WO2003060326A1 - Compressor and vane therefor - Google Patents

Compressor and vane therefor Download PDF

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Publication number
WO2003060326A1
WO2003060326A1 PCT/KR2002/002299 KR0202299W WO03060326A1 WO 2003060326 A1 WO2003060326 A1 WO 2003060326A1 KR 0202299 W KR0202299 W KR 0202299W WO 03060326 A1 WO03060326 A1 WO 03060326A1
Authority
WO
WIPO (PCT)
Prior art keywords
vane
cylinder assembly
oil
compressor
plate
Prior art date
Application number
PCT/KR2002/002299
Other languages
French (fr)
Inventor
Young-Jong Kim
Jae-Sool Shim
Original Assignee
Lg Electronics Inc.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Lg Electronics Inc. filed Critical Lg Electronics Inc.
Priority to AU2002367051A priority Critical patent/AU2002367051A1/en
Publication of WO2003060326A1 publication Critical patent/WO2003060326A1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/028—Means for improving or restricting lubricant flow

Definitions

  • the present invention relates to a compressor, and more particularly, to a compressor and a vane therefor, capable of reducing noise by minimizing friction and improving performance by reducing friction resistance.
  • a compressor is a device for converting mechanical energy into compression energy of compressible fluid
  • a refrigerating compressor is largely classified into a reciprocation compressor, a scroll compressor, a centrifugal compressor, and a rotary compressor by compression methods.
  • the present applicant has developed a Z-compressor with a novel concept, which can be classified as the rotary compressor, and filed an application for the invention to the Korean Intellectual Property Office
  • Figure 1 is a longitudinal sectional view showing a main part of a
  • Figure 2 is a perspective view showing a partially cut compression part in the Z-compressor in accordance with the conventional art
  • Figure 3 is a plan view showing a Z-compressor in accordance with the conventional art.
  • the Z-compressor is a compressor which can be classified as a rotary compressor and it includes a hermetic vessel 10, a motor part 12 which is disposed in the hermetic vessel 10, for generating a rotational force and a compression part 14 for sucking, compressing and discharging gas by the rotational force generated by the motor part 12.
  • the motor part 12 includes a stator 16 and rotor 18 as a conventional motor.
  • the compression part 14 includes a cylinder assembly 31 for forming a compression space V which is fixed inside the hermetic vessel 10 being fixed to the inside of the hermetic vessel 10, a rotational shaft 20 for transmitting a rotational force generated by the rotor 18 of the motor part 12, a Z-plate 23 which rotates being coupled with the rotational shaft 20 and dividing the compression space V of the cylinder assembly 31 into first and second spaces V1 and V2 simultaneously, and first and second vanes 60 and 70 which are respectively contacted with the upper and lower surfaces of the Z-plate 23 and divide the first and second spaces V1 and V2 into suction regions Via and V2a and compression regions V1 b and V2b respectively when the Z-plate 23 rotates.
  • the cylinder assembly 31 includes a cylinder 30 which is formed in a cylindrical shape, and first and second bearing plates 40 and 50 which are fixed at both sides of the cylinder 30, for forming the compression space V.
  • the first and second bearing plates 40 and 50 are formed in a shape of circular plate having a predetermined thickness and area.
  • the first and second bearing plates 40 and 50 include journal portions 42 and 52 which are extended and protruded to have a predetermined height and outer diameter at the center and in which the rotational shaft 20 is inserted rotatably, first and second vane slots 44 and 54 in which the first and second vanes 60 and 70 are inserted at a side of the journal portions 42 and 52 for guiding the first and second vane so that they can perform a reciprocating movement, and a discharge flow path 90 respectively formed at the side of the first and second vane slots 44 and 54, through which compressed gas is discharged.
  • the first and second vane slots 44 and 54 are formed in a shape of a square hole which is perforated through the first and second bearing plates 40 and 50 corresponding to the sizes of the first and second vanes 60 and 70 from the outer circumference of the first and second bearing plates 40 and 50 which are formed in the shape of a circular plate.
  • the rotational shaft 20 includes a shaft portion 21 which is formed to have a predetermined outer diameter and length and inserted in the journal portions 42 and 52 of the first and second bearing plates 40 and 50, a hub portion 22 which is extended and formed at a side of the shaft portion 21 and coupled with the Z-plate 23 and further includes an oil flow path 25 which is bored inside of the shaft portion 21 and through which oil passes. Also, an oil feeder 24 for supplying oil filled at the lower side of the hermetic vessel 10 to the upper side of the hermetic vessel 10 is installed in the lower end of the oil flow path 25.
  • the Z-plate 23 is formed in the shape of the circular plate to slide being contacted on the inner circumferential surface of the cylinder 30, and formed as a cam surface of a sinuous wave curve having an identical thickness from the inner circumferential surface to the outer circumferential surface in the view of projecting a side surface. Accordingly, a surface which forms a upper dead point D1 rotates under the condition that it is contacted with the lower surface of the first bearing plate 40, and a surface which forms a lower dead point D2 rotates under the condition that it is contacted with the upper surface of the second bearing plate 50.
  • the first and second vanes 60 and 70 are formed in a shape of a square plate and formed to be cohered on the sine wave curve of the Z-plate 23 in the compression space V of the cylinder assembly 31.
  • Z-plate contact portions 62 and 72 of a rounding shape which contact with the waveform surface of the Z-plate 23 are formed on a side surface of the vane bodies 61 and 71 which are formed in a square shape having a predetermined thickness.
  • outer surface portions 63 and 73 which are convexly formed to be contacted with the inner wall of the cylinder assembly 31
  • inner surface portions 64 and 74 which are concavely formed to be contacted with the outer circumferential surface of the hub portion 22 of the rotational shaft 20 are formed.
  • Such vanes 60 and 70 divides the compression spaces V1 and V2 into suction regions Vi a and V2a, and compression region V1 b and V2b performing a reciprocating movement in the upward and downward directions according to the height of the cam surface of the Z-plate 23 when the Z-plate 23 rotates in the compression spaces V1 and V2 of the cylinder assembly 31.
  • reference numeral 35 designates a suction flow path through which gas is sucked into the hermetic vessel and cylinder
  • reference numerals 45 and 55 designate discharge mufflers for reducing discharging noise.
  • the first space V1 which is positioned in the upper portion of the Z-plate 23 is divided into the suction region Via and compression region V1 b having the upper dead point D1 of the Z-plate 23 and the first vane 60 as the border
  • the second space V2 which is positioned in the lower portion of the Z-plate 23 is divided into the suction region V2a and compression region V2b having the lower dead point D2 of the Z-plate 23 and the second vane 70 as the border.
  • the Z-plate 23 rotates and accordingly the upper and lower dead points D1 and D2 of the Z-plate 23, thus to vary volumes of the suction regions Via and V2a, and compression regions V1 b and V2b of respective spaces.
  • the first vane 60 and second vane 70 perform a reciprocal movement in different directions according to the height of the cam surface of the Z-plate 23.
  • the compressed gas is simultaneously discharged to the outside of the cylinder assembly 31 through the discharge flow paths 90 of the respective compression spaces V1 and V2 at the moment when the upper and lower dead points D1 and D2 of the Z-plate 23 reach the discharge starting point. Then, the gas passes the respective discharge mufflers 45 and 55 inside of the hermetic vessel 10 and discharged into the outside through the discharge tube (not shown).
  • the oil which is filled in the lower portion of the hermetic vessel 10 by the oil feeder 24 installed in the oil flow path 25 at the lower end of the rotational shaft 20, is upwardly sucked through the oil flow path 25 and is supplied to parts which are slid being flown away at the upper end portion of the rotational shaft 20.
  • Such friction generally occurs inside of the cylinder assembly, and sliding portion such as portions between the vane and Z-plate, between the vane and vane slot, between the Z-plate and the bearing plate, and the like.
  • an object of the present invention is to provide a Z-compressor, capable of improving performance of a compressor and reducing losses caused by abrasion of parts by reducing friction by supplying oil to sliding portions such as between the vane and vane slot, between the vane and Z-plate, between the upper and lower dead points of the Z-plate and the bearing plate, by forming an oil slot in the vane and flowing oil into the cylinder assembly through the oil slot.
  • a compressor including a cylinder assembly which is positioned inside a hermetic vessel having a suction flow path and discharging flow path, a Z-plate for dividing an inner space into a plurality of compression spaces in the cylinder assembly, rotating by a motor part so that gas is sucked, compressed and discharged, and a vane for dividing the respective compression spaces into a suction region and compression region, performing a reciprocating movement being contacted on both surfaces of the Z-plate.
  • an oil slot for flowing oil to the cylinder assembly is formed on a side surface of the vane.
  • Figure 1 is a longitudinal sectional view showing a main part of a Z-compressor in accordance with the conventional art
  • Figure 2 is a perspective view showing a partially cut compression part in the Z-compressor in accordance with the conventional art
  • Figure 3 is a plan view showing a Z-compressor in accordance with the conventional art
  • Figure 4 is a longitudinal sectional view showing a main part of a Z-compressor in accordance with the present invention
  • Figure 5 is a perspective view showing a partially cut compression part in the compressor in which a vane of the Z-compressor in accordance with the present invention is built;
  • Figure 6 is a pian view showing a compression part of the Z-compressor in accordance with the present invention
  • Figure 7 is a graph illustrating change of position of an oil slot according to the change of position of the vane of the Z-compressor in accordance with the present invention
  • Figure 8A is a graph comparing input voltages of the Z-compressors in accordance with the conventional art and the present invention.
  • Figure 8B is a graph comparing performance of the Z-compressors in accordance with the conventional art and the present invention.
  • Figure 9 is a graph comparing generated noise of the Z-compressors in accordance with the conventional art and the present invention.
  • Figure 4 is a longitudinal sectional view showing a main part of a Z-compressor in accordance with the present invention
  • Figure 5 is a perspective view showing a partially cut compression part in the compressor in which a vane of the Z-compressor in accordance with the present invention is built
  • Figure 6 is a plan view showing a the compression part of the Z-compressor in accordance with the present invention.
  • the Z-compressor in accordance with the present invention generally includes a hermetic vessel 110, a motor part 112 which is disposed in the hermetic vessel 110, for generating a rotational force, and a compression part 114 for sucking, compressing and discharging gas by the rotational force generated in the motor part 112.
  • the motor part 112 is composed of a stator 116 and rotor 118.
  • the compression part 114 includes a cylinder assembly 131 which is fixed at the lower part of the hermetic vessel 110, for forming a compression space V in which sucked gas is compressed, a rotational shaft 120 which is connected with the rotor 118 of the motor part 112, for transmitting a rotational force, a Z-plate 123 which is coupled with the rotational shaft 120 inside the cylinder assembly 131 , for dividing the compression space V into a first space V1 and second space V2, and the first and second vanes 160 and 170 which are respectively connected with the upper and lower surfaces of the Z-plate 123, for dividing the first and second spaces V1 and V2 into suction regions Via and V2a and compression regions V1 b and V2b when the Z-plate 123 rotates.
  • the cylinder assembly 131 includes a cylinder 130 in the cylindrical shape and first and second bearing plates 140 and 150 which are fixed on both sides of the cylinder 130, for forming a compression space V together with the cylinder 130.
  • the first and second bearing plates 140 and 150 are formed in a shape of circular plate having a predetermined thickness and area.
  • the first and second bearing plates 140 and 150 include journal portions 142 and 152 which are extended and protruded to have a predetermined height and outer diameter at the center of the first and second bearing plates 140 and 150 and in which the rotational shaft 120 is inserted rotatably, first and second vane slots 144 and 154 in which the first and second vanes 160 and 170 are inserted at a side of the journal portions 142 and 152 for guiding the first and second vanes 160 and 170 so that they can perform a reciprocating movement, and a discharged flow path 190 respectively formed at the side of the first and second vane slots 144 and 154, through which compressed gas is discharged.
  • the rotational shaft 120 includes a shaft portion 121 which is formed to have a predetermined outer diameter and length and is inserted in the journal portions 142 and 152 of the first and second bearing plates 140 and 150, a hub portion 122 which is extended, formed at a side of the shaft portion 121 and coupled with the Z-plate 123, and an oil flow path 125 which penetrates inside the shaft portion 121.
  • an oil feeder 124 for supplying the oil filled in the lower of the hermetic vessel 110 to the upper portion is built.
  • the Z-plate 123 is formed in a shape of a circular plate in projecting a plane so that the outer circumferential surface is contacted sliding on the inner circumferential surface and formed as a cam surface of a sinuous wave curve having an identical thickness from the inner circumferential surface to the outer circumferential surface in view of projecting side surface. Accordingly, a surface which forms the upper dead point D1 is contacted on the lower surface of the first bearing plate 140 and rotates, and a surface which forms the lower dead point D2 is cohered on the upper surface of the second bearing plate 150 and rotates.
  • the first and second vanes 160 and 170 are formed in a square plate shape and formed to be cohered with the sinuous wave surface of the Z-plate 123 in the compression space V of the cylinder assembly 131.
  • Z-plate contact portions 162 and 172 formed in a rounding shape being contacted on the wave form surface of the Z-plate 123 are formed on a side surface of the vane bodies 161 and 171 in the square shape having a predetermined thickness.
  • outer surface portions 163 and 173 which are convexly formed to be contacted on the inner wall of the inner space V of the cylinder assembly 131 , and an inner surface portion 164 which is concavely formed to be contacted on the outer circumferential surface of the rotational shaft 120.
  • Such first and second vanes 160 and 170 are guided to the first and second vane slots 144 and 154 when the Z-plate 123 rotates in the compression space V1 and V2 of the cylinder assembly 131 and divides the compression space V1 and V2 into suction regions Via and V2a, and compression spaces V1b and V2b, performing a reciprocating movement in the upward and downward directions according to the height of the cam surface of the Z-plate 123.
  • oil slots 165 and 175 for flowing the oil positioned outside the cylinder assembly 131 into the compression space inside the cylinder assembly 131 are formed.
  • a plural number of the oil slots 165 and 175 are formed at an equal interval having a predetermined width and depth.
  • the oil slots 165 and 175 are formed in a direction that the first and second vanes moves to efficiently flowing the oil into the cylinder assembly 131 as the vanes 160 and 170 move.
  • Figure 7 is a graph illustrating height of the vane which moves along the wave form surface in the upward and downward directions and change of position of an oil slot when the Z-plate rotates, as the angle of the wave form surface of the Z-plate.
  • the suction regions Vi a and V2a are positioned at the left side of the vanes 160 and 170 and the compression regions V1b and V2b in which gas is compressed is positioned at the right side of the vane.
  • the oil slots 165 and 175 are formed on a surface of the first and second vanes 160 and 170 which is positioned in the suction regions Via and V2a inside the compression space V. That is, because it is difficult to maintain sealing of the compression regions V1 b and V2b in case the oil slots 165 and 175 are formed on a surface of the first and second vanes 160 and 170 which is positioned in the compression regions V1b and V2b inside the compression space V on a surface of the vane body, and it is difficult to flow the oil into the inside of the cylinder assembly 131 due to an internal pressure of the compression regions V1 b and V2b.
  • the oil slot 165 and 175 are formed to having a predetermined length from the outward direction to the inward direction of the cylinder assembly 131 so to connect the outer space and inner space of the cylinder assembly 131 when the vane is contacted on the Z-plate 123 and positioned near from the lower dead point.
  • the oil slots 165 and 175 are formed in a predetermined length.
  • the vanes 160 and 170 move into the cylinder 131 by rotation of the Z-plate 123, since the position of the oil slots 165 and 175 is changed toward the cylinder assembly 131 , the outer and inner sides of the cylinder assembly 131 are gradually communicated each other.
  • the first and second vanes 160 and 170 are moved to the outside of the cylinder assembly 131 , the position of the oil slots 165 and 175 is gradually changed toward the outside of the cylinder assembly 131 , thus to block the outer and inner sides of the cylinder assembly 131.
  • the reference numeral 135 designates a suction flow path that the gas is sucked into the hermetic vessel and cylinder
  • reference numerals 145 and 155 designate discharge mufflers which reduce discharge noise.
  • the Z-plate 123 which is coupled with the rotational shaft 120 rotates in the compression space V inside the cylinder assembly 131.
  • the first and second vanes 160 and 170 which are contacted on the Z-plate 123 are connected together. Therefore, the first and second spaces V1 and V2 which are divided by the Z-plate 123 are respectively converted into suction regions Via and V2a and compression regions V1b and V2b, and the gas is sucked, compressed and discharged into the first and second spaces V1 and V2. The above process is repeated.
  • the first and second vanes 160 and 170 which are vertically and radially positioned of the Z-plate 123 is elastically supported by an elastic supporting means 180 and perform an upward and downward linear reciprocal movement along the wave form surface of the Z-plate 123 as being guided to the first and second vane slots 144 and 154.
  • the oil filled in the lower of the hermetic vessel 110 is sucked upwardly by the oil feeder 124 which is installed in the oil flow path 125 at the lower end of the rotational shaft 120 and flown away in the upper end of the rotational shaft 120.
  • part of the flown oil is flowed into the cylinder assembly 131 through the oil slots 165 and 175 which are formed in the vanes 160 and 170. That is, the oil is flowed into the cylinder assembly 131 through the oil slots 165 and 175 which communicate the inner and outer sides of the cylinder assembly 131 when the first and second vanes 160 and 170 move into the cylinder assembly 131 , and the oil flowed into the cylinder assembly 131 is supplied to sliding portions between the first and second vanes 160 and 170 and the Z-plate, and between the upper or lower dead point D1 or D2 of the
  • Figure 8A is a graph comparing input voltages of the Z-compressors in accordance with the conventional art and the present invention
  • Figure 8B is a graph comparing performance of the Z-compressors in accordance with the conventional art and the present invention
  • Figure 9 is a graph comparing generated noise of the Z-compressors in accordance with the conventional art and the present invention.
  • Figure 8A in case the vane of the Z-compressor in accordance with the present invention is disposed, when the input voltage of the
  • the input voltage of the Z-compressor in accordance with the present invention is 90%.
  • An input voltage reducing effect of 10% is shown.
  • the performance of the Z-compressor in accordance with the present invention shows an improvement effect of 40.1 % when related with the performance of the conventional art.
  • the vane structure of the Z-compressor in accordance with the present invention can reduce friction between the vane and Z-plate, and the upper and lower dead points and bearing plate as the oil slot for flowing oil to the cylinder assembly at a side of the vane, thus to reduce noise and improve performance of the compressor.
  • the oil slot is formed on a side surface of the vane and has the oil flow into the cylinder assembly.
  • performance deterioration of the compression caused by operation noise and friction resistance can be prevented and wearing of the parts can be prevented by reducing friction in the sliding portion inside the cylinder assembly.

Abstract

A compressor includes a cylinder assembly (131) which is positioned inside a hermetic vessel (110) having a suction flow path (135) and discharging flow path, a Z-plate (123) for dividing an inner space into a plurality of compression spaces in the cylinder assembly (131), rotating by a motor part so that gas is sucked, compressed and discharged, and a vane (160, 170) for dividing the respective compression spaces into a suction region and compression region, performing a reciprocating movement being contacted on both surfaces of the Z-plate (123). In addition, an oil slot for inflowing oil into the cylinder assembly (131) is formed on a side surface of the vane. Therefore, friction generated at a sliding portion inside of the cylinder assembly (131) can be reduced and performance deterioration of the compressor caused by operation noise and friction resistance of the compressor can be prevented.

Description

COMPRESSOR AND VANE THEREFOR
TECHNICAL FIELD
The present invention relates to a compressor, and more particularly, to a compressor and a vane therefor, capable of reducing noise by minimizing friction and improving performance by reducing friction resistance.
BACKGROUND ART
Generally, a compressor is a device for converting mechanical energy into compression energy of compressible fluid, and a refrigerating compressor is largely classified into a reciprocation compressor, a scroll compressor, a centrifugal compressor, and a rotary compressor by compression methods.
The present applicant has developed a Z-compressor with a novel concept, which can be classified as the rotary compressor, and filed an application for the invention to the Korean Intellectual Property 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.
The Applicant's invention of the same previously filed application will now be described with reference to accompanying drawings. Figure 1 is a longitudinal sectional view showing a main part of a
Z-compressor in accordance with the conventional art, Figure 2 is a perspective view showing a partially cut compression part in the Z-compressor in accordance with the conventional art, and Figure 3 is a plan view showing a Z-compressor in accordance with the conventional art.
As shown in Figures 1 to 3, the Z-compressor according to the conventional art is a compressor which can be classified as a rotary compressor and it includes a hermetic vessel 10, a motor part 12 which is disposed in the hermetic vessel 10, for generating a rotational force and a compression part 14 for sucking, compressing and discharging gas by the rotational force generated by the motor part 12.
On the lower surface of the hermetic vessel 10, predetermined amount of oil for lubricating sliding portions inside the hermetic vessel 10 is filled. The motor part 12 includes a stator 16 and rotor 18 as a conventional motor.
The compression part 14 includes a cylinder assembly 31 for forming a compression space V which is fixed inside the hermetic vessel 10 being fixed to the inside of the hermetic vessel 10, a rotational shaft 20 for transmitting a rotational force generated by the rotor 18 of the motor part 12, a Z-plate 23 which rotates being coupled with the rotational shaft 20 and dividing the compression space V of the cylinder assembly 31 into first and second spaces V1 and V2 simultaneously, and first and second vanes 60 and 70 which are respectively contacted with the upper and lower surfaces of the Z-plate 23 and divide the first and second spaces V1 and V2 into suction regions Via and V2a and compression regions V1 b and V2b respectively when the Z-plate 23 rotates.
The cylinder assembly 31 includes a cylinder 30 which is formed in a cylindrical shape, and first and second bearing plates 40 and 50 which are fixed at both sides of the cylinder 30, for forming the compression space V.
The first and second bearing plates 40 and 50 are formed in a shape of circular plate having a predetermined thickness and area. The first and second bearing plates 40 and 50 include journal portions 42 and 52 which are extended and protruded to have a predetermined height and outer diameter at the center and in which the rotational shaft 20 is inserted rotatably, first and second vane slots 44 and 54 in which the first and second vanes 60 and 70 are inserted at a side of the journal portions 42 and 52 for guiding the first and second vane so that they can perform a reciprocating movement, and a discharge flow path 90 respectively formed at the side of the first and second vane slots 44 and 54, through which compressed gas is discharged.
The first and second vane slots 44 and 54 are formed in a shape of a square hole which is perforated through the first and second bearing plates 40 and 50 corresponding to the sizes of the first and second vanes 60 and 70 from the outer circumference of the first and second bearing plates 40 and 50 which are formed in the shape of a circular plate.
The rotational shaft 20 includes a shaft portion 21 which is formed to have a predetermined outer diameter and length and inserted in the journal portions 42 and 52 of the first and second bearing plates 40 and 50, a hub portion 22 which is extended and formed at a side of the shaft portion 21 and coupled with the Z-plate 23 and further includes an oil flow path 25 which is bored inside of the shaft portion 21 and through which oil passes. Also, an oil feeder 24 for supplying oil filled at the lower side of the hermetic vessel 10 to the upper side of the hermetic vessel 10 is installed in the lower end of the oil flow path 25.
The Z-plate 23 is formed in the shape of the circular plate to slide being contacted on the inner circumferential surface of the cylinder 30, and formed as a cam surface of a sinuous wave curve having an identical thickness from the inner circumferential surface to the outer circumferential surface in the view of projecting a side surface. Accordingly, a surface which forms a upper dead point D1 rotates under the condition that it is contacted with the lower surface of the first bearing plate 40, and a surface which forms a lower dead point D2 rotates under the condition that it is contacted with the upper surface of the second bearing plate 50.
The first and second vanes 60 and 70 are formed in a shape of a square plate and formed to be cohered on the sine wave curve of the Z-plate 23 in the compression space V of the cylinder assembly 31.
In the first and second vanes 60 and 70, Z-plate contact portions 62 and 72 of a rounding shape which contact with the waveform surface of the Z-plate 23 are formed on a side surface of the vane bodies 61 and 71 which are formed in a square shape having a predetermined thickness. On the both surfaces of the vane bodies 61 and 71 , outer surface portions 63 and 73 which are convexly formed to be contacted with the inner wall of the cylinder assembly 31 , and inner surface portions 64 and 74 which are concavely formed to be contacted with the outer circumferential surface of the hub portion 22 of the rotational shaft 20 are formed.
Such vanes 60 and 70 divides the compression spaces V1 and V2 into suction regions Vi a and V2a, and compression region V1 b and V2b performing a reciprocating movement in the upward and downward directions according to the height of the cam surface of the Z-plate 23 when the Z-plate 23 rotates in the compression spaces V1 and V2 of the cylinder assembly 31.
On the other hand, reference numeral 35 designates a suction flow path through which gas is sucked into the hermetic vessel and cylinder, reference numerals 45 and 55 designate discharge mufflers for reducing discharging noise.
The process that the Z-compressor in accordance with the conventional art with the above described composition is operated will be described as follows.
Firstly, when the rotational shaft 20 is rotated by the driving force generated by the motor part 12, and the Z-plate 23 which is coupled with the rotational shaft 20 simultaneously rotates in the cylinder assembly 31 , and suction, compression and discharge of the gas is operated.
That is, the first space V1 which is positioned in the upper portion of the Z-plate 23 is divided into the suction region Via and compression region V1 b having the upper dead point D1 of the Z-plate 23 and the first vane 60 as the border, and the second space V2 which is positioned in the lower portion of the Z-plate 23 is divided into the suction region V2a and compression region V2b having the lower dead point D2 of the Z-plate 23 and the second vane 70 as the border. Under the above condition, the Z-plate 23 rotates and accordingly the upper and lower dead points D1 and D2 of the Z-plate 23, thus to vary volumes of the suction regions Via and V2a, and compression regions V1 b and V2b of respective spaces. At this time, the first vane 60 and second vane 70 perform a reciprocal movement in different directions according to the height of the cam surface of the Z-plate 23.
Therefore, after the gas is simultaneously sucked into the suction regions Via and V2a of the first and second spaces V1 and V2 through the suction flow path 35 and gradually compressed, the compressed gas is simultaneously discharged to the outside of the cylinder assembly 31 through the discharge flow paths 90 of the respective compression spaces V1 and V2 at the moment when the upper and lower dead points D1 and D2 of the Z-plate 23 reach the discharge starting point. Then, the gas passes the respective discharge mufflers 45 and 55 inside of the hermetic vessel 10 and discharged into the outside through the discharge tube (not shown).
At this time, as the rotational shaft 20 rotates, the oil, which is filled in the lower portion of the hermetic vessel 10 by the oil feeder 24 installed in the oil flow path 25 at the lower end of the rotational shaft 20, is upwardly sucked through the oil flow path 25 and is supplied to parts which are slid being flown away at the upper end portion of the rotational shaft 20.
In the Z-compressor according to the conventional art with the above described composition and operation, one of the most effective factors for the performance of the compressor is friction of the sliding part in the cylinder assembly 31.
Such friction generally occurs inside of the cylinder assembly, and sliding portion such as portions between the vane and Z-plate, between the vane and vane slot, between the Z-plate and the bearing plate, and the like.
Noise is generated by the friction and the parts become worn away and performance of the compressor is degraded by friction resistance.
Also, heat is generated by friction of the above-mentioned sliding portions and a heat loss of refrigerant gas is caused by such heat. However, in the structure of the Z-compressor according to the conventional art, since suction, compression and discharge of gas are performed under the condition that the portion between the vane and the vane slot in which the vane is inserted is hermetically maintained so that the compressed gas from the inner space of the cylinder assembly is not leaked to the outside, oil could not be smoothly supplied into the cylinder assembly and accordingly lubricating of the sliding portion inside the cylinder assembly was difficult.
Therefore, friction and abrasion have occurred between the vane and slot, the vane and the Z-plate, the upper and lower dead points of the Z-plate and the bearing plate, thus to degrade performance of the compressor by the friction loss and cause damage of the parts.
DISCLOSURE OF THE INVENTION Therefore, an object of the present invention is to provide a Z-compressor, capable of improving performance of a compressor and reducing losses caused by abrasion of parts by reducing friction by supplying oil to sliding portions such as between the vane and vane slot, between the vane and Z-plate, between the upper and lower dead points of the Z-plate and the bearing plate, by forming an oil slot in the vane and flowing oil into the cylinder assembly through the oil slot.
To achieve these and other advantages and in accordance with the purpose of the present invention, as embodied and broadly described herein, there is provided a compressor, including a cylinder assembly which is positioned inside a hermetic vessel having a suction flow path and discharging flow path, a Z-plate for dividing an inner space into a plurality of compression spaces in the cylinder assembly, rotating by a motor part so that gas is sucked, compressed and discharged, and a vane for dividing the respective compression spaces into a suction region and compression region, performing a reciprocating movement being contacted on both surfaces of the Z-plate. In addition, an oil slot for flowing oil to the cylinder assembly is formed on a side surface of the vane.
The foregoing and other objects, features, aspects and advantages of the present invention will become more apparent from the following detailed description of the present invention when taken in conjunction with the accompanying drawings. BRIEF DESCRIPTION OF THE DRAWINGS
The accompanying drawings, which are included to provide a further understanding of the invention and are incorporated in and constitute a part of this specification, illustrate embodiments of the invention and together with the description serve to explain the principles of the invention.
In the drawings:
Figure 1 is a longitudinal sectional view showing a main part of a Z-compressor in accordance with the conventional art;
Figure 2 is a perspective view showing a partially cut compression part in the Z-compressor in accordance with the conventional art;
Figure 3 is a plan view showing a Z-compressor in accordance with the conventional art;
Figure 4 is a longitudinal sectional view showing a main part of a Z-compressor in accordance with the present invention; Figure 5 is a perspective view showing a partially cut compression part in the compressor in which a vane of the Z-compressor in accordance with the present invention is built;
Figure 6 is a pian view showing a compression part of the Z-compressor in accordance with the present invention; Figure 7 is a graph illustrating change of position of an oil slot according to the change of position of the vane of the Z-compressor in accordance with the present invention;
Figure 8A is a graph comparing input voltages of the Z-compressors in accordance with the conventional art and the present invention;
Figure 8B is a graph comparing performance of the Z-compressors in accordance with the conventional art and the present invention; and
Figure 9 is a graph comparing generated noise of the Z-compressors in accordance with the conventional art and the present invention.
MODES FOR CARRYING OUT THE PREFERRED EMBODIMENTS
It will be apparent to those skilled in the art that various modifications and variations can be made in the plasma polymerization on the surface of the material of the present invention without departing from the spirit or scope of the invention. Thus, it is intended that the present invention cover modifications and variations of this invention provided they come within the scope of the appended claims and their equivalents.
Reference will now be made in detail to the preferred embodiments of the present invention, examples of which are illustrated in the accompanying drawings.
A vane structure of a Z-compressor in accordance with the present invention will be described with reference to Figure 4 to 6.
Figure 4 is a longitudinal sectional view showing a main part of a Z-compressor in accordance with the present invention, Figure 5 is a perspective view showing a partially cut compression part in the compressor in which a vane of the Z-compressor in accordance with the present invention is built, and Figure 6 is a plan view showing a the compression part of the Z-compressor in accordance with the present invention.
As shown in Figures 4 to 6, the Z-compressor in accordance with the present invention generally includes a hermetic vessel 110, a motor part 112 which is disposed in the hermetic vessel 110, for generating a rotational force, and a compression part 114 for sucking, compressing and discharging gas by the rotational force generated in the motor part 112.
In the hermetic vessel 110, a predetermined amount of oil for lubricating a sliding part inside the hermetic vessel 110 is filled in the lower of the hermetic vessel 110. The motor part 112 is composed of a stator 116 and rotor 118.
The compression part 114 includes a cylinder assembly 131 which is fixed at the lower part of the hermetic vessel 110, for forming a compression space V in which sucked gas is compressed, a rotational shaft 120 which is connected with the rotor 118 of the motor part 112, for transmitting a rotational force, a Z-plate 123 which is coupled with the rotational shaft 120 inside the cylinder assembly 131 , for dividing the compression space V into a first space V1 and second space V2, and the first and second vanes 160 and 170 which are respectively connected with the upper and lower surfaces of the Z-plate 123, for dividing the first and second spaces V1 and V2 into suction regions Via and V2a and compression regions V1 b and V2b when the Z-plate 123 rotates.
The cylinder assembly 131 includes a cylinder 130 in the cylindrical shape and first and second bearing plates 140 and 150 which are fixed on both sides of the cylinder 130, for forming a compression space V together with the cylinder 130.
The first and second bearing plates 140 and 150 are formed in a shape of circular plate having a predetermined thickness and area. The first and second bearing plates 140 and 150 include journal portions 142 and 152 which are extended and protruded to have a predetermined height and outer diameter at the center of the first and second bearing plates 140 and 150 and in which the rotational shaft 120 is inserted rotatably, first and second vane slots 144 and 154 in which the first and second vanes 160 and 170 are inserted at a side of the journal portions 142 and 152 for guiding the first and second vanes 160 and 170 so that they can perform a reciprocating movement, and a discharged flow path 190 respectively formed at the side of the first and second vane slots 144 and 154, through which compressed gas is discharged.
The rotational shaft 120 includes a shaft portion 121 which is formed to have a predetermined outer diameter and length and is inserted in the journal portions 142 and 152 of the first and second bearing plates 140 and 150, a hub portion 122 which is extended, formed at a side of the shaft portion 121 and coupled with the Z-plate 123, and an oil flow path 125 which penetrates inside the shaft portion 121.
Also, at the lower end of the oil flow path 125, an oil feeder 124 for supplying the oil filled in the lower of the hermetic vessel 110 to the upper portion is built.
The Z-plate 123 is formed in a shape of a circular plate in projecting a plane so that the outer circumferential surface is contacted sliding on the inner circumferential surface and formed as a cam surface of a sinuous wave curve having an identical thickness from the inner circumferential surface to the outer circumferential surface in view of projecting side surface. Accordingly, a surface which forms the upper dead point D1 is contacted on the lower surface of the first bearing plate 140 and rotates, and a surface which forms the lower dead point D2 is cohered on the upper surface of the second bearing plate 150 and rotates.
The first and second vanes 160 and 170 are formed in a square plate shape and formed to be cohered with the sinuous wave surface of the Z-plate 123 in the compression space V of the cylinder assembly 131.
Also, referring to Figure 5, in the first and second vanes 160 and 170, Z-plate contact portions 162 and 172 formed in a rounding shape being contacted on the wave form surface of the Z-plate 123 are formed on a side surface of the vane bodies 161 and 171 in the square shape having a predetermined thickness. On the both side surfaces of the vane bodies 161 and 171 , outer surface portions 163 and 173 which are convexly formed to be contacted on the inner wall of the inner space V of the cylinder assembly 131 , and an inner surface portion 164 which is concavely formed to be contacted on the outer circumferential surface of the rotational shaft 120. Such first and second vanes 160 and 170 are guided to the first and second vane slots 144 and 154 when the Z-plate 123 rotates in the compression space V1 and V2 of the cylinder assembly 131 and divides the compression space V1 and V2 into suction regions Via and V2a, and compression spaces V1b and V2b, performing a reciprocating movement in the upward and downward directions according to the height of the cam surface of the Z-plate 123.
Also, on a side surface of the first and second vanes 160 and 170, oil slots 165 and 175 for flowing the oil positioned outside the cylinder assembly 131 into the compression space inside the cylinder assembly 131 are formed.
A plural number of the oil slots 165 and 175 are formed at an equal interval having a predetermined width and depth.
Also, it is desirable that the oil slots 165 and 175 are formed in a direction that the first and second vanes moves to efficiently flowing the oil into the cylinder assembly 131 as the vanes 160 and 170 move.
The oil slots 165 and 175 will be described in more detail with reference to Figure 7.
Figure 7 is a graph illustrating height of the vane which moves along the wave form surface in the upward and downward directions and change of position of an oil slot when the Z-plate rotates, as the angle of the wave form surface of the Z-plate.
In Figure 7, the suction regions Vi a and V2a are positioned at the left side of the vanes 160 and 170 and the compression regions V1b and V2b in which gas is compressed is positioned at the right side of the vane.
As shown in the drawing, the oil slots 165 and 175 are formed on a surface of the first and second vanes 160 and 170 which is positioned in the suction regions Via and V2a inside the compression space V. That is, because it is difficult to maintain sealing of the compression regions V1 b and V2b in case the oil slots 165 and 175 are formed on a surface of the first and second vanes 160 and 170 which is positioned in the compression regions V1b and V2b inside the compression space V on a surface of the vane body, and it is difficult to flow the oil into the inside of the cylinder assembly 131 due to an internal pressure of the compression regions V1 b and V2b.
Also, the oil slot 165 and 175 are formed to having a predetermined length from the outward direction to the inward direction of the cylinder assembly 131 so to connect the outer space and inner space of the cylinder assembly 131 when the vane is contacted on the Z-plate 123 and positioned near from the lower dead point.
That is, the oil slots 165 and 175 are formed in a predetermined length. When the vanes 160 and 170 move into the cylinder 131 by rotation of the Z-plate 123, since the position of the oil slots 165 and 175 is changed toward the cylinder assembly 131 , the outer and inner sides of the cylinder assembly 131 are gradually communicated each other. On the contrary, when the first and second vanes 160 and 170 are moved to the outside of the cylinder assembly 131 , the position of the oil slots 165 and 175 is gradually changed toward the outside of the cylinder assembly 131 , thus to block the outer and inner sides of the cylinder assembly 131.
Here, as the oil slots 165 and 175 are lengthened, a period 200 that the outer and inner sides of the cylinder assembly 131 are communicated each other is lengthened, and accordingly, the amount of oil which flows into the cylinder assembly 131 is increased. Also, in case of shortening the length of the oil slots 165 and 175, since the period 200 that the outer and inner side of the cylinder assembly 131 are communicated each other is shortened, the amount of oil which flows into the cylinder assembly 131 is decreased.
Therefore, since the period 200 that the outer and inner sides of the cylinder assembly 131 are communicated each other is determined according to the length of the oil slots 165 and 175; the inflow amount of the oil can be determined. On the other hand, the reference numeral 135 designates a suction flow path that the gas is sucked into the hermetic vessel and cylinder, and reference numerals 145 and 155 designate discharge mufflers which reduce discharge noise.
The operation of the Z-compressor in accordance with the present invention will be described as follows.
Firstly, when the rotational shaft 120 rotates by receiving a driving force of the motor part 112, the Z-plate 123 which is coupled with the rotational shaft 120 rotates in the compression space V inside the cylinder assembly 131. As the Z-plate 123 rotates in the internal space of the cylinder assembly 131 , the first and second vanes 160 and 170 which are contacted on the Z-plate 123 are connected together. Therefore, the first and second spaces V1 and V2 which are divided by the Z-plate 123 are respectively converted into suction regions Via and V2a and compression regions V1b and V2b, and the gas is sucked, compressed and discharged into the first and second spaces V1 and V2. The above process is repeated.
At this time, as the Z-plate 123 rotates inside the cylinder assembly 131 , the first and second vanes 160 and 170 which are vertically and radially positioned of the Z-plate 123 is elastically supported by an elastic supporting means 180 and perform an upward and downward linear reciprocal movement along the wave form surface of the Z-plate 123 as being guided to the first and second vane slots 144 and 154.
Also, as the rotational shaft 120 rotates, the oil filled in the lower of the hermetic vessel 110 is sucked upwardly by the oil feeder 124 which is installed in the oil flow path 125 at the lower end of the rotational shaft 120 and flown away in the upper end of the rotational shaft 120.
Then, part of the flown oil is flowed into the cylinder assembly 131 through the oil slots 165 and 175 which are formed in the vanes 160 and 170. That is, the oil is flowed into the cylinder assembly 131 through the oil slots 165 and 175 which communicate the inner and outer sides of the cylinder assembly 131 when the first and second vanes 160 and 170 move into the cylinder assembly 131 , and the oil flowed into the cylinder assembly 131 is supplied to sliding portions between the first and second vanes 160 and 170 and the Z-plate, and between the upper or lower dead point D1 or D2 of the
Z-plate 123 and the first and second bearing plates 140 and 150, thus to perform lubricating action and minimize friction resistance of such sliding portions. The effect of the vane structure of the Z-compressor in accordance with the present invention will be described in more detail with reference to Figures 8A, 8B and 9.
Figure 8A is a graph comparing input voltages of the Z-compressors in accordance with the conventional art and the present invention, Figure 8B is a graph comparing performance of the Z-compressors in accordance with the conventional art and the present invention, and Figure 9 is a graph comparing generated noise of the Z-compressors in accordance with the conventional art and the present invention. As shown in Figure 8A, in case the vane of the Z-compressor in accordance with the present invention is disposed, when the input voltage of the
Z-compressor in accordance with the conventional art is 100% in the identical performance condition, the input voltage of the Z-compressor in accordance with the present invention is 90%. An input voltage reducing effect of 10% is shown.
Also, in the comparison of performance of the Z-compressors in accordance with the conventional art and present invention, as shown in Figure
8B, the performance of the Z-compressor in accordance with the present invention shows an improvement effect of 40.1 % when related with the performance of the conventional art.
This shows that reduction of friction resistance by the lubricating effect as the oil is flowed in and the oil is supplied between the first and second vanes 160 and 170 and the cam surface of the Z-plate 123, and between the upper or lower dead point D1 or D2 of the Z-plate 123 and the bearing plates 140 and 150 by formation of the oil slots 165 and 175 in the vanes 160 and 170 and inflow of the oil.
On the other hand, as shown in Figure 9, the occurred noise of the Z-compressor in accordance with the present invention when related with the conventional one is reduced from 69dB to 64dB.
It is a noise reducing effect caused by friction reduction by inflow of oil into a sliding portion inside the cylinder assembly 131.
The vane structure of the Z-compressor in accordance with the present invention can reduce friction between the vane and Z-plate, and the upper and lower dead points and bearing plate as the oil slot for flowing oil to the cylinder assembly at a side of the vane, thus to reduce noise and improve performance of the compressor.
Also, as the oil slot is formed on a surface of the vane, friction between the vane and vane slot is reduced by the oil flowed to the oil slot and contact area between the vane and inner wall of the vane slot is reduced, thus to minimize friction.
Also, since input and output of the oil can be adjusted by upward and downward movement of the vane according to adjustment of the length of the oil slot, the amount of oil which flow to the cylinder assembly can be adjusted.
In the Z-compressor in accordance with the present invention with the above composition and operation, the oil slot is formed on a side surface of the vane and has the oil flow into the cylinder assembly. In addition, performance deterioration of the compression caused by operation noise and friction resistance can be prevented and wearing of the parts can be prevented by reducing friction in the sliding portion inside the cylinder assembly.
As the present invention may be embodied in several forms without departing from the spirit or essential characteristics thereof, it should also be understood that the above-described embodiments are not limited by any of the details of the foregoing description, unless otherwise specified, but rather should be construed broadly within its spirit and scope as defined in the appended claims, and therefore all changes and modifications that fall within the metes and bounds of the claims, or equivalence of such metes and bounds are therefore intended to be embraced by the appended claims.

Claims

1. A compressor, comprising a hermetic vessel; a cylinder assembly disposed in the casing and having a suction flow path and discharging flow path, a Z-plate disposed in the cylinder assembly for dividing an inner space of the cylinder assembly into a plurality of compression spaces in the cylinder assembly, rotating by a motor part so that gas is sucked, a compressed and discharged, and a vane being contacted with the Z-plate for dividing the respective compression spaces into a suction region and compression region, performing a reciprocating movement being contacted on both surfaces of the Z-plate; wherein the vane includes an oil slot formed on one side surface of the vane for inflowing oil to the cylinder assembly.
2. The compressor of claim 1 , wherein the oil slot is formed on a side surface of the vane which is positioned in the suction region of the inner space in the cylinder assembly.
3. The compressor of claim 2, wherein the oil slot is formed in the direction that the vane moves.
4. The compressor of claim 3, wherein the plurality of oil slots are formed at an equal interval.
5. The compressor of claim 3, wherein the oH slot is formed having a predetermined length in the direction along from the outer portion to the inner portion of the cylinder assembly so that the outer and inner portions of the cylinder assembly can be communicated when the vane is contacted with the Z-plate and is positioned near a lower dead point.
6. A vane of a compressor performing a reciprocating movement in the inward and outward directions of a cylinder assembly in which a compression space is formed, and dividing the compression space into a suction region and a compression region, which comprises an oil slot for flowing oil into the cylinder assembly on a side surface.
7. The vane of claim 6, wherein the oil slot is formed on a side surface of the vane which is positioned in an inner space suction region of the cylinder assembly.
8. The vane of claim 6, wherein the oil slot is formed in a direction that the vane moves.
9. The vane of claim 6, wherein the plurality of oil slots are formed at an equal interval.
10. The vane of claim 6, wherein the oil slot is formed having a predetermined length in the direction along from the outer portion to the inner portion of the cylinder assembly so that the outer and inner portions of the cylinder assembly can be communicated along the reciprocating movement of the vane.
PCT/KR2002/002299 2001-12-28 2002-12-06 Compressor and vane therefor WO2003060326A1 (en)

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EP1647714A3 (en) * 2004-09-30 2011-12-07 Sanyo Electric Co., Ltd. Compressor
EP1643128A3 (en) * 2004-09-30 2011-12-14 Sanyo Electric Co., Ltd. Compressor

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JP2011074798A (en) * 2009-09-30 2011-04-14 Sanyo Electric Co Ltd Rotary compressor
JPWO2017061014A1 (en) * 2015-10-08 2018-04-26 三菱電機株式会社 Rotary compressor

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EP1647714A3 (en) * 2004-09-30 2011-12-07 Sanyo Electric Co., Ltd. Compressor
EP1643128A3 (en) * 2004-09-30 2011-12-14 Sanyo Electric Co., Ltd. Compressor

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AU2002367051A1 (en) 2003-07-30
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US20030170134A1 (en) 2003-09-11

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