WO2016098710A1 - Compresseur rotatif - Google Patents

Compresseur rotatif Download PDF

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Publication number
WO2016098710A1
WO2016098710A1 PCT/JP2015/084844 JP2015084844W WO2016098710A1 WO 2016098710 A1 WO2016098710 A1 WO 2016098710A1 JP 2015084844 W JP2015084844 W JP 2015084844W WO 2016098710 A1 WO2016098710 A1 WO 2016098710A1
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WO
WIPO (PCT)
Prior art keywords
end plate
chamber
cylinder
discharge
lower discharge
Prior art date
Application number
PCT/JP2015/084844
Other languages
English (en)
Japanese (ja)
Inventor
尚哉 両角
卓 森下
基信 古川
大輝 片山
田中　順也
Original Assignee
株式会社富士通ゼネラル
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
Priority claimed from JP2014257818A external-priority patent/JP6112104B2/ja
Priority claimed from JP2015235213A external-priority patent/JP6128194B2/ja
Application filed by 株式会社富士通ゼネラル filed Critical 株式会社富士通ゼネラル
Priority to AU2015364875A priority Critical patent/AU2015364875B2/en
Priority to EP15869915.7A priority patent/EP3236075B1/fr
Priority to CN201580068370.1A priority patent/CN107002686B/zh
Priority to US15/537,394 priority patent/US10458408B2/en
Publication of WO2016098710A1 publication Critical patent/WO2016098710A1/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
    • F04C18/356—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
    • 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • 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
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet

Definitions

  • the present invention relates to a two-cylinder rotary compressor used in an air conditioner.
  • Patent Document 1 in a two-cylinder rotary compressor, high-temperature compressed refrigerant that is compressed by a lower cylinder and discharged from a lower discharge hole is transferred from a lower end plate cover chamber (lower muffler chamber) to an upper end plate cover chamber (upper).
  • a lower end plate cover chamber lower muffler chamber
  • an upper end plate cover chamber upper
  • Patent Document 2 high-temperature compressed refrigerant that is compressed in the lower cylinder and discharged from the lower discharge hole suppresses heating of the refrigerant drawn in the suction chamber of the lower cylinder by heating the lower end plate. Techniques for improving the performance are described.
  • the lower end plate cover chamber formed between the lower end plate and the lower end plate cover has a large volume by inflating the lower end plate cover (lower muffler cover). Therefore, the amount of the refrigerant that is compressed by the upper cylinder, discharged from the upper discharge hole, flows backward through the refrigerant passage hole, and flows into the lower muffler chamber is large.
  • the refrigerant passage hole is disposed on the opposite side of the lower discharge valve housing portion with respect to the lower discharge hole provided in the lower end plate, and the refrigerant discharged from the lower discharge hole is lowered. Since it flows into the refrigerant passage hole through the discharge valve accommodating portion, it is necessary to deepen the lower discharge valve accommodating portion. Therefore, the volume of the lower end plate cover chamber (refrigerant discharge space) is increased, and the amount of refrigerant compressed by the upper cylinder and discharged from the upper discharge hole and flowing backward through the refrigerant passage hole and flowing into the lower muffler chamber is large.
  • the flow of the refrigerant from the upper end plate cover chamber into the compressor casing outside the upper end plate cover chamber is the original flow, but the refrigerant flowing from the upper end plate cover chamber to the lower end plate cover chamber is discharged from the upper cylinder. After the end of the process, the refrigerant flows again through the refrigerant passage hole and the upper end plate cover chamber and into the compressor casing outside the upper end plate cover chamber. There is a problem of reducing efficiency.
  • the rotary compressor described in Patent Document 2 suppresses the lower end plate that covers the lower surface of the lower cylinder from being heated by the refrigerant compressed by the lower cylinder.
  • the liquefied refrigerant may accumulate in the compressor housing. Since the density of the liquid refrigerant at a low temperature is larger than the density of the lubricating oil, the liquid refrigerant accumulates at the lowermost part inside the compressor housing.
  • the rotary compressor is started in this state, the liquid refrigerant is sucked up by the oil supply blades from the lower end of the rotating shaft. If the liquid refrigerant is sucked up, the viscosity of the liquid refrigerant is smaller than the viscosity of the lubricating oil, so that the sliding part of the compression part may be poorly lubricated and damaged.
  • the discharged lubricating oil is the refrigerant circuit (refrigeration cycle) of the air conditioner. Is taken into the lower cylinder and the upper cylinder together with the suction refrigerant. The lubricating oil sucked into the lower cylinder is discharged together with the refrigerant from the lower discharge hole into the lower end plate cover chamber.
  • An object of the present invention is to prevent the refrigerant compressed by the upper cylinder from flowing back through the refrigerant passage hole, thereby preventing a reduction in the efficiency of the rotary compressor.
  • the present invention provides a vertically mounted cylindrical compressor housing which is provided with an upper suction pipe and a lower suction pipe which are provided with a discharge pipe for discharging a refrigerant at the upper part and with which a refrigerant is sucked at a lower part of the side surface, and the compressor casing.
  • An accumulator fixed to the side of the body and connected to the upper suction pipe and the lower suction pipe, a motor disposed in the compressor housing, and disposed below the motor in the compressor housing and driven by the motor And a compression part that sucks and compresses the refrigerant from the accumulator through the upper suction pipe and the lower suction pipe and discharges the refrigerant from the discharge pipe, and the compression part includes an annular upper cylinder and a lower cylinder, An upper end plate for closing the upper side of the upper cylinder, a lower end plate for closing the lower side of the lower cylinder, and a lower side of the upper cylinder and the upper side of the lower cylinder, which are disposed between the upper cylinder and the lower cylinder.
  • An upper end plate cover chamber is formed between the lower vane that divides the Linder chamber into a lower suction chamber and a lower compression chamber, and the upper end plate so as to cover the upper end plate, and the interior of the upper end plate cover chamber and the compressor housing
  • An upper end plate cover having an upper end plate cover discharge hole communicating therewith, a lower end plate cover that covers the lower end plate and forms a lower end plate cover chamber between the lower end plate, and the upper compression provided in the upper end plate
  • a refrigerant passage hole that passes through the plate, the upper end plate, and the upper cylinder, and communicates the lower end plate cover chamber and the upper end plate cover chamber.
  • Upper discharge valve that extends in a groove shape from the position A recess, a lower discharge valve receiving recess provided in the lower end plate and extending in a groove shape from the position of the lower discharge hole, a rear end portion is fixed in the upper discharge valve receiving recess by an upper rivet, and a front portion is the upper discharge A reed valve type upper discharge valve that opens and closes the hole and a rear end portion are overlapped with the upper discharge valve, fixed in the upper discharge valve housing recess by the upper rivet, and a front portion is warped so that the upper discharge valve is opened.
  • An upper discharge valve presser for regulating the degree a reed valve type lower discharge valve whose rear end is fixed by a lower rivet in the lower discharge valve accommodating recess and whose front opens and closes the lower discharge hole, and a rear end thereof A lower discharge that is overlapped with a lower discharge valve and fixed in the lower discharge valve housing recess by the lower rivet and whose front part is warped to regulate the opening of the lower discharge valve and is housed in the lower discharge valve housing recess.
  • a lower end plate cover formed in a flat plate shape
  • a lower discharge chamber recess is formed in the lower end plate so as to overlap with the lower discharge hole side of the lower discharge valve housing recess, and the lower discharge chamber recess has a center of the auxiliary bearing portion and a center of the lower discharge hole.
  • the refrigerant passage hole is disposed at a position where at least a part of the refrigerant passage hole overlaps the lower discharge chamber recess and communicates with the lower discharge chamber recess, and the lower end plate cover chamber is formed in the lower discharge chamber recess. And the lower discharge valve housing recess.
  • the present invention can prevent the refrigerant compressed by the lower cylinder from flowing backward through the refrigerant passage hole, thereby preventing a reduction in the efficiency of the rotary compressor.
  • FIG. 1 is a longitudinal sectional view showing a first embodiment of a rotary compressor according to the present invention.
  • FIG. 2 is an upper exploded perspective view illustrating a compression unit of the rotary compressor according to the first embodiment.
  • FIG. 3 is an upper exploded perspective view showing the rotating shaft and the oil supply blades of the rotary compressor of the first embodiment.
  • FIG. 4 is a bottom view showing a lower end plate of the rotary compressor of the first embodiment.
  • FIG. 5 is a longitudinal cross-sectional view showing a lower discharge valve accommodating recess to which the lower discharge valve of the rotary compressor of the first embodiment is attached.
  • FIG. 6 is a longitudinal cross-sectional view showing a lower discharge valve housing recess in which the lower discharge valve of the rotary compressor of the second embodiment is attached.
  • FIG. 1 is a longitudinal sectional view showing a first embodiment of a rotary compressor according to the present invention.
  • FIG. 2 is an upper exploded perspective view illustrating a compression unit of the rotary compressor according to the first
  • FIG. 7 is a longitudinal cross-sectional view showing a lower discharge valve accommodating recess to which a lower discharge valve of the rotary compressor of the third embodiment is attached.
  • FIG. 8 is a bottom view showing a lower end plate of the rotary compressor of the fourth embodiment.
  • FIG. 9 is a bottom view of the lower end plate of the rotary compressor of the fifth embodiment.
  • FIG. 10 is a lower perspective view illustrating the lower end plate of the rotary compressor of the sixth embodiment.
  • FIG. 11 is a bottom view illustrating a state in which the lower end plate and the lower end plate cover of the rotary compressor according to the seventh embodiment are overlapped.
  • FIG. 1 is a longitudinal sectional view showing Embodiment 1 of a rotary compressor according to the present invention
  • FIG. 2 is an upper exploded perspective view showing a compression section of the rotary compressor of Embodiment 1
  • FIG. 3 is an exploded top perspective view showing a rotation shaft and oil supply blades of the rotary compressor according to the first embodiment.
  • the rotary compressor 1 includes a compression unit 12 disposed at a lower portion in a sealed vertical cylindrical compressor housing 10, a compression unit 12 disposed above the compression unit 12, and a rotating shaft 15.
  • a motor 11 that drives the compression unit 12 through the vertical axis, and a vertical cylindrical accumulator 25 that is fixed to a side portion of the compressor housing 10.
  • the accumulator 25 is connected to the upper suction chamber 131T (see FIG. 2) of the upper cylinder 121T via the upper suction pipe 105 and the accumulator upper L-shaped pipe 31T, and is connected to the lower side via the lower suction pipe 104 and the lower L-shaped pipe 31S of the accumulator.
  • the cylinder 121S is connected to the lower suction chamber 131S (see FIG. 2).
  • the motor 11 includes a stator 111 on the outer side and a rotor 112 on the inner side.
  • the stator 111 is shrink-fitted and fixed to the inner peripheral surface of the compressor housing 10, and the rotor 112 is fixed to the rotary shaft 15 by shrink-fitting. Yes.
  • the rotary shaft 15 is supported by a secondary shaft portion 151 below the lower eccentric portion 152S being rotatably fitted to a secondary bearing portion 161S provided on the lower end plate 160S, and a main shaft portion 153 above the upper eccentric portion 152T.
  • An upper eccentric portion 152T and a lower eccentric portion 152S which are rotatably fitted to and supported by a main bearing portion 161T provided on the upper end plate 160T and are provided with a phase difference of 180 degrees from each other, are respectively provided with an upper piston 125T and a lower
  • the entire compression portion 12 is rotatably supported, and the upper piston 125T and the lower piston 125S are respectively rotated on the inner peripheral surfaces of the upper cylinder 121T and the lower cylinder 121S. Revolve along.
  • Lubricating oil 18 is contained in the compressor housing 10 for lubricating the sliding portion of the compression portion 12 and sealing the upper compression chamber 133T (see FIG. 2) and the lower compression chamber 133S (see FIG. 2). 12 is enclosed in an amount that substantially immerses 12.
  • An attachment leg 310 that fixes a plurality of elastic support members (not shown) that support the entire rotary compressor 1 is fixed to the lower side of the compressor housing 10.
  • the compression unit 12 includes an upper end plate cover 170T having a dome-shaped bulging portion from above, an upper end plate 160T, an upper cylinder 121T, an intermediate partition plate 140, a lower cylinder 121S, a lower end plate 160S, and a flat plate shape.
  • the lower end plate cover 170S is laminated.
  • the entire compression unit 12 is fixed by a plurality of through bolts 174 and 175 and auxiliary bolts 176 arranged substantially concentrically from above and below.
  • the upper upper cylinder 121T is provided with an upper suction hole 135T that fits into the upper suction pipe 105.
  • the annular lower cylinder 121S is provided with a lower suction hole 135S that fits into the lower suction pipe 104.
  • An upper piston 125T is disposed in the upper cylinder chamber 130T of the upper cylinder 121T.
  • a lower piston 125S is disposed in the lower cylinder chamber 130S of the lower cylinder 121S.
  • the upper cylinder 121T is provided with an upper vane groove 128T extending radially outward from the upper cylinder chamber 130T, and an upper vane 127T is disposed in the upper vane groove 128T.
  • the lower cylinder 121S is provided with a lower vane groove 128S extending radially outward from the lower cylinder chamber 130S, and a lower vane 127S is disposed in the lower vane groove 128S.
  • the upper cylinder 121T is provided with an upper spring hole 124T at a depth that does not penetrate the upper cylinder chamber 130T at a position overlapping the upper vane groove 128T from the outer surface, and an upper spring 126T is disposed in the upper spring hole 124T.
  • the lower cylinder 121S is provided with a lower spring hole 124S at a position that does not penetrate the lower cylinder chamber 130S at a position overlapping the lower vane groove 128S from the outer surface, and a lower spring 126S is disposed in the lower spring hole 124S.
  • the upper cylinder chamber 130T is closed at the top and bottom by an upper end plate 160T and an intermediate partition plate 140, respectively.
  • the lower cylinder chamber 130S is closed at the top and bottom by an intermediate partition plate 140 and a lower end plate 160S, respectively.
  • the upper cylinder chamber 130T includes an upper suction chamber 131T communicating with the upper suction hole 135T and an upper plate 160T provided by the upper vane 127T being pressed by the upper spring 126T and coming into contact with the outer peripheral surface of the upper piston 125T.
  • the upper compression chamber 133T communicated with the discharge hole 190T.
  • the lower cylinder chamber 130S includes a lower suction chamber 131S communicating with the lower suction hole 135S and a lower plate provided in the lower end plate 160S when the lower vane 127S is pressed by the lower spring 126S and comes into contact with the outer peripheral surface of the lower piston 125S. And a lower compression chamber 133S communicating with the discharge hole 190S.
  • the upper end plate 160T is provided with an upper discharge hole 190T that penetrates the upper end plate 160T and communicates with the upper compression chamber 133T of the upper cylinder 121T, and an annular shape surrounding the upper discharge hole 190T is provided on the outlet side of the upper discharge hole 190T.
  • An upper valve seat (not shown) is formed.
  • the upper end plate 160T is formed with an upper discharge valve accommodating recess 164T extending in a groove shape from the position of the upper discharge hole 190T in the circumferential direction of the upper end plate 160T.
  • the upper discharge valve accommodating recess 164T has a reed valve type upper discharge valve 200T and a rear end whose rear end is fixed by an upper rivet 202T in the upper discharge valve accommodating recess 164T and whose front opens and closes the upper discharge hole 190T.
  • the upper discharge valve holder 201T as a whole is placed on the upper discharge valve 200T and fixed in the upper discharge valve housing recess 164T by the upper rivet 202T, and the front part is curved (warped) to regulate the opening degree of the upper discharge valve 200T. Contained.
  • the lower end plate 160S is provided with a lower discharge hole 190S that penetrates the lower end plate 160S and communicates with the lower compression chamber 133S of the lower cylinder 121S, and an annular shape surrounding the lower discharge hole 190S is provided on the outlet side of the lower discharge hole 190S.
  • a lower valve seat 191S (see FIG. 4) is formed.
  • the lower end plate 160S is formed with a lower discharge valve accommodating recess 164S (see FIG. 4) extending from the position of the lower discharge hole 190T in a groove shape in the circumferential direction of the lower end plate 160S.
  • the lower discharge valve accommodating recess 164S has a reed valve type lower discharge valve 200S and a rear end that are fixed by a lower rivet 202S in the lower discharge valve accommodating recess 164S and the front portion opens and closes the lower discharge hole 190S. All of the lower discharge valve presser 201S that overlaps with the lower discharge valve 200S and is fixed in the lower discharge valve housing recess 164S by the lower rivet 202S and the front part is curved (warped) to regulate the opening degree of the lower discharge valve 200S. Is housed.
  • the upper end plate cover chamber 180T is formed between the upper end plate 160T fixed in close contact with each other and the upper end plate cover 170T having a dome-shaped bulge.
  • a lower end plate cover chamber 180S is formed between the lower end plate 160S and the flat lower end plate cover 170S that are closely fixed to each other (details of the lower end plate cover chamber 180S will be described later).
  • a refrigerant passage hole 136 that penetrates the lower end plate 160S, the lower cylinder 121S, the intermediate partition plate 140, the upper end plate 160T, and the upper cylinder 121T and communicates the lower end plate cover chamber 180S and the upper end plate cover chamber 180T is provided.
  • the rotary shaft 15 is provided with an oil supply vertical hole 155 penetrating from the lower end to the upper end, and an oil supply blade 158 is press-fitted into the oil supply vertical hole 155.
  • a plurality of oil supply lateral holes 156 communicating with the oil supply vertical holes 155 are provided on the side surface of the rotating shaft 15.
  • the upper piston 125T fitted to the upper eccentric portion 152T of the rotary shaft 15 is rotated along the outer peripheral surface of the upper cylinder chamber 130T (the inner peripheral surface of the upper cylinder 121T) by the rotation of the rotary shaft 15.
  • the upper suction chamber 131T sucks refrigerant from the upper suction pipe 105 while expanding the volume
  • the upper compression chamber 133T compresses the refrigerant while reducing the volume, and the pressure of the compressed refrigerant is changed to the upper discharge valve.
  • the upper discharge valve 200T When the pressure is higher than the pressure in the upper end plate cover chamber 180T outside the 200T, the upper discharge valve 200T is opened and the refrigerant is discharged from the upper compression chamber 133T to the upper end plate cover chamber 180T.
  • the refrigerant discharged into the upper end plate cover chamber 180T is discharged into the compressor housing 10 from an upper end plate cover discharge hole 172T (see FIG. 1) provided in the upper end plate cover 170T.
  • the lower piston 125S fitted to the lower eccentric portion 152S of the rotary shaft 15 by the rotation of the rotary shaft 15 causes the outer peripheral surface of the lower cylinder chamber 130S (the inner peripheral surface of the lower cylinder 121S).
  • the lower suction chamber 131S sucks in the refrigerant from the lower suction pipe 104 while increasing the volume
  • the lower compression chamber 133S compresses the refrigerant while reducing the volume, and the pressure of the compressed refrigerant is reduced.
  • the lower discharge valve 200S opens and the refrigerant is discharged from the lower compression chamber 133S to the lower end plate cover chamber 180S.
  • the refrigerant discharged into the lower end plate cover chamber 180S passes through the refrigerant passage hole 136 and the upper end plate cover chamber 180T, and passes through the upper end plate cover discharge hole 172T (see FIG. 1) provided in the upper end plate cover 170T. It is discharged inside.
  • the refrigerant discharged into the compressor housing 10 is a notch (not shown) provided on the outer periphery of the stator 111 that communicates with the upper and lower sides, a gap (not shown) between winding portions of the stator 111, or the stator 111. Is guided to the upper side of the motor 11 through the gap 115 (see FIG. 1) between the rotor 112 and the rotor 112, and is discharged from the discharge pipe 107 at the top of the compressor housing 10.
  • the lubricating oil 18 passes from the lower end of the rotary shaft 15 through the oil supply vertical hole 155 and the plurality of oil supply horizontal holes 156, and slides between the sub bearing portion 161S and the sub shaft portion 151 of the rotary shaft 15, the main bearing portion 161T, Oil is supplied to the sliding surface of the rotating shaft 15 with the main shaft portion 153, the sliding surface of the lower eccentric portion 152S of the rotating shaft 15 and the lower piston 125S, and the sliding surface of the upper eccentric portion 152T and the upper piston 125T, respectively. Lubricate the sliding surface.
  • the oil supply blade 158 sucks up the lubricating oil 18 by applying a centrifugal force to the lubricating oil 18 in the oil supply vertical hole 155, and the lubricating oil 18 is discharged from the compressor housing 10 together with the refrigerant to lower the oil level. In addition, the lubricant 18 is surely supplied to the sliding surface.
  • FIG. 4 is a bottom view showing a lower end plate of the rotary compressor of the first embodiment
  • FIG. 5 is a longitudinal sectional view showing a lower discharge valve housing concave portion to which the lower discharge valve of the rotary compressor of the first embodiment is attached. is there.
  • the lower end plate cover chamber 180S has a lower discharge plate chamber provided in the lower end plate 160S because the lower end plate cover 170S has a flat plate shape and does not have a dome-like bulge portion like the upper end plate cover 170T. It is comprised by the recessed part 163S and the lower discharge valve accommodation recessed part 164S. Lower discharge valve housing recess 164S from the position of the lower discharge holes 190S, a direction which intersects the radial line L 1 connecting the center O 2 of the center O 1 and the lower discharge holes 190S sub bearing portion 161S, in other words, the lower end plate The groove extends linearly in the circumferential direction of 160S.
  • the lower discharge valve housing recess 164S is connected to the lower discharge chamber recess 163S.
  • the lower discharge valve accommodating recess 164S is formed to have a width slightly larger than the width of the lower discharge valve 200S and the lower discharge valve presser 201S, and accommodates the lower discharge valve 200S and the lower discharge valve presser 201S, and the lower discharge valve 200S and The lower discharge valve holder 201S is positioned.
  • the lower discharge chamber recess 163S is formed to the same depth as the lower discharge valve housing recess 164S so as to overlap the lower discharge hole 190S side of the lower discharge valve housing recess 164S.
  • the lower discharge hole 190S side of the lower discharge valve housing recess 164S is housed in the lower discharge chamber recess 163S.
  • Lower discharge chamber recess 163S includes a center O 1 of the sub bearing portion 161S, the midpoint O 4 of the line segment L 2 (length F) connecting the center O 2 and the center O 3 of below rivets 202S of the lower discharge holes 190S , a radial line L 3 through the form in the sector ranging between radial line L 4 open pitch angle 90 ° to the direction of the lower discharge holes 190S around the center O 1 of the sub bearing portion 161S.
  • the refrigerant passage hole 136 is disposed at a position where at least a part thereof overlaps with the lower discharge chamber recess 163S and communicates with the lower discharge chamber recess 163S.
  • an annular lower valve seat 191 ⁇ / b> S that is raised with respect to the bottom of the lower discharge chamber recess 163 ⁇ / b> S is formed at the periphery of the opening of the lower discharge hole 190 ⁇ / b> S, and the lower valve seat 191 ⁇ / b> S serves as the lower discharge valve 200 ⁇ / b> S. Abuts the front.
  • the depth H to the lower valve seat 191S of the lower discharge chamber recess 163S is 1.5 times or less the diameter ⁇ D1 of the lower discharge hole 190S.
  • the opening of the lower discharge valve 200S when the refrigerant is discharged from the lower discharge hole 190S that is, the lift amount of the lower discharge valve 200S with respect to the lower valve seat 191S needs to be a lift amount that does not become a resistance of the discharge flow. Therefore, the depth H to the lower valve seat 160S of the lower discharge chamber recess 163S needs to be determined in consideration of the lift amount of the lower discharge valve 200S and the thicknesses of the lower discharge valve 200S and the lower discharge valve presser 201S. However, 1.5 times the diameter ⁇ D1 of the lower discharge hole 190S is sufficient.
  • the refrigerant passage hole 136 is disposed at a position where at least a part thereof overlaps with the upper discharge chamber recess 163T and communicates with the upper discharge chamber recess 163T.
  • the upper discharge chamber recess 163T and the upper discharge valve accommodating recess 164T formed in the upper end plate 160T are not shown in detail, but the lower discharge chamber recess 163S and the lower discharge valve accommodating recess 164S formed in the lower end plate 160S, It is formed in the same shape.
  • the upper end plate cover chamber 180T is constituted by a dome-shaped bulged portion of the upper end plate cover 170T, an upper discharge chamber recess 163T, and an upper discharge valve housing recess 164T.
  • the distance between the lower discharge hole 190S and the inlet of the refrigerant passage hole 136 can be shortened. Therefore, the volume of the lower end plate cover chamber 180S, that is, the sum of the volume of the lower discharge chamber recess 163S and the volume of the lower discharge valve housing recess 164S can be significantly reduced as compared with the conventional case. As a result, the refrigerant compressed by the upper cylinder 121T and discharged from the upper discharge hole 190T can flow back into the lower end plate cover chamber 180S through the refrigerant passage hole 136, thereby reducing the efficiency of the rotary compressor 1. Decline can be prevented.
  • FIG. 6 is a longitudinal cross-sectional view showing a lower discharge valve housing recess in which the lower discharge valve of the rotary compressor of Example 2 is attached.
  • the depth H2 to the lower valve seat 191S of the lower discharge chamber recess 163S2 and the lower discharge valve housing recess 164S2 formed in the lower end plate 160S2 is The lower discharge chamber recess 163S formed in the lower end plate 160S of the first rotary compressor 1 and the depth H to the lower valve seat 191S of the lower discharge valve housing recess 164S are made shallower.
  • the lower end plate cover 170S2 has a recess 171S2 at a portion facing the front portion of the lower discharge valve retainer 201S, and accommodates a portion where the front portion of the lower discharge valve retainer 201S protrudes from the lower discharge chamber recess 163S2.
  • the depth from the recess 171S2 to the lower valve seat 191S is formed to be 1.5 times or less the diameter ⁇ D1 of the lower discharge hole 190S.
  • the volume of the lower discharge valve accommodating recess 164S2 can be made smaller than that of the rotary compressor 1 of the first embodiment, and thus the compressed by the upper cylinder 121T.
  • the flow rate of the refrigerant discharged from the upper discharge hole 190T backflowing through the refrigerant passage hole 136 and flowing into the lower end plate cover chamber 180S2 can be further reduced, and a reduction in the efficiency of the rotary compressor 1 can be prevented.
  • FIG. 7 is a longitudinal cross-sectional view showing a lower discharge valve housing recess in which the lower discharge valve of the rotary compressor of Example 3 is attached.
  • the front end portion of the lower discharge valve presser 201S3 is formed so that the thickness of the portion adjacent to the lower end plate cover 170S is thinner than the thickness of the other portions. Yes.
  • the depth H2 to the lower valve seat 191S of the lower discharge chamber recess 163S3 and the lower discharge valve housing recess 164S3 is secured while securing the same opening as the lower discharge valve 201S of the rotary compressor 1 of the first embodiment.
  • the depth H2 to the lower valve seat 191S of the lower discharge chamber recess 163S3 and the lower discharge valve housing recess 164S3 is secured while securing the same opening as the lower discharge valve 201S of the rotary compressor 1 of the first embodiment.
  • the volume of the lower end plate cover chamber 180S3 can be made smaller than the rotary compressor 1 of the second embodiment by the volume of the recess 171S2 of the second embodiment.
  • the refrigerant compressed by the upper cylinder 121T and discharged from the upper discharge hole 190T can flow back into the lower end plate cover chamber 180S3 through the refrigerant passage hole 136, thereby further reducing the rotary compressor. 1 can be prevented.
  • FIG. 8 is a bottom view showing a lower end plate of the rotary compressor of the fourth embodiment.
  • the refrigerant passage hole 136N provided in the lower end plate 160S4 (and the lower cylinder 121S, the intermediate partition plate 140, the upper cylinder 121T, and the upper end plate 160T)
  • the diameter is smaller than the refrigerant passage hole 136 of the rotary compressor 1 of the first embodiment, and two are provided (may be three or more).
  • the total cross-sectional area of the two (or three or more) refrigerant passage holes 136N is equal to the cross-sectional area of the refrigerant passage hole 136 of the rotary compressor 1 of the first embodiment.
  • the radius R1 from the center O 1 of the sub bearing portion 161S to the outermost periphery of the refrigerant passage holes 136N, the refrigerant passage holes from the center O 1 of the sub bearing portion 161S of the rotary compressor 1 of the first embodiment shown in FIG. 4 The radius can be smaller than the radius R1 up to the outermost periphery of 136, and the diameter of the circular lower discharge chamber recess 163S4 can be reduced.
  • the bottom area of the lower discharge chamber recess 163S4 is made smaller than the bottom area of the lower discharge chamber recess 163S of the rotary compressor 1 according to the first embodiment.
  • the volume of 163S4 can be reduced, thereby further reducing the flow rate of the refrigerant compressed by the upper cylinder 121T and discharged from the upper discharge hole 190T backflowing the refrigerant passage hole 136N and flowing into the lower end plate cover chamber 180S4. It is possible to prevent the reduction in efficiency of the rotary compressor 1.
  • the radius R2 of the lower end plate 160S4 (and the lower cylinder 121S, the intermediate partition plate 140, the upper cylinder 121T, and the upper end plate 160T) can be made smaller than the radius R1 up to the outermost periphery of the lower end plate of the first embodiment.
  • 160S (and the lower cylinder 121S, the intermediate partition plate 140, the upper cylinder 121T, and the upper end plate 160T) can be made smaller than the radius R2 (see FIG. 4), and the material cost of the compression unit 12 can be reduced.
  • FIG. 9 is a bottom view of the lower end plate of the rotary compressor of the fifth embodiment.
  • the refrigerant passage hole 136M provided in the lower end plate 160S5 (and the lower cylinder 121S, the intermediate partition plate 140, the upper cylinder 121T, and the upper end plate 160T)
  • the refrigerant passage hole 136N is a long hole whose width is smaller than the diameter, and the cross-sectional areas are equal.
  • the refrigerant passage hole (long hole) 136M is formed along the circumferential direction of the lower valve seat 191S.
  • the radius R1 from the center O 1 of the sub bearing portion 161S to the outermost periphery of the refrigerant passage holes 136M, the refrigerant passage holes from the center O 1 of the sub bearing portion 161S of the rotary compressor 1 of the fourth embodiment shown in FIG. 8 The radius can be smaller than the radius R1 up to the outermost periphery of 136N, and the diameter of the circular lower discharge chamber recess 163S5 can be reduced.
  • the bottom area of the lower discharge chamber recess 163S5 is made smaller than the bottom area of the lower discharge chamber recess 163S4 of the rotary compressor 1 of the fourth embodiment.
  • the volume of the concave portion 163S5 can be reduced, whereby the refrigerant compressed by the upper cylinder 121T and discharged from the upper discharge hole 190T further flows back into the lower end plate cover chamber 180S5 through the refrigerant passage hole 136M. Therefore, the efficiency of the rotary compressor 1 can be prevented from being reduced.
  • the radius R1 from the center O 1 of the sub bearing portion 161S to the outermost periphery of the refrigerant passage holes 136M, the refrigerant passage holes from the center O 1 of the sub bearing portion 161S of the rotary compressor 1 of the fourth embodiment shown in FIG. 8 136N The radius R2 of the lower end plate 160S5 (and the lower cylinder 121S, the intermediate partition plate 140, the upper cylinder 121T, and the upper end plate 160T) can be made smaller than the radius R1 up to the outermost periphery of the lower end plate of the fourth embodiment.
  • 160S4 (and the lower cylinder 121S, the intermediate partition plate 140, the upper cylinder 121T, the upper end plate 160T) can be made smaller than the radius R2 (see FIG. 4), and the material cost of the compression unit 12 can be further reduced.
  • FIG. 10 is a lower perspective view showing the lower end plate of the rotary compressor of the sixth embodiment.
  • the lower discharge chamber recess 163S and the lower discharge valve housing of the lower surface of the lower end plate 160S6 (which is a contact surface with the lower end plate cover 170S of the first embodiment).
  • a refrigerant introduction portion 165S6 that is an annular groove having a depth of 1 mm or less surrounding the auxiliary bearing portion 161S is formed inside the plurality of bolt holes 137.
  • the refrigerant introduction portion 165S6 communicates with the lower discharge chamber recess 163S, and the other end communicates with the lower discharge valve accommodation recess 164S (the refrigerant introduction portion 165S6 is connected to the lower discharge chamber recess 163S or the lower discharge valve accommodation recess 164S). You may communicate with only one of them).
  • the refrigerant introduction portion 165S6 communicates with the lower discharge chamber recess 163S or the lower discharge valve housing recess 164S, so that the high-temperature and high-pressure refrigerant discharged from the lower discharge hole 190S passes through the lower discharge chamber recess 163S or the lower discharge valve housing recess 164S. Then, it is guided to the refrigerant introduction part 165S6.
  • the lower end plate cover 170S is heated and the lower part of the compressor casing 10 of the rotary compressor 1 is started when the air conditioner is started from a state of being stopped for a long time.
  • the liquid refrigerant 19 (see FIG. 1) staying in the chamber is heated and vaporized as soon as possible, and the liquid refrigerant 19 is sucked up instead of the lubricating oil 18 for a long time to prevent the sliding portion of the compression section 12 from being damaged. be able to.
  • the volume of the space of the refrigerant introduction portion 165S6 is small within a range in which the heating amount necessary for vaporizing the liquid refrigerant 19 can be secured. Therefore, the depth of the refrigerant introduction part 165S6 is made shallow within a range in which a heating amount necessary for vaporizing the liquid refrigerant 19 can be secured.
  • FIG. 11 is a bottom view showing a state where the lower end plate and the lower end plate cover of the rotary compressor according to the seventh embodiment are overlapped.
  • auxiliary bolts 176 for fastening the lower end plate 160S6 of the sixth embodiment and the lower cylinder 121S to the flat bottom plate cover 170S7.
  • Two auxiliary bolt escape holes 171S7 are provided to prevent the head from hitting the lower end plate cover 170S7.
  • a part of the auxiliary bolt escape hole 171S7 overlaps and communicates with the refrigerant introduction part 165S6 formed in the lower end plate 160S6, and serves as a refrigerant discharge part 172S7.
  • the auxiliary bolt escape hole 171S7 does not overlap with the refrigerant introduction part 165S6, the lower discharge plate recess 170S7 (170S, 170S2) is separately communicated with the lower discharge chamber recess 163S, the lower discharge valve housing recess 164S, or the refrigerant introduction part 165S6.
  • a small hole (not shown) is provided, and this small hole may be used as the refrigerant discharge portion 172S7.
  • the refrigerant discharge unit 172S7 discharges the compressed refrigerant directly into the compressor casing 10 without passing through the refrigerant passage hole 136.
  • the refrigerant discharge portion 172S7 prevents the lowering of the efficiency and noise caused by the lubricating oil 18 accumulating in the lower discharge chamber recess 163S and the lower discharge valve housing recess 164S of the lower end plate 160S6 and the lower discharge hole 190S being immersed in the lubricating oil 18. Can do.
  • the refrigerant discharged from the refrigerant discharge unit 172S7 heats the liquid refrigerant 19 (see FIG. 1) that stays in the lower portion of the compressor housing 10 while stopped for a long time. It also has the effect of promoting vaporization.
  • the embodiment has been described above, but the embodiment is not limited by the above-described content.
  • the above-described constituent elements include those that can be easily assumed by those skilled in the art, those that are substantially the same, and those in a so-called equivalent range.
  • the above-described components can be appropriately combined.
  • at least one of various omissions, substitutions, and changes of the components can be made without departing from the scope of the embodiments.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

Ce compresseur rotatif est caractérisé en ce qu'un recouvrement de plaque d'extrémité inférieure est façonné en forme de plaque, en ce qu'une plaque d'extrémité inférieure (160S) présente une concavité de chambre d'évacuation inférieure (163S) formée de manière à chevaucher un trou d'évacuation inférieur (190S) d'une concavité de logement de soupape d'évacuation inférieure (164S), en ce que la concavité de chambre d'évacuation inférieure (163S) est formée à l'intérieur d'une plage de forme sectorielle se situant entre un diamètre (L3) passant à travers le centre (O1) d'une partie de sous-palier (161S) et un point médian (O4) d'un segment de ligne (L2) interconnectant le centre du trou d'évacuation inférieur (190S) et le centre (O3) d'un rivet inférieur (202S), et un diamètre (L4) ouvert à un angle de pas de 90 degrés autour du centre (O1) de la partie de sous-palier (161S) dans la direction du trou de décharge inférieur (190S), en ce qu'un trou de passage de réfrigérant (136) est agencé au niveau d'une certaine position de manière à être en communication avec la concavité de chambre d'évacuation inférieure (163S) et de manière à chevaucher au moins partiellement cette concavité de chambre d'évacuation inférieure (163S), et en ce qu'une chambre de recouvrement de plaque d'extrémité inférieure (180S) est conçue avec la concavité de chambre d'évacuation inférieure (163S) et la concavité de logement de soupape d'évacuation inférieure (164S).
PCT/JP2015/084844 2014-12-19 2015-12-11 Compresseur rotatif WO2016098710A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
AU2015364875A AU2015364875B2 (en) 2014-12-19 2015-12-11 Rotary compressor
EP15869915.7A EP3236075B1 (fr) 2014-12-19 2015-12-11 Compresseur rotatif
CN201580068370.1A CN107002686B (zh) 2014-12-19 2015-12-11 旋转式压缩机
US15/537,394 US10458408B2 (en) 2014-12-19 2015-12-11 Rotary compressor having communication path hole overlap with discharge chamber concave portion

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
JP2014-257818 2014-12-19
JP2014257818A JP6112104B2 (ja) 2014-12-19 2014-12-19 ロータリ圧縮機
JP2015215273 2015-10-30
JP2015-215273 2015-10-30
JP2015235213A JP6128194B2 (ja) 2015-10-30 2015-12-01 ロータリ圧縮機
JP2015-235213 2015-12-01

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CN106014987A (zh) * 2016-07-15 2016-10-12 珠海凌达压缩机有限公司 压缩机及其气缸
JP2018009534A (ja) * 2016-07-14 2018-01-18 株式会社富士通ゼネラル ロータリ圧縮機
EP3321507A1 (fr) * 2016-11-14 2018-05-16 Fujitsu General Limited Compresseur rotatif
JP2018076802A (ja) * 2016-11-08 2018-05-17 株式会社富士通ゼネラル ロータリ圧縮機
WO2018189827A1 (fr) * 2017-04-12 2018-10-18 三菱電機株式会社 Compresseur à carter renfermé et dispositif à cycle frigorifique
JP6418294B1 (ja) * 2017-08-24 2018-11-07 株式会社富士通ゼネラル ロータリ圧縮機
US10458408B2 (en) 2014-12-19 2019-10-29 Fujitsu General Limited Rotary compressor having communication path hole overlap with discharge chamber concave portion
US20230050050A1 (en) * 2020-01-29 2023-02-16 Fujitsu General Limited Rotary compressor

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WO2014002457A1 (fr) * 2012-06-26 2014-01-03 パナソニック株式会社 Compresseur rotatif
JP2014145318A (ja) * 2013-01-29 2014-08-14 Fujitsu General Ltd ロータリ圧縮機

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JPH11132177A (ja) * 1997-10-30 1999-05-18 Toshiba Corp ロータリコンプレッサ
WO2014002457A1 (fr) * 2012-06-26 2014-01-03 パナソニック株式会社 Compresseur rotatif
JP2014145318A (ja) * 2013-01-29 2014-08-14 Fujitsu General Ltd ロータリ圧縮機

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Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10458408B2 (en) 2014-12-19 2019-10-29 Fujitsu General Limited Rotary compressor having communication path hole overlap with discharge chamber concave portion
JP2018009534A (ja) * 2016-07-14 2018-01-18 株式会社富士通ゼネラル ロータリ圧縮機
CN107620706A (zh) * 2016-07-14 2018-01-23 富士通将军股份有限公司 旋转式压缩机
US10738779B2 (en) 2016-07-14 2020-08-11 Fujitsu General Limited Rotary compressor
CN106014987A (zh) * 2016-07-15 2016-10-12 珠海凌达压缩机有限公司 压缩机及其气缸
JP2018076802A (ja) * 2016-11-08 2018-05-17 株式会社富士通ゼネラル ロータリ圧縮機
WO2018088409A1 (fr) * 2016-11-08 2018-05-17 株式会社富士通ゼネラル Compresseur rotatif
US10563655B2 (en) 2016-11-14 2020-02-18 Fujitsu General Limited Rotary compressor for compressing refrigerant using cylinder
CN108071588A (zh) * 2016-11-14 2018-05-25 富士通将军股份有限公司 旋转式压缩机
JP2018080589A (ja) * 2016-11-14 2018-05-24 株式会社富士通ゼネラル ロータリ圧縮機
EP3321507A1 (fr) * 2016-11-14 2018-05-16 Fujitsu General Limited Compresseur rotatif
CN108071588B (zh) * 2016-11-14 2020-12-25 富士通将军股份有限公司 旋转式压缩机
JP7044463B2 (ja) 2016-11-14 2022-03-30 株式会社富士通ゼネラル ロータリ圧縮機
AU2017251728B2 (en) * 2016-11-14 2022-11-24 Fujitsu General Limited Rotary compressor
WO2018189827A1 (fr) * 2017-04-12 2018-10-18 三菱電機株式会社 Compresseur à carter renfermé et dispositif à cycle frigorifique
JP6418294B1 (ja) * 2017-08-24 2018-11-07 株式会社富士通ゼネラル ロータリ圧縮機
WO2019039182A1 (fr) * 2017-08-24 2019-02-28 株式会社富士通ゼネラル Compresseur rotatif
US20230050050A1 (en) * 2020-01-29 2023-02-16 Fujitsu General Limited Rotary compressor
US11959480B2 (en) * 2020-01-29 2024-04-16 Fujitsu General Limited Rotary compressor including a plurality of recessed portions for retaining lubricating oil

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