WO2014119932A1 - Compresseur rotatif à palettes - Google Patents

Compresseur rotatif à palettes Download PDF

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Publication number
WO2014119932A1
WO2014119932A1 PCT/KR2014/000860 KR2014000860W WO2014119932A1 WO 2014119932 A1 WO2014119932 A1 WO 2014119932A1 KR 2014000860 W KR2014000860 W KR 2014000860W WO 2014119932 A1 WO2014119932 A1 WO 2014119932A1
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WO
WIPO (PCT)
Prior art keywords
rotor
vane
cylinder
rotary compressor
circumferential surface
Prior art date
Application number
PCT/KR2014/000860
Other languages
English (en)
Korean (ko)
Inventor
곽정명
홍선주
임권수
Original Assignee
한라비스테온공조 주식회사
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 KR1020140010064A external-priority patent/KR101964585B1/ko
Application filed by 한라비스테온공조 주식회사 filed Critical 한라비스테온공조 주식회사
Publication of WO2014119932A1 publication Critical patent/WO2014119932A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • 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
    • F04C18/40—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 having a hinged member
    • F04C18/44—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 having a hinged member with vanes hinged to the inner member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2250/00—Geometry
    • F04C2250/20—Geometry of the rotor
    • 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
    • F04C2250/00—Geometry
    • F04C2250/30—Geometry of the stator

Definitions

  • the present invention relates to a vane rotary compressor in which a fluid such as a refrigerant is compressed while the volume of the compression chamber is reduced during rotation of the rotor. More specifically, the vane rotary compressor has a plurality of curved vane type vanes rotatably provided on the outer circumferential surface of the rotor. It is about.
  • the vane rotary compressor is used in an air conditioner and the like and compresses a fluid such as a refrigerant and supplies it to the outside.
  • FIG. 1 is a cross-sectional view schematically showing a conventional vane rotary compressor disclosed in Japanese Patent Laid-Open No. 2010-31759
  • FIG. 2 is a cross-sectional view taken along the line A-A of FIG.
  • the vane rotary compressor 10 As shown in FIG. 1, the vane rotary compressor 10 according to the related art has a housing H composed of a rear housing 11 and a front housing 12, and has a cylindrical shape inside the rear housing 11.
  • the cylinder 13 of is accommodated.
  • the inner peripheral surface of the cylinder 13 has an elliptical cross-sectional shape as shown in FIG.
  • the front cover 14 is coupled to the front of the cylinder 13
  • the rear cover 15 is coupled to the rear of the cylinder 13
  • the discharge space Da is formed between the inner circumferential surface of the rear housing 11, the front cover 14, and the rear cover 15, which face each other.
  • a rotating shaft 17 is rotatably installed in the front cover 14 and the rear cover 15 through the cylinder 13, and a cylindrical rotor 18 is coupled to the rotating shaft 17 so that the rotating shaft 17 In the rotation, it rotates in the cylinder 13 together with the rotation shaft 17.
  • each of the slots (18a) is a linear type of vanes 20 are slidably received.
  • Lubricating oil is supplied into the slot 18a.
  • a stroke in which the volume of the compression chamber 21 is enlarged in accordance with the rotational direction of the rotor 18 is a suction stroke
  • a stroke in which the volume of the compression chamber 21 is reduced is a compression stroke
  • a suction port 24 is formed at an upper portion of the front housing 12, and a suction space Sa communicating with the suction port 24 is formed inside the front housing 12. Is formed.
  • the front cover 14 is provided with a suction port 14b communicating with the suction space Sa, and a suction passage 13b communicating with the suction port 14b is formed through the axial direction of the cylinder 13.
  • discharge chambers 13d recessed inwardly are formed on both sides of the outer circumferential surface of the cylinder 13, and the pair of discharge chambers 13d is compressed by the discharge holes 13a. In communication with 21, a part of the discharge space Da is formed.
  • the rear housing 11 is formed with a high pressure chamber 30 which is partitioned by the rear cover 15 and into which the compressed refrigerant flows. That is, the inside of the rear housing 11 is partitioned into the discharge space Da and the high pressure chamber 30 by the rear cover 15. At this time, the discharge port 15e communicating with the high pressure chamber 30 is formed in any one of the pair of discharge chambers 13d.
  • the high pressure chamber 30 is provided with an oil separator 40 for separating the lubricating oil from the compressed refrigerant introduced into the high pressure chamber 30, the oil separation pipe 43 is installed on the upper portion of the case 41, An oil separation chamber 42 in which the separated oil falls is formed in the lower part of the oil separation pipe 43, and the oil in the oil separation chamber 42 is formed in the oil storage chamber formed under the high pressure chamber 30 through the oil passage 41b ( 32).
  • the oil stored in the oil storage chamber 32 lubricates the sliding surfaces of the rear cover 15 and the rotor 18 through the lubrication space of the bush supporting the rear end of the rotary shaft 17 through the oil supply passage 15d.
  • the oil flows back into the discharge port 15e through the oil return groove 45.
  • the vane 20 of the straight type is applied as in the vane rotary compressor 10 described above, the vane 20 is configured to be protruded out of the rotor 18 along the slot 18a. There is a problem in that hitting noise is generated while the front end of the 20 collides with the inner circumferential surface of the cylinder 13.
  • FIG. 3 is a cross-sectional view schematically showing a vane rotary compressor of a curved blade type disclosed in Japanese Patent Laid-Open No. 2002-130169.
  • the vane rotary compressor shown in FIG. 3 includes a cylindrical cylinder 1, a rotor 2, and a drive shaft 3 thereof. At this time, the cylinder 1 has a suction port 1A and a discharge port 1B, and the rotor 2 is eccentrically installed in the cylinder 1.
  • a plurality of curved vane type vanes 4 are provided on the outer circumferential surface of the rotor 2 to form a plurality of compression chambers 6 between the cylinder 1 and the rotor 2, and one side of the vanes 4 It is hinged to the outer circumferential surface of the rotor 2 by the hinge pin (5).
  • the back portion of the vane 4 is in contact with the inner circumferential surface of the cylinder 1, and only after the suction stroke has progressed to some extent, the vane 4 rapidly develops from the rotor 2, and the tip thereof is closed. (1) Since it is supported on the inner circumferential surface, the volume expansion of the compression chamber 6 is not smoothly performed, resulting in a decrease in suction flow rate.
  • the present invention has been made to solve the problems of the curved vane-type vane compressor as described above, to provide a vane rotary compressor that can prevent the impact noise caused by the vanes during the high-speed operation of the compressor and to reduce the suction flow rate during the suction stroke The purpose.
  • a hollow cylinder in which the suction port is formed on one side;
  • a rotor installed in the hollow and rotating by receiving power from a driving source;
  • a vane whose one end is hinged to one side of the outer circumferential surface of the rotor and rotates in the direction of the inner circumferential surface of the cylinder, wherein the vane has a tip portion of the vane in an entire operating section of the vane that is variable by the rotation of the rotor.
  • a vane rotary compressor is provided having a contact support portion for maintaining contact with the cylinder inner circumferential surface.
  • the vane includes a hinge portion hinged to one side of the outer circumferential surface of the rotor, and a wing portion extending from one side of the hinge portion, wherein the contact support portion is formed at a width greater than the width of the wing portion at the end of the wing portion.
  • the wing portion is formed in the inner region of the virtual circle in which the hinge portion and the contact support portion inscribed at the same time.
  • the wing portion is disposed in the inner region of the virtual circle formed along the circumference of the rotor.
  • the receiving groove of the shape corresponding to the inner surface shape of the vane is formed on one side of the outer circumferential surface of the rotor so that the tip portion of the vane is accommodated in the rotor.
  • a plurality of vanes are formed spaced apart from each other in the circumferential direction of the rotor.
  • the hollow inner circumferential surface of the cylinder may be in the form of an involute curve along the circumferential direction in cross section.
  • the hollow cylinder in which the suction port is formed on one side;
  • a rotor installed in the hollow and rotating by receiving power from a driving source;
  • the vane rotary compressor is characterized in that the contact support is formed at the vane end of the vane.
  • the contact support is formed to have a width larger than the width of the wing portion.
  • the outer edge of the wing portion is recessed inwardly of a virtual circle in which the hinge portion and the contact support portion are inscribed at the same time.
  • one side of the edge of the contact support may be formed to protrude outward.
  • a receiving groove having a shape corresponding to the inner surface shape of the vane is formed at one side of the outer circumferential surface of the rotor to accommodate the vane.
  • a gap is formed between the inner peripheral surface of the cylinder and the wing.
  • the hollow cylinder in which the suction port is formed on one side;
  • a rotor installed in the hollow and rotating by receiving power from a driving source;
  • a vane whose one end is hinged to one side of the outer circumferential surface of the rotor and the tip portion rotates in the direction of the inner circumferential surface of the cylinder, wherein the vane comprises a hinge portion hinged to one side of the outer circumferential surface of the rotor and one side of the hinge portion.
  • the vane In the whole operating section of the vane extending and formed in contact with the inner circumferential surface of the cylinder is formed in a wider width than the wing at the end of the wing portion, the variable variable by the rotation of the rotor,
  • the contact support is continuously in contact with the inner circumferential surface of the cylinder, the vane is provided with a vane rotary compressor, characterized in that it continues to be spaced apart from the inner circumferential surface.
  • the outer edge of the wing portion is formed in the recess of the virtual circle in which the hinge portion and the contact support portion inscribed at the same time.
  • one side of the contact support may be formed to protrude in the direction of the inner peripheral surface of the cylinder.
  • a gap is formed between the inner circumferential surface of the cylinder and the wing portion.
  • the outer edge of the wing portion is disposed in the inner region of the virtual circle formed along the outer diameter of the rotor.
  • FIG. 1 is a longitudinal sectional view schematically showing a conventional vane rotary compressor.
  • FIG. 2 is a cross-sectional view taken along the line A-A of FIG.
  • FIG 3 is a cross-sectional view of a conventional curved vane type vane rotary compressor.
  • Figure 4 is a longitudinal sectional view of the vane rotary compressor according to an embodiment of the present invention.
  • FIG. 5 is a cross-sectional view taken along the line B-B in FIG.
  • Figure 6 is a schematic diagram showing a curved vane type vane according to an embodiment of the present invention.
  • Figure 7 is a schematic diagram showing an example in which the curved vane type vanes according to an embodiment of the present invention is accommodated in the receiving groove of the rotor.
  • FIG. 8 is a schematic diagram showing a cylinder inner peripheral surface contact section of a conventional curved wing type vane.
  • Figure 9 is a schematic diagram showing a cylinder inner peripheral surface contact section of the curved vane type vane according to an embodiment of the present invention.
  • FIG. 10 is a schematic view of a vane rotary compressor according to another embodiment of the present invention.
  • Figure 11 is a schematic cross-sectional view showing an example in the form of involute curve of the cylinder inner peripheral surface according to another embodiment of the present invention.
  • the appearance of the vane rotary compressor is made by the combination of the housing and the second head portion, and describes an example in which the cylinder is accommodated in the housing, the present invention and the housing forming the appearance of such vane rotary compressor Note that it is not limited by the coupling relationship between the head and the cylinder.
  • FIG. 4 is a longitudinal sectional view of a vane rotary compressor according to an embodiment of the present invention.
  • the vane rotary compressor (hereinafter, referred to as a 'compressor') 100 is the compressor 100 by combining the housing 110 and the second head part 114.
  • the overall appearance of can be formed.
  • the housing 110 is formed integrally with the cylinder portion 112 in which the space portion 111 is formed therein, and the cylinder portion 112 in the axial front of the cylinder portion 112, and thus the space portion 111. It includes a first head portion 113 for closing the front of the, space portion 111 is mounted to the cylinder 200 of the hollow form.
  • the inside of the cylinder 200 is rotated by the power of the drive source, the rotating shaft 310, the rotor 300 is rotated with the rotary shaft 310 receives the rotational force of the rotary shaft 310, the rotor 300
  • a plurality of vanes 400 are hinged to the outer circumferential surface of the rotor 300 to be rotatably hinged in the radial direction of the rotor 300.
  • the second head portion 114 is coupled to the axial rear of the housing 110 to close the rear of the space 111.
  • the outer peripheral surface of the first head portion 113 of the housing 110 has a suction port (not shown) for sucking the refrigerant from the outside, and a discharge port for discharging the high-pressure refrigerant compressed in the cylinder 200 to the outside (not shown) H) are provided spaced apart from each other in the circumferential direction.
  • the pulley coupling portion 510 is extended to the front center of the first head 113 to be coupled to the pulley 500 of the electronic clutch (not shown).
  • FIG. 5 is a cross-sectional view taken along the line B-B in FIG.
  • the hollow of the cylinder 200 is slightly eccentrically formed to one side from the center of the cylinder 200 in which the rotating shaft 310 is installed, and the rotor 300 having the vanes 400 in the hollow. By inserting), the hollow of the cylinder 200 forms a compression space in which the introduced refrigerant is compressed by the rotation of the rotor 300.
  • the suction hole 210 is formed on one side of the cylinder 200, one side of the suction hole 210 is in communication with the suction port of the first head portion 113, the other side is a compression space in the cylinder 200 In communication with the suction port 211, the refrigerant sucked through the suction port from the outside is introduced into the hollow of the cylinder 200 which is a compression space through the suction hole 210 and the suction port 211 of the cylinder 200.
  • one side of the outer circumferential surface of the cylinder 200 is formed with a discharge portion 220 in which a compressed high-pressure refrigerant is discharged, and one side of the discharge portion 220 communicates with a plurality of discharge ports communicated with the compression chamber 230 described later. 221 is formed through, and the other side of the discharge portion 220 is formed with a guide flow path (not shown) for guiding the high-pressure refrigerant in the discharge port direction.
  • the rotor 300 is coupled to a rotating shaft 310 connected to a driving motor (not shown) or a clutch (not shown) driven by an engine belt (not shown) to rotate along with the rotating shaft 310.
  • the rotary shaft 310 is mounted along the central axis of the cylinder 200, so that the rotor 300 is slightly deviated to one side from the center of the cylinder 200 hollow, rotated in an eccentric position in the cylinder 200 hollow Done.
  • the vane 400 of the curved wing type is coupled to a plurality of hinges on the outer circumferential surface of the rotor 300 spaced apart from each other.
  • one side of the vane 400 is hinged to the outer peripheral surface slot 320 of the rotor 300, the other end of the vane 400 when the rotor 300 rotates by the centrifugal force and the pressure of the refrigerant of the cylinder 200
  • the compression space is divided into a plurality of compression chambers 230 by rotating in the direction of the inner circumferential surface.
  • each compression chamber 230 is formed by the space which consists of an adjacent pair of vanes 400, the outer peripheral surface of the rotor 300, and the inner peripheral surface of the cylinder 200. As shown in FIG.
  • the tip portion of the vane 400 rotates together in the rotational direction of the rotor 300 along the hollow inner circumferential surface of the cylinder 200, and as the rotor 300 is eccentrically positioned in the hollow, the rotor 300 During the rotation, as the interval between the outer circumferential surface and the hollow inner circumferential surface of the rotor 300 becomes narrower, the volume of the compression chamber 230 decreases, and the refrigerant trapped in the compression chamber 230 is compressed.
  • the vane 400 includes a hinge portion 410 hinged to one side of the outer circumferential surface of the rotor 300, a wing portion 420 formed to be curved from one side of the hinge portion 410, and a wing portion 420. It includes a contact support portion 430 is formed to expand the width at the end.
  • one side of the outer circumferential surface of the rotor 300 is eccentrically arranged to contact the hollow inner circumferential surface of the cylinder 200.
  • a plurality of accommodation grooves 330 for accommodating the wing portion 420 of the vanes 400 are formed in the circumferential direction corresponding to the number of vanes 400, wherein the accommodation grooves 330 includes a wing portion receiving groove 331 for accommodating the wing portion 420 of the vane 400 and a contact support portion receiving groove 332 for accommodating the contact support portion 430 of the vane 400.
  • the hinge portion 410 of the vane 400 is hinged to one side of the outer circumferential surface of the rotor 300, and the hinge portion 410 of the circular cross-sectional shape in the slot 320 having an arc cross section formed on one side of the outer circumferential surface of the rotor 300. ) Is rotatably coupled, in which case the hinge portion 410 is preferably not separated from the radially outer side of the rotor 300.
  • the wing 420 of the vane 400 extends from one side of the hinge 410 toward the hollow inner circumferential surface of the cylinder 200, and the contact support 430 is formed at the end of the wing 420. .
  • one side of the contact support 430 is formed with a curved surface protruding in the outward direction of the wing 420, the curved surface is always maintained in contact with the hollow inner peripheral surface of the cylinder 200 when the rotor 300 rotates Therefore, it is possible to prevent the blow noise generated in the process of the vane 400 is rapidly deployed from the receiving groove 330.
  • FIG. 6 is a schematic view showing a curved vane type vane according to an embodiment of the present invention
  • Figure 7 is a schematic view showing an example in which the curved vane type vanes according to an embodiment of the present invention accommodated in the receiving groove of the rotor.
  • the contact support 430 is formed at the end of the wing 420. It extends to the width w2 larger than the width w1.
  • the wing portion 420 is formed inside the virtual circle (C1, C2, C3) that the hinge portion 410 and the contact support portion 430 inscribed at the same time. That is, the outer rim of the wing 420 facing the hollow inner circumferential surface of the cylinder 200 is recessed into the imaginary circle C1, C2, C3 in which the hinge 410 and the contact support 430 are inscribed at the same time. It is formed.
  • the outer edge of the wing portion 420 connecting the hinge portion 410 and the contact support portion 430 is a curve of the same curvature (eg, a portion of C3 between the hinge portion 410 and the contact support portion 430).
  • the wing portion 420 is an outer circumferential surface of the rotor 300. It is disposed in the inner region of the virtual circle (R) formed along the circumference.
  • the radius r1 from the center of the rotor 300 to the outer edge of the wing portion 420 is the hinge portion 410 and the contact support portion 430. It is formed smaller than the radius r2. At this time, a gap is formed between the hollow inner circumferential surface of the cylinder 200 and the outer edge of the wing 420.
  • the vane 400 contacts the hollow inner circumferential surface of the cylinder 200 with the contact support 430, or the contact support 430 and the hinge 410 simultaneously hollow the cylinder 200. Only in contact with the inner circumferential surface, the wing 420 is always spaced apart from the inner circumferential surface of the cylinder 200.
  • FIG. 8 is a schematic view showing a cylinder inner circumferential contact section of a conventional curved vane type vane
  • FIG. 9 is a schematic view showing a cylinder inner circumferential contact section of a curved vane type vane according to an embodiment of the present invention.
  • the contact section ⁇ over the entire length of the vane portion of the vanes 4 and 3 is defined as the hollow of the cylinder 1 and 3. It is pressed against the inner circumferential surface.
  • the contact point of the vane 4 which contacts the cylinder 1 gradually moves from E to D during the compression stroke, and the vane 4 moves to the outer circumferential surface of the rotor 2 at the end of the compression stroke. Close contact.
  • the contact section between the wing portion 420 and the hollow inner circumferential surface of the cylinder 200 disappears, and as shown in FIG. 9, the contact section ⁇ of one side of the contact support part 430 is Since the state in contact with the hollow inner circumferential surface (1) is maintained, the impact sound caused by the rapid development of the vane 400 is prevented.
  • the vane that was completely accommodated in the receiving groove 330 immediately deploys to the outside of the receiving groove 330, so that the volume expansion of the compression chamber 230 is smoothly performed. It is possible to prevent the problem of reducing the suction flow rate due to the delay of the vane 400 and the rapid deployment of the suction stroke.
  • FIG. 10 is a schematic diagram of a vane rotary compressor according to another embodiment of the present invention.
  • the vane rotary compressor according to another embodiment of the present invention is similar in configuration to the above-described embodiment, except that the contact support part 430 'of the tip of the vane 400' is formed to protrude toward the hollow inner circumferential surface of the cylinder 200. There is a difference.
  • the outer edge of the contact support portion 430 protrudes from the end of the wing portion 420 in the hollow inner circumferential surface of the cylinder 200, and the contact support portion (in the outer circumferential surface direction of the rotor 300)
  • the inner edge of the 430 is formed to protrude, so that the width of the contact support 430 is larger than the width of the wing 420.
  • one side of the outer edge of the contact support part 430 ′ protrudes toward the hollow inner circumferential surface of the cylinder 200, but the contact support part ( The inner edge of 430 ′ is formed in a shape in which the inner edge of the wing 420 extends. At this time, the shape of the outer edge of the contact support 430 ′ protrudes, and the size of the protrusion width and length may be variously selected as necessary.
  • FIG. 11 is a schematic cross-sectional view showing an example in which the cylinder inner peripheral surface is involute curve form according to another embodiment of the present invention.
  • the vanes 400, 400 'of the same configuration as the above embodiments can be applied, the hollow inner peripheral surface of the cylinder 200' is in the form of an involute curve, the cylinder There is a difference in that the 200 'and the rotor 300 have the same central axis.
  • the hollow inner circumferential surface of the cylinder 200 ′ has an involute curve shape.
  • the rotor 300 is installed in the hollow of the cylinder 200 'such that the inner circumferential surface of the cylinder 200' and the outer circumferential surface of the rotor 300 are concentric in cross section.
  • the center of the start point and the end point is coincident with the center of the rotor 300, and thus the rotor 300 is eccentrically arranged as in the above-described embodiment. In comparison, vibration and noise are reduced.
  • the contact support part 430 of the vane 400 moves in contact with the inner circumferential surface of the cylinder 200 ', thus preventing the occurrence of a blow sound and a decrease in suction flow rate due to the rapid deployment of the vane 400 as in the prior art. .
  • the contact support portion is formed at the distal end of the curved vane type vane, and the contact support portion is always supported on the inner circumferential surface of the cylinder when the rotor rotates, so that the suction stroke from the compression stroke It is possible to prevent the impact noise generated by the vane when switching.

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

Abstract

La présente invention concerne un compresseur rotatif à palettes pourvu d'une pluralité de palettes en forme d'ailes incurvées rotatives sur la surface circonférentielle extérieure d'un rotor, le compresseur rotatif à palettes selon un mode de réalisation de la présente invention ayant une partie de support de contact sur l'extrémité avant de chaque palette, de sorte que la palette est en contact continu avec l'espace interne creux d'un cylindre, empêchant ainsi la génération d'un bruit d'impact émis lorsque des palettes classiques se déploient rapidement.
PCT/KR2014/000860 2013-01-31 2014-01-29 Compresseur rotatif à palettes WO2014119932A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
KR20130011390 2013-01-31
KR10-2013-0011390 2013-01-31
KR10-2014-0010064 2014-01-28
KR1020140010064A KR101964585B1 (ko) 2013-01-31 2014-01-28 베인 로터리 압축기

Publications (1)

Publication Number Publication Date
WO2014119932A1 true WO2014119932A1 (fr) 2014-08-07

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Application Number Title Priority Date Filing Date
PCT/KR2014/000860 WO2014119932A1 (fr) 2013-01-31 2014-01-29 Compresseur rotatif à palettes

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4990074A (en) * 1988-09-27 1991-02-05 Aisin Seiki Kabushiki Kaisha Oil pump having pivoting vanes
WO1998048172A1 (fr) * 1997-04-18 1998-10-29 John Eastman Barnes Ameliorations de pompes a helices
JP2002130169A (ja) * 2000-10-20 2002-05-09 Katsunori Onishi ロータリーベーン式回転機械
WO2008050212A2 (fr) * 2006-10-24 2008-05-02 Pierburg Pump Technology Italy S.P.A. Pompe à palettes rotative à débit variable
US20100143174A1 (en) * 2004-03-09 2010-06-10 Maciej Radziwill Rotary Working Machine Provided with an Assembly of Working Chambers and Periodically Variable Volume, In Particular a Compressor

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4990074A (en) * 1988-09-27 1991-02-05 Aisin Seiki Kabushiki Kaisha Oil pump having pivoting vanes
WO1998048172A1 (fr) * 1997-04-18 1998-10-29 John Eastman Barnes Ameliorations de pompes a helices
JP2002130169A (ja) * 2000-10-20 2002-05-09 Katsunori Onishi ロータリーベーン式回転機械
US20100143174A1 (en) * 2004-03-09 2010-06-10 Maciej Radziwill Rotary Working Machine Provided with an Assembly of Working Chambers and Periodically Variable Volume, In Particular a Compressor
WO2008050212A2 (fr) * 2006-10-24 2008-05-02 Pierburg Pump Technology Italy S.P.A. Pompe à palettes rotative à débit variable

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