WO2014103974A1 - Compresseur de gaz - Google Patents

Compresseur de gaz Download PDF

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Publication number
WO2014103974A1
WO2014103974A1 PCT/JP2013/084390 JP2013084390W WO2014103974A1 WO 2014103974 A1 WO2014103974 A1 WO 2014103974A1 JP 2013084390 W JP2013084390 W JP 2013084390W WO 2014103974 A1 WO2014103974 A1 WO 2014103974A1
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WO
WIPO (PCT)
Prior art keywords
pressure
discharge
vane
rotor
vane groove
Prior art date
Application number
PCT/JP2013/084390
Other languages
English (en)
Japanese (ja)
Inventor
津田　昌宏
俊勝 宮地
貴之 飯盛
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
Priority claimed from JP2012283142A external-priority patent/JP5963666B2/ja
Priority claimed from JP2012283143A external-priority patent/JP5963667B2/ja
Priority claimed from JP2013241196A external-priority patent/JP5878157B2/ja
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
Publication of WO2014103974A1 publication Critical patent/WO2014103974A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0818—Vane tracking; control therefor
    • F01C21/0854—Vane tracking; control therefor by fluid means
    • F01C21/0872—Vane tracking; control therefor by fluid means the fluid being other than the working fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C18/3441—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • F01C21/108—Stators; Members defining the outer boundaries of the working chamber with an axial surface, e.g. side plates
    • 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
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/001—Radial sealings for working fluid
    • 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 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 (air conditioning system) is used.
  • This gas compressor discharges the high-pressure gas compressed by the compressor body housed inside the housing to the outside.
  • a vane rotary type gas compressor is known as such a gas compressor (for example, refer to Patent Document 1).
  • the vane rotary type gas compressor has a substantially cylindrical rotor whose compressor body rotates integrally with a rotation shaft, and a cylinder having a contour-shaped inner peripheral surface surrounding the rotor from the outside of the peripheral surface. And a plurality of plate-like vanes that are accommodated in vane grooves formed in the rotor and protrude outwardly from the circumferential surface of the rotor, and the outer circumferential surface of the rotor and the inner circumferential surface of the cylinder, etc.
  • a cylinder chamber which is a space in which gas is sucked, compressed, and discharged, is formed.
  • This cylinder chamber is partitioned into a plurality of compression chambers, with the protruding tip of each vane protruding outward from the outer peripheral surface of the rotor in contact with the inner peripheral surface of the cylinder.
  • each compression chamber The gas compressed to a high pressure in each compression chamber is discharged from the compressor body, and after the oil (such as refrigeration oil) mixed in the discharged gas is separated, it is discharged to the outside.
  • oil such as refrigeration oil
  • the oil separated from the gas is stored at the bottom of the discharge chamber, receives the pressure of the discharged high-pressure gas, is supplied to the vane groove through the oil passage, and functions as a back pressure that causes the vane to protrude.
  • the pressure in the compression chamber before and after the vane may be increased, and the pressure acting on the vane becomes very high. As a result, a very high pressure is required.
  • Patent Document 1 since what is described in Patent Document 1 is a structure that uses an oil component having a pressure corresponding to the pressure of the discharged gas as a back pressure, the back pressure is the pressure (high pressure) of the discharged gas. It does not exceed, and a very high pressure exceeding the pressure of the discharged gas cannot be supplied as a back pressure.
  • the present invention has been made in view of the above circumstances, and is a gas compressor capable of supplying a high pressure exceeding the pressure of the compressed gas discharged from the compression chamber as the back pressure of the vane in the final stage of the compression stroke or in the discharge stroke.
  • the purpose is to provide.
  • the gas compressor according to the present invention cuts off the communication between the rotor vane groove (back pressure space) and the oil passage after the middle stage of the compression stroke, so that the back pressure space is filled with oil (completely oil content). Not only in a state of being filled with only gas, but also in a state where a slight amount of gas is mixed), and as the compression process proceeds, the back pressure space is brought into a liquid compression state by a vane. Thus, a high pressure exceeding the pressure of the compressed gas is obtained as the back pressure of the vane in the final stage of the compression stroke or in the discharge stroke.
  • the gas compressor according to the present invention includes a substantially cylindrical rotor that rotates about an axis, and an inner peripheral surface having a contour shape that surrounds the rotor from the outer peripheral surface with a clearance from the outer peripheral surface of the rotor. And a cylinder that is inserted into a vane groove formed in the rotor, and is provided so as to protrude outwardly from the outer peripheral surface of the rotor by receiving a back pressure from refrigeration oil supplied to the vane groove from a predetermined oil passage.
  • a compressor body having a plurality of plate-like vanes and having a compression chamber formed therein that compresses gas at a rate of once during one rotation of the rotor. Is formed so as to block communication with the vane groove within a predetermined rotation angle range of the rotor.
  • a high pressure exceeding the pressure of the compressed gas discharged from the compression chamber can be supplied to the vane as a back pressure at the end of the compression stroke.
  • FIG. 2 is a cross-sectional view of the compressor body of the vane rotary compressor illustrated in FIG. 1 taken along line AA.
  • FIG. 9B is a sectional view taken along line BB in FIG. 9A.
  • FIG. 13C is a cross-sectional view taken along the line CC of FIG. 13A.
  • FIG. 17D is a sectional view taken along line DD of FIG. 17A.
  • a vane rotary compressor (hereinafter simply referred to as a “compressor”) 1 which is an embodiment of a gas compressor according to the present invention includes an evaporator, a gas compressor, a condenser, and an expansion valve (all of which are installed in an automobile or the like). It is used as a gas compressor in an air conditioning system having (not shown). This air conditioning system constitutes a refrigeration cycle by circulating a refrigerant gas G (gas).
  • the compressor 1 mainly includes a motor 90, a compressor body 60, and an oil separator 70 housed in a housing 10 including a body case 11 and a front cover 12. It is a configuration.
  • 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 while 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 a fastening member. 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 into the housing 10 from an evaporator (not shown) of the air conditioning system 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 (not shown) of the air conditioning system through the inside and the outside of the housing 10. Yes.
  • the motor 90 provided inside the main body case 11 constitutes a multiphase brushless DC motor including a permanent magnet rotor 90a and an electromagnet stator 90b.
  • the stator 90b is fitted and fixed to the inner peripheral surface of the main body case 11, and the rotating shaft 51 is fixed to the rotating rotor 90a.
  • the rotor 90a is rotationally driven by exciting the electromagnet of the stator 90b with the electric power supplied via the power connector 90c attached to the front cover 12.
  • the rotary shaft 51 is driven to rotate about its axis.
  • the compressor 1 of the present embodiment is an electric type using the motor 90, but the gas compressor according to the present invention is not limited to the electric type, and is a mechanical type. May be.
  • the compressor 1 of this embodiment is a mechanical type
  • the rotary shaft 51 is extended from the front cover 12 to the outside and protrudes from the front cover 12. What is necessary is just to set it as the structure provided in the front-end
  • the compressor main body 60 accommodated in the housing 10 together with the motor 90 is arranged side by side with the motor 90 along the direction in which the rotating shaft 51 extends, and is fixed to the main body case 11 by a fastening member 15 such as a bolt. Has been.
  • the compressor main body 60 accommodated in the housing 10 includes a rotating shaft 51 that is rotatable about an axis, a substantially cylindrical rotor 50 that rotates integrally with the rotating shaft 51, and a rotating shaft 51 that rotates integrally with the rotating shaft 51, as shown in FIG.
  • the rotor 50 is inserted into a cylinder 40 having a contoured inner peripheral surface 41 that surrounds the outer peripheral surface 52 from the outside, and a vane groove 59 formed in the rotor 50, respectively.
  • the five plate-like vanes 58 provided to protrude from the outer peripheral surface 52 of the rotor 50 toward the inner peripheral surface 41 of the cylinder 40 under the back pressure by the supplied refrigerating machine oil R, the rotor 50 and the cylinder 40.
  • the two side blocks front side block 20 and rear side block 30
  • the rotating shaft 51 is rotatably supported by bearings 12b formed on the front cover 12 and bearings 27 and 37 formed on the side blocks 20 and 30 of the compressor main body 60, respectively.
  • 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 space on the left side with respect to the compressor body 60 is supplied with the low-pressure refrigerant gas G from the evaporator through the suction port 12a, and the low-pressure refrigerant gas G is compressed.
  • the suction chamber 13 is in a low-pressure atmosphere that passes before being sucked into the machine main body 60, and the motor 90 is disposed in the suction chamber 13.
  • the space on the right side of the compressor body 60 passes before the high-pressure refrigerant gas G discharged from the compressor body 60 via the oil separator 70 is discharged from the discharge port 11a to the condenser.
  • the discharge chamber 14 is a high-pressure atmosphere.
  • the compressor main body 60 has a substantially C-shaped single body 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 cylinder 40 is arranged such that the inner circumferential surface 41 of the cylinder 40 and the outer circumferential surface 52 of the rotor 50 are close to each other in a range of one round (an angle of 360 degrees) around the axis of the rotating shaft 51.
  • the contour shape of the inner peripheral surface 41 is set, and thereby the cylinder chamber 42 forms a single space.
  • the remote portion 49 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 (the distance from the outer peripheral surface 52 of the rotor 50 is minimized).
  • 48 is formed at a position biased upstream in the rotational direction W of the rotor 50 (clockwise direction in FIG. 2).
  • the rotation angle is greater than 180 degrees along the rotation direction W of the rotor 50 (in this embodiment, the angle is 270 degrees or more (less than 360 degrees), but the degree of the bias is 58.
  • the proximity portion 48 is formed at a position that can be changed as appropriate according to the number of sheets.
  • 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 W 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 accommodated in a vane groove 59 formed in the rotor 50, and protrudes outward from the outer peripheral surface 52 of the rotor 50 by back pressure due to the refrigerating machine oil R supplied to the vane groove 59 from an oil passage described later. To do.
  • the vane 58 partitions the single cylinder chamber 42 into a plurality of compression chambers 43, and one compression chamber 43 is provided by two vanes 58 that move back and forth along the rotation direction W of the rotating shaft 51 and the rotor 50. Is formed.
  • the proximity portion 48 and the one vane 58 constitute one closed space, so that the two vanes 58 are provided.
  • the compression chamber 43 in which the proximity portion 48 exists is divided into two compression chambers 43, 43 by the proximity portion 48, so that there are six compression chambers 43 even for five vanes. Is formed.
  • the volume inside 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.
  • a portion of the cylinder chamber 42 on the most upstream side in the rotation direction W of the rotor 50 (the nearest portion on the downstream side with respect to the proximity portion 48 along the rotation direction W of the rotor 50) is formed in the front side block 20.
  • the discharge portion 45 formed in the cylinder 40 faces, and on the upstream side, the discharge hole 46b of the second discharge portion 46 formed in the cylinder 40 faces.
  • the contour shape of the inner peripheral surface 41 of the cylinder 40 is such that the refrigerant gas G is sucked into the compression chamber 43 from the suction chamber 13 through the suction hole 23 formed in the front side block 20, and the refrigerant gas G in the compression chamber 43 is drawn. It is set so that the refrigerant and the discharge of the refrigerant gas G from the compression chamber 43 to the discharge part 45 through the discharge hole 45 b are performed only for one cycle during one rotation of the rotor 50.
  • the cross-sectional contour shape of the inner peripheral surface 41 of the cylinder 40 ranges from the proximity portion 48 substantially in contact with the outer peripheral surface 52 of the rotor 50 to the remote portion 49 set within an angle of 90 degrees along the rotation direction W of the rotor 50.
  • the distance between the inner peripheral surface 41 of the cylinder 40 and the outer peripheral surface 52 of the rotor 50 increases rapidly, and the angle from the remote portion 49 to the proximity portion 48 along the rotational direction W of the rotor 50
  • the distance between the inner peripheral surface 41 of the cylinder 40 and the outer peripheral surface 52 of the rotor 50 is formed so as to be gradually reduced.
  • the pressure inside the compression chamber 43 reaches a predetermined discharge pressure. At that time, when the compression chamber 43 reaches the discharge portions 45 and 46 formed in front of the proximity portion 48, the compression is performed. This is a stroke (discharge stroke) in which the refrigerant gas G inside the chamber 43 is discharged to the discharge portions 45 and 46 through discharge holes 45b and 46b described later.
  • each compression chamber 43 repeats the suction stroke, the compression stroke, and the discharge stroke in this order, so that the low-pressure refrigerant gas G sucked from the suction chamber 13 becomes high pressure and is discharged.
  • the parts 45 and 46 are discharged into the discharge chamber 14 via the oil separator 70.
  • the oil separator 70 separates the refrigerating machine oil R from the refrigerant gas G mixed with the refrigerating machine oil R.
  • the refrigeration oil R is enclosed in order to supply the back pressure of the vane 58.
  • the refrigeration oil R may be a gap between the vane 58 and the vane groove 59, It begins to ooze from a gap between the rotor 50 and the side blocks 20 and 30.
  • the functions such as lubrication and cooling in the contact portion between the rotor 50 and both side blocks 20, 30 and the contact portion between the vane 58 and the cylinder 40 and both side blocks 20, 30 are also exhibited.
  • a part of the refrigerating machine oil R is mixed with the refrigerant gas G inside the compression chamber 43.
  • Each discharge part 45 and 46 has space (henceforth "discharge chamber") 45a and 46a enclosed by the outer peripheral surface of the cylinder 40, the internal peripheral surface of the main body case 11, and the rear side block 30.
  • the discharge chambers 45a and 46a are provided with discharge holes 45b and 46b through which the discharge chambers 45a and 46a and the compression chamber 43 pass, discharge valves 45c and 46c, and valve supports 45d and 46d.
  • the pressure of the refrigerant gas G in the compression chamber 43 is equal to or higher than the pressure in the discharge chambers 45a and 46a (the pressure of the refrigerant gas discharged to the discharge chamber 14 side (hereinafter referred to as “discharge pressure Pd”).
  • discharge pressure Pd the pressure of the refrigerant gas discharged to the discharge chamber 14 side
  • the discharge unit provided on the downstream side in the rotation direction W of the rotor 50 that is, the discharge unit 45 on the side close to the proximity unit 48 is set as the main discharge unit.
  • this discharge part 45 is called "main discharge part 45").
  • the main discharge portion 45 is a portion that always discharges the refrigerant gas G compressed in the compression chamber 43 because the pressure in the compression chamber 43 always reaches the discharge pressure Pd while the compression chamber 43 is facing. It is.
  • discharge part 46 the discharge part provided on the upstream side in the rotation direction W, that is, the discharge part 46 far from the proximity part 48 is defined as a secondary discharge part (hereinafter, referred to as “secondary discharge part”).
  • secondary discharge part 46 This discharge part 46 is referred to as “sub-discharge part 46”).
  • the sub-discharge section 46 is over-compressed in the compression chamber 43 (compressed to a pressure exceeding the discharge pressure Pd) when the discharge pressure Pd is reached before the compression chamber 43 faces the main discharge section 45. This is provided to prevent this. That is, as shown in FIG. 2, only when the pressure of the compression chamber 43 (43A) reaches the discharge pressure Pd during the period when the compression chamber 43 (43A) faces the sub-discharge portion 46, the compression chamber The refrigerant gas G inside 43 (43A) is discharged from the sub discharge part 46.
  • the refrigerant gas G inside the compression chamber 43 (43A) is not discharged from the sub discharge portion 46 but faces the main discharge portion 45. It is discharged from the main discharge part 45 during a certain period.
  • the discharge chamber 45a of the main discharge unit 45 is an oil separator attached to the outer surface of the rear side block 30 through a discharge passage 38 formed so as to penetrate to the outer surface of the rear side block 30 (the surface facing the discharge chamber 14). 70.
  • a communication passage 39 is formed on the outer peripheral portion of the cylinder 40 through the discharge chambers 45a and 46a.
  • the discharge chamber 46 a communicates with the oil separator 70 attached to the outer surface of the rear side block 30 via the communication passage 39, the discharge chamber 45 a and the discharge passage 38.
  • the oil separator 70 separates the refrigerating machine oil R mixed with the refrigerant gas G from the refrigerant gas G.
  • the oil separator 70 is discharged into the discharge chambers 45a and 46a.
  • the refrigerating machine oil R is centrifuged from the refrigerant gas G by centrifugal force generated by swirling spirally. It has a structure.
  • the refrigerating machine oil R separated from the refrigerant gas G is accumulated at the bottom of the discharge chamber 14, and the high-pressure refrigerant gas G after the refrigerating machine oil R is separated is discharged into the discharge chamber 14 and then passes through the discharge port 11a. And discharged to the condenser.
  • the refrigerating machine oil R stored at the bottom of the discharge chamber 14 passes through an oil passage 34a formed in the rear side block 30 by a high-pressure atmosphere due to the high-pressure (same as the discharge pressure Pd) refrigerant gas G discharged into the discharge chamber 14.
  • the rear side block 30 shown in FIG. 3 is supplied to the Sarai groove 31 which is a recess for supplying back pressure formed on the inner surface 35 facing the end surface 55b of the rotor 50.
  • FIG. 3 shows the rear side block 30, the front side block 20 can be expressed substantially symmetrically with respect to the rear side block 30.
  • the refrigerating machine oil R passes through the oil passages 34 a and 34 b formed in the rear side block 30, the oil passage 44 formed in the cylinder 40, and the oil passage 24 formed in the front side block 20. It is supplied to the Sarai groove 21, which is a recess for supplying back pressure, formed on the inner surface 25 facing the end surface 55 a of the rotor 50.
  • each of the Sarai grooves 21 and 31 is formed corresponding to a predetermined rotation angle range ⁇ (predetermined rotation angle range) along the rotation direction W of the rotor 50, and the oil passages 34 a and 34 b. , 44, 24 can be referred to as openings for expanding the outlets of the inner surfaces 25, 35 to a wide range ⁇ of rotation angles.
  • the rotation angle range ⁇ in which the Sarai grooves 21 and 31 are formed approaches the final stage of the compression stroke from when the compression chamber 43 is in the suction stroke (the compression chamber 43 is sub-discharged). Corresponds to the range up to the angular position).
  • the range ⁇ of the rotation angle is a position where the tip of the protruding side of the vane 58 positioned on the upstream side (rear side) in the rotation direction W of the compression chamber 43 is in contact with the proximity portion 48 of the cylinder 40 (rotation angle 0).
  • the specific range of the rotation angle range ⁇ is not limited to the illustrated range, and the cross-sectional contour shape of the inner peripheral surface 41 of the cylinder 40, the number of vanes 58, and the set discharge pressure Pd. It is set as appropriate depending on the value.
  • the oil passages 34a, 34b, 44, and 24 and the Sarai grooves 21 and 31 can be referred to as an oil passage that supplies the refrigerating machine oil R to the vane groove 59.
  • Each vane groove 59 is formed so as to penetrate to both end faces 55a and 55b of the rotor 50, and is open at these both end faces 55a and 55b.
  • the Sarai groove 21 and the vane groove 59 communicate with each other.
  • the refrigerating machine oil R is supplied from the salai groove 21 to the vane groove 59.
  • the vane groove 59 when the vane groove 59 is in the rotation angle range ⁇ (other rotation angle range) excluding the rotation angle range ⁇ in which the Sarai grooves 21 and 31 are formed, the Sarai grooves 21 and 31 and the vane groove 59 are provided. And the supply of the refrigerating machine oil R from the Sarai grooves 21 and 31 to the vane groove 59 is shut off, and the vane groove 59 becomes a closed space.
  • the refrigerating machine oil R supplied to the Sarai groove 31 of the rear side block 30 is very much between the bearing 37 of the rear side block 30 and the outer peripheral surface of the rotating shaft 51 supported by the bearing 37 from the oil passage 34a. It has passed through a narrow gap.
  • the refrigerating machine oil R has a high pressure (discharge pressure Pd) corresponding to the high pressure atmosphere in the discharge chamber 14 in the oil passage 34a, but reaches the salai groove 31 due to a pressure loss while passing through this narrow gap.
  • discharge pressure Pd discharge pressure
  • the pressure Pm is lower than the discharge pressure Pd inside the discharge chamber 14, which is an intermediate pressure Pm.
  • the intermediate pressure Pm is a pressure higher than the pressure of the refrigerant gas G (low pressure Ps) in the suction chamber 13 and lower than the pressure of the refrigerant gas G (discharge pressure Pd) in the discharge chamber 14 (Ps ⁇ Pm). ⁇ Pd).
  • the passage through which the refrigerating machine oil R passes between the oil passage 24 of the front side block 20 and the Sarai groove 21 is the bearing 27 of the front side block 20 and the outer peripheral surface of the rotary shaft 51 supported by the bearing 27. It is a very narrow gap between.
  • the refrigerating machine oil R has a high pressure (discharge pressure Pd) corresponding to the high pressure atmosphere in the discharge chamber 14 in the oil passage 24, but when it reaches the Saray groove 21 due to a pressure loss while passing through this narrow gap. Is a pressure (intermediate pressure Pm) lower than the discharge pressure Pd inside the discharge chamber 14.
  • the back pressure that is supplied from the Sarai grooves 21 and 31 to the vane groove 59 and causes the vane 58 to protrude toward the inner peripheral surface 41 of the cylinder 40 is the intermediate pressure Pm.
  • the Sarai grooves 21 and 31 are formed corresponding to a range (rotational angle range ⁇ ) from when the compression chamber 43 is in the suction stroke until it approaches the final stage of the compression stroke.
  • a range rotational angle range ⁇
  • the back pressure of the vane 58 is insufficient due to the refrigerating machine oil R having the medium pressure Pm supplied from the Sarai grooves 21 and 31 to the vane groove 59.
  • the vane groove 59 shifts to the rotation angle range ⁇ beyond the rotation angle range ⁇ in which the Sarai grooves 21 and 31 are formed, the vane groove 59 does not communicate with the Sarai grooves 21 and 31 and is frozen.
  • Supply of machine oil R was shut off and filled with supplied refrigerating machine oil R (including not only a state where it was completely filled with refrigerating machine oil R but also a state where refrigerant gas G was slightly mixed) It becomes space.
  • the vane 58 enters the bottom side of the vane groove 59 as the compression proceeds, the closed space in the vane groove 59 is in a substantially liquid compression state.
  • the rotation angle range ⁇ corresponds to the range from the position approaching the end of the compression stroke (the angular position at which the compression chamber 43 starts to face the sub-discharge section 46) to the discharge stroke. For this reason, in this range, the pressure inside the compression chamber 43 starts to exceed the intermediate pressure Pm, and the back pressure acting on the vane 58 is maintained at the intermediate pressure Pm if the vane groove 59 continues to communicate with the Sarai grooves 21 and 31. If this is the case, the vane 58 may chatter due to the pressure inside the compression chamber 43.
  • the remote portion 49 is formed to be biased to the upstream side of the rotation direction W with respect to the proximity portion 48, and specifically, the rotation direction from the remote portion 49 to the proximity portion 48.
  • the angle along W is set as wide as 270 degrees or more. For this reason, the length of the compression stroke is further increased, and the internal pressures of the two compression chambers 43A and 43B that are adjacent to each other tend to be close to the discharge pressure Pd.
  • the vane 58 that partitions both the compression chambers 43A and 43B has a high direction opposite to the back pressure (the bottom direction of the vane groove 59). Pressure becomes easy to act. For this reason, the vane 58A may chatter, resulting in a decrease in efficiency and a problem such as abnormal noise.
  • the vane groove 59 is a closed space substantially filled with the refrigerating machine oil R having the medium pressure Pm, and the vane groove 59 as the compression proceeds.
  • the entry amount of the vane 58 entering the bottom side in 59 increases.
  • the pressure inside the vane groove 59 in the substantially liquid compression state rapidly increases.
  • the back pressure acting on the vane 58A causes the discharge pressures Pd of the compression chambers 43A and 43B to be reduced.
  • the pressure Ph exceeds (Pd ⁇ Ph).
  • the pressure inside the compression chambers 43 (compression chambers 43A and 43B in FIG. 2) reaches a high pressure of about the discharge pressure Pd. Even in this case, the pressure Ph exceeding the discharge pressure Pd can be supplied as the back pressure to the vane 58 (the vane 58A in FIG. 2).
  • the pressure inside the compression chamber 43 increases as the compression proceeds.
  • the amount of the vane 58 entering the vane groove 59 increases, and the vane 58 becomes the vane. It is pushed down to the bottom side of the groove 59.
  • the pressure inside the vane groove 59 back pressure of the vane 58
  • the increase in the pressure inside the compression chamber 43 and the increase in the back pressure of the vane 58 are always associated with each other. it can.
  • the compressor 1 of the first embodiment described above is a space in which the vane groove 59 is closed in other rotation angle ranges ⁇ except for the predetermined rotation angle range ⁇ .
  • a refrigerating machine oil R having a medium pressure Pm is supplied. Therefore, the pressure inside the vane groove 59 at the time when the vane groove 59 is closed is the intermediate pressure Pm. Therefore, the starting point of the increase in the back pressure due to the liquid compression of the refrigerator oil R is the intermediate pressure Pm.
  • the compressor of the second embodiment has the same configuration as the compressor 1 of the first embodiment shown in FIGS. 1 and 2 except that both side blocks 20 and 30 are changed from those shown in FIG. 3 to those shown in FIG.
  • the structure is redundant and redundant description is omitted.
  • the rear side block 30 has a rotation angle of the Sarai groove 31 (21) along which the refrigerating machine oil R of medium pressure Pm is supplied along the rotation direction W of the rotor 50 (see FIG. 2).
  • FIG. 4 shows the rear side block 30, the front side block 20 can be expressed substantially symmetrically with respect to the rear side block 30. Therefore, the Sarai groove 21 and the high-pressure oil passage 22 are also formed in the front side block 20 as in FIG.
  • the positions where the high-pressure oil passages 22 and 32 are formed are the width of the vane groove 59 from the downstream end edge of the Sarai grooves 21 and 31 along the rotation direction W of the rotating shaft 51 or slightly more than this width. It is a position separated by a large length.
  • the vane groove 59 of the rotor 50 rotating along the rotation direction W is positioned in the rotation angle range ⁇ (from the time when the compression chamber 43 is in the suction stroke, the end of the compression stroke is approached (the compression chamber is compressed).
  • the refrigerating machine oil R of medium pressure Pm is supplied to the vane groove 59 as in the first embodiment.
  • the vane groove 59 passes through the rotation angle range ⁇ , the vane groove 59 is instantaneously closed, but immediately thereafter, the vane groove 59 leads to the high-pressure oil passages 22 and 32.
  • high-pressure (discharge pressure Pd) refrigerating machine oil R is supplied to the vane groove 59.
  • the high-pressure oil passages 22 and 32 are, for example, branched from the oil passages 24 and 34 a and communicated with the Sarai grooves 21 and 31 (gap between the bearings 27 and 37 and the outer peripheral surface of the rotating shaft 51). It opens to inner surface 25, 35 (refer FIG. 1) of both the side blocks 20 and 30 by another path
  • the high-pressure oil passages 22 and 32 have no pressure loss in the gap between the bearings 27 and 37 and the outer peripheral surface of the rotary shaft 51, so that the refrigerating machine oil R having the discharge pressure Pd that is the atmospheric pressure of the discharge chamber 14 is supplied.
  • the vane groove 59 can be supplied.
  • the high pressure (discharge pressure Pd) refrigerating machine oil R is supplied to the vane groove 59 and the time from when the vane groove 59 passes the rotation angle range ⁇ until the next time the vane groove 59 communicates with the salai grooves 21 and 31.
  • the vane groove 59 is a closed space.
  • a back pressure of a higher pressure Ph ′ (Pd ⁇ Ph ⁇ Ph ′) can be supplied to the vane 58.
  • the pressure inside the vane groove 59 at the time when the vane groove 59 is closed is set to the discharge pressure Pd higher than the intermediate pressure Pm. it can.
  • the very high pressure Ph ′ supplied as the back pressure of the vane 58 is set to a pressure higher than the pressure Ph supplied as the back pressure of the vane 58 in the first embodiment. be able to.
  • the high-pressure oil passages 22 and 32 are formed at positions away from the downstream side edge of the Sarai grooves 21 and 31 by the width of the vane groove 59 or a length slightly larger than this width.
  • the Sarai grooves 21 and 31 to which the medium pressure Pm refrigerating machine oil R is supplied communicate with the high pressure oil passages 22 and 32 to which the high pressure (discharge pressure Pd) refrigerating machine oil R is supplied. This is to prevent it.
  • the tip of the vane 58 can be held in a stable sliding state without leaving the inner peripheral surface 41 of the cylinder 40.
  • the back pressure applied to the vane 58 is further increased due to, for example, a change in the viscosity of the refrigerating machine oil R
  • the pressing load on the inner peripheral surface 41 of the cylinder 40 at the tip of the vane 58 may be excessive.
  • the tip of the vane 58 is damaged due to wear, or unnecessary power is required when the rotor 50 is driven to rotate, resulting in operating efficiency. Decreases.
  • the entire surface of the inner peripheral surface 41 of the cylinder 40 is in the entire range between the vicinity of the end of the compression process and the vicinity of the proximity portion 48 along the rotation direction W of the rotor 50.
  • Fine recesses A are formed by well-known shot peening.
  • the formation range of the fine recesses A on the surface of the inner peripheral surface 41 of the cylinder 40 is such that the vane groove 59 is the salais of both side blocks 20 and 30 as shown in FIG.
  • the range of the rotation angle range ⁇ beyond the rotation angle range ⁇ in which the grooves 21 and 31 are formed corresponds to the range where the vane groove 59 is positioned in the rotation angle range ⁇ .
  • the fine recess A is not formed). That is, the formation range of the fine recess A corresponds to the closed space range in which the vane groove 59 is substantially filled with the refrigerating machine oil R of medium pressure Pm, and the back pressure acting on the vane 58 causes the discharge pressure Pd to be reduced. This is the region where the pressure Ph exceeds.
  • the formation range of the fine recesses A on the surface of the inner peripheral surface 41 of the cylinder 40 is such that the vane groove 59 is the salai groove 21 of both side blocks 20 and 30 as shown in FIG. , 31 exceeds the rotation angle range ⁇ formed and passes through the rotation angle range ⁇ communicated with the high-pressure oil passages 22, 32 to the rotation angle range from the point where the rotation angle reaches the salai grooves 21, 31.
  • the formation range of the fine recess A corresponds to the range of the closed space in which the vane groove 59 is in the liquid compression state with the refrigerating machine oil R having the medium pressure Pm, and the back pressure acting on the vane 58 is higher pressure Ph ′. This is the area.
  • the fine recess A on the surface of the inner peripheral surface 41 of the cylinder 40 causes a large number of hard shot materials having a particle size of several ⁇ m to several tens of ⁇ m to collide with the surface of the inner peripheral surface 41 at high speed.
  • the surface layer portion is work-hardened.
  • the shot material used is preferably molybdenum disulfide powder having high lubricating performance as a solid lubricant.
  • the formation range of the fine recesses A is formed so that the vane groove 59 is formed corresponding to only the range of the closed space in the liquid compression state with the refrigerating machine oil R having the medium pressure Pm. It is not necessary to provide the entire circumference, and the working time can be shortened and the working cost can be reduced.
  • FIG. 7A shows changes in the vane back pressure (a in the figure) acting on the vane 58 and changes in the pressure in the compression chamber 43 (b in the figure) in the intake stroke, compression stroke, and discharge stroke of the compressor 1 described above. It is a figure. 7A, Pd is the discharge pressure (high pressure) value, and Ps is the pressure (low pressure) value of the refrigerant gas sucked into the compression chamber 43.
  • the rotation angle of the rotor 50 is near 0 degrees (360 degrees) when the vane 58 is positioned near the proximity portion 48 along the rotation direction W of the compression chamber 43 (the discharge stroke and the discharge stroke).
  • the rotor 50 makes one rotation (the rotation angle is 0 to 360 degrees), whereby the one-stroke suction stroke, compression stroke, and discharge stroke are performed.
  • the back pressure (vane back pressure) acting on the vane 58 rises from near the end of the compression stroke (rotation angle of the rotor 50 is around 270 degrees), and immediately before the discharge stroke (rotation of the rotor 50).
  • the pressure Ph is reached at an angle of around 355 degrees.
  • the tip of the vane 58 can be satisfactorily brought into contact with the inner peripheral surface of the cylinder 40, but in the vicinity of the end of the compression stroke (from immediately before and immediately after the discharge stroke). Then, since the pressure Ph that is significantly higher than the pressure in the compression chamber 43 (about the discharge pressure Pd) acts as the vane back pressure, the tip of the vane 58 abuts the inner peripheral surface of the cylinder 40 more strongly than necessary. There is.
  • a throttle hole 80 for releasing a part of the back pressure is formed in the inner surface 35 of the rear side block 30.
  • the throttle hole 80 is in the rotation angle range ⁇ excluding the rotation angle range ⁇ in which the salai groove 31 is formed, and is near the end of the compression stroke (near the discharge stroke in the main discharge portion 45). It is formed corresponding to the region.
  • the throttle hole 80 communicates with the oil discharge port 81 formed in the outer surface 36 of the rear side block 30 through a passage 82.
  • the passage 82 is included in a part of the throttle hole 80, and the throttle hole 80 and the passage 82 constitute the entire throttle hole.
  • an oil separator (not shown) is installed at the oil discharge port 81 of the outer surface 36 of the rear side block 30.
  • the oil discharge port 81 communicates with the discharge path 38 via an oil flow path groove 83.
  • the throttle hole 80 communicates with the bottom 59 a in the vane groove 59.
  • the refrigerating machine oil R refrigerant gas is mixed
  • the oil separator 70 see FIG. 1 from the oil discharge port 81.
  • the refrigerating machine oil discharged to the oil separator 70 is returned to the bottom in the discharge chamber 14.
  • a part of the refrigerating machine oil that is supplied to the bottom 59a in the vane groove 59 and is in a liquid compressed state passes through the passage 82 in the rear side block 30 from the throttle hole 80 to the oil separator 81.
  • 70 discharge chamber 14
  • the same hole is formed on the front side block 20 side, and the hole is discharged from the hole to the suction chamber 13 through a passage formed in the front side block 20. It may be.
  • the back pressure (vane back pressure) acting on the vane 58 increases from the vicinity of the end of the compression stroke (rotation angle of the rotor 50 is about 270 degrees), and immediately before the discharge stroke (the rotation of the rotor 50).
  • the pressure Ph is reached at a rotation angle of around 355 degrees.
  • the tip of the vane 58 can be satisfactorily brought into contact with the inner peripheral surface of the cylinder 40, but in the vicinity of the end of the compression stroke (from immediately before and immediately after the discharge stroke). Then, since the pressure Ph that is significantly higher than the pressure in the compression chamber 43 (about the discharge pressure Pd) acts as the vane back pressure, the tip of the vane 58 abuts the inner peripheral surface of the cylinder 40 more strongly than necessary. There is.
  • a hole 100 for releasing a part of the back pressure is formed in the inner surface 35 of the rear side block 30.
  • This hole 100 is a region that is in the vicinity of the end of the compression stroke (near the immediately before the discharge stroke in the main discharge portion 45) in the rotation angle range ⁇ excluding the rotation angle range ⁇ in which the salai groove 31 is formed. It is formed corresponding to.
  • the hole 100 further has a discharge stroke in the main discharge section 45 from the vicinity of the final stage of the compression stroke within a rotation angle range ⁇ excluding the rotation angle range ⁇ in which the salai groove 31 is formed. It is provided near one end (in the vicinity of the right end of the communication groove 81 in FIG. 11) in the concave communication groove 84 formed corresponding to the nearby region.
  • FIG. 12 shows the positional relationship among the hole 100, the communication groove 84, and the vane groove 59.
  • the hole 100 communicates with the oil discharge port 81 formed in the outer surface 36 of the rear side block 30 through the passage 82.
  • the passage 82 is included in a part of the hole 100, and the hole 100 and the passage 82 constitute the whole hole.
  • an oil separator (not shown) is installed at the oil discharge port 81 on the outer surface 36 of the rear side block 30.
  • the oil discharge port 81 communicates with the discharge path 38 through an oil passage groove 83.
  • a trigger valve type pressure regulating valve (hereinafter referred to as “first relief valve”) 85 is disposed in the large diameter portion formed on the oil discharge port 81 side of the passage 82.
  • the first relief valve 85 includes a spherical valve body 86 and a spring member 87, and normally the valve body 86 is urged by the urging force (spring force) of the spring member 87 to close the small diameter side of the passage 82. The valve is closed.
  • the first relief valve 85 has a pressure between the vane groove 59 (vane back pressure) and a discharge pressure (a discharge pressure of high-pressure gas (refrigerant gas) discharged into the discharge chamber 14 through the discharge path 38 in the discharge stroke).
  • a predetermined pressure Pa ⁇ Ph
  • the valve is closed.
  • the valve is opened against the biasing force of the spring member 87. It is configured as follows.
  • the communication groove 84 communicates with the bottom 59 a in the vane groove 59 from the vicinity of the end of the compression stroke to the vicinity of the end of the compression stroke (nearly immediately after the discharge stroke). It is in a positional relationship.
  • the hole 100 is in communication with the bottom 59a in the vane groove 59 through the communication groove 84, so that one of the vane back pressures (refrigerating machine oil R supplied to the bottom 59a in the vane groove 59 and in a liquid compression state). The portion is discharged from the hole 100 to the passage 82 side.
  • the first relief valve 85 is opened against the urging force of the spring member 87 when the differential pressure becomes a predetermined pressure Pa or more, and a part of the refrigerating machine oil R in the liquid compression state is oil discharge port 81.
  • the refrigerating machine oil discharged to the oil separator 70 is returned to the bottom in the discharge chamber 14. And in a discharge process, since a vane back pressure falls, the 1st relief valve 85 will be in a valve closing state.
  • a hole 101 for releasing a part of the back pressure is formed in the inner surface 35 of the rear side block 30.
  • This hole 101 is a region that is in the rotation angle range ⁇ excluding the rotation angle range ⁇ in which the salai groove 31 is formed, and is near the end of the compression stroke (near the discharge stroke in the main discharge portion 45). It is formed corresponding to.
  • the hole 101 is in the vicinity of the discharge stroke at the main discharge portion 45 from the vicinity of the end of the compression stroke within the rotation angle range ⁇ excluding the rotation angle range ⁇ in which the saray grooves 31 are formed. It is provided in the vicinity of the other end in the concave communication groove 84 formed corresponding to the region (in FIG. 16, in the vicinity of the left end of the communication groove 84).
  • the hole 101 communicates with the outer surface 36 (that is, the discharge chamber 14: see FIG. 1) through a passage 82a formed in the rear side block 30.
  • the passage 82a is included in a part of the hole 110, and the hole 110 and the passage 82a constitute the entire hole.
  • an oil separator (not shown) is installed at the oil discharge port 81 of the outer surface 36 of the rear side block 30. Further, the oil discharge port 81 communicates with the discharge path 38 via the oil flow path groove 83.
  • a reed valve type pressure regulating valve (hereinafter referred to as “second relief valve”) 88 is disposed in a region where the passage 82a of the outer surface 36 of the rear side block 30 communicates.
  • the base end side of the second relief valve 88 is fixed to the outer surface 36 by a fixing screw 88a, and is normally in a closed state in which the passage 82a is closed by the urging force (elastic force) of the second relief valve 88.
  • the second relief valve 88 is a pressure between the pressure in the vane groove 59 (vane back pressure) and the discharge pressure (discharge pressure of the high-pressure gas (refrigerant gas) discharged into the discharge chamber 14 through the discharge path 38 in the discharge stroke).
  • the valve is operated with a differential pressure, and when the differential pressure is less than or equal to a predetermined pressure Pa ( ⁇ Ph), the valve is closed, and when the differential pressure exceeds the predetermined pressure Pa, the valve is opened.
  • the positional relationship is such that the communication groove 84 communicates with the bottom 59a in the vane groove 59 from the vicinity of the end of the compression stroke to the vicinity of the end of the compression stroke (from immediately before to immediately after the discharge stroke). is there. Accordingly, since the hole 101 is in communication with the bottom 59a in the vane groove 59 through the communication groove 84, one of the vane back pressures (refrigerating machine oil R supplied to the bottom 59a in the vane groove 59 and in a liquid compression state). The portion is discharged from the hole 101 toward the passage 82a.
  • the second relief valve 88 is opened when the differential pressure exceeds a predetermined pressure Pa, and a part of the refrigerating machine oil R in the liquid compression state passes through the passage 82a to the outer surface 36 of the rear side block 30 (that is, the discharge pressure). To the chamber 14). In addition, since the vane back pressure is reduced in the discharge stroke, the second relief valve 88 is closed.

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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

L'invention porte sur un compresseur de gaz, qui applique une contrepression à haute pression aux aubes dans l'étage final de l'étape de compression. Un corps principal de compresseur (60) est fourni dans un boîtier (10) et comprend : un rotor (50) dans lequel sont formées des rainures d'aube (59) ; un cylindre (40) ayant une surface circonférentielle intérieure (41) dont la forme de contour entoure, à partir de l'extérieur, la surface périphérique extérieure (52) du rotor (50) ; et cinq aubes du type plaque (58), qui sont introduites dans les rainures d'aube (59) et fournies de manière à pouvoir recevoir la contrepression d'une huile réfrigérante (R), acheminée des rainures de drainage (21, 31) aux rainures d'aube (59), et à faire saillie vers la surface circonférentielle intérieure (41) du cylindre (40). Une chambre de compression (43), qui comprime un gaz réfrigérant aspiré (G) une fois par rotation du rotor (50), est formée dans le corps principal de cylindre. Les rainures de drainage (21, 31) communiquent avec les rainures d'aube (59) dans une plage d'angle de rotation prescrite (α) du rotor (50), et les rainures d'aube (59) forment un espace fermé dans une autre plage d'angle de rotation (β) qui exclut la plage d'angle de rotation (α), les rainures de drainage (21, 31) communiquant avec les rainures d'aube (59).
PCT/JP2013/084390 2012-12-26 2013-12-23 Compresseur de gaz WO2014103974A1 (fr)

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
JP2012-283142 2012-12-26
JP2012283142A JP5963666B2 (ja) 2012-12-26 2012-12-26 気体圧縮機
JP2012-283143 2012-12-26
JP2012283143A JP5963667B2 (ja) 2012-12-26 2012-12-26 気体圧縮機
JP2013-241196 2013-11-21
JP2013241196A JP5878157B2 (ja) 2012-12-26 2013-11-21 気体圧縮機

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WO2014103974A1 true WO2014103974A1 (fr) 2014-07-03

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020034511A1 (fr) * 2018-08-17 2020-02-20 珠海格力电器股份有限公司 Compresseur et climatiseur présentant celui-ci

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS496733Y1 (fr) * 1968-03-30 1974-02-18
JP2001165081A (ja) * 1999-12-10 2001-06-19 Matsushita Electric Ind Co Ltd 圧縮機およびその圧縮機を有する冷凍サイクルを備えた冷凍または冷却装置
JP2001221179A (ja) * 2000-02-09 2001-08-17 Matsushita Electric Ind Co Ltd ロータリ圧縮機
JP2002339083A (ja) * 2001-05-16 2002-11-27 Honda Motor Co Ltd 二硫化モリブデン投射用材料
JP2006112331A (ja) * 2004-10-15 2006-04-27 Matsushita Electric Ind Co Ltd 圧縮機
JP2008169810A (ja) * 2007-01-15 2008-07-24 Calsonic Compressor Inc 気体圧縮機
JP2009250155A (ja) * 2008-04-09 2009-10-29 Calsonic Kansei Corp 容量可変型気体圧縮機

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS496733Y1 (fr) * 1968-03-30 1974-02-18
JP2001165081A (ja) * 1999-12-10 2001-06-19 Matsushita Electric Ind Co Ltd 圧縮機およびその圧縮機を有する冷凍サイクルを備えた冷凍または冷却装置
JP2001221179A (ja) * 2000-02-09 2001-08-17 Matsushita Electric Ind Co Ltd ロータリ圧縮機
JP2002339083A (ja) * 2001-05-16 2002-11-27 Honda Motor Co Ltd 二硫化モリブデン投射用材料
JP2006112331A (ja) * 2004-10-15 2006-04-27 Matsushita Electric Ind Co Ltd 圧縮機
JP2008169810A (ja) * 2007-01-15 2008-07-24 Calsonic Compressor Inc 気体圧縮機
JP2009250155A (ja) * 2008-04-09 2009-10-29 Calsonic Kansei Corp 容量可変型気体圧縮機

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020034511A1 (fr) * 2018-08-17 2020-02-20 珠海格力电器股份有限公司 Compresseur et climatiseur présentant celui-ci

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