WO2016190380A1 - Compresseur - Google Patents

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Publication number
WO2016190380A1
WO2016190380A1 PCT/JP2016/065538 JP2016065538W WO2016190380A1 WO 2016190380 A1 WO2016190380 A1 WO 2016190380A1 JP 2016065538 W JP2016065538 W JP 2016065538W WO 2016190380 A1 WO2016190380 A1 WO 2016190380A1
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WO
WIPO (PCT)
Prior art keywords
oil
oil storage
compressor
storage spaces
cylinder
Prior art date
Application number
PCT/JP2016/065538
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English (en)
Japanese (ja)
Inventor
秋田　修
Original Assignee
株式会社ヴァレオジャパン
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.)
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Publication date
Application filed by 株式会社ヴァレオジャパン filed Critical 株式会社ヴァレオジャパン
Priority to EP16800084.2A priority Critical patent/EP3336360A4/fr
Publication of WO2016190380A1 publication Critical patent/WO2016190380A1/fr

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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
    • 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
    • F04C29/026—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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • 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
    • F04C18/356—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 outer member
    • F04C18/3562—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 outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
    • F04C18/3564—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 outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • 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
    • 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

Definitions

  • the present invention relates to a compressor including an oil separator and an oil storage chamber for storing lubricating oil separated by the oil separator, and more particularly to a vane type compressor having an improved gas venting structure in the oil storage chamber.
  • lubricating oil is mixed in the refrigerant gas in order to lubricate the sliding parts of the compressor compression mechanism and bearings.
  • the lubricating oil is mixed with the refrigerant gas and compressed.
  • the lubricating oil adheres to the inside of the heat exchanger such as an evaporator or a condenser, and there is a disadvantage that the heat exchange capacity of the heat exchanger is lowered.
  • a centrifugal oil separator that separates the lubricating oil from the working fluid compressed by the compression mechanism is provided, and the separated lubricating oil is compressed.
  • a centrifugal oil separator that separates the lubricating oil from the working fluid compressed by the compression mechanism is provided, and the separated lubricating oil is compressed.
  • a compressor that is stored in an oil storage chamber provided in a lower part of the machine.
  • a centrifugal oil separator is provided in the rear housing, and an oil storage chamber is formed between the fixed side plate of the fixed scroll and the rear housing.
  • the separated lubricating oil is stored in the oil storage chamber.
  • the space between the fixed side plate of the fixed scroll and the rear housing is divided into a discharge chamber located on the upper side by a partition wall suspended from the fixed side plate of the fixed scroll and the bottom wall of the rear housing, and the lower housing. It is divided into an oil storage chamber located on the side.
  • the partition partitioning the discharge chamber and the oil storage chamber is provided curved downward so as to bypass the discharge port opened at the radial center of the fixed side plate of the fixed scroll. For this reason, the upper region of the oil storage chamber is divided into left and right upper expansion regions by a partition wall curved downward.
  • An oil drain hole for dropping the lubricating oil separated by the oil separator is connected to one of the two upper expansion areas.
  • the gas vent passage described above is formed so that the intermediate portion is curved downward with respect to both end portions along the end face of the partition wall of the rear housing. Therefore, when the lubricating oil enters the gas vent passage, Lubricating oil may accumulate in the middle of the extraction passage. Lubricating oil that remains in the middle part blocks the flow of gas through the gas vent passage, and therefore draws the gas in the upper expansion area that is not connected to the oil exhaust hole to the upper expansion area that is connected to the oil exhaust hole. This makes it impossible to effectively use the upper expansion area where the oil drain hole is not connected as an oil storage chamber.
  • This invention is made
  • a compressor includes a compression mechanism that compresses a fluid containing lubricating oil, an oil separator that separates the lubricating oil from the fluid discharged from the compression mechanism, and the oil separation
  • the lubricating oil separated by the separator is stored, and the oil storage chamber including a plurality of oil storage spaces and the lubricating oil separated by the oil separator are supplied to any of the plurality of oil storage spaces
  • the extraction passage is characterized by having an intermediate portion that protrudes upward with respect to the connection points to the plurality of oil storage spaces.
  • a vane type compressor when used as the compressor, a cylinder that is closed by being sandwiched by side members on both sides in the axial direction, and a plurality of vane grooves that are accommodated in the cylinder and formed.
  • a drive shaft that is connected to the rotor and transmits a rotational force from the outside to the rotor, and is provided on one of the side members, and separates the lubricating oil from the working fluid compressed in the compression chamber formed between the vanes.
  • An oil separator and the lubricating oil separated by the oil separator are stored and formed by combining the one side member and the cylinder.
  • An oil storage chamber constituted by two oil storage spaces, an oil discharge hole for supplying lubricating oil separated by the oil separator to one of the two oil storage spaces, and the two oil storage spaces
  • a communication passage that communicates the lower region of the two, and further, a gas vent passage that communicates the upper region of the two oil storage spaces is provided, and the gas vent passage is connected to the two oil storage spaces. It is preferable to have an intermediate portion that is convex upward.
  • the oil storage space in which the oil drain holes are not opened and the oil storage space in which the oil drain holes are opened are the upper side. Since there is a communication through a degassing passage having a convex middle portion, the gas in the oil storage space where the oil drainage hole is not opened is passed through the gas drainage passage. It is possible to withdraw to the oil storage space. Therefore, even in the configuration in which the lubricating oil separated by the oil separator is supplied to only one of the plurality of oil storage spaces via the oil drainage hole, the oil storage space where the oil drainage hole is not opened is used.
  • the lubricating oil is supplied through the communication path that connects the lower region, and it is possible to make the level of the lubricating oil the same in each oil storage space, and any oil storage space stores the lubricating oil. It becomes possible to function effectively as a space.
  • the gas vent passage has an intermediate portion that protrudes upward with respect to the connection points to the plurality of oil storage spaces, oil is discharged through the intermediate portion where there is no risk of the lubricating oil remaining. Ventilation can be reliably ensured between the oil storage space where the holes are not opened and the oil storage space where the oil drainage holes are opened, and the oil is reliably introduced into each oil storage space. It becomes possible.
  • the plurality of oil storage spaces are constituted by spaces formed when two members constituting the compressor are combined, and the gas vent passage is an end face where the two members constituting the compressor are abutted against each other It is good to form by the groove
  • the gas vent passage may be formed by a groove formed in one or both of the end surfaces where one side member and the cylinder face each other. According to such a configuration, it is not necessary to make a gas vent passage in the member constituting the compressor, so that the gas vent passage can be easily formed.
  • the gas vent passage is provided with an annular groove formed on one or both peripheral edges of the end surfaces of the two members constituting the compressor, and the annular groove is formed in the oil storage space. It is good to form by the connection groove
  • the gas vent passage is provided with an annular groove formed on one or both peripheral edges of the end face where one side member and the cylinder are abutted, and the annular groove is used for the oil storage. It is good to form by the connection groove
  • an oil supply passage to a communication passage communicating with the lower region of each oil storage space, and supply the lubricating oil stored in the oil storage chamber to the compression mechanism from the oil supply passage.
  • the oil storage chamber for storing the lubricating oil separated by the oil separator is constituted by a plurality of oil storage spaces, and the lower region of the plurality of oil storage spaces is formed.
  • the oil drain hole is opened.
  • the upper region of the oil storage space that is not open and the upper region of the oil storage space in which the oil drainage holes are opened communicate with each other through the gas vent passage, and the gas vent passage is connected to a plurality of oil storage spaces.
  • each oil storage space Since there is an intermediate portion that protrudes upward with respect to the connection location, there is no inconvenience that the lubricating oil is not introduced into each oil storage space, and each oil storage space has a space for storing the lubricating oil. It is possible to effectively function as a. Therefore, it is not necessary to form the oil storage space so as to extend largely to the side of the compressor in order to secure the volume of the storage chamber, and the compressor can be reduced in size.
  • FIG. 1 is a side sectional view showing an example of a compressor according to the present invention.
  • FIG. 2 is a cross-sectional view taken along line AA in FIG.
  • FIG. 3 is a view of the rear head (rear side member) viewed from the cylinder side.
  • FIG. 4 is a perspective view showing a rear head and a cylinder assembled to the rear head.
  • FIG. 5 is a graph comparing the oil circulation rate (OCR) between a conventional compressor having no gas vent passage and a compressor having the gas vent passage shown in the embodiment of the present invention.
  • OCR oil circulation rate
  • the vane compressor includes a cylinder 1, a rotor 3 rotatably accommodated in the cylinder, and fixed to a drive shaft 2, and a vane 5 inserted into a plurality of vane grooves 4 provided in the rotor 3.
  • a rear head (rear side member) 6 that closes the rear side end surface of the cylinder 1; a front head that closes the front side end surface of the cylinder 1 and surrounds the outer peripheral surface of the cylinder 1; (A front side member) 7.
  • the cylinder 1 is formed with a hole 10 having an elliptical cross section, and in this example, the long diameter portion of the cylinder is provided so as to face substantially in the vertical direction of the compressor.
  • the rotor 3 fixed to the shaft 2 is rotatably accommodated in the hole 10.
  • the rotor 3 has a cylindrical shape with a substantially circular cross section having a diameter substantially the same as the elliptical minor axis of the hole 10, and the inner peripheral surface of the rotor 3 and the minor axis part of the hole 10 are close to each other.
  • two compression spaces 11 are formed between the inner peripheral surface of the long diameter portion of the hole 10 and the outer peripheral surface of the rotor 3.
  • a plurality of vane grooves 4 provided in the rotor 3 are formed in parallel to the drive shaft 2 and at equal intervals in the circumferential direction (five in this example).
  • the rotor 3 is provided so as to be inclined at a predetermined angle in the rotation direction of the rotor 3 with respect to the radial direction from the center.
  • Each vane 5 is slidably inserted into each vane groove 4 and is urged radially outward by the centrifugal force accompanying the rotation of the rotor 3 and the pressure supplied to the bottom of the vane groove.
  • the inner wall of the hole 10 is in sliding contact. Therefore, the compression space 11 is partitioned by the vanes 5 to be formed in the plurality of compression chambers 12, and the volume of each compression chamber 12 increases when the vane 5 advances from the long diameter portion to the short diameter portion of the hole 10 as the rotor 3 rotates.
  • the working fluid is gradually reduced to compress the working fluid in the compression chamber 12.
  • the drive shaft 2 is rotatably supported by the front head 7 and the rear head 6 via bearings 13 and 14, and one end portion thereof protrudes from the front head 7.
  • a drive pulley is connected to a portion of the drive shaft 2 protruding from the front head 7 via an electromagnetic clutch (not shown) so that rotational power is transmitted from a vehicle engine via a drive belt.
  • one end side of the drive shaft 2 is hermetically sealed with the front head 7 through a seal member 15 provided between the drive shaft 2 and the front head 7.
  • the front head 7 is formed by integrating a side block portion 7 a that contacts the cylinder 1 and a cylinder portion 7 b that surrounds a part of the cylinder 1 and the rear head 6.
  • the front head 7 includes a working fluid (refrigerant).
  • a suction port 17 for sucking gas through the check valve 16 and a suction chamber (low pressure chamber) 18 through which the suction port 17 communicates are formed.
  • the suction chamber 18 communicates with the compression chamber 12 from the front in the rotation direction of the rotor 3 to the vicinity of the long diameter portion of the hole 10 with respect to the short diameter portion of the hole 10 of the cylinder 1.
  • the cylinder 1 is formed with radially projecting flange portions 1a and 1b at both axial end portions thereof, and the respective flange portions 1a and 1b are matched to the inner peripheral shape of the cylindrical portion 7b of the front head 7. It is formed into a shape.
  • the front side end surface including the flange portion 1 b of the cylinder 1 is in contact with the end surface of the side block portion 7 a of the front head 7.
  • the rear side end surface including the flange portion 1 a of the cylinder 1 is in contact with the end surface of the rear head 6.
  • a discharge port 19 that can communicate with the compression chamber 12 is provided on the outer peripheral surface of the cylinder 1 in the vicinity of the short diameter portion of the hole 10 of the cylinder 1. Further, between the outer peripheral surface of the cylinder 1 and the inner peripheral surface of the cylinder portion 7 b of the front head 7, a discharge valve storage chamber 20 defined between flange portions 1 a and 1 b formed at both ends of the cylinder 1. Is formed.
  • the discharge port 19 opens into the discharge valve storage chamber 20, and the compression chamber 12 formed between the vanes can communicate with the discharge valve storage chamber 20 through the discharge port 19.
  • the discharge port 19 is opened and closed by a discharge valve 21 housed in the discharge valve housing chamber 20.
  • the rear head 6 is formed with a discharge chamber (high pressure chamber) 23 communicating with the discharge valve storage chamber 20 and a discharge port 22 for discharging the working fluid to the outside of the compressor.
  • a discharge chamber (high pressure chamber) 23 communicating with the discharge valve storage chamber 20 and a discharge port 22 for discharging the working fluid to the outside of the compressor.
  • a plurality of separate recesses 101 a to 101 d extending along the circumferential direction are formed in the vicinity of the outer peripheral edge of the end surface of the rear head 6 facing the cylinder 1. .
  • the recesses 101a to 101d are closed by a region where the hole 10 is not opened on the rear side end surface including the flange portion 1a of the cylinder 1 to form a closed space.
  • the discharge chamber 23 is formed using at least one of the closed spaces (in this example, a closed space formed by closing the recess 101d).
  • the discharge chamber 23 and the discharge valve storage chamber 20 are separated by a flange portion 1a provided in the cylinder 1 and communicated with each other through a through hole 24 penetrating the flange portion 1a.
  • the through holes 24 are desirably formed at positions where the distances from the respective discharge ports 19 are substantially equal.
  • the working fluid including the refrigerant and the lubricating oil flows into the suction chamber 18 from the evaporator of the refrigeration cycle through the check valve 16 of the suction port 17 and is compressed. After being compressed in the chamber 12, it flows out into the discharge chamber 23 through the discharge valve housing chamber 20, and is discharged from the discharge chamber 23 through the discharge port 22 toward the condenser of the refrigeration cycle.
  • the rear head 6 is provided with a centrifugal oil separator 30 for separating the lubricating oil mixed in the discharge gas.
  • the oil separator 30 is formed integrally with the rear head 6 and includes an oil separation chamber 32 that forms a cylindrical space communicating with the discharge chamber 23 through the introduction hole 31.
  • a substantially cylindrical separation cylinder (separator pipe) 33 formed integrally with the rear head 6 is coaxially arranged.
  • the oil separation chamber 32 is formed so as to extend in a direction substantially perpendicular to the axial direction of the drive shaft 2 and to have its axis inclined obliquely with respect to the vertical line.
  • the upper end portion of the oil separation chamber 32 communicates with the buffer space 25 via the separation cylinder 33, and further communicates with the discharge port 22 via the buffer space 25.
  • the lower end portion of the oil separation chamber 32 opens to the outer peripheral surface of the rear head 6, and this opening portion is hermetically sealed by the lid member 34.
  • an oil drain hole 36 communicating with an oil storage chamber 35 provided at the lower portion of the compressor is formed at the lower portion of the oil separation chamber 32.
  • the working fluid that has flowed into the oil separation chamber 32 swirls around the separation cylinder 33 provided in the oil separation chamber 32, and the mixed lubricating oil is separated in the process.
  • the discharge gas from which the lubricating oil has been separated and removed is guided to the buffer space 25 through the hole in the center of the separation cylinder 33 and then sent to the refrigeration cycle via the discharge port 22.
  • the separated lubricating oil is stored in an oil storage chamber 35 formed at the lower portion of the compressor through an oil drain hole 36 provided at the lower portion of the oil separation chamber 32.
  • the oil storage chamber 35 includes the plurality of recesses 101a to 101d extending in the circumferential direction in the vicinity of the outer peripheral edge of the end surface of the rear head 6 facing the cylinder 1, and the rear side end surface including the flange portion 1a of the cylinder 1.
  • the two closed spaces disposed in the lower region are used as oil storage spaces 35a and 35b.
  • the recesses 101a and 101b forming the oil storage spaces 35a and 35b are formed so that the holes 10 of the cylinder 1 of the rear head 6 do not overlap with the holes 10 of the cylinder 1 arranged with the elliptical long-diameter portion facing the vertical direction. It is formed on both sides of the facing part (in FIG. 3, the phantom line of the hole 10 of the cylinder 1 is indicated by a two-dot chain line).
  • Each of the recesses 101 a and 101 b extends upward from the vicinity of the lower end of the rear head 6 along the periphery.
  • a communication recess 37 is formed in which the lower ends of the oil storage spaces 35 a and 35 b communicate with each other.
  • the oil storage space 35 a and the oil storage space 35 b communicate with each other via the communication recess 37 serving as a communication path, thereby forming the oil storage chamber 35.
  • the lowermost end portion of the oil storage chamber 35 (the portion where the lower end portion of the first oil storage space 35a and the lower end portion of the second oil storage space 35b communicate with each other, ie, the communication recess 37) is connected to the rear head 6.
  • An oil supply passage 38 that is formed between the formed recess 101a and recess 101b and communicates with the sliding portion of the compression mechanism is connected.
  • the oil supply passage 38 supplies the lubricating oil stored in the oil storage chamber 35 to each lubricating portion based on the pressure difference between the oil storage chamber 35 and each lubricating portion, and the vane 5 in the vane groove 4 of the rotor 3. To be sent to the space behind.
  • the vane 5 is pressed against the inner peripheral surface of the cylinder 1 to ensure stable compression.
  • the oil drain hole 36 that connects the oil separation chamber 32 and the oil storage chamber 35 of the oil separator 30 is connected to the first oil storage space 35a. Therefore, the lubricating oil separated by the oil separator 30 is The oil is introduced into the first oil storage space 35 a through the oil drain hole 36, and then introduced into the second oil storage space 35 b through the communication recess 37.
  • the second oil storage space 35b is a closed space closed by the rear side end face of the cylinder 1.
  • this second oil storage space is a complete bag path without escape for the gas accumulated inside
  • the second oil storage space 35b remains filled with gas
  • Lubricating oil is not introduced from the first oil storage space 35a to the second oil storage space 35b via the communication recess 37 (the liquid level of the lubricating oil cannot be increased in the second oil storage space 35b).
  • the second oil storage space 35b cannot function effectively.
  • a degassing passage 40 that connects the upper portion of the first oil storage space 35a and the upper portion of the second storage space 35b is formed at the abutting portion between the rear head 6 and the cylinder 1.
  • the degassing passage 40 forms a groove that communicates the upper region of the first oil storage space 35a and the upper region of the second oil storage space 35b on the end face of the rear head 6 that is in contact with the cylinder 1. It is formed by closing the end face of the flange portion 1a of the cylinder 1.
  • annular groove formed in the gas vent passage 40 so as to surround the radially outer side of the oil storage spaces 101a to 101d at the end surface of the peripheral portion of the rear head 6 that contacts the flange portion 1a of the cylinder 1.
  • 40a and connection grooves 40b and 40c that connect the annular groove 40a and the upper regions of the oil storage spaces 35a and 35b.
  • the annular groove 40a can be formed by a lathe process, and the connection grooves 40b and 40c are formed at the same time when the rear head 6 is cast-molded, or the molded rear head 6 is processed later by an end mill or the like. It is formed by.
  • the two oil storage spaces constituting the oil storage chamber 35 (the second oil storage space 35b in which the oil discharge hole 36 is not opened and the first oil storage space in which the oil discharge hole 36 is opened). Since the upper regions of the spaces 35a) communicate with each other via the gas vent passage 40, the gas in the second oil storage space 35b moves to the first oil storage space 35a via the gas vent passage 40. It becomes possible to make it. As a result, even in the configuration in which the oil drain hole 36 of the oil separator 30 is connected only to the first oil storage space 35 a, the lubricating oil introduced into the first oil storage space 35 a is passed through the communication recess 37. 2 It becomes possible to supply to the oil storage space 35b.
  • connection grooves 40b, 40c respectively of the oil storage space 35a, to sections that are connected to 35b
  • the upper portion 40a 1 of the annular groove 40a is a convex shape toward the upper side. That is, the gas vent passage 40 includes an intermediate portion 40a 1 of the convex upward with respect to each of the oil storage space 35a, the connection into the 35b. Therefore, even if the accumulated lubricating oil in the lower portion 40a 2 of the annular groove 40a, the upper portion 40a 1 of the annular groove 40 never lubricating oil retention, the first oil storage space 35a first There is no inconvenience that the ventilation state is hindered between the two storage spaces 35b, and oil can be reliably introduced into the oil storage spaces 35a and 35b.
  • FIG. 5 shows an oil circulation rate (OCR: Oil) during operation between a conventional compressor having no gas vent passage 40 and a compressor having the gas vent passage 40 described above in a compressor having an oil storage chamber of the same shape. Circulation (Rate) comparison results are shown. As is apparent from FIG. 5, the oil circulation rate of the compressor having the above-described gas vent passage 40 is almost halved as compared with the conventional compressor in which the gas vent passage 40 is not formed. Thus, it was confirmed that the lubricating oil was sufficiently stored, and the two oil storage spaces 35a and 35b functioned effectively as spaces for storing the lubricating oil.
  • OCR Oil
  • the gas vent passage 40 is formed by a groove formed on the rear head side of the abutted end surfaces of two members (cylinder 1 and rear head 6) constituting the compressor, in order to form the gas vent passage It is not necessary to make holes in the cylinder or the rear head, and the gas vent passage 40 can be easily formed.
  • the gas vent passage 40 is formed in the annular groove 40a formed in the peripheral edge portion of the butted end surface of the rear head 6, and the connection grooves 40b and 40c connecting the annular groove 40a and the oil storage space, respectively. Therefore, the annular groove 40a can be formed by lathe processing, and the gas vent passage 40 can be formed more easily.
  • the gas vent passage 40 that connects the first oil storage space 35a and the second oil storage space 35b is formed on the rear head side of the butted end surfaces of the cylinder 1 and the rear head 6.
  • it may be configured by a groove formed on the cylinder side, or may be configured by overlapping the grooves formed on both the rear head side and the cylinder side.
  • the first oil storage space 35a and the second oil storage space 35b are communicated with each other via the communication recess 37 formed in the cylinder 1 at the lower portion.
  • the partition wall portion in which the oil supply passages 6 are formed may be recessed and communicated.
  • the oil storage chamber 35 is formed by communicating the two oil storage spaces 35a and 35b at the lower part of each other is shown, but three or more oil storage spaces are formed in each other. Even in the case where the oil is communicated at the lower part, the oil storage space in which the oil drain hole 36 is not opened and the oil storage space in which the oil drain hole 36 is opened are further detoured above each upper part. It is also possible to make all the oil storage spaces function effectively as spaces for storing lubricating oil by communicating with each other through the venting passage.

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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)

Abstract

L'objet de la présente invention est de fournir un compresseur qui comprend un séparateur d'huile destiné à séparer l'huile lubrifiante et une chambre de stockage d'huile destinée à stocker l'huile lubrifiante séparée, tout l'espace prévu pour la chambre de stockage d'huile pouvant être utilisé efficacement pour stocker l'huile lubrifiante. Une chambre 35 de stockage d'huile destinée à stocker l'huile lubrifiante est formée à partir d'une pluralité d'espaces 35a et 35b de stockage d'huile, des régions inférieures de chacun de la pluralité d'espaces de stockage d'huile sont amenées à communiquer les unes avec les autres, et l'huile lubrifiante qui a été séparée au moyen d'un séparateur 30 d'huile est fournie à la chambre 35 de stockage d'huile par l'intermédiaire d'un trou 36 d'évacuation d'huile formé dans l'un quelconque de la pluralité d'espaces 35a et 35b de stockage d'huile. Une région supérieure de l'espace 35b de stockage d'huile dans laquelle n'a pas été formé de trou 31 d'évacuation d'huile, et une région supérieure de l'espace 35a de stockage d'huile dans laquelle a été formé le trou 36 d'évacuation d'huile sont amenées à communiquer l'une avec l'autre par l'intermédiaire d'un passage 40 de dispersion de gaz, et le passage 40 de dispersion de gaz est pourvu d'une partie intermédiaire (une partie de face supérieure 40a1 d'une rainure annulaire 40a) qui fait saillie vers le haut depuis les emplacements au niveau desquels le passage 40 de dispersion de gaz est relié à chacun des espaces 35a et 35b de stockage d'huile.
PCT/JP2016/065538 2015-05-28 2016-05-26 Compresseur WO2016190380A1 (fr)

Priority Applications (1)

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EP16800084.2A EP3336360A4 (fr) 2015-05-28 2016-05-26 Compresseur

Applications Claiming Priority (2)

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JP2015-108218 2015-05-28
JP2015108218A JP6543094B2 (ja) 2015-05-28 2015-05-28 圧縮機

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WO2016190380A1 true WO2016190380A1 (fr) 2016-12-01

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2020148159A (ja) * 2019-03-15 2020-09-17 株式会社豊田自動織機 圧縮機

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2018173075A (ja) * 2017-03-31 2018-11-08 株式会社豊田自動織機 ベーン型圧縮機
JP2020020280A (ja) * 2018-07-31 2020-02-06 サンデン・オートモーティブコンポーネント株式会社 スクロール圧縮機
JP2020020281A (ja) * 2018-07-31 2020-02-06 サンデン・オートモーティブコンポーネント株式会社 スクロール圧縮機

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2005171859A (ja) * 2003-12-10 2005-06-30 Sanden Corp 圧縮機
JP2006029280A (ja) * 2004-07-21 2006-02-02 Mitsubishi Heavy Ind Ltd 圧縮機
JP2008196421A (ja) * 2007-02-14 2008-08-28 Sanden Corp オイルセパレータ内蔵圧縮機

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003113790A (ja) * 2001-10-03 2003-04-18 Seiko Instruments Inc 気体圧縮機
JP4007577B2 (ja) * 2002-01-09 2007-11-14 カルソニックコンプレッサー株式会社 気体圧縮機

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2005171859A (ja) * 2003-12-10 2005-06-30 Sanden Corp 圧縮機
JP2006029280A (ja) * 2004-07-21 2006-02-02 Mitsubishi Heavy Ind Ltd 圧縮機
JP2008196421A (ja) * 2007-02-14 2008-08-28 Sanden Corp オイルセパレータ内蔵圧縮機

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP3336360A4 *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2020148159A (ja) * 2019-03-15 2020-09-17 株式会社豊田自動織機 圧縮機

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JP2016223315A (ja) 2016-12-28
EP3336360A1 (fr) 2018-06-20
EP3336360A4 (fr) 2019-04-17
JP6543094B2 (ja) 2019-07-10

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