EP2520802A1 - Structure d'alimentation en huile lubrifiante pour compresseur de type à palette - Google Patents

Structure d'alimentation en huile lubrifiante pour compresseur de type à palette Download PDF

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Publication number
EP2520802A1
EP2520802A1 EP10840783A EP10840783A EP2520802A1 EP 2520802 A1 EP2520802 A1 EP 2520802A1 EP 10840783 A EP10840783 A EP 10840783A EP 10840783 A EP10840783 A EP 10840783A EP 2520802 A1 EP2520802 A1 EP 2520802A1
Authority
EP
European Patent Office
Prior art keywords
back pressure
vane
pressure chamber
recessed portion
lubricating oil
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Withdrawn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
EP10840783A
Other languages
German (de)
English (en)
Other versions
EP2520802A4 (fr
Inventor
Tomoyasu Takahashi
Takanori Teraya
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 EP2520802A1 publication Critical patent/EP2520802A1/fr
Publication of EP2520802A4 publication Critical patent/EP2520802A4/fr
Withdrawn legal-status Critical Current

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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
    • F04C18/34—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
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0818—Vane tracking; control therefor
    • F01C21/0854—Vane tracking; control therefor by fluid means
    • 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
    • F04C29/021—Control systems for the circulation of the lubricant
    • 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
    • F04C29/028—Means for improving or restricting lubricant flow
    • 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
    • F04C2240/50—Bearings
    • F04C2240/52—Bearings for assemblies with supports on both sides
    • 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
    • F04C2240/56—Bearing bushings or details thereof
    • 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
    • F04C2240/60—Shafts
    • F04C2240/605—Shaft sleeves or details thereof

Definitions

  • the present invention relates to a vane-type compressor which is mounted on an air conditioner such as a vehicle-use air conditioner, for example, and more particularly to the structure for supplying lubricating oil to bearings for supporting a drive shaft of the vane-type compressor.
  • a vane-type compressor which includes: a cylinder whose both sides are closed by being sandwiched by blocks; a rotor which is rotatably housed in the cylinder; vanes which slide in a plurality of vane grooves which are formed on the rotor; and a drive shaft which is connected to the rotor and transmits a rotational force from the outside to the rotor, wherein the drive shaft is rotatably supported in the above-mentioned both blocks by way of bearings respectively, and a slide bearing (plain bearing) is used as a kind of the above-mentioned both bearings.
  • a slide bearing plain bearing
  • Patent document 1 JP-A-2007-64163
  • the vane-type compressor disclosed in patent document 1 may adopt the structure where an oil reservoir chamber is provided in the vicinity of one side of a drive shaft in the axial direction, oil delivered from the oil reservoir chamber reaches a drive shaft housing space through an oil supply passage and is supplied to one slide bearing and, thereafter, oil passes through a back pressure chamber and is supplied to the other slide bearing.
  • oil from the oil reservoir chamber is uniformly supplied to both slide bearings, lubrication on either one of these slide bearings becomes insufficient thus giving rise to a possibility that an abnormal sound and wear of the slide bearing are liable to occur.
  • the number of back pressure chambers formed on bottom portions of the vane grooves formed on a rotor becomes small and, eventually, an area of a flow passage which connects areas in the vicinity of front and rear bearings becomes small and hence, an amount of oil supplied to the slide bearing on a side remote from the oil reservoir chamber becomes smaller than an amount of oil supplied to the slide bearing on a side close to the oil reservoir chamber.
  • the vane-type compressor may adopt the structure where lubricating oil is supplied to the slide bearing positioned on a side remote from the oil reservoir chamber through a path other than the back pressure chamber.
  • working for forming the path becomes further necessary so that a manufacturing cost of the vane-type compressor is pushed up.
  • an attempt has been made to limit the number of blocks which constitute a profile of the vane-type compressor to two in order to aim at the reduction of the number of parts for reducing the cost particularly.
  • it becomes further difficult for the vane-type compressor to adopt the structure where oil supply paths are provided in addition to back pressure chambers.
  • a vane-type compressor which includes: a cylinder whose both end surfaces are closed by blocks; a rotor which is housed in the cylinder and on which a plurality of vane grooves are formed; vanes which are housed in the vane grooves formed on the rotor, allow side surfaces thereof to slide on inner surfaces of the vane grooves, allow distal ends thereof to project from the vane grooves and to slide on an inner peripheral surface of the cylinder; back pressure chambers formed on bottom portions of the vane grooves; a drive shaft which is supported on the blocks by way of respective bearings, is connected to the rotor, and transmits a rotational force from the outside to the rotor; and an oil reservoir chamber in which lubricating oil is temporarily stored, characterized in that the lubricating oil supply structure comprises a lubricating oil path through which the lubricating oil flows, the lubricating oil path being configured such that the
  • the lubricating oil supply structure of a vane-type compressor according to the present invention can acquire advantageous effects of the present invention more effectively when the bearing is a slide bearing such as a plain bearing, for example.
  • the cylinder may be a cylinder whose both end surfaces are closed by a block which is integrally formed with the cylinder and a block which is formed as a separate body from the cylinder, or a cylinder whose both end surfaces are closed respectively by blocks which are formed as separate bodies from the cylinder.
  • opening or closing of the communication state with the back pressure chamber or enlargement or contraction of a communication region with the back pressure chamber is included.
  • the same definition is applicable to a vane-type compressor described hereinafter.
  • the lubricating oil supply structure of a vane-type compressor according to the invention is characterized in that lubricating oil is supplied to the back pressure chamber by making timing at which the communication between the first recessed portion and the back pressure chamber is opened different from timing at which the communication between the second recessed portion and the back pressure chamber is opened and, further, by linking the difference in opening timing between the communication between the first recessed portion and the back pressure chamber and the communication between the second recessed portion and the back pressure chamber and a period during which a stroke amount of the vane is increased to each other.
  • the period during which the stroke amount of the vane is increased and timing at which the communication between the first recessed portion and the back pressure chamber is opened earlier than the communication between the second recessed portion and the back pressure chamber are made to correspond to each other.
  • a volume of the back pressure chamber formed on the bottom portion of the vane groove is enlarged so that a pressure in the back pressure chamber is relatively lowered whereby, at timing at which only the first recessed portion is opened and the period during which a stroke amount of the vane is increased coincide with each other, lubricating oil is supplied to the back pressure chamber from the oil reservoir chamber through the first recessed portion.
  • a vane-type compressor which includes: a cylinder whose both end surfaces are closed by blocks; a rotor which is housed in the cylinder and on which a plurality of vane grooves are formed; vanes which are housed in the vane grooves formed on the rotor, allow side surfaces thereof to slide on inner surfaces of the vane grooves, allow distal ends thereof to project from the vane grooves and to slide on an inner peripheral surface of the cylinder; back pressure chambers formed on bottom portions of the vane grooves; a drive shaft which is supported on the blocks by way of respective bearings, is connected to the rotor, and transmits a rotational force from the outside to the rotor; and an oil reservoir chamber in which lubricating oil is temporarily stored, characterized in that the lubricating oil supply structure comprises a lubricating oil path through which the lubricating oil flows, the lubricating oil path being configured such that
  • the lubricating oil supply structure of a vane-type compressor according to the invention is characterized in that lubricating oil is delivered from the back pressure chamber by making timing at which the communication between the first recessed portion and the back pressure chamber is closed different from timing at which the communication between the second recessed portion and the back pressure chamber is closed and, further, by linking the difference in closing timing between the communication between the first recessed portion and the back pressure chamber and the communication between the second recessed portion and the back pressure chamber and a period during which a stroke amount of the vane is decreased to each other.
  • the period during which the stroke amount of the vane is decreased and timing at which the communication between the first recessed portion and the back pressure chamber is closed earlier than the communication between the second recessed portion and the back pressure chamber are made to correspond to each other.
  • a volume of the back pressure chamber formed on the bottom portion of the vane groove is relatively decreased so that the pressure in the back pressure chamber is relatively increased whereby the timing at which only the second oil groove is opened and the period during which the stroke amount of the vane is decreased coincide with each other, lubricating oil existing in the back pressure chamber is delivered to the second recessed portion side from the back pressure chamber and is supplied to an area in the vicinity of the bearing of the other block.
  • the lubrication oil supply structure of a vane-type compressor according to the invention is characterized in that at least one of the first recessed portion and the second recessed portion is divided into a portion where a depth of the drive shaft in the axial direction is relatively large and a portion where the depth of the drive shaft in the axial direction is relatively small in the lateral widthwise direction of the vane-type compressor, and the communication state with the back pressure chamber is changed by making use of the difference in depth.
  • the recessed portion which is not divided into a portion where a depth of the recessed portion in the axial direction of the drive shaft is relatively large and a portion where the depth of the recessed portion in the axial direction of the drive shaft is relatively small has a depth, over the whole region thereof, equal to the depth of the portion where the depth is relatively large of the recessed portion which is divided into the portion where the depth is small and the portion where the depth is narrow.
  • a flow rate of lubricating oil at the time of delivering lubricating oil to the clearance between the drive shaft and the other block out of the blocks which close the cylinder from the back pressure chamber becomes larger than a flow rate of lubricating oil at the time of supplying lubricating oil to the back pressure chamber from the clearance between the drive shaft and the other block out of the blocks which close the cylinder and hence, the flow rate of lubricating oil delivered to the clearance between the drive shaft and the other block out of the blocks which close the cylinder from the back pressure chamber is increased corresponding to the difference in flow rate.
  • the present invention by setting opening or closing of the communication state with the back pressure chamber or enlargement or contraction of the communication region in conformity with a period of increasing or decreasing a stroke amount of the vane with respect to the first recessed portion and the second recessed portion such that a flow rate of lubricating oil when the lubricating oil is delivered from the back pressure chamber to a clearance formed between the drive shaft and the other block out of the blocks which close the cylinder becomes larger than a flow rate of lubricating oil when the lubricating oil is delivered from the clearance formed between the drive shaft and the other block out of the blocks which close the cylinder to the back pressure chamber, the flow rate of lubricating oil delivered from the back pressure chamber to the clearance formed between the drive shaft and the other block out of the blocks which close the cylinder can be increased corresponding to the difference in flow rate.
  • a volume of the back pressure chamber formed on the bottom portion of the vane groove is enlarged and hence, a pressure in the back pressure chamber is relatively lowered. Accordingly, at timing at which only the first recessed portion is opened and a period during which a stroke amount of the vane is increased coincide with each other, lubricating oil can be supplied to the back pressure chamber from the oil reservoir chamber through the first recessed portion. Further, according to the inventions, during the period where a stroke amount of the vane is decreased, a volume of the back pressure chamber formed on the bottom portion of the vane groove is relatively decreased and hence, a pressure in the back pressure chamber is relatively increased.
  • lubricating oil existing in the back pressure chamber is delivered to the second recessed portion side from the back pressure chamber whereby lubricating oil can be supplied to an area in the vicinity of the bearing of the other block. Accordingly, it is possible to prevent the occurrence of a phenomenon where an abnormal sound is generated or wear is generated in the other bearing due to shortage of lubricating oil to the other bearing and hence, the durability of the bearing, eventually, the durability of the vane-type compressor can be enhanced.
  • a flow rate of lubricating oil at the time of delivering lubricating oil to the clearance between the drive shaft and the other block out of the blocks which close the cylinder from the back pressure chamber becomes larger than a flow rate of lubricating oil at the time of supplying lubricating oil to the back pressure chamber from the clearance between the drive shaft and the other block out of the blocks which close the cylinder and hence, the flow rate of lubricating oil delivered to the clearance between the drive shaft and the other block out of the blocks which close the cylinder from the back pressure chamber is increased corresponding to the difference in flow rate.
  • Fig. 1 to Fig. 6 show the overall constitution or partial constitutions of one example of an embodiment 1 of a vane-type compressor to which the lubricating oil supply structure according to the present invention is applicable.
  • the vane-type compressor 1 is suitable for a refrigerating cycle where, for example, a refrigerant is used as a working fluid, and is used in a vehicle-use air conditioner or the like. Further, as shown in Fig. 1 , the vane-type compressor 1 is of a 2 block type where the vane-type compressor 1 includes a drive shaft 2, a rotor 3 which is fixed to the drive shaft 2 and is movable along with the rotation of the drive shaft 2, and a block 5 and a block 6 which define a compression space 4 described later together with the rotor 3, wherein a housing which houses the drive shaft 2, the rotor 3 and the like is also constituted of the block 5 and the block 6.
  • the block 6 is formed of a cylinder 6a for housing the rotor 3, and a rear-side block 6b which is positioned on a rear side of the cylinder 6a in the axial direction of the drive shaft 2 and is integrally formed with the cylinder 6a.
  • the cylinder 6a is opened on a block 5 side, and includes a cylinder hole 6c which is closed by connecting the cylinder 6a and the block 5.
  • the block 5 is constituted of a front-side block 5a which is brought into contact with a front-side end surface of the cylinder 6a which is positioned on a front side of the cylinder 6a in the axial direction of the drive shaft 2, and a shell 5b which extends from the front-side block 5a in the axial direction of the drive shaft 2, and surrounds outer peripheral surfaces of the cylinder 6a and the rear-side block 6b of the block 6.
  • the block 5 is connected to the block 6 by way of connecting jigs 7 such as bolts.
  • a plurality of O rings 11 are fixedly mounted with favorable air tightness in an interposed manner between the shell 5b of the block 5 and the outer peripheral surfaces of the cylinder 6a and the rear-side block 6b of the block 6.
  • a boss portion 5c which extends to a side opposite to the shell 5b along the axial direction of the drive shaft 2 from the front-side block 5a is formed on the block 5.
  • a pulley (not shown in the drawing) for transmitting rotational power to the drive shaft 2 is rotatably and exteriorly mounted on the boss portion 5c, and rotational power is transmitted to the drive shaft 2 from the pulley by way of an electromagnetic clutch (not shown in the drawing).
  • the rotor 3 is rotatably housed in the cylinder hole 6c formed in the cylinder 6a of the block 6, and is constituted of a rotor body 3a which is fixed to the drive shaft 2, and a plurality of (two in this embodiment) vanes 9 inserted into a plurality of (two in this embodiment) vane grooves 8 formed on the rotor body 3a.
  • the vane grooves 8 open not only in the cylinder hole 6c of the block 6 but also on a front-side block 5a side of the block 5 and a rear-side block 6b side of the block 6, and back pressure chambers 10 are formed to face the bottom portions of the vanes 9 which constitute a depth side in the slide direction.
  • the back pressure chambers 10 also open on the front-side block 5a side of the block 5 and the rear-side block 6b side of the block 6.
  • Side surfaces of the vane 9 slide on inner side surfaces of the vane groove 8, and a distal end of the vane 9 projects from the vane groove 8 in an extensible and retractable manner and slides on an inner peripheral surface of the cylinder 6a.
  • a projection amount of the vane 9 from the vane groove 8 is defined as a stroke amount.
  • the drive shaft 2 is rotatably supported on the front-side block 5a of the block 5 and the rear-side block 6b of the block 6 by way of plain bearings 12, 13 respectively.
  • the bearings are not limited to the plain bearings 12, 13.
  • a seal member 14 is interposed between the drive shaft 2 and an inner peripheral surface of the block 5 so that leaking of a working fluid to the outside from an opening of the boss portion 5c can be prevented.
  • a inlet 16 and a outlet 17 for a working fluid are formed in the block 5, and a space portion 18 which is positioned on an inner side with respect to the inlet 16 in the radial direction of the drive shaft 2 is formed in the block 5.
  • a suction space (low pressure space) 15 is defined by the space portion 18 and a recessed portion 22 which is formed on the cylinder 6a of the block 6 and opens on a block 5 side.
  • a discharge space (high pressure space) 24 is defined by the cylinder 6a of the block 6 and the shell 5b of the block 5, and the discharge space 24 is communicated with the outlet 17.
  • an oil separator 25 is arranged between the discharge space 24 and the outlet 17, and oil separated from a working fluid by the oil separator 25 is temporarily stored in an oil reservoir chamber 19 described later.
  • the rotor body 3a of the rotor 3 and the cylinder hole 6c of the cylinder 6a have a complete circular shape as shown in Fig. 3A , Fig. 4A , Fig. 5A , and Fig. 6A , as viewed in cross section where an end surface of the rotor body 3a is observed through an opening of the cylinder hole 6c by cutting the cylinder 6a in the radial direction of the drive shaft 2.
  • the rotor body 3a is housed in the cylinder hole 6c in a state where an axis P1 of the rotor body 3a is displaced toward the inlet 16 and the outlet 17 side from the center P2 of the cylinder hole 6c. This displacement is 1/2 of the difference between an inner diameter size of the cylinder hole 6c and an outer diameter size of the rotor body 3a, for example.
  • an outer peripheral surface of the rotor body 3a is brought into contact with an inner peripheral surface of the cylinder hole 6c with a minute gap therebetween within a predetermined range at one portion in the circumferential direction thus defining a compression space 4 between the outer peripheral surface of the rotor body 3a and the cylinder hole 6c.
  • the compression space 4 is divided into a plurality of compression chambers 21 by being partitioned by the vanes 9. A volume of each compression chamber 21 is configured to be changed due to the rotation of the rotor 3.
  • the discharge port which is communicated with the discharge space 24 is formed in the inner peripheral surface of the cylinder hole 6c. Accordingly, when the cylinder 6a of the block 6 is fitted into the shell 5b of the block 5, between the outer peripheral surface of the cylinder 6a and the inner peripheral surface of the shell 5b, the discharge space 24 which is defined by flanges 26, 27 whose both end portions project from both ends of the cylinder 6a in the axial direction of the drive shaft 2 in the radial direction of the drive shaft 2 is formed, and the discharge space 24 is communicable with the compression space 4 through the discharge port.
  • the discharge port is opened or closed by a discharge valve (not shown in the drawing) which is housed in the discharge space 24.
  • a suction operation, a compression operation and a discharge operation of a working fluid in the vane-type compressor 1 become as follows. That is, when rotational power from a power source not shown in the drawing is transmitted to the drive shaft 2 by way of a pulley and an electromagnetic clutch so that the rotor 3 is rotated, a working fluid which flows into the suction space 15 through the inlet 16 is sucked into the compression space 4 through the suction port.
  • a volume of the compression chamber 21 partitioned by the vanes 9 in the compression space 4 is changed due to the rotation of the rotor 3 and hence, the working fluid which is confined between the vane 9 and the vane 9 is compressed, and is delivered into the discharge space 24 from the discharge port not shown in the drawing through a discharge valve not shown in the drawing.
  • the working fluid delivered into the discharge space 24 is moved in the circumferential direction along the outer peripheral surface of the cylinder 6a and, thereafter, oil is separated from the working fluid by the oil separator 25 and, thereafter, the working fluid is delivered to an external circuit from the outlet 17.
  • the vane-type compressor 1 further includes the lubricating oil supply structure for supplying oil in the oil reservoir chamber 19 to the plain bearings 12, 13 as a lubricant.
  • the oil reservoir chamber 19 constitutes a starting point
  • a communication passage 30 which connects the drive shaft housing space 29 for housing the drive shaft 2 in the rear-side block 6b of the block 6 and the oil reservoir chamber 19 is formed in the rear-side block 6b of the block 6.
  • a downstream-side opening of the communication passage 30, in this embodiment, opens below an end portion of the drive shaft 2 or below a front side of the end portion of the drive shaft 2 in the drive shaft housing space 29.
  • the drive shaft housing space 29 is a hole which extends along the axial direction of the drive shaft 2 in the rear-side block 6b of the block 6 while surrounding an outer periphery of the drive shaft 2, and an inner diameter size of a main portion of the drive shaft housing space 29 is set approximately equal to an outer diameter size of the structure in a state where the plain bearing 13 is mounted on the drive shaft 2.
  • the above-mentioned plain bearing 13 is mounted on the rear-side block 6b.
  • the lubricating oil supply structure is provided with a drive shaft housing space 31 for housing the drive shaft 2 in the front-side block 5a of the block 5.
  • the drive shaft housing space 31 is a hole which extends along the axial direction of the drive shaft 2 in the front-side block 5a of the block 5 while surrounding the outer periphery of the drive shaft 2, and the drive shaft housing space 31 reaches an opening of the boss portion 5c, and includes a seal chamber 32 which houses the seal member 14 in a middle portion thereof.
  • An inner diameter size of a portion of the drive shaft housing space 31 behind the seal chamber 32 is set approximately equal to an outer diameter size of the structure in a state where the plain bearing 12 is mounted on the drive shaft 2.
  • the above-mentioned plain bearing 12 is mounted on the front-side block 5a at a portion of the drive shaft housing space 31 behind the seal chamber 32.
  • the plain bearings 12, 13 are formed of a cylindrical body, and an inner diameter size of the plain bearing 12, 13 is set slightly larger than an outer diameter size of the drive shaft 2. Accordingly, when the plain bearings 12, 13 are mounted on the blocks 5, 6, as shown in Fig. 3B , Fig. 4B , Fig. 5B and Fig. 6B , lubricating oil supply passages 33, 34 having a circular annular shape are formed between the outer peripheral surface of the drive shaft 2 and inner peripheral surfaces of the plain bearings 12, 13.
  • lubricating oil supply passages 33, 34 are, as described in detail later, communicable with each other through a first recessed portion 36, a second recessed portion 37, and the back pressure chambers 10 which are defined by a bottom portion side of the vane grooves 8.
  • the first recessed portion 36 is positioned in front of the plain bearing 13 in the axial direction of the drive shaft 2 (rotor 3 side) with respect to the drive shaft housing space 29 formed in the rear-side block 6b of the block 6, and is formed continuously with the drive shaft housing space 29, while the second recessed portion 37 is positioned behind the plain bearing 13 in the axial direction of the drive shaft 2 (rotor 3 side) with respect to the drive shaft housing space 31 formed in the front-side block 5a of the block 5, and is formed continuously with the drive shaft housing space 31.
  • the first recessed portion 36 and the second recessed portion 37 are formed on the rear-side block 6b of the block 6 or the front-side block 5a of the block 5.
  • the first recessed portion 36 and the second recessed portion 37 have the same shape, and take the positional relationship where the first recessed portion 36 and the second recessed portion 37 are displaced from each other due to the rotation at a predetermined angle using the axis P1 of the drive shaft 2 as the center of rotation.
  • the second recessed portion 37 has a shape which directly uses a circular line L1 forming a circular opening edge of the drive shaft housing space 31 as an inner edge thereof and expands outwardly in the radial direction of the drive shaft 2 from the circular line L1.
  • This second recessed portion 37 has a communication state forming portion 37a which has a relatively large size in the radial direction of the drive shaft 2 and a communication state forming non-corresponding portion 37b which has a smaller size in the radial direction of the drive shaft 2 than the communication state forming portion 37a.
  • a size of an arcuate line L2 which forms an arcuate outer edge of the communication state forming portion 37a is set approximately equal to a size of a bottom surface position of the vane 9 when the vane 9 takes a minimum stroke amount, for example.
  • a size of an arcuate line L3 which forms an arcuate outer edge of the communication state forming non-corresponding portion 37b is set to a size smaller than a size of a position of a drive shaft 2 side of the back pressure chamber 10. That is, the size of the arcuate line L3 which forms the arcuate outer edge of the communication state forming non-corresponding portion 37b is set to a size which prevents the communication between the back pressure chamber 10 and the second recessed portion 37. Further, in this embodiment, both ends of the arcuate line L2 and both ends of the arcuate line L3 are contiguously connected with each other by straight lines L4, L5 which extend radially from the axis P1 of the drive shaft 2.
  • the first recessed portion 36 has a shape which directly uses a circular line L1 forming a circular opening edge of the drive shaft housing space 29 as an inner edge thereof and expands outwardly in the radial direction of the drive shaft 2 from the circular line L1, and also has a communication state forming portion 37a and a communication state forming non-corresponding portion 37b.
  • a size of an arcuate line L2 which forms an arcuate outer edge of the communication state forming portion 36a is set approximately equal to a size of a bottom surface position of the vane 9 when the vane 9 takes a minimum stroke amount, for example.
  • a size of an arcuate line L3 which forms an arcuate outer edge of the communication state forming non-corresponding portion 36b is set to a size smaller than a size of a position of a drive shaft 2 side of the back pressure chamber 10. That is, the size of the arcuate line L3 which forms the arcuate outer edge of the communication state forming non-corresponding portion 36b is set to a size which prevents the communication between the back pressure chamber 10 and the first recessed portion 36.
  • both ends of the arcuate line L2 and both ends of the arcuate line L3 of the communication state forming non-corresponding portion 36b are contiguously connected with each other by two straight lines L4, L5 which extend radially from the axis P1 of the drive shaft 2.
  • a point referred to as X2 is provided in front of a point X1 in the rotational direction of the rotor 3 where an outer peripheral surface of the rotor body 3a of the rotor 3 and an inner peripheral surface of the cylinder hole 6c are brought into contact with each other with a minimum clearance therebetween, and straight lines L5, S1 are formed such that the back pressure chamber 10 formed on the bottom portion of the vane groove 8 is positioned on a boundary line between the communication state forming portion 36a and the communication state forming non-corresponding portion 36b of the first recessed portion 36 when a distal end of the vane 9 is positioned at the point X2.
  • the positional relationship is set such that a boundary line S2 of the second recessed portion is further displaced by a predetermined angle in the advancing direction along the rotational direction of the rotor body 3a.
  • the back pressure chamber 10 is, as shown in Fig. 3 , within a range from the extension S1 to the extension S2, communicated with the communication state forming portion 36a with respect to the first recessed portion 36.
  • the back pressure chamber 10 is closed by the communication state forming non-corresponding portion 36b and, thereafter, as shown in Fig.
  • the back pressure chamber 10 goes beyond the extension S2 so that the back pressure chamber 10 is brought into a state where the back pressure chamber 10 is communicated with both the first recessed portion 36 and the second recessed portion 37 through the communication state forming portions 36a, 37a.
  • the first recessed portion 36 firstly assumes an open state where the back pressure chamber 10 is communicated with only the communication state forming portion 36a of the first recessed portion 36 and, thereafter, the back pressure chamber 10 is communicated also with the communication state forming portion 37a of the second recessed portion 37 so that the second recessed portion 37 is also brought into an open state.
  • lubricating oil supplied to the communication passage 30 and the drive shaft housing space 29 from the oil reservoir chamber 19 passes through the lubricating oil supply passage 34 between the plain bearing 13 and the drive shaft 2 and, thereafter, can surely reach the back pressure chamber 10 through the communication state forming portion 36a of the first recessed portion 36.
  • a point referred to as X3 is provided behind the contact point X1 in the rotational direction of the rotor 3 where the outer peripheral surface of the rotor body 3a of the rotor 3 and the inner peripheral surface of the cylinder hole 6c are brought into contact with each other, and straight lines L4, S4 are formed such that the back pressure chamber 10 formed on the bottom portion of the vane groove 8 is positioned on a boundary line between the communication state forming portion 37a and the communication state forming non-corresponding portion 37b of the second recessed portion 37 when the distal end of the vane 9 is positioned at the point X3.
  • the positional relationship is set such that a boundary line S3 of the first recessed portion is further displaced by a predetermined angle in the advancing direction along the rotational direction of the rotor body 3a.
  • the back pressure chamber 10 of the vane 9 is, as shown in Fig.
  • the back pressure chamber 10 is firstly closed by the communication state forming non-corresponding portion 36b with respect to the first recessed portion 36. Accordingly, the back pressure chamber 10 is, after the communication state with the first recessed portion 36 is closed, closed by the communication state forming non-corresponding portion 37b also with respect to the second recessed portion 37 and hence, the communication state with the second recessed portion 37 is also closed.
  • a stroke amount of the vane 9 positioned behind the contact point X1 is decreased and hence, a volume of the back pressure chamber 10 is decreased whereby a pressure in the back pressure chamber 10 is relatively increased compared to a pressure outside the back pressure chamber 10. Accordingly, at least lubricating oil in the back pressure chamber 10 can surely reach the plain bearing 12 through the communication state forming portion 37a of the second recessed portion 37.
  • Fig. 7 to Fig. 14 show the partial constitutions of plural examples of an embodiment 2 of the vane-type compressor 1 to which the lubricating oil supply structure according to the present invention is applicable.
  • the first example to the third example of the embodiment 2 of the vane-type compressor are explained in conjunction with Fig. 7 to Fig. 14 .
  • the overall constitution of the vane-type compressor 1 is substantially equal to the constitution shown in Fig. 1 of the previously-mentioned embodiment 1 and hence, the overall constitution of the vane-type compressor 1 is not shown in the drawing, and the explanation of the overall constitution is also omitted.
  • the explanation is made basically with respect to a first recessed portion 36 and a second recessed portion 37 which differ from the corresponding parts of the embodiment 1, and the common constitutions with the embodiment 1 are given the same symbols and the explanation of the common constitutions is omitted.
  • Fig. 7 to Fig. 10 the first example of the embodiment 2 of the vane-type compressor 1 to which the lubricating oil supply structure according to the present invention is applicable is shown.
  • the second recessed portion 37 described in the first example of the embodiment 2 is formed in the front-side block 5a of the block 5, and is positioned behind the plain bearing 13 in the axial direction of the drive shaft 2 (rotor 3 side) with respect to the drive shaft housing space 31 formed in the front-side block 5a of the block 5, and is formed continuously with the drive shaft housing space 31. Further, as shown in Fig.
  • the second recessed portion 37 has a shape where a circular line L1 forming a circular opening edge of the drive shaft housing space 31 is directly used as an inner edge of the second recessed portion 37 and a circular line L6 which is concentric with the circular line L1 is used as an outer edge so that the second recessed portion 37 expands outwardly in the radial direction of the drive shaft 2 from the circular line L1 over the whole circumference with a substantially same size.
  • a size of the circular line L6 which forms a circumferential outer edge of the second recessed portion 37 has the approximately same size as a bottom surface position of the vane 9 when the vane 9 takes a minimum stroke amount, for example.
  • the second recessed portion 37 has, as shown in Fig. 7 , Fig. 9 and Fig. 10 , a deep recessed portion 37c and a shallow recessed portion 37d.
  • the deep recessed portion 37c and the shallow recessed portion 37d are, as shown in Fig. 9A and Fig. 10A , partitioned by two boundary lines S5, S6 which extend along a straight line which passes both the axis P1 of the rotor body 3a and the center P2 of the cylinder hole 6c with respect to the second recessed portion 37, wherein a depth of the deep recessed portion 37c in the axial direction of the drive shaft is set larger than a depth of the shallow recessed portion 37d in the axial direction of the drive shaft.
  • the first recessed portion 36 described in the first example of the embodiment 2 is formed on the rear-side block 6b of the block 6, and is positioned in front of the plain bearing 13 in the axial direction of the drive shaft 2 (rotor 3 side) with respect to the drive shaft housing space 29 formed in the rear-side block 6a, and is formed continuously with the drive shaft housing space 29. Further, as shown in Fig.
  • the first recessed portion 36 has a shape where a circular line L1 forming a circular opening edge of the drive shaft housing space 29 is directly used as an inner edge of the first recessed portion 36 and a circular line L6 which is concentric with the circular line L1 is used as an outer edge so that the first recessed portion 36 expands outwardly in the radial direction of the drive shaft 2 from the circular line L1 over the whole circumference with a substantially same size.
  • a size of the circular line L6 which forms a circumferential outer edge of the first recessed portion 36 has the approximately same size as a bottom surface position of the vane 9 when the vane 9 takes a minimum stroke amount, for example.
  • a depth of the first recessed portion 36 in the axial direction of the drive shaft is uniform over the whole region. Further, the depth of the first recessed portion 36 is set equal to the depth of the deep recessed portion 37c of the second recessed portion 37 in the axial direction of the drive shaft. Due to such a constitution, even when an opening of the back pressure chamber 10 on a rear-side block 6b side faces any range of the first recessed portion 36 in an opposed manner, a communication region where lubricating oil passes through the first recessed portion 36 is brought into a relatively expanded state.
  • Fig. 9A and Fig. 10A assume a point at which the boundary line S5 and an inner peripheral surface of the cylinder hole 6c intersects with each other as X5 and a point at which the boundary line S6 and the inner peripheral surface of the cylinder hole 6c intersects with each other as X6, and assume the rotational direction of the rotor 3 as "counterclockwise" as indicated by an arrow in Fig. 9A and Fig. 10A which show a state of the vane-type compressor 1 as viewed from a front side and the rotational direction of the rotor 3 as "clockwise” as indicated by an arrow in Fig. 9C and Fig.
  • the second recessed portion 37 is communicated with the back pressure chamber 10 through the shallow recessed portion 37d and hence, the communication region between the second recessed portion 37 and the back pressure chamber 10 is relatively decreased whereby the back pressure chamber 10 mainly receives the supply of lubricating oil from the first recessed portion 36 as indicated by an arrow which expresses an amount of lubricating oil which is supplied to the back pressure chamber 10 from the lubricating oil supply passage 33 shown in Fig. 9B and by an arrow which expresses an amount of lubricating oil which is supplied to the back pressure chamber 10 from the lubricating oil supply passage 34 shown in Fig. 9B .
  • the timing at which the opening of the other back pressure chamber 10 on a front-side block 5a side and the deep recessed portion 37c of the second recessed portion 37 face each other in an opposed manner and the period during which a stroke amount of the vane 9 is decreased coincide with each other. Accordingly, as shown in Fig. 10B , as the vane 9 slides in the vane groove 8 in the direction that the stroke amount of the vane 9 is decreased, a volume of the back pressure chamber 10 is decreased so that pressure in the back pressure chamber 10 becomes relatively higher than pressure in lubricating oil supply passages 33, 34 whereby lubricating oil is delivered to the lubricating oil supply passages 33, 34 from the back pressure chamber 10.
  • the second recessed portion 37 is communicated with the back pressure chamber 10 through the deep recessed portion 37c and hence, the communication region between the second recessed portion 37 and the back pressure chamber 10 is relatively enlarged whereby the back pressure chamber 10 uniformly delivers lubricating oil to the first recessed portion 36 and the second recessed portion 37 as indicated by an arrow which expresses an amount of lubricating oil to the lubricating oil supply passage 33 shown in Fig. 10B and by an arrow which expresses an amount of lubricating oil to the lubricating oil supply passage 34 shown in Fig. 10B .
  • a flow rate of lubricating oil supplied to the back pressure chamber 10 from the lubricating oil supply passage 33 through the second recessed portion 37 is smaller than a flow rate of lubricating oil supplied to the lubricating oil supply passage 33 from the back pressure chamber 10 through the second recessed portion 37 and hence, as viewed in a comprehensive manner, it is possible to increase a flow rate of lubricating oil supplied to the lubricating oil supply passage 33 from the back pressure chamber 10.
  • Fig. 11 to Fig. 12 a second example of the embodiment 2 of the vane-type compressor 1 to which the lubricating oil supply structure according to the present invention is applicable is shown.
  • a second recessed portion 37 shown in the second example of the embodiment 2 has, as shown in Fig. 11A and Fig. 12A , the same constitution as the above-mentioned first example of the embodiment 2, while a first recessed portion 36 shown in the second example of the embodiment 2 has, as shown in Fig. 11C and Fig. 12C , a deep recessed portion 37c and a shallow recessed portion 37d. Accordingly, the explanation of the second recessed portion 37 is omitted by giving the same symbol as the first example of the embodiment 2, and the explanation is made only with respect to the first recessed portion 36 hereinafter.
  • a position where the first recessed portion 36 is formed and the like are equal to those of the first example of the embodiment 2 and hence, their explanation is omitted.
  • the first recessed portion 36 has a shape where a circular line L1 forming a circular opening edge of the drive shaft housing space 31 is directly used as an inner edge of the first recessed portion 36 and a circular line L6 which is concentric with the circular line L1 is used as an outer edge so that the first recessed portion 36 expands outwardly in the radial direction of the drive shaft 2 from the circular line L1 over the whole circumference with a substantially same size.
  • a size of the circular line L6 which forms a circumferential outer edge of the first recessed portion 36 has the approximately same size as a bottom surface position of the vane 9 when the vane 9 takes a minimum stroke amount, for example.
  • the deep recessed portion 36c and the shallow recessed portion 36d which the first recessed portion 36 has are, as shown in Fig. 11C and Fig. 12C , partitioned by two boundary lines S5, S6 which extend along a straight line which passes both the axis P1 of the rotor body 3a and the center P2 of the cylinder hole 6c with respect to the first recessed portion 36, wherein a depth of the deep recessed portion 36c in the axial direction of the drive shaft is set larger than a depth of the shallow recessed portion 36d in the axial direction of the drive shaft.
  • Fig. 12A and Fig. 12C assume a point at which the boundary line S5 and an inner peripheral surface of the cylinder hole 6c intersects with each other as X5 and a point at which the boundary line S6 and the inner peripheral surface of the cylinder hole 6c intersects with each other as X6, and assume the rotational direction of the rotor 3 as "counterclockwise" as indicated by an arrow in Fig. 11A and Fig. 12A which show a state of the vane-type compressor 1 as viewed from a front side and the rotational direction of the rotor 3 as "clockwise” as indicated by an arrow in Fig. 11C and Fig.
  • the back pressure chamber 10 mainly receives the supply of lubricating oil from the first recessed portion 36 as indicated by an arrow which expresses an amount of lubricating oil which is supplied to the back pressure chamber 10 from the lubricating oil supply passage 33 shown in Fig. 11B and by an arrow which expresses an amount of lubricating oil which is supplied to the back pressure chamber 10 from the lubricating oil supply passage 34 shown in Fig. 11B .
  • the timing at which the opening of the other back pressure chamber 10 on a front-side block 5a side and the deep recessed portion 37c of the second recessed portion 37 face each other in an opposed manner and the period during which a stroke amount of the vane 9 is decreased coincide with each other, and the timing at which the opening of the other back pressure chamber 10 on a rear-side block 6b side and the shallow recessed portion 36d of the first recessed portion 36 face each other in an opposed manner and the period during which a stroke amount of the vane 9 is decreased coincide with each other. Accordingly, as shown in Fig.
  • a volume of the back pressure chamber 10 is decreased so that pressure in the back pressure chamber 10 becomes relatively higher than pressure in the lubricating oil supply passages 33, 34 whereby lubricating oil is delivered to the lubricating oil supply passages 33, 34 from the back pressure chamber 10.
  • the back pressure chamber 10 delivers lubricating oil mainly to the second recessed portion 37 as indicated by an arrow which expresses an amount of lubricating oil to the lubricating oil supply passage 33 shown in Fig. 12B and by an arrow which expresses an amount of lubricating oil to the lubricating oil supply passage 34 shown in Fig. 12B .
  • a flow rate of lubricating oil supplied to the lubricating oil supply passage 33 from the back pressure chamber 10 through the second recessed portion 37 is larger than a flow rate of lubricating oil supplied to the lubricating oil supply passage 34 from the back pressure chamber 10 through the first recessed portion 36, and is also larger than a flow rate of lubricating oil supplied to the back pressure chamber 10 from the lubricating oil supply passage 33 through the second recessed portion 37 and hence, as viewed in a comprehensive manner, it is possible to increase a flow rate of lubricating oil supplied to the lubricating oil supply passage 33 from the back pressure chamber 10.
  • Fig. 13 to Fig. 14 the third example of the embodiment 2 of the vane-type compressor 1 to which the lubricating oil supply structure according to the present invention is applicable is shown.
  • a first recessed portion 36 shown in the third example of the embodiment 2 has, as shown in Fig. 13A and Fig. 14A , the same constitution as the above-mentioned second example of the embodiment 2, while the first recessed portion 36 shown in the second example of the embodiment 2 does not have, as shown in Fig. 13C and Fig. 13C , the deep recessed portion 37c and the shallow recessed portion 37d. Accordingly, the explanation of the first recessed portion 36 is omitted by giving the same symbols as the second example of the embodiment 2, and the explanation is made only with respect to the second recessed portion 37 hereinafter.
  • a position where the second recessed portion 37 is formed and the like are equal to the first example and the second example of the embodiment 2 and hence, their explanation is omitted.
  • the second recessed portion 37 has, in the same manner as the first recessed portion 36 shown in Fig. 8 , a shape where a circular line L1 forming a circular opening edge of the drive shaft housing space 31 is directly used as an inner edge of the second recessed portion 37 and a circular line L6 which is concentric with the circular line L1 is used as an outer edge so that the second recessed portion 37 expands outwardly in the radial direction of the drive shaft 2 from the circular line L1 over the whole circumference with a substantially same size.
  • a size of the circular line L6 which forms a circumferential outer edge of the second recessed portion 37 has the approximately same size as a bottom surface position of the vane 9 when the vane 9 takes a minimum stroke amount, for example.
  • a depth of the second recessed portion 37 in the axial direction of the drive shaft is uniform over the whole region. Further, in this third example, the depth of the second recessed portion 37 is set equal to the depth of the deep recessed portion 36c of the first recessed portion 36 in the axial direction of the drive shaft. Due to such a constitution, even when an opening of the back pressure chamber 10 on a front-side block 5a side faces any range of the second recessed portion 37 in an opposed manner, a communication region where lubricating oil passes through the second recessed portion 36 is brought into a relatively expanded state.
  • the first recessed portion 36 is communicated with the back pressure chamber 10 through the deep recessed portion 37c and hence, the communication region between the first recessed portion 36 and the back pressure chamber 10 is relatively enlarged whereby the back pressure chamber 10 receives the supply of lubricating oil uniformly from both the first recessed portion 36 and the second recessed portion 37 as indicated by an arrow which expresses an amount of lubricating oil which is supplied to the back pressure chamber 10 from the lubricating oil supply passage 33 shown in Fig. 13B and by an arrow which expresses an amount of lubricating oil which is supplied to the back pressure chamber 10 from the lubricating oil supply passage 34 shown in Fig. 13B .
  • the timing at which the opening of the other back pressure chamber 10 on a rear-side block 6b side and the shallow recessed portion 36d of the first recessed portion 36 face each other in an opposed manner and the period during which a stroke amount of the vane 9 is decreased coincide with each other. Accordingly, as shown in Fig. 14B , as the vane 9 slides in the vane groove 8 in the direction that the stroke amount of the vane 9 is decreased, a volume of the back pressure chamber 10 is decreased so that pressure in the back pressure chamber 10 becomes relatively higher than pressure in lubricating oil supply passages 33, 34 whereby lubricating oil is delivered to the lubricating oil supply passages 33, 34 from the back pressure chamber 10.
  • the first recessed portion 36 is communicated with the back pressure chamber 10 through the shallow recessed portion 36d and hence, the communication region between the first recessed portion 36 and the back pressure chamber 10 is relatively shrunken whereby the back pressure chamber 10 mainly delivers lubricating oil to the second recessed portion 37 as indicated by an arrow which expresses an amount of lubricating oil to the lubricating oil supply passage 33 shown in Fig. 14B and by an arrow which expresses an amount of lubricating oil to the lubricating oil supply passage 34 shown in Fig. 14B .
  • a flow rate of lubricating oil supplied to the lubricating oil supply passage 34 from the back pressure chamber 10 through the first recessed portion 36 is smaller than a flow rate of lubricating oil supplied to the back pressure chamber 10 from the lubricating oil supply passage 34 through the first recessed portion 36 and hence, as viewed in a comprehensive manner, it is possible to increase a flow rate of lubricating oil supplied to the lubricating oil supply passage 33 from the back pressure chamber 10.
  • the present invention is not always limited to the two-block vane-type compressor 1.
  • the present invention is also applicable to a vane-type compressor which has a cylinder where both sides of the cylinder are closed by being sandwiched by a front-side block and a rear-side block, and the cylinder is provided a separate body from these blocks.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP10840783.4A 2009-12-29 2010-12-28 Structure d'alimentation en huile lubrifiante pour compresseur de type à palette Withdrawn EP2520802A4 (fr)

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JP2009299093 2009-12-29
PCT/JP2010/007589 WO2011080924A1 (fr) 2009-12-29 2010-12-28 Structure d'alimentation en huile lubrifiante pour compresseur de type à palette

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JP5963436B2 (ja) * 2011-12-21 2016-08-03 株式会社ヴァレオジャパン 電動圧縮機
JP5708570B2 (ja) * 2012-06-19 2015-04-30 株式会社豊田自動織機 ベーン型圧縮機
JP6083408B2 (ja) * 2014-03-25 2017-02-22 株式会社豊田自動織機 ベーン型圧縮機
CN109737065B (zh) 2019-02-27 2024-04-16 珠海格力电器股份有限公司 泵体组件、压缩机及空调设备

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CN107701447A (zh) * 2017-09-29 2018-02-16 珠海格力电器股份有限公司 一种压缩机的油路结构和压缩机
WO2019061892A1 (fr) * 2017-09-29 2019-04-04 格力电器（武汉）有限公司 Structure de conduite d'huile de compresseur et compresseur
CN107701447B (zh) * 2017-09-29 2019-08-06 珠海格力电器股份有限公司 一种压缩机的油路结构和压缩机
US11248609B2 (en) 2017-09-29 2022-02-15 Gree Electric Appliances (Wuhan) Co., Ltd Oil line structure of compressor and compressor

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CN102667162A (zh) 2012-09-12
EP2520802A4 (fr) 2016-06-01
BR112012016134A2 (pt) 2016-05-31
JP5707337B2 (ja) 2015-04-30
WO2011080924A1 (fr) 2011-07-07

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