WO2005071269A1 - スイング圧縮機 - Google Patents
スイング圧縮機 Download PDFInfo
- Publication number
- WO2005071269A1 WO2005071269A1 PCT/JP2005/000770 JP2005000770W WO2005071269A1 WO 2005071269 A1 WO2005071269 A1 WO 2005071269A1 JP 2005000770 W JP2005000770 W JP 2005000770W WO 2005071269 A1 WO2005071269 A1 WO 2005071269A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- roller
- sliding surface
- swing compressor
- drive shaft
- blade
- Prior art date
Links
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
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/32—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members
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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
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/32—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members
- F04C18/322—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members with vanes hinged to the outer member and reciprocating with respect to the outer member
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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
-
- 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
Definitions
- the present invention relates to a compressor.
- a compressor As a compressor, a cylinder that forms a cylinder chamber, a cylindrical roller that rotates while revolving in the cylinder chamber, and a roller that is separate from the cylinder and directed to the cylinder toward the cylinder chamber
- a rotary compressor provided with a blade held so as to be able to move forward and backward, and a drive shaft having an eccentric portion fitted to an inner peripheral sliding surface of the roller.
- the rotary compressor rotates and drives the drive shaft so that the roller rotates and revolves in the cylinder chamber, and moves relative to the blade.
- the cylinder and chamber are partitioned into a suction chamber and a compression chamber by the rollers and blades to perform a suction action and a compression action.
- the narrow portion of the outer peripheral sliding surface of the eccentric portion of the drive shaft is formed mainly by machining.
- the center of the main body of the drive shaft positioned on both sides in the axial direction of the eccentric portion is eccentric with respect to the center of the rotating shaft of the processing machine, and the center of the eccentric portion is It is necessary to perform the work of processing the narrow portion of the eccentric part by accurately positioning the work at the center of the eccentric portion, and this work is extremely complicated. Therefore, processing of the narrow portion requires an extremely large number of steps, and as a result, the conventional compressor has a high cost. Disclosure of the invention
- an object of the present invention is to reduce the viscous shear loss of lubricating oil between an outer peripheral sliding surface of an eccentric portion of a drive shaft and an inner peripheral sliding surface of a roller to reduce mechanical loss.
- Another object of the present invention is to provide an inexpensive and high-precision compressor which is easy to process and which is inexpensive.
- the present inventor has found that in the above-described conventional rotary compressor, the roller and the blade are separate bodies, and the roller rotates. Therefore, as the roller rotates, the inner circumferential sliding surface of the roller becomes lighter. Since the load side and the heavy load side change, it is not possible to provide a narrow part and a wide part on the inner peripheral sliding surface of the roller. It was considered that a narrow portion and a wide portion were provided. Accordingly, the present inventor has proposed that the roller be prevented from rotating on its own and the light load side and the heavy load side of the inner peripheral sliding surface of the roller be fixed. It has been considered that it is possible to provide a wide part and a wide part.
- a cylinder forming a cylinder chamber
- a piston comprising a substantially cylindrical roller that revolves along the inner surface of the cylinder chamber, and a blade formed integrally with the roller and held swingably in the cylinder;
- a drive shaft having an eccentric portion that is slidably fitted to the inner peripheral sliding surface of the roller
- the piston partitions the cylinder chamber into a suction chamber and a compression chamber, and performs a swinging motion by rotation of the drive shaft.
- the inner circumferential sliding surface of the roller is a first circumferential sliding surface of the roller.
- the rollers revolve and do not rotate.
- the piston in which the roller and the blade are integrated with each other makes a swinging motion and does not rotate. Therefore, the heavy load side and the light load side of the inner circumferential sliding surface of the roller are fixed and do not change. Therefore, according to the present invention, the narrow portion of the inner circumferential sliding surface of the roller is always located on the light load side where wear and seizure hardly occur, and the wide portion is always located on the heavy load side.
- the viscous shear loss of the lubricating oil between the outer peripheral sliding surface of the eccentric portion of the drive shaft and the inner peripheral sliding surface of the roller can be reduced by the narrow width portion, and the mechanical loss can be reduced.
- An inexpensive and highly accurate swing compressor that is easy to process can be provided. Further, on the heavy load side, wear and seizure can be prevented by the wide portion of the inner circumferential sliding surface of the roller.
- the roller has a cylindrical shape and the inner peripheral surface and the outer peripheral surface are substantially cylindrical surfaces concentric, the machining of the narrow portion of the inner peripheral sliding surface of the roller requires the eccentric portion of the drive shaft. Compared to machining a narrow part of the outer peripheral sliding surface, it is easier, cheaper and more accurate.
- the drive shaft main body and the eccentric portion are not on the same plane orthogonal to the center axis of the drive shaft, whereas the rollers and the blades are located on substantially the same plane orthogonal to the center axis of the rollers. Therefore, the machining of the narrow portion of the inner circumferential sliding surface of the roller can be easily performed at low cost and with high precision.
- the narrow width portion is defined by using, as a reference line, an intersection line between a plane parallel to the blade passing through the center of the blade and the inner circumferential sliding surface of the roller.
- the sliding surface is formed in a range from a line displaced by 30 ° in the rotation direction of the drive shaft from the reference line to a line displaced by 180 ° from the reference line.
- the narrow portion is defined as an intersection line between a plane passing through the center of the blade and parallel to the blade and an inner peripheral sliding surface of the roller as a reference line. Since the inner sliding surface is formed in the range from the reference line to the line displaced by 30 ° in the rotation direction of the drive shaft from the reference line to the line displaced by 180 °, that is, the starting point of the narrow portion is lightly loaded. It is shifted by 30 ° from the connection between the blade and the roller, which is the starting point of the part, so even if a large load is applied to the vicinity of the connection between the blade and the roller during the discharge operation, the area near the connection is narrow. Since it is not a part but a wide part, there is no breakage, sufficient durability can be secured, and safety can be secured.
- the narrow portion is provided on the inner peripheral sliding surface in a region that is displaced from the reference line by 30 ° in the rotation direction of the drive shaft, a sufficient connection portion between the blade and the roller is provided. strength The inability to secure the degree helped. Further, when the narrow portion is provided on the inner peripheral sliding surface at a position displaced from the reference line by more than 180 ° in the rotation direction of the drive shaft, the narrow portion is located on the heavy load side. In the meantime, it helped to cause burn-in.
- the narrow portion has a range on the inner circumferential sliding surface of the roller from a line displaced by 30 ° in the rotational direction of the drive shaft from the reference line to a line displaced by 180 ° in the rotation direction of the drive shaft. It is formed inside.
- sufficient strength can be ensured at the connecting portion between the blade and the roller, that is, near the root portion of the blade, and the outer peripheral sliding surface of the eccentric portion of the drive shaft and the roller can be secured.
- the viscous shear loss of the lubricating oil between the narrow portion of the inner peripheral sliding surface and the lubricating oil can be reduced to reduce mechanical loss and prevent seizure.
- the narrow portion is provided on the cylinder and on a suction port side communicating with the suction chamber with respect to a plane parallel to the blade passing through the center of the blade. I have.
- the narrow portion is provided on the suction port side of the cylinder with respect to a plane passing through the center of the blade and parallel to the blade. Therefore, the narrow portion is located on the light load side peculiar to the inner circumferential sliding surface of the roller of the swing compressor, and is not located on the heavy load side. Therefore, seizure of the inner circumferential sliding surface of the roller can be prevented.
- the piston is arranged to revolve along a horizontal plane, and the upper edge of the narrow portion is located lower than the upper edge of the wide portion.
- the upper edge of the narrow portion is located below the upper edge of the wide portion! /, So that the upper edge of the narrow portion extends from the upper edge of the narrow portion.
- the area leading to the upper edge of the roller functions as an oil reservoir for lubricating oil. Can be prevented.
- a portion above the upper edge of the narrow portion of the inner circumferential sliding surface of the roller is formed in such a manner that a cutout portion is provided in an axially upper portion of the horizontally arranged roller.
- This cut-off portion functions as an oil sump during operation of the compressor, and can prevent shortage of lubricating oil on the sliding surface between the outer peripheral sliding surface of the eccentric portion and the inner peripheral surface of the roller, Wear and seizure can be prevented.
- the drive shaft is arranged to be inclined with respect to a horizontal plane, and the upper edge of the narrow portion is lower than the upper edge of the wide portion in the direction of the drive shaft. It is located in.
- the upper edge of the narrow portion is located lower than the upper edge of the wide portion in the direction of the drive shaft, the upper edge of the narrow portion is The area between the eccentric portion and the upper edge of the wide portion functions as an oil reservoir for lubricating oil to prevent wear and seizure on the outer peripheral sliding surface of the eccentric portion and the inner peripheral sliding surface of the mouthpiece. Can be.
- the drive shaft is disposed in a vertical direction.
- the entire area between the upper edge of the narrow portion and the upper edge of the wide portion can be used as an oil reservoir, and a large-capacity oil reservoir is formed to form the eccentric portion. Wear and seizure of the outer peripheral sliding surface and the inner peripheral sliding surface of the roller can be reliably prevented.
- the piston is formed of a sintered material.
- the piston is made of a porous sintered material, lubricating oil is held in the holes formed on the surface and inside of the piston, and sufficient lubricity can be secured. Also, if the piston is formed of a sintered material, post-processing can be omitted, and the manufacturing cost of the piston can be reduced. In particular, when the narrow portion is formed by providing the cut portion, the cut portion can be formed at the same time when the piston is formed, so that the product accuracy can be improved and the product cost can be reduced. .
- the present invention it is possible to reduce the viscous shear loss of lubricating oil between the outer peripheral sliding surface of the eccentric portion of the drive shaft and the inner peripheral sliding surface of the roller, thereby reducing mechanical loss. Besides, it is possible to provide a compressor which is easy to process, inexpensive and has high precision.
- FIG. 1 is a perspective view showing a roller of a swing compressor according to one embodiment of the present invention.
- FIG. 2A is a plan view of the roller.
- FIG. 2B is a developed view of an inner peripheral sliding surface of the roller.
- FIG. 3 (A), (B), (C), (D) are schematic plan views showing the operating state of the swing compressor.
- FIG. 4 is a developed view showing a modification of the sliding surface of the roller.
- FIG. 5 is a development view showing another modification of the sliding surface of the roller.
- FIG. 3 (A), (B), (C), and (D) are simplified plan views of main parts of the swing compressor.
- the swing compressor is used, for example, as a compressor of a refrigerator using HFC (Hide Port Fluorocarbon) based refrigerant.
- This swing compressor has a piston 4 in which a substantially cylindrical roller 2 and a blade 3 protruding radially outward of the roller 2 are integrally formed.
- the outer cylindrical surface and the inner cylindrical surface of the roller 2 are concentric.
- the inner peripheral cylindrical surface of the roller 2 of the piston 4, that is, the inner peripheral sliding surface is slidably fitted to the outer peripheral sliding surface of the eccentric portion 5 formed integrally with the drive shaft 1.
- the piston 4 is housed in a cylinder chamber 8 formed in a cylinder 6 and having a substantially circular cross section.
- a bush fitting hole 7 is formed in the cylinder 6 in contact with the cylinder chamber 8, and bushings 9, 9 having a substantially semi-cylindrical shape are fitted into the bush fitting hole 7.
- the bushes 9, 9 have the flat surfaces of the bushes 9, 9 opposed to each other, and slidably sandwich both side surfaces of the blade 3 of the piston 4 between the flat surfaces.
- the cylinder chamber 8 is divided into two chambers by the roller 2 and the blade 3 of the piston 4, that is, a suction chamber 12 and a compression chamber 13.
- a suction port 11 is opened on the inner peripheral surface of the cylinder chamber 8 to form a suction chamber 12.
- FIGS. 3 (B), 3 (C), and 3 (D) the left side chamber of the blade 3 has a discharge port (not shown) opened to the inner peripheral surface of the cylinder chamber 8 to form a discharge chamber 13. I have.
- the eccentric portion 5 rotates eccentrically around the axis of the drive shaft 1 in the same direction as the clock hand, and the roller 2 fitted to the eccentric portion 5 rotates
- the surface contacts the inner peripheral surface of the cylinder chamber 8 and revolves.
- the compressor is arranged horizontally, and the roller 2 revolves along a horizontal plane. Roller 2 revolves in cylinder chamber 8
- the blade 3 is held on both sides by the bushes 9 and 9, and moves forward and backward while swinging.
- a low-pressure HFC-based refrigerant is sucked into the suction chamber 12 from the suction port 11 (FIGS. 3 (B) and 3 (C)), compressed in the discharge chamber 13 to a high pressure, and then discharged (FIG. High-pressure HFC-based refrigerant (Fig. 3 (C), (D), (A)).
- the HFC-based refrigerant is mixed with a synthetic oil as a lubricating oil, and when the swing compressor performs a compression operation, a sliding surface inside the swing compressor, for example, an inner peripheral surface of the roller 2, an eccentric portion is formed.
- the outer peripheral surface of the roller 5, the outer peripheral surface of the roller 2, and the inner peripheral surface of the cylinder chamber 8 are lubricated by the lubricating oil mixed with the refrigerant.
- the piston 4 of the swing compressor is formed of, for example, an iron-based sintered material.
- the bushes 9, 9 are also formed of, for example, an iron-based sintered material.
- an inner peripheral sliding surface 14 on which the eccentric portion 5 slides is formed on the inner periphery of the roller 2.
- the inner peripheral sliding surface 14 has a wide portion 15 in which the axial width of the roller 2 is wide, and a narrow portion 16 which is narrower than the wide portion 15.
- the narrow portion 16 is formed in such a manner that a trapezoidal cutout portion 17 in FIG. 2B, which is a developed view, is provided on the upper portion in the axial direction of the roller 2 that is horizontally arranged. That is, the upper surface of the wide portion 15 of the sliding surface 14 having the width W is cut off by a predetermined width u (about 20% of the width W).
- the narrow portion 16 starts at point A, which is 30 degrees ahead of the connecting point O of the blade 3 on the roller 2 in the direction of rotation of the drive shaft 1 which is the direction of rotation of the clock hand, and then starts driving. It is located in the range ending at point B, which is 150 ° in the direction of rotation of shaft 1. The reason is as follows.
- this point on the sliding surface 14, that is, the connecting portion O of the blade 3 on the roller 2 is used as a base point, and then reaches a point B that advances in the rotation direction of the drive shaft 1.
- the 180 ° range up to is the light load part.
- a narrow portion 16 is formed in this light load portion to reduce the viscous shear loss of oil on the sliding surface between the outer peripheral surface of the eccentric portion 5 and the inner peripheral surface of the roller 2, thereby reducing mechanical loss. It is.
- the reason why the starting point A of the narrow portion 16 is shifted by 30 ° from the connecting portion O of the blade 3 which is the base point of the lightly loaded portion is that the blade 3 is displaced during the discharge operation (FIG. 3 (D)). This is to ensure safety in consideration of the load acting near the joint O.
- the load acting on the sliding surface of the roller 2 with which the eccentric portion 5 of the drive shaft 1 slides becomes large on the heavy load side when the load amount is large.
- the wide part 5 secures a sufficient sliding area to withstand this heavy load, and the wide part 15 of the sliding surface 14 of the eccentric part 5 and the sliding surface 14 of A sufficient oil film thickness can be ensured during this period, so that wear and seizure due to this sliding can be prevented.
- the narrow portion 16 on the sliding surface 14 of the lightly loaded portion where the load is small the sliding surface 14 is less affected by wear and seizure, the sliding area is reduced, and the eccentricity is reduced.
- the inner peripheral surface of the generally cylindrical roller 2 may be machined, so that the eccentric portion 5 is removed as in the related art.
- the machining operation can be performed easily and inexpensively, and the force can be performed with high precision. That is, since the roller 2 is cylindrical and the inner peripheral sliding surface 14 and the outer peripheral surface are concentric substantially cylindrical surfaces, machining of the narrow portion 16 of the inner peripheral sliding surface 14 of the roller 2 is a conventional example. As compared with the mechanical processing in which a narrow portion is provided on the outer peripheral sliding surface of the eccentric portion 5 of the drive shaft 1, it is easier, cheaper and more accurate.
- the roller 2 and the blade 3 are substantially perpendicular to the center axis of the roller 2. Since they are located on the same plane, machining of the narrow width portion 16 of the inner peripheral sliding surface 14 of the roller 2 can be easily performed at low cost and with high precision.
- the blade 3 is displaced during the discharging operation (FIG. 3D). Near the connecting part O Even when a load is applied, sufficient durability can be secured, and safety can be secured.
- the narrow width portion 16 is formed by a plane P passing through the center of the blade 3 and being parallel to the blade 3 and the roller P.
- the inner peripheral sliding surface 14 With the intersection line O with the inner peripheral sliding surface 14 as the reference line O, the inner peripheral sliding surface 14 is displaced by 180 ° from the line A displaced by 30 ° in the rotation direction of the drive shaft 1 from the reference line O on the inner peripheral sliding surface 14.
- the starting point A of the narrow part 16 is shifted by 30 ° from the connecting part O between the blade and the roller, which is the starting point O of the light load part.
- the vicinity is not the narrow part 16 but the wide part 15, so there is no breakage. Sufficient durability can be secured, and safety can be secured.
- the narrow portion 16 is provided on the inner peripheral sliding surface 14 of the roller 2 in a region less than 30 ° displaced from the reference line O in the rotation direction of the drive shaft 1, the blade It was a component that sometimes it was not possible to ensure sufficient strength at the connection between Roller 3 and Roller 2. If the narrow portion 16 is provided on the inner circumferential sliding surface 14 at a position displaced from the reference line O by more than 180 ° in the rotation direction of the drive shaft 1, the narrow portion 16 will Being located on the side, it was a component that could cause seizure. Therefore, in this embodiment, the narrow portion 16 is displaced by 180 ° on the inner circumferential sliding surface 14 of the roller 2 from a line displaced by 30 ° in the rotation direction of the drive shaft 1 from the reference line O.
- the narrow portion 16 may be provided on the entire intake port 11 side of the cylinder 6 with respect to a plane P passing through the center of the blade 3 and parallel to the blade 3 (FIGS. 2A and 2B). And Figure 3 (A), (B), (C), (D)).
- the narrow portion 16 is located on the light load side peculiar to the inner circumferential sliding surface of the roller 2 of the swing compressor, and is not located on the heavy load side. Therefore, seizure of the inner peripheral sliding surface 14 of the roller 2 can be prevented.
- the narrow width portion 16 of the roller 2 is formed in such a manner that a cutout portion 17 is provided at an upper portion in the axial direction of the horizontally arranged roller 2.
- the upper edge of the narrow portion 6 is formed such that the cutout portion 17 is located above the narrow portion 16 of the inner peripheral sliding surface 14 of the roller 2. It is located below the upper edge of the wide portion 15. Therefore, the cutout portion 17 functions as an oil sump during operation of the compressor, and can prevent the occurrence of insufficient lubrication on the sliding surface between the outer peripheral surface of the eccentric portion 5 and the inner peripheral surface of the roller 2. Wear and seizure can be prevented. Further, since the piston 4 is made of a porous sintered material, lubricating oil is held in the holes formed on the surface and inside of the piston 4, and sufficient lubricity can be secured.
- the post-processing of the piston 4 can be omitted, so that the manufacturing cost of the piston 4 can be reduced.
- the cutout 17 can be formed at the time of molding, so that the product accuracy can be improved and the product cost can be reduced.
- the drive shaft 1 is disposed inclined with respect to a horizontal plane, and the upper edge of the narrow portion 16 is lower than the upper edge of the wide portion 15 in the direction of the drive shaft 1. It may be located at In this case, the area from the upper edge of the narrow portion 16 to the upper edge of the wide portion 15 functions as an oil reservoir for lubricating oil. Wear and seizure of the surface 14 can be prevented.
- the piston 4 is made of a porous sintered material, lubricating oil is retained in the holes formed on the surface and inside of the piston 4, and sufficient lubricity can be secured. .
- the piston 4 is formed of a sintered material, the post-processing can be omitted, so that the manufacturing cost of the piston 4 can be reduced.
- the narrow portion 16 is formed by providing a cutout portion, the cutout portion can be formed at the same time as the piston 4 is formed, so that the product accuracy can be improved and the product cost can be reduced. be able to.
- the sintered material forming the piston 4 is not limited to an iron-based material, and may be an aluminum-ium-based material, a titanium-based material, or a -ckenole-based material. Further, the piston may be formed of ceramics.
- the narrow portion 16 of the roller 2 is Force formed by providing cutouts 17 in the axially upper part of moving surface 14 As shown in Fig. 4, cutouts 17, 17 are provided in the upper and lower portions of the normal sliding surface 14 of roller 2. Alternatively, it may be formed. Further, as shown in FIG. 5, a narrow portion 16 may be formed by forming a concave portion 19 in a central portion of a normal sliding surface 14 of the roller 2.
- the concave portion functions as an oil sump 19, which can prevent insufficient lubrication on the sliding surface between the outer peripheral surface of the eccentric portion 5 and the inner peripheral surface of the roller 2, and can cause wear and seizure due to sliding. Can be prevented.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
ES05703991.9T ES2594620T3 (es) | 2004-01-22 | 2005-01-21 | Compresor oscilante |
AU2005207221A AU2005207221B2 (en) | 2004-01-22 | 2005-01-21 | Swing compressor |
US10/586,741 US7556484B2 (en) | 2004-01-22 | 2005-01-21 | Compressor having a small-width portion and a large-width portion in an inner circumferential sliding surface of a swinging roller |
EP05703991.9A EP1710439B1 (en) | 2004-01-22 | 2005-01-21 | Swing compressor |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2004014273A JP3731127B2 (ja) | 2004-01-22 | 2004-01-22 | スイング圧縮機 |
JP2004-014273 | 2004-01-22 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2005071269A1 true WO2005071269A1 (ja) | 2005-08-04 |
Family
ID=34805413
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2005/000770 WO2005071269A1 (ja) | 2004-01-22 | 2005-01-21 | スイング圧縮機 |
Country Status (8)
Country | Link |
---|---|
US (1) | US7556484B2 (ja) |
EP (1) | EP1710439B1 (ja) |
JP (1) | JP3731127B2 (ja) |
KR (1) | KR100730456B1 (ja) |
CN (1) | CN100427761C (ja) |
AU (1) | AU2005207221B2 (ja) |
ES (1) | ES2594620T3 (ja) |
WO (1) | WO2005071269A1 (ja) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7988430B2 (en) | 2006-01-16 | 2011-08-02 | Lg Electronics Inc. | Linear compressor |
Families Citing this family (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP3731127B2 (ja) * | 2004-01-22 | 2006-01-05 | ダイキン工業株式会社 | スイング圧縮機 |
JP5556450B2 (ja) * | 2010-07-02 | 2014-07-23 | パナソニック株式会社 | 回転式圧縮機 |
WO2012086577A1 (ja) | 2010-12-22 | 2012-06-28 | ダイキン工業株式会社 | 圧縮機 |
CN103299079B (zh) * | 2010-12-27 | 2016-04-27 | 大金工业株式会社 | 压缩机 |
CZ2014195A3 (cs) * | 2013-04-17 | 2015-08-19 | Mitsubishi Electric Corporation | Chladicí kompresor |
CN107120286B (zh) * | 2016-02-25 | 2024-05-17 | 珠海凌达压缩机有限公司 | 低压腔压缩机及空调 |
JP6881558B1 (ja) * | 2019-12-17 | 2021-06-02 | ダイキン工業株式会社 | 圧縮機 |
JP6930576B2 (ja) * | 2019-12-17 | 2021-09-01 | ダイキン工業株式会社 | 圧縮機 |
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JPH05164071A (ja) * | 1991-12-13 | 1993-06-29 | Daikin Ind Ltd | ロータリー圧縮機 |
EP1640614A1 (en) | 2003-06-10 | 2006-03-29 | Daikin Industries, Ltd. | Rotary fluid machinery |
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DE1428140A1 (de) * | 1964-03-11 | 1969-11-20 | Inpaco Trust Reg | Kompressor mit exzentrisch bewegtem Kreiskolben |
JPS57176686U (ja) * | 1981-05-01 | 1982-11-08 | ||
JP2514052B2 (ja) * | 1987-11-20 | 1996-07-10 | 日本ピストンリング株式会社 | コンプレッサ用ロ―ラ |
DK0591539T3 (da) * | 1992-04-28 | 1999-05-10 | Daikin Ind Ltd | Rotationskompressor, hvori blad og rulle er integreret |
JP2780580B2 (ja) * | 1992-11-16 | 1998-07-30 | ダイキン工業株式会社 | 揺動型ロータリ圧縮機 |
JP3473066B2 (ja) * | 1993-12-06 | 2003-12-02 | ダイキン工業株式会社 | 揺動型ロータリー圧縮機 |
US5577903A (en) * | 1993-12-08 | 1996-11-26 | Daikin Industries, Ltd. | Rotary compressor |
JP3473067B2 (ja) * | 1993-12-08 | 2003-12-02 | ダイキン工業株式会社 | 揺動型ロータリー圧縮機 |
JP3622216B2 (ja) * | 1993-12-24 | 2005-02-23 | ダイキン工業株式会社 | 揺動型ロータリー圧縮機 |
JP3802940B2 (ja) * | 1994-10-31 | 2006-08-02 | ダイキン工業株式会社 | ロータリー圧縮機及び冷凍装置 |
JPH08165995A (ja) * | 1994-12-14 | 1996-06-25 | Matsushita Refrig Co Ltd | 回転式圧縮機 |
KR100311994B1 (ko) * | 1999-06-11 | 2001-11-03 | 가나이 쓰토무 | 회전 압축기 |
JP3829607B2 (ja) * | 2000-09-06 | 2006-10-04 | 株式会社日立製作所 | 揺動ピストン形圧縮機およびそのピストンの製造方法 |
JP3731127B2 (ja) * | 2004-01-22 | 2006-01-05 | ダイキン工業株式会社 | スイング圧縮機 |
-
2004
- 2004-01-22 JP JP2004014273A patent/JP3731127B2/ja not_active Expired - Fee Related
-
2005
- 2005-01-21 KR KR1020067014874A patent/KR100730456B1/ko not_active IP Right Cessation
- 2005-01-21 ES ES05703991.9T patent/ES2594620T3/es active Active
- 2005-01-21 WO PCT/JP2005/000770 patent/WO2005071269A1/ja active Application Filing
- 2005-01-21 US US10/586,741 patent/US7556484B2/en not_active Expired - Fee Related
- 2005-01-21 AU AU2005207221A patent/AU2005207221B2/en not_active Ceased
- 2005-01-21 EP EP05703991.9A patent/EP1710439B1/en not_active Not-in-force
- 2005-01-21 CN CNB2005800029954A patent/CN100427761C/zh active Active
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
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JPH05164071A (ja) * | 1991-12-13 | 1993-06-29 | Daikin Ind Ltd | ロータリー圧縮機 |
JP2541182B2 (ja) | 1991-12-13 | 1996-10-09 | ダイキン工業株式会社 | ロ―タリ―圧縮機 |
EP1640614A1 (en) | 2003-06-10 | 2006-03-29 | Daikin Industries, Ltd. | Rotary fluid machinery |
Non-Patent Citations (1)
Title |
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See also references of EP1710439A4 * |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7988430B2 (en) | 2006-01-16 | 2011-08-02 | Lg Electronics Inc. | Linear compressor |
Also Published As
Publication number | Publication date |
---|---|
AU2005207221A1 (en) | 2005-08-04 |
EP1710439B1 (en) | 2016-09-14 |
CN1910369A (zh) | 2007-02-07 |
JP3731127B2 (ja) | 2006-01-05 |
US7556484B2 (en) | 2009-07-07 |
ES2594620T3 (es) | 2016-12-21 |
CN100427761C (zh) | 2008-10-22 |
AU2005207221B2 (en) | 2007-11-22 |
EP1710439A1 (en) | 2006-10-11 |
JP2005207302A (ja) | 2005-08-04 |
EP1710439A4 (en) | 2010-11-10 |
KR100730456B1 (ko) | 2007-06-19 |
KR20060129299A (ko) | 2006-12-15 |
US20080240961A1 (en) | 2008-10-02 |
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