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
  • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
  • F04C18/3568—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member with axially movable vanes

Definitions

• the present invention relates a vane structure for a compressor in which a vane is in contact with a Z-plate, a rotation member, so that a fluid can be compressed in a compression chamber and discharged therefrom
• compressors convert a mechanical energy into a compression energy of an compressible fluid, of which a freezing compressor is classified into a reciprocating compressor, a scroll type compress, a centrifugal type compressor and rotary type compressor depending on a compression method.
• the present applicant has developed a compressor with a novel concept, which can be classified into the rotary compressor, and filed an application for the invention to the Korean Industrial Patent Office (Application No. 10-1999-0042381 , Application date: October 1 , 1999), which has been laid open May 7, 2001 with a publication number 2001-0035687.
• Figure 1 is a vertical sectional view showing a compressor of the former application invention of the present invention.
• a compressor of the former application invention of the present invention includes: a electric mechanism unit 4 consisting of a stator and a rotor 3 inside a casing 1 and generating a rotational force; and a compression mechanism unit 10 for compressing a fluid by a rotational force generated from the rotor 3 of the electric mechanism unit 4 and discharging it.
• Figure 2 is a partial cut-out perspective view showing the compression mechanism unit 10.
• the compression mechanism unit 10 includes: a cylinder 11 fixed at a lower portion of the casing 1 ; a first bearing plate 13 and a second bearing plate 14 fixed at an upper surface and a lower surface of the cylinder 11 and forming a compression space (V) together with the cylinder 11 ; a rotational shaft 12 for transmitting a rotational driving force generated from the rotor 3 of the electric mechanism unit 4 to the compression mechanism unit; a Z-plate 15 coupled at the rotational shaft 12 and rotated, and dividing the compression space (V) of the cylinder 11 into a first space (V1) and a second space (V2); and a first vane 17 and a second vane 18 each being in contact with the upper surface and lower surface of the Z-plate and dividing the spaces V1 and V2 into suction areas (V1s and V2s) and compression area (V1p and V2p) when the Z-plate is rotated.
• the cylinder 11 , the first bearing plate 13 and the second bearing plate 14 are cylinder assembly forming the compression space (V).
• reference number 5 denotes a suction pipe through which a fluid is sucked into the casing 1
• 6 denotes a discharge pipe through which a fluid is discharged.
• Reference numerals 11a and 11b denote suction passages through which a fluid is sucked into the compression space (V) of the cylinder 11
• 13a and 14a denote discharge passages for discharging a compressed fluid
• 13b and 14b denote discharge valves.
• Reference numerals 19 and 20 denote discharge mufflers for reducing a discharge noise
• 19a and 20a denote discharge holes formed at the discharge mufflers 19 and 20, through which a compressed fluid is discharged.
• the Z-plate 15 is formed as disk type when projected on plane so that its outer circumference face can slidably contact an inner circumferential face of the cylinder 11 , and its side is formed with a cam surface of a sine wave curve which has the same thickness from the inner circumferential face to the outer cicumferential face in its development, so that its upper dead point (R1) is in contact with the lower surface of the first bearing plate 13 and rotated, and a lower dead point (R2) is closely adhered to the upper surface of the second bearing plate 14 and rotated.
• the first vane 17 and the second vane 18 are formed in square plate shape with a certain thickness, penetrating each bearing plate 13 and 14, so that when the rotational shaft 12 is rotated the first vane 17 and the second vane 18 linearly and reciprocally moved in the axial direction along the cam surface of the Z-plate 17 while being in contact with the upper surface and lower surface of the Z-plate 15, respectively.
• the first vane 17 and the second vane 18 receives an elastic force from springs 21 and 22 supplied by the bearing plates 13 and 14 at their rear portion 17a (refer to Figure 1).
• An outer side 17b of each vane 17 and 18 is in contact with the inner circumferential face of the cylinder 11 , and an inner side of each vane 17 and 18 is in contact with the outer circumferential face of the rotational shaft 12.
• a front end portion 17d of each vane 17 and 18 slidably contacts the upper surface and the lower surface of the Z-plate 15 (reference to Figure 2).
• the first space V1 positioned at an upper portion of the Z-plate 15 is divided into a suction area V1s and a compression area V1p by taking the upper dead point (R1) and the first vane 17 as a boundary
• the second space V2 positioned at the lower portion of the Z-piate 15 is divided into a suction area (V2s) and a compression area (V2p) by taking the lower dead point (R2) and the second vane 18 as a boundary.
• first vane 17 and the second vane 18 are reciprocally moved in the mutually opposite direction up to as high as the cam face of the Z-plate.
• an object of the present invention is to provide a vane structure of a compressor that is capable of heightening an efficiency and a reliability of a compressor by reducing a friction loss and abrasion between a vane and a Z-plate.
• a vane structure for a compressor including a cylinder assembly having a suction passage and a discharge passage, a Z-plate dividing an inner space of the cylinder assembly into a plurality of compression spaces, and sucking, compressing and discharging a fluid while being rotated by a driving unit, and vanes being in contact with both sides of the Z-plate to make a reciprocal movement, and dividing each compression space into a suction area and a compression area, wherein the vane has a vane roller being in rolling-contact with the Z-plate.
• the vane includes a vane plate reciprocally moved along both sides of the Z-plate and a vane roller provided at the vane plate and being in a rolling-contact with the Z-plate.
• the vane plate includes a roller receiving hole into which the vane roller is inserted and mounted.
• the vane roller is formed having a bar structure with the same diameter on the whole, and the roller receiving hole is formed in a hole structure having the same inner diameter.
• An opened portion of the roller receiving hole so that the vane roller comes in contact with the Z-plate therethrough is smaller than a diameter of the vane roller to prevent the vane roller from releasing.
• At least one of both sides of the roller receiving hole has an opened structure.
• a roller support extended from the vane plate is formed at both sides of the roller receiving hole, and the vane roller can be rotatably supported by the roller support.
• the vane roller is installed at the roller support through a pin member.
• the vane roller is formed in a bar structure with a tapering shape, and the roller receiving hole is formed in a tapering hole structure.
• the vane roller is positioned such that a side with a relatively smaller diameter is directed inward of the cylinder assembly and a side with a relatively greater diameter is directed outward of the cylinder assembly.
• the vane structure for a compressor of the present invention has effects that by mounting the vane roller being in rotatably contact with the Z- plate in the vane, a friction resistance between the Z-plate and the vane can be reduced when a compressor is operated, according to which a friction between the Z-plate and the vane can be minimized, a noise is restrained from generating, a durability of parts can be lengthened, and a reliability of the compressor can be heightened.
• Figure 1 is a vertical-sectional view showing a compressor of a former application invention of the present invention
• Figure 2 is a partial cut-out perspective view showing a compression mechanism unit of a compressor of the former .application invention of the present invention
• Figure 3 is a perspective view of a vane of the compressor of the former application invention of the present invention
• Figure 4 is a vertical-sectional view showing a compression mechanism unit of a compressor in accordance with the present invention
• Figures 5 and 6 are a perspective view and an exploded perspective view showing a vane structure in accordance with a first embodiment of the present invention
• Figures 7 and 8 are a perspective view and an exploded perspective view showing a vane structure in accordance with a second embodiment of the present invention
• Figure 9 is an exploded perspective view showing a vane structure and a vane installation structure in accordance with a third embodiment of the present invention.
• Figures 10 and Figure 11 are explanatory side views showing a vane operation state of the third embodiment of the present invention.
• Figure 4 is a vertical-sectional view showing a compression mechanism unit of a compressor in accordance with the present invention
• Figures 5 and 6 are a perspective view and an exploded perspective view showing a vane structure in accordance with a first embodiment of the present invention.
• a compression mechanism unit 10 of a compressor where vanes are installed includes: a rotational shaft 12 coupled at a rotor of an electric mechanism unit provided inside a casing 1 ; a Z-plate 15 dividing the inner space of the cylinder assembly including the cylinder 11 coupled with the rotational shaft 12 into a first space V1 and a second space V2; and a first vane 50 and a second vane 55 respectively inserted into the first and second bearing plates 13 and 14 and linearly and reciprocally moved along the cam face of the Z-plate 15.
• each vane 50 and 55 include vane rollers 52 and 57 at their front end portion so as to be in rolling-contact with the Z-plate 15.
• reference number 5 is suction pipes through which a fluid is sucked into the casing 1
• 19 and 20 denote discharge mufflers for reducing a discharge noise
• 19a and 20a denote discharge holes formed at the discharge mufflers 19 and 20, through which a compressed fluid is discharged.
• the first and second bearing plats 13 and 14 are respectively mounted at an upper side and a lower side of the cylinder 11 , which form a compression space of the cylinder assembly together with the cylinder 11.
• the suction passages 11a and 11b are respectively formed at the cylinder 11 , communicating with the first space V1 and the second space V2, in order to suck a fluid from outside.
• Discharge passages 13a and 14a are formed at each bearing plate 13 and 14, which respectively include discharge valves 13b and 14b.
• the Z-plate 15 is formed as a disk type when viewed from plane projection so that its outer circumferential surface can slidably contact the inner circumferential surface of the cylinder 11 , and the circumferential side is formed as a cam face of a sine wave curve having the same thickness from the inner circumferential face to the outer circumference face when the side is opened.
• the first vane 50 and the second vane 55 include a vane plate 51 formed in a square plate structure with a certain thickness and area; and a vane roller 52 rotatably mounted at a front end portion of the vane plate 51 and being in rolling-contact with the upper surface and the lower surface of the Z-plate 15.
• the vane plate 51 is supplied by springs 21 and 22 at its rear portion 51a, and both sides 51b and 51c are respectively in contact with the inner circumferential face of the cylinder and the outer circumferential face of the rotational shaft 12.
• a long circular roller receiving hole 51 e is formed at a front end portion
• the roller receiving hole 51 e has a certain inner diameter as large as the vane roller 51 can be inserted.
• the roller receiving hole 51 e is preferably formed in such a structure that both sides of the vane plate 51 are all opened, but according to a designing condition, either one side may be opened or both sides may not be opened.
• the vane roller 52 is formed in a circular bar structure with an outer diameter and length corresponding to the inner diameter and length of the roller receiving hole 51 e and is in rolling-contact with the cam face constituted by upper and lower sides of the Z-plate 15. The vane roller 52 is inserted and mounted in the roller receiving hole
• the both end portions of the vane roller 52 may be mounted exposed outwardly of the roller receiving hole 51e.
• the vanes 50 and 55 are respectively inserted into the vane slots of the first and second bearing plates 13 and 14, so that the vane roller 52 of the front end portion 51 d is in rolling-contact at the upper surface and the lower surface of the Z-plate, and the both sides 51b and 51c of the vane plate 51 are respectively in contact with the inner circumferential surface of the cylinder 11 and the outer circumferential surface of the rotational shaft 12.
• the vanes 50 and 55 are positioned in a radial direction, directing to the center of the Z-plate, and positioned perpendicular to the rotational shaft 12.
• the roller receiving hole 51 e is formed such that a center of the circular section thereof is positioned at a rather inner side than the front end portion 51 d of the vane plate 51 so that the vane rollers 52 and 57 are not released therefrom.
• the roller receiving hole 51 e has a space (L) between both ends smaller than the diameter (D) of the vane rollers 52 and 57.
• the vane rollers 52 and 57 provided at the front end portion roratably contact along the cam face of the Z-plate 15 when the vane rollers 52 and 57 are rotated, so that a friction resistance between the Z-plate 15 and the vanes 50 and 55 can be considerably reduced.
• the Z-plate 15 makes a rotational motion centering around the rotational shaft 12, whereas the vanes 50 and 55 make a linear motion in an axial direction of the rotational shaft 12 while being in contact at the cam face of the Z-plate. Accordingly the motion direction of the Z-plate 15 and the
• vanes 50 and 55 makes 90°, causing a problem of generation of a severe
• the vane rollers 52 and 57 are provided at the vanes 50 and 55, to make a rolling motion between the vanes 50 and 55 and the Z-plate 15, agreeing with the rotation direction of the Z-plate 15.
• a friction resistance between the Z-plate 15 and the vanes 50 and 55 can be minimized.
• Figures 7 and 8 are a perspective view and an exploded perspective view showing a vane structure in accordance with a second embodiment of the present invention.
• the second embodiment of the present invention proposes a structure that both sides of vanes 60 and 65 are rotatably supported by vane plates 61 and 66.
• roller receiving holes 61 e and 66e are formed at a front end portion being in contact with the Z-plate, of which both sides are not opened, and roller supports 61b and 66b are formed to rotatably support the vane rollers 62 and 67by means of pin members 63 and 68.
• Pin through holes 62a, 67a, 61c and 66c are formed at the vane rollers 62 and 67 and at the roller supports 61b and 66b, into which the pin members 63 and 68 are inserted
• roller supports 61b and 66b is adjusted such that they are formed less protruded than the vane rollers 62 and 67 so as not directly to be in contact with the Z-plate.
• protrusions may be formed at both ends of the vane rollers 62 and 67 and inserted and mounted into grooves of the roller supports 61b and 66b, without installing pin members.
• Figure 9 is an exploded perspective view showing a vane structure and a vane installation structure in accordance with a third embodiment of the present invention
• Figures 10 and Figure 11 are explanatory side views showing a vane operation state of the third embodiment of the present invention.
• a vane roller 72 in the third embodiment has a structure that it is tapering off.
• a roller receiving hole 71 e of a vane plate 71 is form in a conical shape, for which the vane roller 72 inserted into the roller receiving hole 71 e is also formed in a conical bar shape corresponding to the roller receiving hole 71 e.
• the conical vane roller 72 is in rolling-contact with the Z- plate 15.
• the vane roller 72 has a length corresponding to the length of the roller receiving hole 71 e and different diameters at both end portions as it tapers off to form a conical bar shape.
• the roller receiving hole 71 e is formed in a conical shape with different inner diameters at both ends, of which lower surface being in contact with the Z-plate is opened.
• the roller receiving hole 71 e is preferably formed from the side being in contact with an outer circumference of the rotational shaft 12 to the side being in contact with an inner wall of the cylinder 11.
• the roller receiving hole 71 e is preferably formed penetrating both sides of the vane plate 71.
• one side of the roller receiving hole 71e may penetrate one side of the vane plate 71 with some portion of the other side remaining, or otherwise, a roller support may be formed at both sides likewise in the second embodiment of the present invention.
• the center of the roller receiving hole 71 e is to be formed inclined against the front end side of the vane plate 71. The reason for this is to allow the contact surface of the tapering vane roller 72 inserted into the roller receiving hole 71 e to tightly adhered onto the upper surface or the lower surface of the Z-plate 15, being level therein without a gap.
• the tapering vane roller 72 is inserted such that the side with smaller diameter is positioned at the side of the rotational shaft 12 and the side with a larger diameter is positioned at the side of the inner wall of the cylinder 11.
• the tapering vane roller 72 is in rolling-contact with the Z-plate and both sides of the vane plate 71 are respectively in contact with the outer circumferential face of the rotational shaft 12 and the inner circumferential face of the cylinder 11.
• the vane 70 is positioned in a radial direction toward the center of the Z-plate 15 and positioned perpendicular to the rotational shaft 12.
• the vane 70 is elastically supported by a spring coupled at one side of the bearing plate 13. Accordingly, the vane 70 makes a rolling movement as the tapering vane roller is in line-contact with the Z-plate with an elastic force constantly.
• the vane slot 13a into which the vane 70 is inserted, is penetratingly formed at the bearing plate 13, having a width corresponding to the thickness of the vane 70 and a length corresponding to the length of the vane 70.
• the vane slot 13a has the same section and shape with the vane plate 71 of the vane 70.
• the Z-plate 15 When a rotational shaft 12 is rotated upon receiving a driving force from the electric mechanism unit, the Z-plate 15 is rotated along with the rotational shaft 12, to respectively and successively change the first and second spaces within the cylinder assembly into a suction area and a compression area together with vanes 70, to suck and compress and discharge a fluid.
• vanes 70 being in contact with the waveform cam surface of the Z-plate are vertically moved along the cam surface, and at this time, the vane roller 72 of the vane 70 is rotated in a state of being in line-contact with the waveform curved surface of the Z-plate 15.
• the vane roller 72 of the vane 70 makes a rolling movement in a state of being in line-contact with the Z-plate 15, changing the first and second space within the cylinder assembly consisting of the cylinder 11 and the bearing plate to each suction area and compression area.
• a friction resistance between the Z-plate 15 and the vane 70 can be minimized and movement of the vane 70 can be smoothly made.
• the vane structure for a compressor of the present invention by mounting the vane roller being in rotatably contact with the Z-plate in the vane, a friction resistance between the Z-plate and the vane can be reduced when the compressor is operated.
• abrasion between the Z-plate and the vane can be minimized, a noise occurrence can be restrained, durability of parts can be lengthened, and accordingly, a reliability of the compressor can be heightened.

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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)

Applications Claiming Priority (5)

Publications (2)

Family

ID=26638957

Family Applications (1)

Country Status (6)

Families Citing this family (3)

Citations (4)

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• 2002
  • 2002-04-10 JP JP2002581841A patent/JP2004522048A/ja active Pending
  • 2002-04-10 US US10/296,390 patent/US20030235510A1/en not_active Abandoned
  • 2002-04-10 AU AU2002249641A patent/AU2002249641B2/en not_active Ceased
  • 2002-04-10 WO PCT/KR2002/000639 patent/WO2002084123A1/en active IP Right Grant
  • 2002-04-10 BR BRPI0208780-4A patent/BR0208780B1/pt not_active IP Right Cessation
  • 2002-04-10 EP EP02718657A patent/EP1384006A4/de not_active Withdrawn

Patent Citations (4)

Non-Patent Citations (1)

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