EP2565457A2 - Drehschieber-Kompressor - Google Patents

Drehschieber-Kompressor Download PDF

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Publication number
EP2565457A2
EP2565457A2 EP12182075A EP12182075A EP2565457A2 EP 2565457 A2 EP2565457 A2 EP 2565457A2 EP 12182075 A EP12182075 A EP 12182075A EP 12182075 A EP12182075 A EP 12182075A EP 2565457 A2 EP2565457 A2 EP 2565457A2
Authority
EP
European Patent Office
Prior art keywords
rotor
cylinder
peripheral surface
vane
solid lubricant
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.)
Withdrawn
Application number
EP12182075A
Other languages
English (en)
French (fr)
Other versions
EP2565457A3 (de
Inventor
Tomoyasu Takahashi
Takanori Teraya
Takaaki Nakamura
Isao Yamada
Michihiro Hori
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Valeo Japan Co Ltd
Original Assignee
Valeo Japan Co Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Valeo Japan Co Ltd filed Critical Valeo Japan Co Ltd
Publication of EP2565457A2 publication Critical patent/EP2565457A2/de
Publication of EP2565457A3 publication Critical patent/EP2565457A3/de
Withdrawn legal-status Critical Current

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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
    • F04C18/30—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
    • F04C18/34—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 the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/344—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 the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C18/3441—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 the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • 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
    • F04C29/02—Lubrication; Lubricant separation
    • 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
    • F04C2230/00—Manufacture
    • F04C2230/10—Manufacture by removing material
    • 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
    • F04C2230/00—Manufacture
    • F04C2230/20—Manufacture essentially without removing material
    • 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
    • F04C2230/00—Manufacture
    • F04C2230/90—Improving properties of machine parts
    • F04C2230/91—Coating
    • 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
    • F04C2240/00—Components
    • F04C2240/20—Rotors
    • 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
    • F04C2240/00—Components
    • F04C2240/30—Casings or housings
    • 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
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • F04C2240/52—Bearings for assemblies with supports on both sides
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2251/00—Material properties
    • F05C2251/14—Self lubricating materials; Solid lubricants

Definitions

  • the present invention relates to a vane-type compressor which is used in a refrigerating cycle or the like of a vehicle-use air conditioner, for example.
  • a compressive action is performed alternately at compressive portions positioned on both sides in the radial direction from the center of a shaft. Accordingly, even when a clearance between the shaft and a bearing which supports the shaft is set as small as possible, the rotor assembly alternately vibrates along the ellipse short-axis direction of the elliptical cylinder within a range of the clearance.
  • the rotor assembly vibrates in such a manner that an outer peripheral surface of the rotor and an inner peripheral surface of the cylinder on a top dead center side are separated from each other thus increasing the clearance, while the outer peripheral surface of the rotor and the inner peripheral surface of the cylinder on a side opposite to the top dead center approach each other thus decreasing the clearance.
  • the rotor assembly vibrates as described above and hence, when the clearance between the outer peripheral surface of the rotor and the inner peripheral surface of the cylinder in the ellipse short-axis direction of the elliptical cylinder is excessively small. Accordingly, there is a possibility that the outer peripheral surface of the rotor and the inner peripheral surface of the cylinder are brought into contact with each other in the ellipse short-axis direction of the elliptical cylinder.
  • a solid lubricant film may be formed by applying by coating a solid lubricant such as polytetrafluoroethylene (hereinafter PTFE) to one or both of the inner peripheral surface of the elliptical cylinder and the outer peripheral surface of the rotor.
  • PTFE polytetrafluoroethylene
  • Patent Literature 1 there is disclosed the structure where a solid lubricant film made of a fluororesin or the like is formed on one or both of an inner peripheral surface of an elliptical cylinder and an outer peripheral surface of a rotor.
  • a thickness of the solid lubricant film is also taken into account in addition to the degree of accuracy of shapes of respective parts and hence, irregularities in clearance between the inner peripheral surface of the cylinder and the outer peripheral surface of the rotor become relatively large. Accordingly, a specific controlling process is adopted in general where in conformity with an actually measured size of one of the inner peripheral surface of the cylinder and the outer peripheral surface of the rotor, the other is machined such that the clearance takes a proper value thus controlling the clearance (hereinafter "matching process").
  • a solid lubricant film which is formed on the outer peripheral surface of the rotor in an initial stage has a thickness of approximately 100 ⁇ m including a surplus amount, for example, by taking into account the deformation of the rotor at the time of press-fitting a shaft and the machining allowance. Accordingly, when expensive PTFE is applied by coating as a solid lubricant, there arises a drawback that it is necessary to use a large amount of PTFE although the PTFE is to be removed in machining process.
  • a vane-type compressor includes: a housing which has a suction opening and a discharge opening, and forms an outer shell; a cylinder which is integrally formed with the housing or is formed as a body separate from the housing, and has a complete round inner peripheral surface; a complete round rotor which is housed in the cylinder such that the center of the rotor is arranged at a position offset from the center of the cylinder; vane grooves which open on an outer peripheral surface of the rotor; vanes which are housed in the vane grooves in an extensible and retractable manner while being brought into slide contact with the inner peripheral surface of the cylinder; a shaft which is combined with the rotor by being press-fitted into the rotor thus forming a rotor assembly and transmits power from the outside to the rotor; and bearing portions which are provided in the housing and rotatably supports the shaft, and the vane-type compressor is characterized in that a solid lubricant film is formed on the outer peripheral surface of the rot
  • the vane-type compressor is characterized in that a clearance between the rotor assembly and the cylinder is controlled by machining only the inner peripheral surface of the cylinder based on a size of a predetermined position of the rotor assembly.
  • a clearance between the rotor assembly and the cylinder is controlled by machining only the inner peripheral surface of the cylinder based on a size of a predetermined position of the rotor assembly.
  • PTFE or the like is used as a solid lubricant.
  • a solid lubricant film is formed by applying a solid lubricant or the like by coating.
  • the cylinder having the complete round inner peripheral surface is used and hence, it is possible to apply matching process by machining the inner peripheral surface of the cylinder with a lathe. Accordingly, it becomes unnecessary to machine the outer peripheral surface and the side surface of the rotor for the matching process by grinding, and also it becomes unnecessary to apply by coating a surplus solid lubricant to the rotor assembly by taking into account machining allowance and hence, a coating amount of a solid lubricant can be relatively decreased.
  • the vane-type compressor is constituted of the cylinder having the complete round inner peripheral surface and the complete round rotor which is housed in the cylinder such that the center of the rotor is arranged at a position offset from the center of the cylinder and hence, the rotor is always pushed toward a side opposite to a top dead center due to a pressure in the cylinder. Therefore, even when a clearance between the shaft and the bearing portion is large, there is no possibility that the rotor assembly vibrates.
  • the clearance can be controlled to a proper value by only applying matching process to the inner peripheral surface of the cylinder based on a numerical value from one point on the outer peripheral surface of the rotor to an outer peripheral surface of the shaft on a side opposite to a side where the point on the outer peripheral surface of the rotor exists.
  • the vane-type compressor according to the present invention is characterized in that a solid lubricant film is also formed on either side surface of the rotor on which a through hole into which the shaft is inserted opens, and the rotor assembly is housed in the cylinder also without applying machining process to the solid lubricant film on the side surface of the rotor.
  • a solid lubricant film is also formed on either side surface of the rotor on which a through hole into which the shaft is inserted opens, and the rotor assembly is housed in the cylinder also without applying machining process to the solid lubricant film on the side surface of the rotor.
  • the vane-type compressor according to the present invention is characterized in that a thickness of the solid lubricant film of the rotor falls within a range from 10 ⁇ m to 20 ⁇ m.
  • An optimal thickness of the solid lubricant film is 15 ⁇ m, for example.
  • the vane-type compressor according to the present invention is characterized in that a plain bearing is used as a bearing of each bearing portion. Due to such a constitution, compared to a case where a needle bearing is used as a bearing portion, a relatively large clearance between the bearing portion and the shaft can be allowable. Further, unlike the case where the needle bearing is used as the bearing portion, the direct measurement becomes possible when the position of one point on the bearing portion positioned on a side opposite to one point positioned on the inner peripheral surface of the cylinder is measured.
  • the vane-type compressor according to the present invention is characterized in that a side block which constitutes the housing is integrally formed with the cylinder.
  • a side block which constitutes the housing is integrally formed with the cylinder.
  • the vane-type compressor according to the present invention is characterized in that a recessed portion which is indented in the axial direction of the through hole is formed on the side surface of the rotor around an opening periphery of the through hole. Due to such a constitution, the recessed portion can be utilized as an area where it is unnecessary to take into account sliding or interference with a part which faces the recessed portion.
  • matching process can be applied by machining the inner peripheral surface of the cylinder with a lathe. Therefore, unlike a conventional case where matching process is performed on a rotor assembly side by grinding an outer peripheral surface and a side surface of a rotor, matching process can be performed on a cylinder side. Accordingly, it is enough for the solid lubricant film formed on the rotor assembly to have a minimum thickness and hence, it is unnecessary to apply a surplus solid lubricant to the rotor assembly by coating whereby a coating amount of the solid lubricant can be relatively decreased. Thus, a manufacturing cost of the vane-type compressor can be reduced.
  • the solid lubricant film formed on the rotor assembly can surely have the thickness which falls within a range from 10 ⁇ m to 20 ⁇ m, and more preferably a thickness of 15 ⁇ m.
  • a solid lubricant can be applied by coating to both the outer peripheral surface and the side surface of the rotor simultaneously and hence, an operation of applying a solid lubricant to the rotor by coating can be performed efficiently and rapidly.
  • a needle bearing is used as a bearing portion
  • the direct measurement becomes possible at the time of measuring the position of one point on the inner periphery of the bearing portion.
  • a plain bearing can be used with a relatively large clearance compared to a needle bearing.
  • a needle bearing for controlling a clearance between the bearing portion and the shaft to a predetermined clearance value, it is necessary to perform matching process with respect to an outer diameter of the shaft in conformity with an inner diameter of the bearing portion.
  • the side block is integrally formed with the cylinder as described in Claim 5, by performing matching process such that the bottom surface of the cylinder (corresponding to the side surface of the rotor) is made to match with a length of the rotor after the formation of the solid lubricant film, a thrust clearance between the rear side block and the rotor can be also easily controlled.
  • the indented recessed portion is formed on the side surface of the rotor around an opening periphery of the through hole into which the shaft is inserted and hence, this recessed portion can be used as an area where it is unnecessary to take into account sliding or interference with a part which faces the recessed portion.
  • the recessed portion formed on the side surface of the rotor as a support portion at the time of press-fitting the shaft into the rotor, even when the periphery of the support portion is damaged or bulged due to a press-fitting load, it is unnecessary to take into account slide failure or interference with the side block.
  • Fig. 1a and Fig. 1b are cross-sectional views showing one example of a vane-type compressor according to the present invention, wherein Fig. 1a is a cross-sectional view of the vane-type compressor taken so as to make a discharge opening viewable, and Fig. 1b is a cross-sectional view of the vane-type compressor taken so as to make a suction opening viewable.
  • Fig. 2 is a cross-sectional view taken along a line A-A in Fig. 1b .
  • Fig. 3 is a cross-sectional view with a part broken away showing the internal constitution of the vane-type compressor according to the present invention.
  • Fig. 4a to Fig. 4c are explanatory views showing a rotor assembly which constitutes the vane-type compressor according to the present invention and the constitution of a rotor which constitutes a part of the rotor assembly, wherein Fig. 4a is a perspective view of the rotor assembly, Fig. 4b is a perspective view of the rotor, and Fig. 4c is an explanatory view showing a thickness of a solid lubricant film formed on an outer surface of the rotor.
  • Fig. 5 is an explanatory view showing the reference in setting a clearance between an outer peripheral surface of the rotor and an inner peripheral surface of a cylinder.
  • Fig. 1a to Fig. 4c show one example of a vane-type compressor used in a refrigerating cycle of a vehicle-use air conditioner, for example.
  • the vane-type compressor 1 includes: a shaft 3; a rotor 4 which is fixed to the shaft 3 and is rotated along with the rotation of the shaft 3; and a first housing member 8 and a second housing member 9 which define a compression space 18 described later together with the rotor 4.
  • a housing 2 is constituted of the first housing member 8 and the second housing member 9.
  • a part (A) shown in Fig. 4a formed by assembling the rotor 4 to the shaft 3 is also referred to as a rotor assembly.
  • the first housing member 8 is formed of: a cylinder 8a which houses the rotor 4 therein; and a rear-side block 8b which is positioned on a rear side of the cylinder 8a in the axial direction of the shaft 3, is integrally formed with the cylinder 8a, and closes a rear side of the cylinder 8a.
  • the cylinder 8a may be constituted as a body separate from the rear-side block 8b, that is, the cylinder 8a may not be constituted as a portion of the first housing member 8, and alternatively, the cylinder 8a may be integrally formed with a front-side block 9a.
  • the rotor 4 which is housed in the cylinder 8a is formed into a circular columnar shape having a complete round shape in cross section, and as shown in Fig. 4b , a through hole 4a into which the shaft 3 can be press-fitted is formed at the center P1 of the complete round shape. Further, as shown in Fig. 4b , the rotor 4 includes a plurality of (two in this embodiment) vanes 6 inserted into a plurality of (two in this embodiment) vane grooves 5 which open on an outer peripheral surface of the rotor 4.
  • the vane grooves 5 open not only to the cylinder 8a but also to a front-side block 9a and a rear-side block 8b, and back pressure chambers 5a are defined in bottom portions of the vane grooves 5 which are arranged on a depth side in the slide direction of the vanes 6. Accordingly, the back pressure chambers 5a are also configured to open to the front-side block 9a side and the rear-side block 8b side.
  • the vane 6 slides on an inner peripheral surface of the cylinder 8a in such a manner that side surfaces of the vane 6 slide on inner side surfaces of the vane groove 5, and a distal end of the vane 6 projects from the vane groove 5 in an extensible and retractable manner.
  • a recessed portion 4d formed on a side surface 4c of the rotor 4 is described later.
  • the inner peripheral surface of the cylinder 8a is formed into a complete round shape having an inner diameter size larger than an outer diameter size of the rotor 4.
  • the rotor 4 is housed in the inside of the cylinder 8a in such a manner that the center P2 of the cylinder 8a and the center P1 of the rotor 4 are offset from each other so as to form a minute clearance at one portion in the circumferential direction between the outer peripheral surface of the rotor 4 and the inner peripheral surface of the cylinder 8a (a portion where the cylinder 8a and the rotor 4 approach each other most closely: top dead center P3).
  • An offset amount between the center P2 of the cylinder 8a and the center P1 of the rotor 4 is approximately 1/2 of the difference between the inner diameter size of the cylinder 8a and the outer diameter size of the rotor 4, for example.
  • the rotor 4 is housed in the inside of the cylinder 8a and hence, a compression space 18 is defined between the inner peripheral surface of the cylinder 8a and the outer peripheral surface of the rotor 4.
  • the compression space 18 is divided into a plurality of compression chambers 19 by being partitioned by the vanes 6 which are housed in the plurality of vane grooves 5 formed in the rotor 4, and a volume of each compression chamber 19 is configured to be changed due to the rotation of the rotor 4.
  • the second housing member 9 is an integral body constituted of: the front-side block 9a which is brought into contact with a front-side end surface of the cylinder 8a; and a shell 9b which extends from the front-side block 9a in the axial direction of the shaft 3 and surrounds outer peripheral surfaces of the cylinder 8a and the rear-side block 8b. Further, the second housing member 9 is connected to the first housing member 8 by means of connecting jigs 7 such as bolts.
  • a pulley 20 to which rotational power is transmitted from a power source (not shown in the drawing) of a vehicle by way of a belt (not shown in the drawing) is rotatably and exteriorly mounted on a boss portion 9c which is integrally formed with the front-side block 9a, and rotational power is transmitted to the shaft 3 from the pulley 20 by way of an electromagnetic clutch 21.
  • a suction opening 11 and a discharge opening 12 for a working fluid (refrigerant gas) are formed in the second housing member 9, and the suction opening 11 is communicated with a suction space 14 which is defined by a space portion 14a formed in the second housing member 9 and a recessed portion 14b formed on the cylinder 8a.
  • the shaft 3 is rotatably supported on the front-side block 9a of the second housing member 9 and the rear-side block 8b of the first housing member 8 by way of plain bearings 23, 24 which constitute bearing portions and are held by the front-side block 9a and the rear-side block 8b respectively. Further, at a position in the vicinity of a proximal end of the boss portion 9c of the second housing member 9, a seal member 13 is interposed between the shaft 3 and the inner peripheral surface of the second housing member 9 so as to prevent leaking of a working fluid to the outside from an opening of the boss portion 9c.
  • a suction port 25 which is communicated with the suction space 14 and discharge ports 26 which are communicated with a discharge space 15 are formed on the peripheral surface of the cylinder 8a corresponding to the compression space 18. Accordingly, when the cylinder 8a is fitted into the shell 9b, the suction space 14 is communicated with the compression chamber 19 through the suction port 25, the discharge space 15 whose both end sides are partitioned by flange portions 8c, 8d is formed between the outer peripheral surface of the cylinder 8a and the inner peripheral surface of the shell 9b, and the discharge space 15 is communicable with the compression chamber 19 through the discharge ports 26.
  • the discharge ports 26 is opened or closed by a discharge valve 27 which is housed in the discharge space 15.
  • the discharge space 15 is communicated with an oil separator 16 through a through hole 28 formed in the flange portion 8d. Further, the oil separator 16 is communicated with the discharge opening 12.
  • the working fluid discharged into the discharge space 15 is moved in the circumferential direction along the outer peripheral surface (the inner peripheral surface of the shell 9b) of the cylinder 8a and flows substantially around the periphery of the cylinder 8a and, thereafter, is guided into an oil separation chamber of the oil separator 16 formed in the rear-side block 8b through the through hole 28 formed in the flange potion 8d. Thereafter, oil is separated from the working fluid in the process where the working fluid whirls in the inside of the oil separation chamber of the oil separator 16 and, then, the working fluid is discharged to an external circuit from the discharge opening 12.
  • a solid lubricant film 30 is formed on the outer peripheral surface 4b and the side surface 4c of the rotor 4 shown in Fig. 4b .
  • a solid lubricant for forming the solid lubricant film 30 PTFE is used, for example.
  • a clearance value W between the outer peripheral surface of the rotor 4 and the inner peripheral surface of the cylinder 8a is suitably controlled by a following method as shown in Fig. 5 .
  • a rotor-assembly-side size R identified by the distance from a point S1 positioned on the outer peripheral surface 4b of the rotor 4 to a point S2 positioned at the opposite side of the point S1 on a peripheral surface of the shaft 3 is measured.
  • a value obtained by subtracting a numerical value of the rotor-assembly-side size R from a numerical value of the cylinder-side size C corresponds to a numerical value of the clearance W between the outer peripheral surface of the rotor 4 and the inner peripheral surface of the cylinder 8a during the compressor operation. Accordingly, an optimum numerical value C' (not shown in the drawing) is decided based on the numerical value R and the numerical value C which are measured in advance such that a numerical value of W becomes a preferred value (for example, 20 ⁇ m), and the cylinder 8a is machined for matching process such that a numerical value of the cylinder-side size C which is the size of the cylinder 8a from the point S3 to the point S4 takes such an optimum numerical value C'.
  • the reason why the clearance W can be controlled by applying matching process to the cylinder 8a is that the inner peripheral surface of the cylinder 8a is formed into a complete round shape so that machining process to a cylinder 8a side can be performed using a lathe.
  • the center P1 of the rotor 4 is offset from the center P2 of the cylinder 8a, by holding and rotating the cylinder 8a while chucking the cylinder 8a in an offset manner, the inner peripheral surface of the offset cylinder 8a can be machined by a lathe.
  • the bearing portion in measuring the above-mentioned cylinder-side size C, if the bearing portion were constituted of a needle bearing, a plurality of needles (rollers) would be exposed to an inner peripheral surface of the bearing portion and hence, the point S4 could not be directly measured.
  • the bearing portion is constituted of the plain bearing 24 and hence, the point S4 which becomes the reference can be directly measured.
  • the needle bearing were used as the bearing portion, it would be necessary to control a clearance between an inner diameter of the bearing portion and a shaft within a predetermined clearance range by taking into account reliability of needles. Accordingly, it would be necessary to measure an inner diameter size of an actual bearing portion and, thereafter, to perform matching process for adjusting a machined amount with respect to an outer diameter size of the shaft to acquire a predetermined clearance. In this embodiment, by constituting the bearing portion using the plain bearings 23, 24, a control of the clearance between the bearings 23, 24 and the shaft 3 becomes unnecessary.
  • a thickness L of the solid lubricant film 30 which is formed on the outer peripheral surface and the side surface of the rotor 4 to a thickness of approximately 100 ⁇ m, for example, which includes a surplus thickness by taking into account a machining allowance.
  • the recessed portion 4d which is indented in the axial direction of the through hole 4a is formed on the side surface 4c of the rotor 4 around an opening periphery of the through hole 4a.
  • the recessed portion 4d constitutes a support portion for supporting a press-fitting load in forming the rotor assembly A by press-fitting the shaft 3 into the rotor 4 on which the solid lubricant film 30 is formed.
  • a thickness of the solid lubricant film 30 can be set to a preferred size from the beginning, for example, a size within a range from 10 ⁇ m to 20 ⁇ m (for example, an optimum size of 15 ⁇ m) and hence, a coating amount of the solid lubricant is relatively decreased, and finish working for setting a thickness of the solid lubricant film to a preferred size can be also made unnecessary. Accordingly, a manufacturing cost of the vane-type compressor 1 can be reduced.
  • the first housing member 8 may be an integral body formed of the cylinder 8a and the rear-side block 8b. Due to such constitution, both a thrust clearance and a radial clearance can be continuously formed by machining at a stroke from the cylinder 8a to the rear-side block 8b in accordance with sizes of an actual rotor assembly A. Accordingly, a working time can be shortened. Further, although an error in size is liable to be generated each time a part is held by a tool when the process is divided into steps, a possibility that the errors are generated due to the division of the process into steps is decreased so that the accuracy of the rotor assembly can be enhanced.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)
EP12182075.7A 2011-08-30 2012-08-28 Drehschieber-Kompressor Withdrawn EP2565457A3 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2011187100A JP2013050038A (ja) 2011-08-30 2011-08-30 ベーン型圧縮機

Publications (2)

Publication Number Publication Date
EP2565457A2 true EP2565457A2 (de) 2013-03-06
EP2565457A3 EP2565457A3 (de) 2017-06-14

Family

ID=46880955

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JP6242606B2 (ja) * 2013-06-27 2017-12-06 株式会社ヴァレオジャパン ベーン型圧縮機
CN105649983A (zh) * 2016-01-14 2016-06-08 陈勇翔 一种空气压缩泵
CN108343608B (zh) * 2018-04-26 2024-10-22 广东威灵汽车部件有限公司 压缩机
KR102545597B1 (ko) 2022-01-14 2023-06-21 엘지전자 주식회사 로터리 압축기

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EP2565457A3 (de) 2017-06-14
JP2013050038A (ja) 2013-03-14
CN102966543A (zh) 2013-03-13
BR102012021909A2 (pt) 2013-11-12
CN102966543B (zh) 2016-01-20

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