EP3239530A1 - Compresseur de gaz - Google Patents

Compresseur de gaz Download PDF

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Publication number
EP3239530A1
EP3239530A1 EP15872843.6A EP15872843A EP3239530A1 EP 3239530 A1 EP3239530 A1 EP 3239530A1 EP 15872843 A EP15872843 A EP 15872843A EP 3239530 A1 EP3239530 A1 EP 3239530A1
Authority
EP
European Patent Office
Prior art keywords
supply section
vane
back pressure
pressure space
pressure
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP15872843.6A
Other languages
German (de)
English (en)
Other versions
EP3239530A4 (fr
Inventor
Masahiro Tsuda
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Marelli Corp
Original Assignee
Calsonic Kansei Corp
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 JP2014260492A external-priority patent/JP5878971B1/ja
Priority claimed from JP2014260491A external-priority patent/JP5878970B1/ja
Priority claimed from JP2014260500A external-priority patent/JP5831619B1/ja
Application filed by Calsonic Kansei Corp filed Critical Calsonic Kansei Corp
Publication of EP3239530A1 publication Critical patent/EP3239530A1/fr
Publication of EP3239530A4 publication Critical patent/EP3239530A4/fr
Withdrawn legal-status Critical Current

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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
    • 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
    • F04C18/348—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 vanes positively engaging, with circumferential play, an outer rotatable member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • F01C21/0863—Vane tracking; control therefor by fluid means the fluid being the working fluid
    • 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

Definitions

  • the present invention relates to a so-called vane rotary-type gas compressor.
  • Patent Literature 1 Conventionally, various gas compressors have been proposed as indicated in Patent Literature 1.
  • Fig. 16 shows a compression block disposed in a gas compressor pertaining to Patent Literature 1.
  • This compression block has a cylinder block 100 and a pair of side blocks 101 disposed on the left and right of the cylinder block 100.
  • a cylinder chamber 105 is formed in the cylinder block 100 and the pair of the side blocks 101.
  • the cylinder block 100 is provided with a suction port 110 and two discharge ports 108.
  • a rotor 102 is rotatably disposed in the cylinder chamber 105.
  • the rotor 102 is formed with a plurality of vane grooves 106 at intervals.
  • a vane 103 is disposed in each vane groove 106 so as to freely retractable from an outer peripheral surface of the rotor 102.
  • a back pressure space 107 (107A, 107B and 107C) is formed in the vane groove 106 on the back surface side of the vane 103. The back pressure space 107 opens to both side surfaces of the rotor 102.
  • An intermediate-pressure supply groove 113 and a high-pressure supply groove 114 are formed in a wall surface on the cylinder chamber 105 side of each side block 101, on a rotation locus of the back pressure space 107.
  • An intermediate pressure that is a pressure higher than that of a sucked refrigerant and is lower than that of the discharged refrigerant is supplied to the intermediate-pressure supply groove 113.
  • High pressure that is a pressure equivalent to that of the discharged refrigerant is supplied to the high-pressure supply groove 114.
  • Compression chambers 105a, 105b and 105c are formed in the cylinder chamber 105 by being surrounded by the two vanes 103.
  • the compression chambers 105a, 105b and 105c perform a suction process, a compression process and a discharged process and repeat this series of the processes, at the time of rotation of the rotor 102.
  • the refrigerant is sucked from the suction port 110 by gradual increase in volumes of the compression chambers 105a, 105b and 105c.
  • the refrigerant is compressed by gradual decrease in volumes of the compression chambers 105a, 105b and 105c.
  • an open/close valve 109 opens and the refrigerant is discharged from the discharge port 108.
  • each of the vane 103 although the refrigerant pressures in the compression chambers 105a, 105b and 105c press each of the vanes 103 in a direction (hereinafter, a "storage direction") in which each of the vane 103 is stored in the vane groove 106, a tip of each of the vane 103 slides along an inner wall of the cylinder chamber 105 by a back pressure acting on the back pressure space 107 and thereby the compression chambers 105a, 105b and 105c are able to reliably compress the refrigerant.
  • a storage direction hereinafter, a "storage direction”
  • an intermediate pressure from the intermediate-pressure supply groove 113 is made to act as the back pressure.
  • high pressure from the high-pressure supply groove 114 is made to act as the back pressure.
  • Patent Literature I Japanese Patent Laid-Open Publication No. 2013-194549
  • Fig. 17 is a graph showing changes in a pressure P105a in the compression chamber 105a, a pressure P105b in the compression chamber 105b and a pressure P107A in the back pressure space 107A in accordance with a rotation angle of the rotor. As shown in Fig. 17 , at an angle of 180 degrees, the back pressure space 107A having completed communication with the intermediate-pressure supply groove 113 communicates with the high-pressure supply groove 114.
  • the pressure P107B in the rotation upstream back pressure space 107B is intermediate pressure
  • the pressure P107A in the rotation downstream back pressure space 107A that communicates with the rotation upstream back pressure space 107B via the high-pressure supply groove 114 becomes temporarily lower than a pressure to be supplied to the high-pressure supply groove 114 as shown by P in Fig. 17 .
  • the pressures of the refrigerant in the compression chambers 105a, 105b and 105c which are in the later stage of the compression process and in the discharged process act in the storage direction of the vane 103, there is a possibility that the vane 103 may be temporarily stored in the vane groove 106 and chattering may occur.
  • the present invention has been made in view of the above-mentioned circumstances and an object of the present invention is to prevent occurrence of chattering of the vane by a temporary reduction in pressure in the back pressure space of the vane, for example, in the later stage of the compression process and in the discharged process, and to maintain operating performance as a gas compressor.
  • a gas compressor of the present invention includes:
  • a gas compressor 1 includes a substantially cylindrical housing 2, a compression section 3 stored in the housing 2, a motor section 4 that transmits driving force to the compression section 3 and an inverter section 5 which is fixed to the housing 2 and which controls driving of the motor section 4.
  • the housing 2 is configured by a front head 7 in which a not shown suction port is formed and a bottomed cylindrical rear case 9 whose opening is closed by the front head 7.
  • the compression section 3 is fixed to an inner wall 13 of the rear case 9.
  • the compression section 3 is formed with a suction chamber 11 on one side and is formed with a discharge chamber 15 on the other side so as to partition the inside of the housing 2.
  • a not shown discharge port which communicates the discharge chamber 15 with a refrigerating cycle is formed in an outer periphery of the rear case 9.
  • an oil sump 17 which stores an oil O for maintaining lubricity of the compression section 3 is formed under the discharge chamber 15.
  • the compression section 3 includes a compression block 19 that forms a cylinder chamber 33, an oil separator 21 fixed to the compression block 19, a rotor 23 that is rotatably stored in the cylinder chamber 33, a vane 25 (refer to Fig. 3 ) that protrudes and retracts from the rotor 23 to partition the cylinder chamber 33, and a drive shaft 27 that is fixed integrally with the rotor 23 to transmit the driving force thereto.
  • the compression block 19 is configured by a cylinder block 29, a pair of side blocks 31, and the cylinder chamber 33 formed on an inner periphery of the cylinder block 29.
  • the cylinder block 29 has the distorted elliptical cylinder chamber 33 therein. An opening of this cylinder chamber 33 is closed by holding both ends of the cylinder block 29 by the pair of the side blocks 31.
  • the rotor 23 is disposed such that one place is in contact with an inner wall of the cylinder chamber 33, is disposed with a position displaced from the center (the center of gravity) of the cylinder chamber 33 being set as the center of rotation, and is provided with a vane groove 75 that opens to an outer peripheral surface of the rotor 23, and a back pressure space 77 on the back surface side of the vane 25.
  • the cylinder chamber 33 is partitioned into a plurality of pieces in a rotation direction X of the rotor 23 by the plurality of vanes 25 that protrudes and retracts from the plurality of vane grooves 75 in the rotor 23.
  • a plurality of compression chambers 33a, 33b and 33c is formed between an inner peripheral surface 33d of the cylinder chamber 33 and an outer peripheral surface 23a of the rotor 23.
  • the cylinder block 29 is provided with a suction slot 39 through which the refrigerant is sucked into the cylinder chamber 33, a discharge slot 35 through which the refrigerant having been compressed in the cylinder chamber 33 is discharged, an open/close valve 37 which opens/closes the discharge slot 35 and a cylinder-side oil supply path 41 which communicates with an oil supply path of the side block 31.
  • the pair of the side blocks 31 are configured by a front-side block 31a and a rear-side block 31b and the oil separator 21 is fixed to the rear-side block 31b.
  • the front-side block 31a is provided with a front-side end surface 43 that abuts on the cylinder block 29, a not shown suction slot that communicates with the suction slot 39 and sucks the refrigerant from the suction chamber 11, a front-side bearing 47 that rotatably supports the drive shaft 27 and a front-side oil supply path 49 that communicates with the cylinder-side oil supply path 41.
  • the front-side end surface 43 is provided with a pressure supply groove, and the pressure supply groove includes an intermediate-pressure supply groove 51 that supplies, to the back pressure space 77, an intermediate pressure (a middle pressure) higher than that of the sucked refrigerant and lower than that of the discharged refrigerant and a high-pressure supply groove 53 that is provided at a position facing a high-pressure supply groove 69 on the rear-side block 31b side.
  • an intermediate-pressure supply groove 51 that supplies, to the back pressure space 77, an intermediate pressure (a middle pressure) higher than that of the sucked refrigerant and lower than that of the discharged refrigerant and a high-pressure supply groove 53 that is provided at a position facing a high-pressure supply groove 69 on the rear-side block 31b side.
  • front-side bearing 47 is formed with an annular front-side annular groove 55, which is provided in communication with the one-end side of the front-side oil supply path 49. Note that the other-end side of the front-side oil supply path 49 is in communication with the cylinder-side oil supply path 41.
  • the rear-side block 31b includes a rear-side end surface 57 that abuts on the cylinder block 29, an oil supply hole 59 through which the oil O stored under the discharge chamber 15 is sucked, a rear-side bearing 63 that rotatably supports the drive shaft 27, and a rear-side oil supply path 59b that communicates with the cylinder-side oil supply path 41.
  • the rear-side end surface 57 includes a discharge hole 61 through which the refrigerant having been compressed in the cylinder chamber 33 is discharged, an intermediate-pressure supply groove 67 (corresponding to an intermediate-pressure supply section in the claims) which supplies, to the back pressure space 77, the oil of intermediate pressure higher than pressure (suction pressure) of the sucked refrigerant and lower than pressure (discharged pressure) of the discharged refrigerant, and the high-pressure supply groove 69 (corresponding to a high-pressure supply section in the claims) which supplies, to the back pressure space 77, the oil of high pressure that is the pressure (the discharge pressure) of the discharged refrigerant.
  • the high-pressure supply groove 69 is divided into mutually independent first supply section 69a (corresponding to an upstream-side supply section) and second supply section 69b (corresponding to a downstream-side supply section) in the rotation direction X of the rotor 23.
  • high-pressure supply paths 71a and 71b respectively open to the first supply section 69a and the second supply section 69b, and the respective high-pressure supply paths 71a and 71b are in communication with a rear-side annular groove 73 on their one-end sides and are in communication with the first supply section 69a and the second supply section 69b, respectively, on their other-end sides.
  • the high-pressure supply groove 53 of the front-side block 31a facing the high-pressure supply groove 69 is also divided into two supply sections (not shown) which are similar to the first supply section 69a and the second supply section 69b.
  • the back pressure space 77 (refer to Fig. 3 and Fig. 4 ) formed in the rotor 23 communicates with the intermediate-pressure supply grooves 51 and 67 at a compression first-half position and communicates with the high-pressure supply grooves 53 and 69 at a compression later-half position, by rotation of the rotor 23.
  • a back pressure space 77B of the vane groove 75 in a vane 25B which partitions the compression chamber 33b having moved from a suction process to a compression process and the compression chamber 33a that is positioned on the downstream side of the compression chamber 33b in the rotation direction X of the rotor 23 and has moved from the compression process to a discharged process by rotation of the rotor 23 terminates communication with the intermediate-pressure supply groove 67.
  • the back pressure space 77B is about to communicate with the first supply section 69a that is positioned on the upstream side of the rotation direction X of the rotor 23, from now on.
  • a back pressure space 77A of the vane groove 75 in a vane 25A that precedes the vane 25B in the downstream side of the vane 25B in the rotation direction X of the rotor 23 has already completed communication with the first supply section 69a and is in communication with the second supply section 69b positioned on the downstream side in the rotation direction X.
  • the first supply section 69a is formed into a shape in which the back pressure space 77A of the preceding vane 25A and the back pressure space 77B of the next vane 25B that follows the vane 25A do not communicate with the first supply section 69a simultaneously.
  • the first supply section is formed such that an angle range in which the first supply section 69a extends becomes smaller than a difference between the angle at which the back pressure space 77A is positioned and the angle at which the back pressure space 77B is positioned.
  • a distance between the back pressure space 77A and the back pressure space 77B in the rotation direction X of the rotor 23 is set larger than a width of the first supply section 69a.
  • the second supply section 69b is formed into a shape in which the back pressure space 77A of the preceding vane 25A and the back pressure space 77B of the next vane 25B that follows the vane 25A do not communicate with the second supply section 69b simultaneously.
  • the second supply section is formed such that an angle range in which the second supply section 69b extends becomes smaller than the difference between the angle at which the back pressure space 77A is positioned and the angle at which the back pressure space 77B is positioned.
  • the distance between the back pressure space 77A and the back pressure space 77B in the rotation direction X of the rotor 23 is set larger than a width of the second supply section 69b.
  • the shapes of the first supply section 69a and the second supply section 69b are determined on the basis of the angle at which the back pressure space 77 is positioned in the rotation direction X of the rotor 23.
  • a distance between the intermediate-pressure supply groove 67 and the first supply section 69a and a distance between the second supply section 69b and the intermediate-pressure supply groove 67 in the rotation direction X of the rotor 23 are set larger than a width of the back pressure space 77 in the rotation direction X of the rotor 23.
  • the oil supply hole 59 is formed in communication with a rear-side oil supply path 59a, and the rear-side oil supply path 59b is formed by branching from the rear-side oil supply path 59a.
  • the rear-side oil supply path 59b is in communication with the cylinder-side oil supply path 41.
  • the rear-side bearing 63 is formed with the annular rear-side annular groove 73, which is in communication with a rear-side communication path 65.
  • the rear-side communication path 65 is in communication with the rear-side annular groove 73 on its one-end side and opens to the high-pressure supply groove 69 on its other-end side.
  • the oil separator 21 is fixed to the rear-side block 31b, the refrigerant having been compressed in the cylinder chamber 33 flows into the oil separator 21, and the refrigerant and the oil O are separated from each other therein.
  • the drive shaft 27 is fixed to the rotor 23 on its one side and is rotatably supported by the bearings 47 and 63 of the respective side blocks 31a and 31b.
  • the motor section 4 is fixed to the other side of the drive shaft 27.
  • the motor section 4 includes a stator 79 fixed to the inner wall 13 of the rear case 9 and a motor rotor 81 that is rotatably disposed on the inner periphery side of the stator 79 and rotates by a magnetic force.
  • the motor rotor 81 transmits a rotational drive force to the compression section 3, due to the rotation by the magnetic force.
  • the distance between the first supply section 69a and the second supply section 69b in the rotation direction X of the rotor 23 is set narrower than the width of the back pressure space 77 in the rotation direction X of the rotor 23.
  • FIG. 5 is an explanatory diagram showing a virtual example of a case where the first supply section and the second supply section of the high-pressure supply groove in Fig. 3 are separately disposed at an interval at which the back pressure space of the vane groove does not communicate with any of them.
  • Fig. 6 is a graph showing changes in a pressure P33a in the compression chamber 33a, a pressure P33b in the compression chamber 33b and a pressure P77B of the back pressure space 77B, in accordance with a rotation angle of the rotor. As shown in Fig. 6 , at an angle of 180 degrees, the back pressure space 77B having completed communication with the intermediate-pressure supply groove 67 communicates with the high-pressure supply groove 69.
  • the high-pressure supply groove 69 is constituted by the first supply section 69a and the second supply section 69b, and the back pressure space 77B communicates with the first supply section 69a and thereafter communicates with the second supply section 69b, along with rotation of the rotor 23 that rotates in the rotation direction X.
  • the vane 25B stored in the vane groove 75, the back pressure space 77B of which is positioned between the first supply section 69a and the second supply section 69b receives force acting in a direction of intruding into the vane groove 75 from the inner peripheral surface 33d of the cylinder chamber 33 since the compression chambers 33a and 33b partitioned by the vane 25B stay from the later stage of the compression process to the discharged process.
  • the back pressure space 77B is positioned between the first supply section 69a and the second supply section 69b, the volume of the back pressure space 77B is in a state of being reduced.
  • the back pressure space 77B does not communicate with any of the first supply section 69a and the second supply section 69b at this position, it is not possible to release the high pressure of the amount corresponding to the reduced volume of the back pressure space 77B to any place other than the back pressure space 77B. Accordingly, in the middle stage of shifting the communication destination of the back pressure space 77B from the first supply section 69a to the second supply section 69b, the pressure in the back pressure space 77 temporarily rises as shown by P1 in Fig. 6 .
  • the back pressure space 77 when the back pressure space 77 is in communication with the first supply section 69a and the second supply section 69b, it is possible to release the high pressure in the back pressure space 77 to the high-pressure supply paths 71a and 71b through which the high pressure oil O is supplied to the first supply section 69a and the second supply section 69b, and the rear-side communication path 65 continued to the high-pressure supply paths 71a and 71b, the rear-side annular groove 73, the rear-side oil supply path 59a, and the oil supply hole 59.
  • an electric current flows through a coil having been wound on the stator 79 of the motor section 4 by control of the inverter section 5 shown in Fig. 1 .
  • Magnetic force is generated by electric current flowing through the coil, and the motor rotor 81 disposed on the inner periphery of the stator 79 rotates.
  • the drive shaft 27 on the one-end side of which the motor rotor 81 is fixed rotates by rotation of the motor rotor 81, and also the rotor 23 which is fixed on the other-end side of the drive shaft 27 rotates.
  • the refrigerant flows into the suction chamber 11 together with rotation of the rotor 23, and the refrigerant is sucked into the cylinder chamber 33 from the suction chamber 11 via a suction slot (not shown) of the front-side block 31a (the suction process).
  • the refrigerant having been sucked into the cylinder chamber 33 enters the compression chambers 33a, 33b and 33c formed in the cylinder chamber 33 by the plurality of vanes 25, and thereby the refrigerant in the compression chambers 33a, 33b and 33c is compressed by rotation of the rotor 23 (the compression process).
  • the refrigerant having been compressed in the cylinder chamber 33 pushes the open/close valve 37 open, and is discharged from the discharge slot 35 (the discharged process) and is discharged from the discharge hole 61 into the discharge chamber 15 via the oil separator 21.
  • the refrigerant having been discharged from the discharge hole 61 is separated into the refrigerant and the oil O by the oil separator 21, the refrigerant is discharged from a not shown discharge port to the not shown refrigerating cycle, and the oil O is stored under the discharge chamber 15.
  • the oil having been stored under the discharge chamber 15 is supplied from the oil supply hole 59 in the rear-side block 31b to the rear-side bearing 63 through the rear-side oil supply path 59a.
  • the high-pressure oil having been supplied to the rear-side bearing 63 is reduced to intermediate pressure higher than the pressure (the suction pressure) of the sucked refrigerant and lower than the pressure (the discharged pressure) of the discharged refrigerant, by being squeezed between the rear-side bearing 63 and the drive shaft 27, and the oil O having been reduced to the intermediate pressure is supplied to the intermediate-pressure supply groove 67 through a gap between the drive shaft 27 and the rear-side block 31b.
  • the intermediate pressure oil O having been supplied to the intermediate-pressure supply groove 67 supplies the intermediate pressure to the back pressure space 77 and supplies the intermediate pressure to the back surface of the vane 25 such that the vane 25 projects from the vane groove 75, over a range from the refrigerant suction process to the compression process as shown in Fig. 3 .
  • the high-pressure oil O having been supplied to the rear-side bearing 63 is supplied from the high-pressure supply paths 71a and 71b opening to the rear-side end surface 57 to the first supply section 69a and the second supply section 69b of the high-pressure supply groove 69, via the rear-side communication path 65.
  • the high-pressure oil O having been supplied to the first supply section 69a and the second supply section 69b supplies the high pressure to the back pressure space 77 and supplies the high pressure to the back surface of the vane 25 such that the vane 25 projects from the vane groove 75, over a range from the refrigerant compression process to the discharged process as shown in Fig. 3 .
  • the first supply section 69a and the second supply section 69b communicate with the not shown respective corresponding supply sections of the high-pressure supply groove 53 on the front-side block 31a side via the back pressure space 77, and the high pressure is also supplied from each of the supply sections of the high-pressure supply groove 53 to the back pressure space 77.
  • the high-pressure oil O flows into the rear-side oil supply path 59a from the oil supply hole 59, passes through the rear-side oil supply path 59b by being branched from the rear-side oil supply path 59a, and is supplied from the front-side oil supply path 49 to the front-side bearing 47 via the cylinder-side oil supply path 41.
  • the high-pressure oil O having been supplied to the front-side bearing 47 has intermediate pressure by being squeezed between the front-side bearing 47 and the drive shaft 27, and the oil O having been reduced to the intermediate pressure is supplied to the intermediate-pressure supply groove 51 through the gap between the drive shaft 27 and the front-side block 31 a.
  • the high-pressure oil O having been supplied from the high-pressure supply grooves 53 and 69 of the front-side block 31a and the rear-side block 31b is supplied to the back pressure space 77 of the rotor 23 at a rotation latter-half position of the rotor 23 to impart the back pressure for making the vane 25 project from the vane groove 75.
  • the back pressure space 77 of the vane groove 75 having completed communication with the intermediate-pressure supply groove 67 communicates with the first supply section 69a of the high-pressure supply groove 69, and the high pressure is supplied from the first supply section 69a thereto.
  • this back pressure space 77 completes communication with the first supply section 69a before the back pressure space 77 of the next vane groove 75 that is positioned on the upstream side of the rotation direction X communicates with the first supply section 69a and communicates with the second supply section 69b that is independent of the first supply section 69a and is positioned on the downstream side of the rotation direction X, and thus the high pressure is again supplied to the back pressure space.
  • the back pressure space 77 having completed communication with the intermediate-pressure supply groove 67 communicates with the first supply section 69a of the high-pressure supply groove 69, the preceding back pressure space 77 adjacent to the back pressure space 77 on the downstream side in the rotation direction X does not communicate with the first supply section 69a simultaneously.
  • FIG. 4 there is shown a situation in which the back pressure space 77A completes communication with the first supply section 69a before the back pressure space 77B of the next vane groove 75 that is positioned on the upstream side in the rotation direction X communicates with the first supply section 69a and communicates with the second supply section 69b that is independent of the first supply section 69a and is positioned on the downstream side in the rotation direction X, and thus the high pressure is again supplied to the back pressure space 77A.
  • the preceding back pressure space 77A adjacent to the back pressure space 77B on the downstream side in the rotation direction X does not communicate with the first supply section 69a simultaneously at a time point when the back pressure space 77B communicates with the first supply section 69a of the high-pressure supply groove 69.
  • the similar relation is established not only between the back pressure space 77A and the back pressure space 77B, but also between the back pressure space 77B and the back pressure space 77C, and between the back pressure space 77C and the backpressure space 77A.
  • the back pressure space 77 completes communication with the second supply section 69b before the back pressure space 77 of the next vane groove 75 which is positioned on the upstream side in the rotation direction X communicates with the second supply section 69b. Accordingly, at a time point when the back pressure space 77 having completed communication with the first supply section 69a of the high-pressure supply groove 69 communicates with the second supply section 69b of the high-pressure supply groove 69, the preceding back pressure space 77 adjacent to the downstream side of the back pressure space 77 in the rotation direction X does not communicate with the second supply section 69b simultaneously.
  • Fig. 8 is a graph showing changes in the pressure P33a of the compression chamber 33a, the pressure P33b of the compression chamber 33b and the pressure P77B of the back pressure space 77B in accordance with the rotation angle of the rotor.
  • the back pressure space 77B having completed communication with the intermediate-pressure supply groove 67 communicates with the high-pressure supply groove 69.
  • the high-pressure supply groove 69 is constituted by the first supply section 69a and the second supply section 69b and the back pressure space 77B communicates with the first supply section 69a and thereafter communicates with the second supply section 69b, along with rotation of the rotor 23 that rotates in the rotation direction X.
  • the total of the communication cross-sectional areas S1 and S3 of the back pressure space 77 with the first supply section 69a and the second supply section 69b when the communication destination of the back pressure space 77 shifts from the first supply section 69a to the second supply section 69b is set to be a minimum path cross-sectional area or more of the supply route of the high-pressure oil O to the first supply section 69a and the second supply section 69b.
  • the back pressure space 77 communicates, in the minimum path cross-sectional area or more, with at least one of the first supply section 69a or the second supply section 69b, and thus there can be ensured a destination to which the high pressure in the back pressure space 77 is released.
  • the second supply section 69b of the high-pressure supply groove 69 be formed into a shape of the largest possible size in the rotation direction X within a range in which the two back pressure spaces 77 mutually adjacent in the rotation direction X of the rotor 23 do not simultaneously communicate with each other. Consequently, it is possible to allow the back pressure space 77 in which pressure has been increased from the intermediate pressure toward the high pressure due to communication with the first supply section 69a to communicate with the second supply section 69b from an earlier stage of the compression process of the compression chambers 33a, 33b and 33c, and thereafter to stabilize the pressure in the back pressure space 77 to the high pressure.
  • the open/close valve 37 of the discharge slot 35 is opened at an earlier stage and the high-pressure refrigerant in the compression chambers 33a, 33b and 33c is efficiently and sufficiently discharged, and thereby it is possible to achieve enhancement of refrigerant compression efficiency.
  • the high-pressure supply groove 69 is divided into the two mutually independent first supply section 69a and second supply section 69b in the rotation direction X.
  • the present invention is applicable also in a case where the high-pressure supply groove 69 is divided into three or more supply sections in the rotation direction X.
  • the relation of the present invention is applied to the communication cross-sectional area of an upstream-side supply section or a downstream-side supply section with the back pressure space 77 when the back pressure space 77 moves striding over the two adjacent supply sections in the rotation direction X.
  • Fig. 9 and Fig. 10 show a structure of a vane rotary-type gas compressor according to the second embodiment.
  • the gas compressor of the second embodiment has a rear-side block 31b2 different from the rear-side block 31b of the first embodiment.
  • Configurations other than the rear-side block 31b2 are the configurations that are similar to those of the first embodiment.
  • the same symbols are attached to the same constituent points as those in the first embodiment, a description thereof is omitted and only different configurations will be described.
  • an interval 69c having a size that is not less than that of the back pressure space 77 of the vane groove 75 is provided between the first supply section 69a and the second supply section 69b in the rotation direction X of the rotor 23. Namely, the interval 69c provided between the first supply section 69a and the second supply section 69b is set larger than the width of the back pressure space 77 of the vane groove 75.
  • Fig. 12 is an explanatory diagram showing a positional relation between the region in which the projection stroke of the vane 25B relative to the vane groove 75 is reduced at a rate equal to or more than a constant level and the interval 69c.
  • the volume of the back pressure space 77B is reduced at a rate in accordance with a reduction rate of the projection stroke of the vane 25B in a state where the back pressure space 77B is isolated from the first supply section 69a and the second supply section 69b, and the pressure in the back pressure space 77B temporarily rises as indicated by P1 in Fig. 13 .
  • a region in which the reduction rate of the projection stroke of the vane 25 relative to the vane groove 75 along with rotation of the rotor 23 in the rotation direction X on the inner peripheral surface 33d of the cylinder chamber 33 becomes a reduction rate not more than a predetermined threshold value which is lower than the above-mentioned constant rate is set as a region in which the reduction rate of the projection stroke is small, and the interval 69c is disposed so that the back pressure space 77 communicates with the interval 69c when the vane 25 comes into sliding contact with the region in which the reduction rate of the projection stroke concerned is small in the gas compressor 1 of the present embodiment.
  • the inner peripheral surface 33d of the cylinder chamber 33 is, as shown in Fig. 14 , formed so that four regions of:
  • the interval 69c is disposed at a position where the back pressure space 77 communicates with the interval when the vane 25 is in sliding contact with the region (c) in which the reduction rate of the projection stroke of the vane 25 along with rotation of the rotor 23 in the rotation direction X is the smallest.
  • the preceding back pressure space 77 adjacent to the back pressure space 77 on the downstream side in the rotation direction X does not communicate with the first supply section 69a simultaneously.
  • the back pressure space 77 having completed communication with the intermediate-pressure supply groove 67 communicates with the first supply section 69a of the high-pressure supply groove 69, the preceding back pressure space 77 adjacent to the back pressure space 77 on the downstream side in the rotation direction X does not communicate with the first supply section 69a simultaneously.
  • the back pressure space 77 completes communication with the second supply section 69b before the back pressure space 77 of the next vane groove 75 which is positioned on the upstream side in the rotation direction X communicates with the second supply section 69b. Accordingly, at a time point when the back pressure space 77 having completed communication with the first supply section 69a of the high-pressure supply groove 69 communicates with the second supply section 69b of the high-pressure supply groove 69, the preceding back pressure space 77 adjacent to the downstream side of the back pressure space 77 in the rotation direction X does not communicate with the second supply section 69b simultaneously.
  • the interval 69c between the first supply section 69a and the second supply section 69b is positioned such that, when the back pressure space 77 communicates with the interval 69c between the first supply section 69a and the second supply section 69b, the vane 25 stored in the vane groove 75 of the back pressure space 77 comes into sliding contact with the region (c) in which the reduction rate of the projection stroke of the vane 25 along with rotation of the rotor 23 in the rotation direction X is the smallest.
  • the second supply section 69b of the high-pressure supply groove 69 be formed into a shape of the largest possible size in the rotation direction X within a range in which the two back pressure spaces 77 mutually adjacent in the rotation direction X of the rotor 23 do not simultaneously communicate with each other. Consequently, it is possible to allow the back pressure space 77 in which pressure has been increased from the intermediate pressure toward the high pressure due to communication with the first supply section 69a to communicate with the second supply section 69b from an earlier stage of the compression process of the compression chambers 33a, 33b and 33c, and thereafter to stabilize the pressure in the back pressure space 77 to the high pressure.
  • the open/close valve 37 of the discharge slot 35 is opened at an earlier stage and the high-pressure refrigerant in the compression chambers 33a, 33b and 33c is efficiently and sufficiently discharged, and thereby it is possible to achieve enhancement of refrigerant compression efficiency.
  • the interval 69c provided between the first supply section 69a and the second supply section 69b is set larger than the width of the back pressure space 77 of the vane groove 75
  • the interval 69c may have a size smaller than that of the back pressure space 77 in the rotation direction X of the rotor 23.
  • the communication cross-sectional area of the back pressure space 77 for each of the supply sections 69a and 69b is reduced by an amount of overlapping the interval 69c.
  • the interval 69c is disposed at a position where the back pressure space 77 communicates with the interval 69c when the vane 25 is in sliding contact with the region (c) in which the reduction rate of the projection stroke of the vane 25 along with rotation of the rotor 23 in the rotation direction X is the smallest. Therefore, there can be prevented a temporary rise in the pressure in the back pressure space 77 by reduction in the releasing efficiency of the high pressure in the back pressure space 77.
  • a region of the inner peripheral surface 33d of the cylinder chamber 33 with which the vane 25 comes into sliding contact when the back pressure space 77 communicates with the interval 69c was determined by the use of the reduction rate of the projection stroke of the vane 25 to the vane groove 75 as a standard.
  • an upper limit value of an allowable range of the reduction rate of the projection stroke of the vane 25 to the vane groove 75 is determined in accordance with an allowable range for a temporary increase in pressure in the back pressure space 77.
  • the determined upper limit value is set as a predetermined threshold value, and there is determined a region in which the reduction rate of the projection stroke of the vane 25 on the inner peripheral surface 33d of the cylinder chamber 33 becomes not more than this threshold value.
  • the interval 69c may be disposed such that, when the vane 25 comes into sliding contact with the thus determined region on the inner peripheral surface 33d of the cylinder chamber 33, the back pressure space 77 communicates with the interval 69c.
  • the high-pressure supply groove 69 is divided into the two mutually independent first supply section 69a and second supply section 69b in the rotation direction X.
  • the present invention is applicable also in a case where the high-pressure supply groove 69 is divided into three or more supply sections in the rotation direction X. In that case, the relation of the present invention is applied to a relative position of the interval between the two supply sections adjacent to each other in the rotation direction X and the inner peripheral surface of the cylinder chamber.
  • the second supply section 69b of the high-pressure supply groove 69 was set to have a size at which the two back pressure spaces 77 adjacent to each other in the rotation direction X of the rotor 23 do not communicate with each other simultaneously.
  • the second supply section 69b may have a space of a size larger than the size of the first supply section 69a in the rotation direction X.
  • the open/close valve 37 of the discharge slot 35 is opened at an earlier stage and the high-pressure refrigerant in the compression chambers 33a, 33b and 33c is efficiently and sufficiently discharged, and thereby it is possible to achieve enhancement of refrigerant compression efficiency.
  • the supply section positioned second from the most upstream side of the rotation direction X becomes at least an object to be formed into a shape in which the two back pressure spaces 77 adjacent to each other in the rotation direction X do not communicate with each other simultaneously.
  • each of the third and subsequent supply sections from the most upstream side becomes the object to be formed into a shape in which the two back pressure spaces 77 adjacent to each other in the rotation direction X do not communicate with each other simultaneously, in a case of communicating with the back pressure space 77 when the pressure of the back pressure space 77 is in the middle of rising from the intermediate pressure to the high pressure.
  • the back pressure space of the vane groove having completed communication with the intermediate-pressure supply section communicates with the first supply section of the high-pressure supply section until the refrigerant pressure in each of the compression chambers having been partitioned by the vane stored in the vane groove reaches the highest pressure, and then the high pressure is supplied from the first supply section. Thereafter, this back pressure space completes communication with the first supply section before the back pressure space of the next vane groove on the upstream side of the rotation direction communicates with the first supply section, and then communicates with the next second supply section that is independent of the first supply section and subsequently the high pressure is again supplied thereto.
  • the preceding back pressure space which is adjacent to the back pressure space on the downstream side in the rotation direction does not communicate with the first supply section simultaneously. Consequently, the pressure in the preceding back pressure space is prevented from being temporarily lowered from the high pressure by the intermediate pressure of the following next back pressure space and the occurrence of chattering of the vane by a temporary reduction in pressure in the back pressure space of the vane can be prevented.

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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)
EP15872843.6A 2014-12-24 2015-12-16 Compresseur de gaz Withdrawn EP3239530A4 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2014260492A JP5878971B1 (ja) 2014-12-24 2014-12-24 気体圧縮機
JP2014260491A JP5878970B1 (ja) 2014-12-24 2014-12-24 気体圧縮機
JP2014260500A JP5831619B1 (ja) 2014-12-24 2014-12-24 気体圧縮機
PCT/JP2015/085193 WO2016104274A1 (fr) 2014-12-24 2015-12-16 Compresseur de gaz

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EP3239530A1 true EP3239530A1 (fr) 2017-11-01
EP3239530A4 EP3239530A4 (fr) 2018-01-10

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JP6825530B2 (ja) * 2017-09-29 2021-02-03 株式会社豊田自動織機 ベーン型圧縮機
DE102017128972B4 (de) * 2017-12-06 2025-11-27 Joma-Polytec Gmbh Vakuumpumpe
KR102223283B1 (ko) * 2018-11-16 2021-03-05 엘지전자 주식회사 베인 로터리 압축기
CN111997898A (zh) * 2020-09-10 2020-11-27 常州康普瑞汽车空调有限公司 一种旋叶式压缩机背压优化结构及方法
CN115573905B (zh) * 2022-09-20 2026-02-17 江苏梅花机械有限公司 一种真空泵及其控制方法、以及农业机械用制动装置
KR102765935B1 (ko) * 2023-03-16 2025-02-12 엘지전자 주식회사 로터리 압축기

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JPS5690489U (fr) * 1979-12-14 1981-07-18
US4455129A (en) * 1981-05-19 1984-06-19 Daikin Kogyo Co., Ltd. Multi-vane type compressor
JPH01141391U (fr) * 1988-03-23 1989-09-28
JPH02248682A (ja) * 1989-03-20 1990-10-04 Diesel Kiki Co Ltd ベーン型圧縮機
JP4060149B2 (ja) * 2002-08-30 2008-03-12 カルソニックコンプレッサー株式会社 気体圧縮機
JP2006112331A (ja) * 2004-10-15 2006-04-27 Matsushita Electric Ind Co Ltd 圧縮機
JP2009041470A (ja) * 2007-08-09 2009-02-26 Calsonic Kansei Corp ベーン形圧縮機
JP5395713B2 (ja) * 2010-01-05 2014-01-22 日立オートモティブシステムズ株式会社 ベーンポンプ
JP5826686B2 (ja) * 2012-03-16 2015-12-02 カルソニックカンセイ株式会社 気体圧縮機
US9751384B2 (en) * 2011-11-24 2017-09-05 Calsonic Kansei Corporation Gas compressor with discharge section and sub-discharge section
JP5729343B2 (ja) * 2012-03-29 2015-06-03 株式会社豊田自動織機 タンデム式ベーン型圧縮機

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WO2016104274A1 (fr) 2016-06-30
CN107110158B (zh) 2019-01-22
US20170350391A1 (en) 2017-12-07
EP3239530A4 (fr) 2018-01-10

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