WO2013172144A1 - Compresseur de gaz - Google Patents

Compresseur de gaz Download PDF

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Publication number
WO2013172144A1
WO2013172144A1 PCT/JP2013/061378 JP2013061378W WO2013172144A1 WO 2013172144 A1 WO2013172144 A1 WO 2013172144A1 JP 2013061378 W JP2013061378 W JP 2013061378W WO 2013172144 A1 WO2013172144 A1 WO 2013172144A1
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WO
WIPO (PCT)
Prior art keywords
rotor
discharge
chamber
compressor
peripheral surface
Prior art date
Application number
PCT/JP2013/061378
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English (en)
Japanese (ja)
Inventor
川村　誠
Original Assignee
カルソニックカンセイ株式会社
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 カルソニックカンセイ株式会社 filed Critical カルソニックカンセイ株式会社
Priority to CN201380025764.XA priority Critical patent/CN104302923A/zh
Publication of WO2013172144A1 publication Critical patent/WO2013172144A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C18/3441—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/20—Rotors

Definitions

  • the present invention relates to a gas compressor, and more particularly, to an improvement of a vane rotary type gas compressor.
  • a gas compressor for compressing a gas such as a refrigerant gas and circulating the gas in the air conditioning system is used.
  • a compressor main body that is driven to rotate and compresses gas is accommodated in the housing, and high-pressure gas is discharged from the compressor main body into the housing by the housing and the compressor main body.
  • a discharge chamber is formed in a partitioned manner, and high-pressure gas is discharged from the discharge chamber to the outside of the housing.
  • the compressor body includes a rotating shaft that rotates about an axis, a substantially cylindrical rotor that rotates integrally with the rotating shaft, and a contour that surrounds the rotor from the outer peripheral surface of the rotor with a clearance from the outer peripheral surface of the rotor.
  • a cylinder having a shape inner peripheral surface, a plurality of plate-like vanes provided so as to protrude outward from the outer peripheral surface of the rotor, and a bearing that rotatably supports a rotating shaft protruding from both end surfaces of the rotor.
  • a cylinder chamber which is a space in which gas is sucked, compressed, and discharged, is formed.
  • each vane protruding from the outer peripheral surface of the rotor is in contact with the inner peripheral surface of the cylinder, so that the cylinder chamber is divided into a plurality of spaces, and the plurality of spaces formed by the division are respectively It becomes a compression chamber.
  • each compression chamber is defined by the outer peripheral surface of the rotor, the inner peripheral surface of the cylinder, the inner surfaces of both side blocks, and the surfaces of two vanes that follow each other along the rotation direction of the rotor.
  • the volume of each compression chamber changes according to the rotation of the rotating shaft and the rotor, and in the stroke in which the volume increases, the gas is sucked into the compression chamber, and in the stroke in which the volume decreases, the gas in the compression chamber is compressed, In the process of further reducing the volume of the compression chamber, the gas compressed to a high pressure in the compression chamber is discharged into the discharge chamber.
  • the configuration for realizing the process of discharging the high-pressure gas from the compression chamber is, for example, the gas discharged from the compression chamber between the cylinder that is the outer peripheral wall of the compression chamber and the housing disposed further outside the cylinder.
  • the discharge hole that is a passage formed in the cylinder so as to allow the compression chamber and the discharge chamber to communicate with each other, It is equipped with a discharge valve that opens and closes the discharge hole, and discharges the gas discharged to the discharge chamber through a discharge port formed as a passage through these spaces in the side block that partitions the discharge chamber and the discharge chamber. It flows in the chamber (Patent Document 1).
  • This invention is made in view of the said situation, Comprising: It aims at providing the gas compressor which can reduce components, such as a discharge valve, and can reduce manufacturing cost.
  • the gas compressor according to the present invention includes a rotor in each compression chamber of the compressor main body and a side block facing the discharge chamber formed by partitioning the housing and the compressor main body with a predetermined axis around the rotor axis.
  • the gas compressor according to the present invention includes a substantially cylindrical rotor that rotates around an axis inside the housing, and a contour shape that surrounds the rotor from the outer peripheral surface of the rotor with a clearance from the outer peripheral surface of the rotor.
  • a cylinder having an inner peripheral surface, a plurality of plate-like vanes provided so as to protrude outwardly from the outer peripheral surface of the rotor, and two end surfaces of the rotor and the cylinder in contact with the two end surfaces.
  • a compressor body having two side blocks, and a discharge chamber into which high-pressure gas discharged from the compressor body is discharged is formed in the housing, and the rotor is formed in the compressor body.
  • a compression chamber partitioned by an outer peripheral surface of the rotor, an inner peripheral surface of the cylinder, inner surfaces of the side blocks, and the vanes, and has a predetermined rotation angle range around the axis of the rotor.
  • a discharge passage formed between the compression chamber and the discharge chamber is formed in the rotor and the side block, and the gas compressed in the compression chamber passes through the discharge passage in the predetermined rotation angle range. It is characterized by being discharged.
  • the gas compressor according to the present invention it is possible to reduce the manufacturing cost by reducing parts such as a discharge valve.
  • FIG. 4 is a view showing a cross section taken along line AA in FIG. 3.
  • attached was integrated in the cylinder.
  • FIG. 7B is a schematic cross-sectional view corresponding to FIG.
  • FIG. 7B illustrating the operation of the compressor according to the embodiment, and shows a state where the upstream discharge passage in the rotation direction of the rotor starts to communicate. It is typical sectional drawing equivalent to FIG. 7B explaining the effect
  • FIG. 7B is a schematic cross-sectional view corresponding to FIG. 7B, illustrating the operation of the compressor according to the embodiment, and shows a state in which the discharge passage on the downstream side in the rotation direction of the rotor starts to communicate.
  • FIG. 7B is a schematic cross-sectional view corresponding to FIG. 7B, illustrating the operation of the compressor according to the embodiment, and shows a state where the downstream discharge passage finishes communicating.
  • FIG. 7B is a schematic cross-sectional view corresponding to FIG. 7B, illustrating the operation of the compressor according to the embodiment, and shows a state where the downstream discharge passage finishes communicating.
  • FIG. 9 is a cross-sectional view of an essential part corresponding to FIGS. 8A to 8D, showing a modification in which two discharge holes of the rear side block are merged into one. It is a perspective view which shows the rotor in the compressor of other embodiment. It is a perspective view which shows an example of the rear side block combined with the rotor shown in FIG. It is a typical principal part sectional view explaining the operation of the compressor of other embodiments, and shows the state where only the discharge passage on the upstream side in the rotation direction of the rotor began to communicate. It is a typical principal part sectional view explaining an operation of a compressor of other embodiments, and shows a state where only an upstream discharge passage is connected.
  • a vane rotary compressor 100 (hereinafter simply referred to as a compressor 100), which is an embodiment of a gas compressor according to the present invention, is an air having an evaporator, a gas compressor, a condenser, and an expansion valve installed in an automobile or the like. Used as a gas compressor in harmony systems.
  • This air conditioning system constitutes a refrigeration cycle by circulating a refrigerant gas G (gas).
  • the compressor 100 has a configuration in which a compressor main body 60 is accommodated in a housing 10 mainly composed of a main body case 11 and a front cover 12.
  • the main body case 11 has a substantially cylindrical shape, and is formed such that one end of the cylindrical shape is closed, and the other end is opened.
  • the front cover 12 is formed in a lid shape so as to close the opening in a state of being in contact with the opening side end portion of the main body case 11. In this state, the front cover 12 is fastened to the main body case 11 by the fastening member 18. 11 and a housing 10 having a space inside is formed.
  • the front cover 12 is formed with a suction port 12a through which the low-pressure refrigerant gas G is introduced from the evaporator of the air conditioning system into the housing 10 through the inside and the outside of the housing 10.
  • the main body case 11 is formed with a discharge port 11a through which the high-pressure refrigerant gas G is discharged from the inside of the housing 10 to the condenser of the air conditioning system through the inside and the outside of the housing 10.
  • the compressor main body 60 accommodated in the housing 10 includes a rotary shaft 51 that is rotatable around an axis C, a substantially cylindrical rotor 50 that rotates integrally with the rotary shaft 51, and the rotor 50.
  • a cylinder 40 having a contoured inner peripheral surface 41 surrounding the outer peripheral surface 52 from the outside, and three plate-like members provided so as to protrude from the outer peripheral surface 52 of the rotor 50 toward the inner peripheral surface 41 of the cylinder 40.
  • a vane 58 and two side blocks (front side block 20 and rear side block 30) that block both ends of the rotor 50 and the cylinder 40 are provided.
  • the rotating shaft 51 has a shaft center C by a bearing 12 b formed on the front cover 12 and bearings 27 and 37 formed on the side blocks 20 and 30 of the compressor body 60.
  • a portion of the rotating shaft 51 that protrudes from the front cover 12 to the outside is supported so as to be rotatable about the rotation shaft, and a pulley or the like is provided. 51 rotates around the axis C.
  • the compressor main body 60 partitions the space inside the housing 10 into a left space and a right space sandwiching the compressor main body 60.
  • the front side block 20 is in contact with the front cover 12 to maintain the airtightness of the left space, while the rear side block 30 is in contact with the main body case 11 to maintain the airtightness of the right space.
  • the space on the left side of the compressor main body 60 is a suction chamber 13 in a low-pressure atmosphere into which low-pressure refrigerant gas G is introduced from the evaporator through the suction port 12a.
  • the space on the right side of the compressor main body 60 in the drawing is a discharge chamber 14 having a high-pressure atmosphere in which high-pressure refrigerant gas G is discharged to the condenser through the discharge port 11a.
  • the compressor main body 60 has a substantially C-shaped single unit surrounded by an inner peripheral surface 41 of the cylinder 40, an outer peripheral surface 52 of the rotor 50, and both side blocks 20 and 30.
  • a cylinder chamber 42 is formed.
  • the inner peripheral surface 41 of the cylinder 40 and the outer peripheral surface 52 of the rotor 50 are close to each other in one range (angle 360 [degrees]) around the axis C of the rotating shaft 51.
  • the contour shape of the inner peripheral surface 41 of the cylinder 40 is set, whereby the cylinder chamber 42 forms a single space.
  • the proximity portion 48 formed as a portion where the inner peripheral surface 41 of the cylinder 40 and the outer peripheral surface 52 of the rotor 50 are closest to each other in the contour shape of the inner peripheral surface 41 of the cylinder 40 is the inner peripheral surface 41 of the cylinder 40. From the remote portion 49 formed as the most distant portion of the rotor 50 and the outer peripheral surface 52 of the rotor 50 along the rotational direction W of the rotor 50 (counterclockwise direction in FIG. 4) at an angle of 270 degrees or more ( 360 [degrees] or less).
  • the contour shape of the inner peripheral surface 41 of the cylinder 40 is such that the outer peripheral surface 52 of the rotor 50 and the inner peripheral surface 41 of the cylinder 40 extend from the remote portion 49 to the proximity portion 48 along the rotation direction 51 of the rotating shaft 51 and the rotor 50.
  • the shape is set such that the distance between and gradually decreases.
  • the vane 58 is fitted in a vane groove 59 formed in the rotor 50, and protrudes outward from the outer peripheral surface 52 of the rotor 50 due to the back pressure by the refrigerating machine oil R supplied to the vane groove 59.
  • the vane 58 partitions the single cylinder chamber 42 into a plurality of compression chambers 43, and one compression chamber 43 is formed by two vanes 58 that move back and forth along the rotation direction W of the rotating shaft 51 and the rotor 50. It is formed. Therefore, in the present embodiment in which the three vanes 58 are installed around the rotation shaft 51 at equal angular intervals of 120 [degrees], three to four compression chambers 43 are formed.
  • the compression chamber in which the proximity portion exists between the two vanes 58 and 58 a single closed space is formed by the proximity portion and one vane, so that the space between the two vanes 58 and 58 is between them.
  • the compression chamber 43 in which the proximity portion is present becomes two compression chambers, so that four compression chambers 43 are formed even for three vanes.
  • the internal volume of the compression chamber 43 obtained by partitioning the cylinder chamber 42 by the vane 58 gradually decreases along the rotation direction W from the remote portion 49 to the proximity portion 48, and from the proximity portion 48. It rapidly grows up to the remote part 49.
  • a suction hole formed in the front side block 20 and leading to the suction chamber 13 is formed in the most upstream side portion of the cylinder chamber 42 in one rotation along the rotation direction W with respect to the proximity portion 48.
  • the volume of the compression chamber 43 increases with the rotation of the rotor 50, the refrigerant gas from the suction chamber 13 through the suction hole 23 flows into the compression chamber 43 located on the downstream side of the proximity portion 48. G is inhaled.
  • the suction hole 23 is formed up to the vicinity of the position of the vane 58 that partitions the upstream side (rear side in the rotation direction W) of the compression chamber 43 when the volume of the compression chamber 43 becomes maximum in one rotation of the rotor 50. Therefore, the refrigerant gas G is sucked into the compression chamber 43 until the compression chamber 43 is in the rotation angle range including the remote portion 49 and the volume thereof is maximized.
  • the period in which the compression chamber 43 faces the suction hole 23 is a suction stroke for sucking the refrigerant gas G into the compression chamber 43.
  • the inner circumferential surface 41 of the cylinder 40 and the outer circumferential surface 52 of the rotor 50 move toward the downstream side in the rotation direction W. Since the contour shape of the inner peripheral surface 41 is set so that the interval gradually decreases, the volume of the compression chamber 43 decreases with the rotation of the rotor 50, and the refrigerant gas G confined inside the compression chamber 43. Is compressed. Therefore, this process becomes a compression process.
  • the portion of the rotor 50 corresponding to each compression chamber 43 has a rear side block from the outer peripheral surface 52 of the rotor 50 near the vane 58 that partitions the upstream side in the rotation direction W.
  • a notch 54 (a part of the discharge passage formed in the rotor) is formed up to an end face 53 (hereinafter referred to as a rear side block facing surface 53) on the side facing 30.
  • a surface 35 of the rear side block 30 facing the rear side block facing surface 53 (hereinafter referred to as a rotor facing surface 35) communicates from the rotor facing surface 35 to the discharge chamber 14.
  • Discharge holes 38 and 39 (a part of the discharge passage formed in the side block) are formed.
  • Each of the discharge holes 38 and 39 has an arc shape along the rotation direction W (clockwise in FIG. 7A) of the rotor, and shallow grooves 38b and 39b (long holes) that do not penetrate to the discharge chamber 14, and these shallow grooves 38b, A part of 39b includes through holes 38a and 39a penetrating to the discharge chamber 14.
  • the through hole 38a is formed in an end portion (side closer to the rotation angle position ⁇ 3) corresponding to the downstream side in the rotation direction W of the rotor 50 in the arc-shaped shallow groove 38b.
  • the through hole 39a is formed in an end portion (side closer to the rotation angle position ⁇ 1) corresponding to the downstream side in the rotation direction W of the rotor 50 in the arc-shaped shallow groove 39b.
  • the notch 54 of the rotor 50 and the discharge holes 38 and 39 of the rear side block 30 are formed at positions where the radii from the axis C are substantially equal, as shown in FIGS. 8A, 8B, 8C, and 8D.
  • the rotor 50 is formed so as to communicate within a predetermined rotation angle range.
  • the compression chamber 43 and the discharge chamber 14 communicate with each other through the notch 54 and the discharge hole 38 or the discharge hole 39, and the refrigerant gas G compressed in the compression chamber 43 is discharged. It is discharged into the chamber 14.
  • the predetermined rotation angle range of the rotor 50 through which the notch 54 and the discharge hole 38 communicate with each other is based on the rotation angle position when the notch 54 and the proximity portion 48 coincide (the rotation angle position 0 [degree]). ) Is a range from the vicinity of the rotation angle position ⁇ 4 where the notch 54 communicates with the discharge hole 38 to the vicinity of the rotation angle position ⁇ 3 (FIGS. 8A and 8B).
  • rotation angle position when the tip of the vane 58 (the end on the side contacting the inner peripheral surface 41 of the cylinder 40) and the proximity portion 48 coincide with each other is set as a reference (rotation angle position 0 [degree])
  • rotation angle position 0 [degree] When the rotation angle position when the tip of the vane 58 (the end on the side contacting the inner peripheral surface 41 of the cylinder 40) and the proximity portion 48 coincide with each other is set as a reference (rotation angle position 0 [degree]), “predetermined The “rotational angle range” is based on the rotational angular position when the notch 54 and the proximity portion 48 coincide with each other by the phase (angle) shift between the position of the tip of the vane 58 and the position of the notch 54. In this case, the position is in front of the “predetermined rotation angle range”.
  • the predetermined rotation angle range of the rotor 50 through which the notch 54 and the discharge hole 39 communicate is also the same as when the notch 54 and the proximity portion 48 coincide with each other, as in the case where the notch 54 and the discharge hole 38 communicate with each other.
  • the range is from the vicinity of the rotation angle position ⁇ 2 where the notch 54 communicates with the discharge hole 39 to the vicinity of the rotation angle position ⁇ 1 (FIGS. 8C and 8D). .
  • the refrigerant gas G discharged into the discharge chamber 14 is discharged to an external condenser through the discharge port 11a.
  • the predetermined rotation angle range of the rotor 50 through which the cutout 54 and the discharge hole 38 communicate, and the rotor through which the cutout 54 and the discharge hole 39 communicate In a predetermined rotation angle range of 50, the refrigerant gas G inside the compression chamber 43 can be discharged into the discharge chamber 14 respectively.
  • the notch 54 as a part of the discharge passage to the discharge chamber 14 corresponding to each compression chamber 43 of the rotating rotor 50 has a rotation angle range of the rotor 50 within a predetermined rotation angle range. Only when the rotation angle position of the rotor 50 is outside the predetermined rotation angle range, the notch 54 of the rotor 50 and the rear side are communicated with the discharge holes 38 and 39 as a part of the discharge passage of the rear side block 30.
  • the discharge holes 38 and 39 of the block 30 do not communicate with each other, and the refrigerant gas G can be compressed in the compression chamber 43 as usual, and the refrigerant gas G flows backward from the discharge chamber 14 into the compression chamber 43. Can be prevented.
  • the shallow groove 38b of the discharge hole 38 and the shallow groove 39b of the discharge hole 39 formed in the rear side block 30 are elongated holes extending along the rotation direction W of the rotor 50, respectively. Not only the notch 54 formed in the rotor 50 and the discharge holes 38 and 39 formed in the rear side block 30 communicate with each other only at a specific rotation angle position, but also in the entire rotation angle range in which the long hole extends. It can be made to communicate over.
  • the compressor 100 has a refrigerant gas when the volume ratio of the compression chamber 43 reaches a specific value regardless of the pressure of the refrigerant gas G inside the compression chamber 43. G can be discharged from the compression chamber 43 to the discharge chamber 14.
  • the predetermined rotation angle range of the rotor 50 through which the notch 54 and the discharge hole 38 communicate and the predetermined rotation angle range of the rotor 50 through which the notch 54 and the discharge hole 39 communicate. Since the compression chamber 43 and the discharge chamber 14 do not communicate with each other, there is a rotation angle range in which the discharge is interrupted.
  • the width of the notch 54 (the length along the rotation direction W around the axis C) is larger than the rotation angle range from the notch rotation angle position ⁇ 2 to the rotation angle position ⁇ 3.
  • the shallow groove 38b and the shallow groove 39b are also communicated along the rotational direction W from the shallow groove 38b side (along the direction opposite to the rotational direction W from the shallow groove 39b side). Can be made continuous.
  • the refrigerant gas G inside the compression chamber 43 is discharged without being continuously interrupted from the rotation angle position ⁇ 4 to the rotation angle position ⁇ 1. It can be discharged into the chamber.
  • one of the two through holes 38a and 39a (for example, the through hole 38a) is omitted, and FIG. As shown, only one through hole (for example, the through hole 39a) may be formed.
  • the compressor main body 60 performs compression at a rate of once during one rotation along the rotation direction W around the axis C of the rotor 50, and the compression chamber.
  • the notch 54 of the rotor 50 communicates with the discharge hole 38.
  • the notch 54 faces during the period (rotation angle range) from the beginning (rotation angle position) to when the notch 54 of the rotor 50 is communicated with the discharge hole 39 (rotation angle position).
  • the compression chamber 43 continues to communicate with the discharge chamber, the refrigerant gas G is supplied from the two adjacent compression chambers 43 and 43 that are positioned in the rotation angle range and adjacent to each other along the rotation direction W of the rotor 50. At the same time in the discharge chamber 14 It is possible to pass through.
  • the shallow grooves 38b and 39b of the discharge holes 38 and 39 which are portions of the discharge passage on the side formed in the rear side block 30, are formed as long holes.
  • the part on the side may be formed as a long hole extending over a predetermined rotation angle range ⁇ along the rotation direction W of the rotor 50.
  • a long groove 55b as a part of the long hole extending over the rotation angle range ⁇ is formed, and a vent hole 55a extending from the outer peripheral surface 52 of the rotor 50 facing the compression chamber 43 to the long groove 55b is formed.
  • the vent hole 55a and the long groove 55b constitute a discharge hole 55 (a portion of the discharge passage formed in the rotor).
  • This discharge hole 55 is formed corresponding to each compression chamber 43.
  • the rear side block 30 is formed with discharge holes 38 and 39 (portions formed in the side block in the discharge passage) penetrating from the rotor facing surface 35 to the surface facing the discharge chamber 14. ing.
  • the rotation angle range between the outer edges along the rotation direction W between the discharge holes 38 and 39 is ⁇ , and the rotation angle range between the inner edges is ⁇ .
  • the discharge hole 55 of the rotor 50 and the discharge holes 38, 39 of the rear side block 30 communicate with each other, whereby the compression chamber 43 and the discharge chamber 14 communicate with each other.
  • the refrigerant gas G inside the compression chamber 43 is discharged into the discharge chamber.
  • FIG. 12A the discharge hole 55 of the rotor 50 and the discharge hole 38 of the rear side block 30 begin to communicate with each other at the rotation angle position ⁇ 4 within a predetermined rotation angle range of the rotor 50, and FIGS. , 12D, during the period in which the discharge hole 55 of the rotor 50 and the discharge hole 38 of the rear side block 30 communicate with each other, the refrigerant gas inside the compression chamber 43 through this discharge passage (discharge hole 55 and discharge hole 38). G is discharged into the discharge chamber 14.
  • the rotation angle range ⁇ between the inner edges of the two discharge holes 38 and 39 of the rear side block 30 is shorter than the rotation angle range ⁇ along the rotation direction W of the long groove 55b of the discharge hole 55 ( ⁇ ⁇ ). Is formed.
  • the refrigerant gas G discharged into the discharge chamber 14 is discharged to an external condenser through the discharge port 11a.
  • the compressor 100 of each of the embodiments described above has two discharge passages (a discharge passage having a discharge hole 38 as a part and a discharge passage having a discharge hole 39 as a part) except for the form shown in FIG.
  • a discharge passage a discharge passage having a part of the discharge hole 38, hereinafter referred to as an upstream discharge passage located upstream in the rotational direction W of the rotor 50 is
  • the pressure inside the compression chamber 43 communicated with the upstream discharge passage does not always reach a desired discharge pressure during the period when the upstream discharge passage communicates.
  • the pressure inside the compression chamber 43 has not yet reached the desired discharge pressure, but the rotation of the rotor 50 proceeds, and the upstream discharge passage. During this period, the pressure inside the compression chamber 43 may reach a desired discharge pressure.
  • the refrigerant gas G that has not reached the desired discharge pressure is discharged from the compression chamber 43 to the discharge chamber 14 through the upstream discharge passage.
  • the refrigerant gas G that has reached a desired discharge pressure is discharged into the discharge chamber 14 only the discharge passage on the upstream side of the refrigerant gas G exceeds the desired discharge pressure.
  • the rear side block 30 may be provided with a discharge valve set to open the discharge hole 38 and close the discharge hole 38 below the desired discharge pressure.
  • a discharge passage (a discharge passage having the discharge hole 39 as a part, hereinafter referred to as a downstream discharge passage) located on the downstream side in the rotation direction W of the rotor 50 is downstream of the discharge passage.
  • the pressure inside the compression chamber 43 that is in communication with the discharge passage is set to be always higher than the desired discharge pressure during the period in which the discharge passage on the downstream side is in communication. There is no need to provide a discharge valve for opening and closing the hole 39.
  • the compressor 100 of the embodiment described above has three vanes 58, but the gas compressor according to the present invention is not limited to this form, and the number of vanes is 2, 4, and 5. 6 and the like can be appropriately selected, and the same operation and effect as the above-described embodiment and the compressor 100 can be obtained also by the gas compressor to which the selected number of vanes are applied.
  • the gas compressor according to the present invention is not limited to a so-called one-stage one in which one cycle of the suction, compression, and discharge is performed only once during one rotation of the rotating shaft, and the two-stage one. However, it is preferably applied to a one-stage one that can ensure a relatively long period of the compression stroke and the discharge stroke.
  • the one-stage gas compressor performs the suction, compression, and discharge of the gas (refrigerant gas G) only for one cycle during one rotation of the rotor, the suction and compression of gas during one rotation of the rotor.
  • the gas can be compressed more slowly, reducing the required power and reducing the differential pressure between two adjacent compression chambers in the rotational direction.
  • gas leakage between the compression chambers can be suppressed.
  • the proximity portion of the inner peripheral surface of the cylinder can be formed far away from the remote portion along the rotation direction of the rotor (for example, at an angle of 270 degrees or more). It is possible to compress the gas more gently than the gas compressor having the inner peripheral surface of the contour shape that is only separated by an angle of 180 [deg.] From the angle, and the degree of reduction in efficiency can be further reduced.

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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)

Abstract

Selon l'invention, de façon à réduire les coûts de fabrication par élimination de pièces, telles que des soupapes de refoulement, un compresseur de gaz comprend, dans un corps (10), une unité principale de compresseur (60) ayant un rotor (50) qui tourne autour d'un centre axial (C), un cylindre (40), des palettes (58), un bloc côté avant (20) et un bloc côté arrière (30). Une chambre de refoulement (14), à partir de laquelle un gaz frigorigène à haute pression (G : gaz) est distribué, est formée dans le corps (10) ; une pluralité de chambres de compression (43), qui sont séparées par le rotor (50), le cylindre (40), les blocs des deux côtés (20, 30) et deux palettes (58, 58), sont formées ; une encoche (54) et des ouvertures de distribution (38, 39 : canaux de distribution) sont formés pour relier la chambre de compression (43) et la chambre de distribution (14) dans une plage d'angle de rotation prescrite autour du centre axial (C) du rotor (50) ; et le gaz frigorigène (G) est distribué de la chambre de compression (43) à la chambre de distribution (14) en passant par les canaux de distribution dans la plage d'angle de rotation prescrite.
PCT/JP2013/061378 2012-05-18 2013-04-17 Compresseur de gaz WO2013172144A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201380025764.XA CN104302923A (zh) 2012-05-18 2013-04-17 气体压缩机

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EP3252313A4 (fr) * 2015-01-28 2018-08-08 Gree Green Refrigeration Technology Center Co. Ltd. of Zhuhai Compresseur à palette et sa structure d'échappement
CN109611332A (zh) * 2017-10-05 2019-04-12 桂林航天工业学院 一种双排气压力的滚动转子式压缩机

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CN109611334B (zh) * 2017-10-05 2023-09-22 桂林航天工业学院 一种双排气压力滚动转子压缩机
CN109611337B (zh) * 2017-10-05 2023-09-26 桂林航天工业学院 一种滚动转子式压缩机
CN112145417B (zh) * 2020-07-24 2023-04-28 珠海格力电器股份有限公司 一种压缩机和空调器
CN111963433B (zh) * 2020-07-24 2022-08-05 珠海格力电器股份有限公司 一种压缩机和空调器
CN111963432B (zh) * 2020-07-24 2022-06-28 珠海格力电器股份有限公司 一种压缩机和空调器
CN111963435B (zh) * 2020-07-24 2022-08-05 珠海格力电器股份有限公司 一种压缩机和空调器

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