting wrap on an orbiting end plate, the orbiting scroll being revolved with the eccentric axial portion of the driving shaft with respect to the stationary scroll to allow the inner stationary wrap to engage with the inner orbiting wrap to form an inner volume-variable chamber within the inner stationary wrap and to allow the outer stationary wrap to engage with the outer orbiting wrap to form an outer volume-variable chamber between the inner and outer stationary wraps, the stationary end plate having an outer intake port radially inward far from a circumference and an outer discharge port at the circumference within the outer volume variable chamber and having an inner intake port at the center and an inner discharge port radially far from a center in the inner volume-variable chamber, the inner volume-variable chamber having substantially the same compression ratio as that of the outer volume-variable chamber, a gas introduced from the inner intake port being decompressed in the outer volume-variable chamber with revolution of the orbiting scroll and discharged from the outer discharge port, a gas introduced from the outer intake port being decompressed in the inner volume-variable chamber with the revolution of the orbiting scroll and discharged from the outer discharge port under substantially the same low-pressure as what is discharged from the inner discharge port.
6. A scroll fluid machine as claimed in claim 5 wherein the outer volume-variable chamber comprises an outer beginning-end volume-variable chamber communicating with the outer intake port and an outer terminating-end volume-variable chamber communicating with the outer discharge port, the inner volume-variable chamber comprising an inner beginning-end volume-variable chamber communicating with the inner intake port and an inner terminating-end volume-variable chamber communicating with the inner discharger port, a volume ratio of the outer terminating-end volume-variable chamber to the outer beginning-end volume-variable chamber being substantially equal to that of the inner terminating-end volume variable chamber to the inner beginning-end volume-variable chamber.
7. A scroll fluid machine as claimed in claim 5 wherein the inner discharge port of the inner volume-variable chamber is connected to the outer intake port of the outer volume-variable chamber.
8. A scroll fluid machine as claimed in claim 5 wherein the scroll fluid machine is a scroll decompressor.
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2005-25766 | 2005-02-02 | ||
JP2005025766 | 2005-02-02 | ||
JP2006001669A JP2006242173A (en) | 2005-02-02 | 2006-01-06 | Low pressure large capacity scroll fluid machinery |
JP2006-1669 | 2006-01-06 |
Publications (1)
Publication Number | Publication Date |
---|---|
US20060198746A1 true US20060198746A1 (en) | 2006-09-07 |
Family
ID=36143180
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US11/307,082 Abandoned US20060198746A1 (en) | 2005-02-02 | 2006-01-23 | Scroll fluid machine |
Country Status (4)
Country | Link |
---|---|
US (1) | US20060198746A1 (en) |
EP (1) | EP1696127A2 (en) |
JP (1) | JP2006242173A (en) |
KR (1) | KR100732841B1 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR100732841B1 (en) | 2005-02-02 | 2007-06-27 | 아네스토 이와타 가부시키가이샤 | Scroll fluid machine |
KR101141831B1 (en) | 2006-02-09 | 2012-05-07 | 알테어 세미콘덕터 엘티디. | Dual-function wireless data terminal |
Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4157234A (en) * | 1977-08-15 | 1979-06-05 | Ingersoll-Rand Company | Scroll-type two stage positive fluid displacement apparatus |
US6050792A (en) * | 1999-01-11 | 2000-04-18 | Air-Squared, Inc. | Multi-stage scroll compressor |
US6139287A (en) * | 1995-12-19 | 2000-10-31 | Daikin Industries, Ltd. | Scroll type fluid machine |
US20020057976A1 (en) * | 2000-10-20 | 2002-05-16 | Hideyuki Kimura | Scroll fluid machine |
US20030059327A1 (en) * | 2001-09-21 | 2003-03-27 | Anest Iwata Corporation | Scroll-type fluid machine |
US20030161747A1 (en) * | 2001-09-27 | 2003-08-28 | Tohru Satoh | Scroll-type fluid machine |
US6659743B2 (en) * | 2001-03-07 | 2003-12-09 | Anest Iwata Corporation | Scroll fluid machine having multistage compressing part |
US20060099096A1 (en) * | 2004-11-08 | 2006-05-11 | Shaffer Robert W | Scroll pump system |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR100195166B1 (en) * | 1996-12-31 | 1999-06-15 | 신영주 | Scroll compressor |
JP4044311B2 (en) | 2001-09-27 | 2008-02-06 | アネスト岩田株式会社 | Air-cooled scroll fluid machine |
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
Patent Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4157234A (en) * | 1977-08-15 | 1979-06-05 | Ingersoll-Rand Company | Scroll-type two stage positive fluid displacement apparatus |
US6139287A (en) * | 1995-12-19 | 2000-10-31 | Daikin Industries, Ltd. | Scroll type fluid machine |
US6050792A (en) * | 1999-01-11 | 2000-04-18 | Air-Squared, Inc. | Multi-stage scroll compressor |
US20020057976A1 (en) * | 2000-10-20 | 2002-05-16 | Hideyuki Kimura | Scroll fluid machine |
US6659743B2 (en) * | 2001-03-07 | 2003-12-09 | Anest Iwata Corporation | Scroll fluid machine having multistage compressing part |
US20030059327A1 (en) * | 2001-09-21 | 2003-03-27 | Anest Iwata Corporation | Scroll-type fluid machine |
US20030161747A1 (en) * | 2001-09-27 | 2003-08-28 | Tohru Satoh | Scroll-type fluid machine |
US20060099096A1 (en) * | 2004-11-08 | 2006-05-11 | Shaffer Robert W | Scroll pump system |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR100732841B1 (en) | 2005-02-02 | 2007-06-27 | 아네스토 이와타 가부시키가이샤 | Scroll fluid machine |
KR101141831B1 (en) | 2006-02-09 | 2012-05-07 | 알테어 세미콘덕터 엘티디. | Dual-function wireless data terminal |
Also Published As
Publication number | Publication date |
---|---|
KR100732841B1 (en) | 2007-06-27 |
JP2006242173A (en) | 2006-09-14 |
EP1696127A2 (en) | 2006-08-30 |
KR20060088824A (en) | 2006-08-07 |
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Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: ANEST IWATA CORPORATION, JAPAN Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:FUJIOKA, TAMOTSU;UNAMI, ATSUSHI;REEL/FRAME:017049/0576 Effective date: 20060116 |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |