WO2005100789A1 - 圧縮機 - Google Patents
圧縮機 Download PDFInfo
- Publication number
- WO2005100789A1 WO2005100789A1 PCT/JP2005/002559 JP2005002559W WO2005100789A1 WO 2005100789 A1 WO2005100789 A1 WO 2005100789A1 JP 2005002559 W JP2005002559 W JP 2005002559W WO 2005100789 A1 WO2005100789 A1 WO 2005100789A1
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- WO
- WIPO (PCT)
- Prior art keywords
- drive shaft
- oil
- bearing
- supplied
- compressor according
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B27/1036—Component parts, details, e.g. sealings, lubrication
- F04B27/109—Lubrication
Definitions
- the present invention relates to a compressor including a swash plate housed in a crank chamber and rotating with the rotation of a drive shaft, and a piston reciprocatingly sliding in a cylinder bore with the rotation of the swash plate.
- the present invention relates to a drive shaft held in a housing via a slide bearing.
- a housing that defines a crankcase, a drive shaft that is rotatably supported by a radial bearing in the housing, and a power transmission mechanism that is arranged in the crankcase and rotates in synchronization with the rotation of the drive shaft.
- a piston having a piston reciprocatingly sliding in a cylinder bore formed in the housing as the power transmission mechanism rotates, and a suction chamber and a discharge chamber selectively communicating with the cylinder bore by reciprocating sliding of the piston.
- Patent Document 1 JP-A-2002-310067
- the present invention has been made in view of the above-described circumstances, and provides a compressor that can obtain good lubrication of a bearing portion when a slide bearing is used as a bearing of a drive shaft.
- the main task is to do.
- a compressor includes a housing defining a crank chamber, a drive shaft rotatably supported on the housing via a radial bearing, and the crank chamber.
- a power transmission mechanism disposed in the housing and rotating in synchronization with the rotation of the drive shaft; a piston reciprocatingly sliding in a cylinder bore formed in the housing with the rotation of the power transmission mechanism; and a reciprocating sliding of the piston.
- a suction chamber and a discharge chamber selectively communicating with the cylinder bore, and the radial bearing is constituted by a slide bearing.
- the radial bearing is provided in a discharge region including the discharge chamber and discharges to the discharge chamber.
- An oil separating mechanism for separating oil mixed in the working fluid, and an oil path formed inside the drive shaft. Oil maintained at a pressure higher than the pressure of the crank chamber is supplied between the slide bearing and the drive shaft via an oil passage of the drive shaft. ).
- the oil held at a pressure higher than the pressure of the crank chamber separated by the oil separation mechanism is forcibly forced between the sliding bearing and the drive shaft via the oil passage of the drive shaft. Since the oil is supplied, an oil film can be actively formed during this time, and good lubrication between the bearing and the drive shaft can be ensured. For this reason, seizure between the bearing and the drive shaft is prevented, and at the same time, friction loss is reduced and mechanical efficiency can be improved.
- the oil passage has a shaft hole formed in the axial direction of the drive shaft and a lateral hole formed in the radial direction from the shaft hole, and is provided between the slide bearing and the drive shaft.
- the oil may be supplied through the lateral hole (claim 2).
- the drive shaft and the sliding bearing are fitted with a certain clearance, but the drive shaft is connected to the bearing by the moment due to the compression reaction force on the drive shaft. Since a part that is strongly pressed is formed, the position where the lateral hole opens between the slide bearing and the drive shaft is located more in the rotation direction of the drive shaft than the part where the minimum gap between the drive shaft and the slide bearing is. It is preferable that the phase be in front (claim 3). With such a configuration, it is possible to draw the oil supplied between the slide bearing and the drive shaft through the lateral hole into the minimum clearance, thereby forming good lubrication in the minimum clearance. It is possible to effectively prevent image sticking.
- the oil supplied through the oil passage is also supplied to the thrust bearing.
- the oil supplied through the oil passage may be supplied to the radial bearing and then to the thrust bearing (claim 5).
- the oil supplied to the radial bearing via the oil passage may be supplied to the seal member. (Claim 6).
- a power transmission mechanism is fixedly mounted on the drive shaft and rotatably supported on the inner wall surface of the housing via a thrust bearing, and an oblique flange connected to the thrust flange via a link member.
- oil supplied through an oil passage is supplied to the sliding member. May also be supplied (claim 7).
- a pressure reducing means or a filter for reducing the pressure of the oil may be provided in a path leading to the oil path of the drive shaft from the oil separating mechanism.
- the above-described sliding bearing may be provided with grooves on its inner peripheral surface or subjected to abrasion resistance treatment (claims 10 and 11), and the drive shaft has an outer peripheral surface on which the sliding bearing slides.
- the grooves may be subjected to an abrasion resistance treatment (claims 12 and 13).
- the above configuration is particularly effective for a compressor of a high-pressure specification, for example, a compressor using carbon dioxide as a working fluid (claim 14).
- the radial bearing for receiving the drive shaft is formed of a slide bearing
- the pressure is higher than the pressure of the crank chamber separated by the oil separation mechanism. High! ⁇ Since the oil held at the pressure is supplied between the slide bearing and the drive shaft via the oil path formed on the drive shaft, the oil film is forcibly applied between the drive shaft and the slide bearing. Can be formed, and good lubrication of the bearing portion can be obtained. For this reason, when a sliding bearing is used as a radial bearing, it is possible to avoid problems such as seizure due to insufficient lubrication.
- FIG. 1 is a cross-sectional view showing a configuration example of a compressor according to the present invention.
- FIG. 2 is an exploded perspective view showing a drive shaft and a slide bearing slidably fitted to the drive shaft.
- FIG. 3 is an exaggerated cross-sectional view showing a relationship between a drive shaft and a slide bearing slidably fitted to the drive shaft.
- FIGS. 4 (a) to 4 (c) are diagrams showing another example of the configuration of the slide bearing.
- FIG. 5 (a) —FIG. 5 (c) are diagrams showing another configuration example of the outer peripheral surface on which the sliding bearing of the drive shaft slides.
- FIG. 6 is a cross-sectional view showing an example in which a filter is provided in an oil reservoir of the compressor according to the present invention.
- FIG. 7 is a cross-sectional view showing another configuration example of the compressor according to the present invention in which lubricating oil supply paths are different.
- FIG. 8 is a cross-sectional view showing still another configuration example in which a lubricating oil supply path is changed in the compressor according to the present invention.
- a variable displacement compressor suitable for the present invention is shown.
- This compressor is assembled so as to cover a cylinder block 1, a rear head 3 attached to the rear side of the cylinder block 1 via a valve plate 2, and the cylinder block 1.
- a front head 5 that defines a crank chamber 4.
- the front head 5, the valve plate 2, and the rear head 3 are fastened in the axial direction by fastening bolts 6, and constitute a compressor housing.
- a drive shaft 7 having one end protruding from the front head 5 is accommodated.
- a drive pulley 9 fixed in the axial direction by bolts 8 is rotatably fitted to the boss 5a of the front head 5 via a bearing 10 at a portion of the drive shaft 7 where the front head 5 also protrudes. .
- One end of the drive shaft 7 is hermetically sealed from the front head 5 via a seal member 11 provided between the drive shaft 7 and the slide shaft and constitutes a radial bearing.
- the drive shaft 7 is rotatably supported, and the other end of the drive shaft 7 is provided with a thrust bearing 14 housed in a support recess 13 of the cylinder block 1 and a sliding bearing constituting a radial bearing provided adjacent thereto. It is rotatably supported by bearings 15 (see Fig. 2).
- the slide bearings 12, 15 are also made of a metal cylindrical member such as aluminum (A1) or iron (Fe), and are known per se containing a solid lubricant and a body (Cu).
- the cylinder block 1 is formed with the support recess 13 in which the slide bearing 15 is accommodated, and a plurality of cylinder bores 16 arranged at equal intervals on a circumference centered on the support recess 13.
- a single-headed piston 17 is inserted into each of the cylinder bores 16 so as to be reciprocally slidable.
- a thrust flange 18 that rotates integrally with the drive shaft 7 in the crank chamber 4 is fixed to the drive shaft 7.
- the thrust flange 18 is rotatably supported on the inner wall surface of the front head 5 formed substantially perpendicular to the drive shaft 7 via a thrust bearing 19.
- a swash plate 21 is connected to the thrust flange 18 via a link member 20.
- the swash plate 21 is tiltably held via a hinge ball 22 provided on the drive shaft 7!
- the thrust flange 18 is rotated integrally with the rotation of the thrust flange 18! /, Ru.
- the thrust flange 18 and the swash plate 21 constitute a power transmission mechanism that rotates in synchronization with the rotation of the drive shaft 7.
- the engaging portion 17b of the single-headed piston 17 is moored at the peripheral portion of the swash plate 21 via a pair of front and rear shoes 23.
- the rear head 3 defines a suction chamber 25 and a discharge chamber 26 formed around the suction chamber 25.
- the valve plate 2 includes a suction valve (not shown) including the suction chamber 25 and the compression chamber 24. And a discharge hole 28 that connects the discharge chamber 26 and the compression chamber 24 via a discharge valve (not shown).
- the rear head 3 has an air supply passage A that allows the discharge chamber 26 to communicate with the crank chamber 4, and a bleed passage B that allows the crank chamber 4 to communicate with the suction chamber 25.
- a pressure control valve 30 for adjusting the communication state is mounted, and the pressure control valve 30 controls the pressure in the crank chamber 4 to adjust the piston stroke, that is, the discharge capacity.
- the piston stroke is determined by the pressure acting on the front surface of the piston 17, ie, the pressure in the compression chamber 24 (the pressure in the cylinder bore 16), and the pressure acting on the rear surface of the piston 17, ie, the pressure in the crank chamber 4 ( The pressure difference is determined by the pressure difference between the compression chamber 26 and the crank chamber 4.
- the crank chamber pressure is increased, the differential pressure between the compression chamber 26 and the crank chamber 4 is reduced, so that the piston stroke is reduced.
- the differential pressure between the compression chamber 24 and the crank chamber 4 increases, so that the piston stroke increases.
- the rear head 3 is provided with a centrifugal oil separation mechanism 31 for separating oil mixed in the discharge gas discharged into the discharge chamber 26.
- the oil separation mechanism 31 includes an oil separation chamber 33 that communicates with the discharge chamber 26 via an introduction port 32.
- the oil separation chamber 33 is formed by a space extending in the vertical direction, and is formed inside the oil separation chamber 33.
- the separation tube 34 is inserted from above to below. Therefore, the refrigerant gas discharged into the discharge chamber 26 is introduced into the oil separation chamber 33 from the side via the introduction port 32, and is guided downward while turning around the separation cylinder 34. Mixed oil is separated.
- the discharge gas from which the oil has been separated is sent out from a discharge port 35 formed above the oil separation mechanism 31 via a separation cylinder 34, and the separated oil is connected to the bottom of the oil separation chamber 33.
- the oil can be stored in an oil sump chamber 38 disposed below the oil separation chamber 33 via an oil outflow passage 37.
- the oil sump chamber 38 is provided inside the suction chamber 25, that is, in the center of the rear head 3, and accommodates a bolt 39 for fixing the cylinder block 1 and the valve plate 2. Formed to tolerate! Puru.
- the bolt 39 is provided so that its axis is substantially aligned with the drive shaft 7, and the bolt 39 has a through hole 39a formed in the axial direction.
- the drive shaft 7 has an end portion inserted into the cylinder block 1 and an axial hole 40a formed in the axial direction. One end is connected to the axial hole 40a, and the other end is in sliding contact with the slide bearings 12, 15.
- the oil passage 40 is formed by the lateral holes 40b and 40c opened in the outer peripheral portion.
- a discharge region 36 is formed by the discharge chamber 26 and the oil separation chamber 33 connected thereto via the introduction port 32, and the oil outlet passage 37, the oil reservoir 38, and the bolt 39
- a lubricating oil supply path connecting the discharge region 36 and the crank chamber 4 is formed by a gap between the lubricating oil supply passage 7 and the like.
- the gap between the radial bearing composed of the sliding bearings 12 and 15 and the drive shaft 7 is set such that an oil amount of 50 gZ min-200 g / min is ensured. If the gap is smaller than 50 gZ min, oil may run short due to lack of oil, and if it is larger than 200 g / min, the amount of separated oil generated may not be enough, and a large amount of gas refrigerant may be mixed. . Also, in order to prevent an excessive flow of oil in accordance with the flow rate setting described above, a through hole 39a formed in the bolt 39 is squeezed into an orifice shape so that the oil pressure is higher than the crank chamber pressure and is maintained at the pressure. You may try to depressurize with.
- the lateral holes 40b and 40c of the oil passage 40 are such that the position where the opening between the slide bearing and the drive shaft is the minimum gap between the drive shaft and the slide bearing It is formed so that the phase comes before the phase. That is, the drive shaft and the sliding bearing are fitted with the above-mentioned predetermined clearance secured, but the drive shaft is biased by the moment due to the compression reaction force applied to the drive shaft and is strongly pressed against the bearing. Since the part is formed, the position where the lateral hole opens is 45 degrees to 135 degrees smaller than the part where the minimum clearance between the drive shaft and the sliding bearing is located, with respect to the part that is pressed against such a bearing and has the minimum clearance. It is provided at the point where the phase is advanced in the range of.
- the oil separated in the oil separation chamber 33 and stored in the oil storage chamber 38 is in a high-pressure state, and the high-pressure oil is supplied to the closed space through the through hole 39 a of the bolt 39.
- the pressure is reduced upon reaching 41, and is led to the oil path 40 (shaft hole 40a, lateral holes 40b, 40c) of the drive shaft 7. Since the oil guided to the oil passage 40 of the drive shaft 7 is maintained at a pressure higher than the crankcase pressure, the oil is driven through the oil passage 40 to the rear and front slide bearings 12 and 15. Forcibly supplied to the gap between the shaft 7 and the rear side, the guide is guided to the thrust bearing 14 through the gap between the slide bearing 15 and the drive shaft 7, and after passing through the thrust bearing 14, the crank Returned to room 4.
- the lateral holes 40b and 40c of the oil path 40 are opened on the outer peripheral surface of the drive shaft so that the phase is ahead of the portion where the minimum gap between the drive shaft 7 and the slide bearings 12 and 15 is located.
- the oil supplied between the sliding bearings 12, 15 and the drive shaft 7 through the lateral holes 40b, 4Oc can be easily drawn into the minimum clearance, and good lubrication can be achieved in the minimum clearance. And seizure can be effectively prevented.
- the sliding bearings 12, 15 are those having no irregularities on the inner peripheral surface.
- a spiral groove 45 is formed on the inner surface.
- a plurality of annular grooves 46 may be formed on the inner surface.
- the inner surfaces of the sliding bearings 12, 15 may be subjected to a wear-resistant treatment such as Teflon (registered trademark) coating 47.
- the outer peripheral surface of the drive shaft 7 with which the sliding bearings 12 and 15 are in sliding contact is formed in a cylindrical shape having a smooth curved surface without irregularities.
- an annular groove 48 may be formed, and a lateral hole 40c may be opened in this annular groove portion.
- the annular groove 48 may be constituted by a plurality of annular grooves 48a, 48b, 48c as shown in FIG.
- the outer peripheral surface of the drive shaft 7 where the slide bearings 12, 15 are in sliding contact may be subjected to a wear-resistant treatment such as Teflon (registered trademark) coating 49.
- a filter 44 is provided in the oil reservoir 38 as shown in FIG. 6, and the oil sent from the oil separation chamber 33 through the oil outlet passage 37 is filtered. Contaminants may be captured by passing through.
- a filter formed in a mesh shape of 2 m-3 O / z m may be used. If it is less than 2 m, clogging is likely to occur, and if it is more than 30 / z m, it becomes difficult to catch contaminants, and there is no point in providing the filter 44.
- FIG. 7 shows another configuration example of the lubricating oil supply path described above!
- the oil guided to the closed space via the through hole of the oil sump capillar bolt is guided to the oil path of the drive shaft, and from the closed space, the rear sliding bearing and the drive are driven. It is different from the above-described configuration in that it is supplied between the shaft and the shaft, passes through the thrust bearing through this gap, and returns to the crankcase. Since other configurations are the same as those of the above configuration example, the same portions are denoted by the same reference numerals and description thereof will be omitted.
- FIG. 8 shows another configuration example of the lubricating oil supply path described above!
- one end is connected to the shaft hole 7a of the drive shaft 7, and the other end is provided with a lateral hole 40d which is open to the outer peripheral portion in sliding contact with the hinge ball 22. It differs in that it composes oilway 40. Since other configurations are the same as those of the above configuration example, the same portions are denoted by the same reference numerals and description thereof will be omitted.
- the drive shaft 7 is further provided with a lateral hole 40e having one end connected to the shaft hole 40a and the other end opened to the outer peripheral surface communicating with the thrust bearing 19, as shown by a broken line.
- the oil path 40 may be formed, and pressurized oil may be supplied to the thrust bearing 19 via the oil path 40 of the drive shaft 7.
- the diameter of the lateral hole 40e is preferably set to be larger than the diameters of the other lateral holes 40b, 40c, and 40d in order to supply a sufficient amount of oil.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressor (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2004121709A JP2005307749A (ja) | 2004-04-16 | 2004-04-16 | 圧縮機 |
JP2004-121709 | 2004-04-16 |
Publications (1)
Publication Number | Publication Date |
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WO2005100789A1 true WO2005100789A1 (ja) | 2005-10-27 |
Family
ID=35150060
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2005/002559 WO2005100789A1 (ja) | 2004-04-16 | 2005-02-18 | 圧縮機 |
Country Status (2)
Country | Link |
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JP (1) | JP2005307749A (ja) |
WO (1) | WO2005100789A1 (ja) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP4648845B2 (ja) | 2006-01-30 | 2011-03-09 | 株式会社デンソー | 斜板型および揺動斜板型の可変容量圧縮機 |
KR101979027B1 (ko) * | 2012-11-23 | 2019-05-16 | 학교법인 두원학원 | 용량 가변형 사판식 압축기 |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5431611A (en) * | 1977-08-12 | 1979-03-08 | Sentoraru Jidoushiya Kougiyou | Cooling medium compressor |
JPS5627090A (en) * | 1979-08-07 | 1981-03-16 | Nippon Denso Co Ltd | Swash plate-type compressor |
JPH02141682U (ja) * | 1989-04-28 | 1990-11-29 | ||
JP2002005026A (ja) * | 2000-06-16 | 2002-01-09 | Toyota Industries Corp | ピストン式圧縮機 |
JP2002310067A (ja) * | 2001-04-10 | 2002-10-23 | Toyota Industries Corp | 圧縮機 |
-
2004
- 2004-04-16 JP JP2004121709A patent/JP2005307749A/ja active Pending
-
2005
- 2005-02-18 WO PCT/JP2005/002559 patent/WO2005100789A1/ja active Application Filing
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5431611A (en) * | 1977-08-12 | 1979-03-08 | Sentoraru Jidoushiya Kougiyou | Cooling medium compressor |
JPS5627090A (en) * | 1979-08-07 | 1981-03-16 | Nippon Denso Co Ltd | Swash plate-type compressor |
JPH02141682U (ja) * | 1989-04-28 | 1990-11-29 | ||
JP2002005026A (ja) * | 2000-06-16 | 2002-01-09 | Toyota Industries Corp | ピストン式圧縮機 |
JP2002310067A (ja) * | 2001-04-10 | 2002-10-23 | Toyota Industries Corp | 圧縮機 |
Non-Patent Citations (1)
Title |
---|
OGURI F. ET AL: "Kikai Sekkei Know How Series", KIKAI SEKKEI NI OKERU TABOO GUIDE BOOK, 1 October 1996 (1996-10-01), pages 85, XP002992608 * |
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Publication number | Publication date |
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JP2005307749A (ja) | 2005-11-04 |
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