CA2005935A1 - Scroll compressor with axial compliancy - Google Patents
Scroll compressor with axial compliancyInfo
- Publication number
- CA2005935A1 CA2005935A1 CA002005935A CA2005935A CA2005935A1 CA 2005935 A1 CA2005935 A1 CA 2005935A1 CA 002005935 A CA002005935 A CA 002005935A CA 2005935 A CA2005935 A CA 2005935A CA 2005935 A1 CA2005935 A1 CA 2005935A1
- Authority
- CA
- Canada
- Prior art keywords
- crankcase
- scroll
- orbiting scroll
- forming
- 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
Links
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
- F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
- F04C27/005—Axial 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
- 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
- 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
- F04C23/008—Hermetic pumps
Abstract
ABSTRACT OF THE DISCLOSURE
Axial compliancy is achieved in a scroll compressor by providing a fluid pressure bias to the back of the orbiting scroll. The fluid pressure bias is supplied by one or more pockets configured to combine the efficient use of the available area with ease of manufacture.
Axial compliancy is achieved in a scroll compressor by providing a fluid pressure bias to the back of the orbiting scroll. The fluid pressure bias is supplied by one or more pockets configured to combine the efficient use of the available area with ease of manufacture.
Description
xo~ s SCROLL COMPRESSOR WITH AXIAL COMPLIANCY
Backqround of The Invention During the compression process in a scroll compressor the pressure of the gas being compressed acts against the scroll elements tending to separate them both radially and axially.
To achieve axial compliancy and axial sealing between the scroll elements, ~ sealed, high pressure chamber can be created between the back of the orbiting scroll and the crankcase. The chamber should not have any radial or axial interference with the Oldham coupling ring, the orbiting scroll slots, the crankcase slots and the internal bore.
Such a sealed high pressure pocket can be created by using two annular O-ring grooves such that the O-rings are compressed against the back of the orbiting scroll. The major disadvantage of this design is the size limitation of the sealed high pressure gas pocket. One way of increasing the area is to enlarge the diameter of the Oldham coupling ring which results in a wider crankcase and thus a larger compressor shell diameter. Generally, the compressor sheil diameter is dictated by the motor frame necessary to produce the re~uired output and anything larger is undesirable.
Summary Of The Invention The ideal configuration provides a pocket~s) wlth the maximum area. The available area for the pocket(s) surrounds the bearing and the boss of the orbiting scroll and has an outer boundary of a generally figure eight shape due to the coaction of the Oldham coupling riny and slots~
Ob~iously, the available area is not of a simple configuration. Using the waist portion of the figure eight shape as the axis of symmetry, the available area can be generally defined by: (1) a pair of kidney shaped pockets;
Backqround of The Invention During the compression process in a scroll compressor the pressure of the gas being compressed acts against the scroll elements tending to separate them both radially and axially.
To achieve axial compliancy and axial sealing between the scroll elements, ~ sealed, high pressure chamber can be created between the back of the orbiting scroll and the crankcase. The chamber should not have any radial or axial interference with the Oldham coupling ring, the orbiting scroll slots, the crankcase slots and the internal bore.
Such a sealed high pressure pocket can be created by using two annular O-ring grooves such that the O-rings are compressed against the back of the orbiting scroll. The major disadvantage of this design is the size limitation of the sealed high pressure gas pocket. One way of increasing the area is to enlarge the diameter of the Oldham coupling ring which results in a wider crankcase and thus a larger compressor shell diameter. Generally, the compressor sheil diameter is dictated by the motor frame necessary to produce the re~uired output and anything larger is undesirable.
Summary Of The Invention The ideal configuration provides a pocket~s) wlth the maximum area. The available area for the pocket(s) surrounds the bearing and the boss of the orbiting scroll and has an outer boundary of a generally figure eight shape due to the coaction of the Oldham coupling riny and slots~
Ob~iously, the available area is not of a simple configuration. Using the waist portion of the figure eight shape as the axis of symmetry, the available area can be generally defined by: (1) a pair of kidney shaped pockets;
(2) a pair of crescent shaped pockets defined by two symmetrical circular cuts; or (3) a pair of symmetrical circular cuts and a central circular cut are made such that 21)05~35 their combined outer periphery is of a figure eight shape with a central circular periphery to define an annular pocket.
It is an object of this invention to provide axial compliancy using the orbiting scroll without increasing bearing loading and without increasing the orbiting scroll outer diameter envelope.
It is another object of this invention to locate the pocket(s) in a housing which overhangs the bearing.
It is a further object of this invention to locate the bearing support close to the gas compression force by overhanging the pocket(s) and thereby minimizing the tipping moment.
It is another object of this invention to lift the orbiting scroll off the crankcase so that it rides on the seals and thereby reduces frictional forces due to the reduced loading.
It is an additional object of this invention to permit the Oldham coupling groove to be located close to the center to thereby reduce the envelope of the compressor. These objects, and others as will become apparent hereinafter, are accomplished by the present invention.
Basically, axial compliancy is achieved in an orbiting scroll without increasing the bearing loading or the outer diameter envelope of the orbiting scroll by locating one or two *luid pockets in the crankcase facing the back of the orbiting scroll and shaped to efficiently use the available space.
2~5.9~
Brief Description Of The Drawings For a fuller understanding of the present invention, reference should now be made to the following detailed description thereof taken in conjunction with the accompanying drawings wherein:
Figure 1 is a vertical sectional view taken along line 1-1 of Figure 3 of a portion of a scroll compressor which is in the unenergized ~tate employing the present invention;
Figure 2 is a vertical sectional view taken along line 2-2 of Figure 3 of a portion of a scroll compressor with the axial compliance mechanism energized;
Figure 3 is a horizontal sectional view taken along 3-3 of Figure l;
Figure 4 i.s a view corresponding to Figure 3 but showing a second embodiment of the invention;
Figure 5 is a view corresponding to Figure 3 but showing a third embodiment of the invention; and Figure 6 is a partial sectional view taken along line 6-6 of Figure 3.
Description Of The Preferred Embodiment In the Figures, the numeral 10 generally designates a low side scroll compressor. Muffler/separator plate 14 overlies fixed scroll 20 and defines a high pressure chamber 13 within shell 12. Crankcase 40 overhangs crankshaft 60 and is bolted or otherwise suitably secured to fixed scroll 20.
Orbiting scroll 30 has a wrap 31 which is in operati~e engagement with wrap 21 of fixed scroll 20 while one side of plate portion 32 engages fixed scroll 20 and the other side coacts with Oldham ring 64, as is conventional.
~)OS935 Additionally, the other side of plate portion 32 also is in sealing engagement with seals 66 and 68 which are located in kidney shaped grooves 42 and 43 which surround pock~ts 50 and 5~, respectively. Pockets 50 and 52 are in fluid communication with discharge pressure in high pressure chamber 13 via a flow path which is best illustrated in Figures 1, 3 and 6 and which serially includes passage 14-1 in muffler separator plate 14, bores 20-1 and 2 in fixed scroll 20, bore 40-1 and bore 40-2 which branches into bores 40-3 and 40-4 which are in fluid communication with pockets 50 and 52, respectively.
When the scroll compressor 10 is in operation, gas at discharge pressure is delivered from outlet port 16, through muffler/separator plate 14 into high pressure chamber 13 which is connected to the compressor discharge line (not illustrated). The gas at discharge pressure is supplied from chamber 13 to pockets 50 and 52 via passage 14-1 and bores 20-1 and 2 and 40-1 to 4. The high pressure fluid in pockets 50 and 52 acts on the plate 32 of the orbiting scroll 30 lifting orbiting scroll 30 off of the crankcase 40 so that orbiting scroll 30 rides on seals 66 and 68 as shown in Figure 2. A small net ~orce acting on the fixed scroll ~0 tends to keep fixed scroll 20 and orbiting scroll 30 in axial contact in opposition to the separating forces produced in compressing gas due to the coaction of the fixed and orbiting scrolls while greatly reducing friction forces.
In machining the embodiment of Figures 1-3, two kidney shaped grooves 42 and 43 are machined or otherwise suitably formed in crankcase 40. Circular or other suitably shaped seals 66 and 68 may then be placed in grooves 42 and 43.
In the Figure 4 embodiment, two displaced circular grooves 142 and 143 in the form of interlocked rings are machined or otherwise suitably formed in crankcase 140 resulting in the ~05 i5~
formation of two crescent shaped pockets 150 and 152. The seal 166 is in the shape of two interlocXed rings corresponding to grooves 142 and 143. All of the extreme positions of Oldham ring 164 are illustrated to show the available area for pockets 150 and 152. Fluid pressure would be supplied to pockets 150 and 152 via bores 140-3 and 140-4, respectively, in the same manner as the embodiment of Figures 1-3.
In the Figure 5 embodiment, there are two displaced circular grooves 242 and 243 in the form of interlocking rings, as in the Figure 4 embodiment, plus a third circular groove 244 surrounding opening 241 in crankcase 240. The seal 266 is located only in the outermost portion of grooves 242 and 243 and seal 2Ç8 is in groove 244. As a result, there is a single annular pocket, 250, formed and defined by the area between seals 266 and 268. Because there is only one pocket, the fluid communication with pocket 250 can be by bore 240-3 but otherwise in the same manner as the embodiments of Figures 1-4. The location of bore 240-3 can be changed so that it is a vertical path rather than a slanted path in order to simplify machining.
Although preferred embodiments of the present invention have been illustrated and described, other changes will occur to those skilled in the art. For example, although discharge pressure is described as supplied to the pockets, intermediat~ pressure can be used. It is therefore intended that the scope of the present invention is to be limited only by the scope of the appended claims.
It is an object of this invention to provide axial compliancy using the orbiting scroll without increasing bearing loading and without increasing the orbiting scroll outer diameter envelope.
It is another object of this invention to locate the pocket(s) in a housing which overhangs the bearing.
It is a further object of this invention to locate the bearing support close to the gas compression force by overhanging the pocket(s) and thereby minimizing the tipping moment.
It is another object of this invention to lift the orbiting scroll off the crankcase so that it rides on the seals and thereby reduces frictional forces due to the reduced loading.
It is an additional object of this invention to permit the Oldham coupling groove to be located close to the center to thereby reduce the envelope of the compressor. These objects, and others as will become apparent hereinafter, are accomplished by the present invention.
Basically, axial compliancy is achieved in an orbiting scroll without increasing the bearing loading or the outer diameter envelope of the orbiting scroll by locating one or two *luid pockets in the crankcase facing the back of the orbiting scroll and shaped to efficiently use the available space.
2~5.9~
Brief Description Of The Drawings For a fuller understanding of the present invention, reference should now be made to the following detailed description thereof taken in conjunction with the accompanying drawings wherein:
Figure 1 is a vertical sectional view taken along line 1-1 of Figure 3 of a portion of a scroll compressor which is in the unenergized ~tate employing the present invention;
Figure 2 is a vertical sectional view taken along line 2-2 of Figure 3 of a portion of a scroll compressor with the axial compliance mechanism energized;
Figure 3 is a horizontal sectional view taken along 3-3 of Figure l;
Figure 4 i.s a view corresponding to Figure 3 but showing a second embodiment of the invention;
Figure 5 is a view corresponding to Figure 3 but showing a third embodiment of the invention; and Figure 6 is a partial sectional view taken along line 6-6 of Figure 3.
Description Of The Preferred Embodiment In the Figures, the numeral 10 generally designates a low side scroll compressor. Muffler/separator plate 14 overlies fixed scroll 20 and defines a high pressure chamber 13 within shell 12. Crankcase 40 overhangs crankshaft 60 and is bolted or otherwise suitably secured to fixed scroll 20.
Orbiting scroll 30 has a wrap 31 which is in operati~e engagement with wrap 21 of fixed scroll 20 while one side of plate portion 32 engages fixed scroll 20 and the other side coacts with Oldham ring 64, as is conventional.
~)OS935 Additionally, the other side of plate portion 32 also is in sealing engagement with seals 66 and 68 which are located in kidney shaped grooves 42 and 43 which surround pock~ts 50 and 5~, respectively. Pockets 50 and 52 are in fluid communication with discharge pressure in high pressure chamber 13 via a flow path which is best illustrated in Figures 1, 3 and 6 and which serially includes passage 14-1 in muffler separator plate 14, bores 20-1 and 2 in fixed scroll 20, bore 40-1 and bore 40-2 which branches into bores 40-3 and 40-4 which are in fluid communication with pockets 50 and 52, respectively.
When the scroll compressor 10 is in operation, gas at discharge pressure is delivered from outlet port 16, through muffler/separator plate 14 into high pressure chamber 13 which is connected to the compressor discharge line (not illustrated). The gas at discharge pressure is supplied from chamber 13 to pockets 50 and 52 via passage 14-1 and bores 20-1 and 2 and 40-1 to 4. The high pressure fluid in pockets 50 and 52 acts on the plate 32 of the orbiting scroll 30 lifting orbiting scroll 30 off of the crankcase 40 so that orbiting scroll 30 rides on seals 66 and 68 as shown in Figure 2. A small net ~orce acting on the fixed scroll ~0 tends to keep fixed scroll 20 and orbiting scroll 30 in axial contact in opposition to the separating forces produced in compressing gas due to the coaction of the fixed and orbiting scrolls while greatly reducing friction forces.
In machining the embodiment of Figures 1-3, two kidney shaped grooves 42 and 43 are machined or otherwise suitably formed in crankcase 40. Circular or other suitably shaped seals 66 and 68 may then be placed in grooves 42 and 43.
In the Figure 4 embodiment, two displaced circular grooves 142 and 143 in the form of interlocked rings are machined or otherwise suitably formed in crankcase 140 resulting in the ~05 i5~
formation of two crescent shaped pockets 150 and 152. The seal 166 is in the shape of two interlocXed rings corresponding to grooves 142 and 143. All of the extreme positions of Oldham ring 164 are illustrated to show the available area for pockets 150 and 152. Fluid pressure would be supplied to pockets 150 and 152 via bores 140-3 and 140-4, respectively, in the same manner as the embodiment of Figures 1-3.
In the Figure 5 embodiment, there are two displaced circular grooves 242 and 243 in the form of interlocking rings, as in the Figure 4 embodiment, plus a third circular groove 244 surrounding opening 241 in crankcase 240. The seal 266 is located only in the outermost portion of grooves 242 and 243 and seal 2Ç8 is in groove 244. As a result, there is a single annular pocket, 250, formed and defined by the area between seals 266 and 268. Because there is only one pocket, the fluid communication with pocket 250 can be by bore 240-3 but otherwise in the same manner as the embodiments of Figures 1-4. The location of bore 240-3 can be changed so that it is a vertical path rather than a slanted path in order to simplify machining.
Although preferred embodiments of the present invention have been illustrated and described, other changes will occur to those skilled in the art. For example, although discharge pressure is described as supplied to the pockets, intermediat~ pressure can be used. It is therefore intended that the scope of the present invention is to be limited only by the scope of the appended claims.
Claims (4)
1. In a hermetic scroll compressor having a fixed scroll, an orbiting scroll, a crankcase and a crankshaft an axial compliance structure characterized by: a generally flat surface with pocket means (50 and 52; 150 and 152; and 250) formed therein and surrounded by grooves (42 and 43; 142 and 143; 242, 243 and 244) with seal means (66 and 68; 166;
266 and 268) therein; fluid pressure supply means (40-3, and 40-4; 140-3 and 140-4; and 240-3) for supplying pressurized fluid to said pocket means for providing an axial force to said orbiting scroll whereby when said orbiting scroll is driven by said crankshaft said orbiting scroll engages said seal means and coacts therewith to isolate the pocket means.
266 and 268) therein; fluid pressure supply means (40-3, and 40-4; 140-3 and 140-4; and 240-3) for supplying pressurized fluid to said pocket means for providing an axial force to said orbiting scroll whereby when said orbiting scroll is driven by said crankshaft said orbiting scroll engages said seal means and coacts therewith to isolate the pocket means.
2. The axial compliance means of claim 1 wherein said pocket means is two pockets (50 and 52) and said pocket means, groove (42, 43) and seal means (66 and 68) are generally kidney shaped and symmetrically located with respect to said crankcase means.
3. In a hermetic scroll compressor having a fixed scroll, an orbiting scroll, and a crankcase, a method for manufacturing axial compliance structure comprising the steps of; forming pocket means (50 and 52; 150 and 152; 250) in a generally flat surface of said crankcase; forming grooves (42 and 43: 142 and 143; 242, 243 and 244) surrounding said pocket means; forming fluid pressure supply means (40-3 and 40-4; 140-3 and 140-4; and 240-3) in the crankcase terminating in the pocket means; locating seal means (66 and 68; 166; 266 and 268) in the grooves; securing the crankcase to the fixed scroll with the orbiting scroll therebetween and in engagement with the seal means to thereby isolate said pocket means.
4. The method of claim 3 wherein the step of forming pocket means includes the forming of two kidney shaped pockets symmetrically located in the crankcase.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US07/299,574 US4938669A (en) | 1989-01-23 | 1989-01-23 | Scroll compressor with axial compliancy |
| US299,574 | 1989-01-23 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2005935A1 true CA2005935A1 (en) | 1990-07-23 |
Family
ID=23155394
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA002005935A Abandoned CA2005935A1 (en) | 1989-01-23 | 1989-12-19 | Scroll compressor with axial compliancy |
Country Status (9)
| Country | Link |
|---|---|
| US (1) | US4938669A (en) |
| EP (1) | EP0380439B1 (en) |
| JP (1) | JPH02238189A (en) |
| AR (1) | AR241036A1 (en) |
| BR (1) | BR9000211A (en) |
| CA (1) | CA2005935A1 (en) |
| DE (1) | DE69005835T2 (en) |
| ES (1) | ES2049011T3 (en) |
| MX (1) | MX168719B (en) |
Families Citing this family (21)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5040956A (en) * | 1989-12-18 | 1991-08-20 | Carrier Corporation | Magnetically actuated seal for scroll compressor |
| US5145345A (en) * | 1989-12-18 | 1992-09-08 | Carrier Corporation | Magnetically actuated seal for scroll compressor |
| US5256044A (en) * | 1991-09-23 | 1993-10-26 | Carrier Corporation | Scroll compressor with improved axial compliance |
| EP0634576B1 (en) * | 1993-07-14 | 1997-09-10 | Atlas Copco Airpower N.V. | Transmission with revolving bearing and seal used hereby |
| BE1008365A3 (en) * | 1993-07-14 | 1996-04-02 | Atlas Copco Airpower Nv | Drive with moving around lower and thus used seal. |
| KR100414079B1 (en) * | 1996-12-21 | 2004-04-03 | 엘지전자 주식회사 | Back pressure structure of scroll compressor |
| DE19720790A1 (en) * | 1997-05-17 | 1998-12-03 | Bitzer Kuehlmaschinenbau Gmbh | compressor |
| US5994468A (en) * | 1998-05-06 | 1999-11-30 | Bridgestone Corporation | High damping gels derived from nylon grafted polymers |
| US6139295A (en) * | 1998-06-22 | 2000-10-31 | Tecumseh Products Company | Bearing lubrication system for a scroll compressor |
| US6220839B1 (en) | 1999-07-07 | 2001-04-24 | Copeland Corporation | Scroll compressor discharge muffler |
| US6302664B1 (en) * | 2000-05-31 | 2001-10-16 | Westinghouse Air Brake Company | Oilers rotary scroll air compressor axial loading support for orbiting member |
| US6283737B1 (en) * | 2000-06-01 | 2001-09-04 | Westinghouse Air Brake Technologies Corporation | Oiless rotary scroll air compressor antirotation assembly |
| JP2002242858A (en) * | 2001-02-14 | 2002-08-28 | Mitsubishi Heavy Ind Ltd | Scroll compressor |
| US7861541B2 (en) | 2004-07-13 | 2011-01-04 | Tiax Llc | System and method of refrigeration |
| US8157551B2 (en) * | 2009-02-03 | 2012-04-17 | Scrollabs Corporation | Scroll compressor with back pressure pocket receiving discharge pressure fluid |
| US8167594B2 (en) | 2009-02-03 | 2012-05-01 | Scrolllabs Corporation | Scroll compressor with materials to allow run-in |
| JP5601404B1 (en) * | 2013-06-20 | 2014-10-08 | ダイキン工業株式会社 | Scroll compressor |
| KR102506914B1 (en) * | 2016-09-20 | 2023-03-06 | 엘지전자 주식회사 | A co-rotating scroll compressor having back pressure structure |
| DE102016125392A1 (en) * | 2016-12-22 | 2018-06-28 | OET GmbH | Scroll compressor |
| DE102016125384A1 (en) * | 2016-12-22 | 2018-06-28 | OET GmbH | Scroll compressor |
| KR102002125B1 (en) * | 2018-03-02 | 2019-07-19 | 엘지전자 주식회사 | Scorll compressor |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6073080A (en) * | 1983-09-30 | 1985-04-25 | Toshiba Corp | Scroll type compressor |
| JPS6073081A (en) * | 1983-09-30 | 1985-04-25 | Toshiba Corp | Scroll type compressor |
| JPS60166779A (en) * | 1984-02-09 | 1985-08-30 | Matsushita Refrig Co | Scroll type compressor |
| GB2162899B (en) * | 1984-06-27 | 1988-06-15 | Toshiba Kk | Scroll compressors |
| US4600369A (en) * | 1985-09-11 | 1986-07-15 | Sundstrand Corporation | Positive displacement scroll type apparatus with fluid pressure biasing the scroll |
| JPS62139991A (en) * | 1985-12-13 | 1987-06-23 | Matsushita Electric Ind Co Ltd | Scroll type compressor |
| JPS63106387A (en) * | 1986-10-23 | 1988-05-11 | Daikin Ind Ltd | Scroll type fluid device |
| MY104296A (en) * | 1987-03-12 | 1994-03-31 | Matsushita Electric Ind Co Ltd | Scroll compressor |
-
1989
- 1989-01-23 US US07/299,574 patent/US4938669A/en not_active Expired - Lifetime
- 1989-12-19 CA CA002005935A patent/CA2005935A1/en not_active Abandoned
-
1990
- 1990-01-17 MX MX019158A patent/MX168719B/en unknown
- 1990-01-19 BR BR909000211A patent/BR9000211A/en not_active IP Right Cessation
- 1990-01-22 AR AR315982A patent/AR241036A1/en active
- 1990-01-23 DE DE69005835T patent/DE69005835T2/en not_active Expired - Fee Related
- 1990-01-23 EP EP90630024A patent/EP0380439B1/en not_active Expired - Lifetime
- 1990-01-23 JP JP2013460A patent/JPH02238189A/en active Pending
- 1990-01-23 ES ES90630024T patent/ES2049011T3/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| EP0380439A2 (en) | 1990-08-01 |
| DE69005835T2 (en) | 1994-06-16 |
| EP0380439B1 (en) | 1994-01-12 |
| EP0380439A3 (en) | 1991-01-09 |
| AR241036A1 (en) | 1991-04-30 |
| MX168719B (en) | 1993-06-04 |
| BR9000211A (en) | 1990-11-13 |
| DE69005835D1 (en) | 1994-02-24 |
| ES2049011T3 (en) | 1994-04-01 |
| JPH02238189A (en) | 1990-09-20 |
| AR241036A2 (en) | 1991-04-30 |
| US4938669A (en) | 1990-07-03 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| EEER | Examination request | ||
| FZDE | Discontinued |