EP1134413A2 - Swash plate for compressor - Google Patents
Swash plate for compressor Download PDFInfo
- Publication number
- EP1134413A2 EP1134413A2 EP01106655A EP01106655A EP1134413A2 EP 1134413 A2 EP1134413 A2 EP 1134413A2 EP 01106655 A EP01106655 A EP 01106655A EP 01106655 A EP01106655 A EP 01106655A EP 1134413 A2 EP1134413 A2 EP 1134413A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- swash plate
- contact surface
- coating
- layer
- head side
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Withdrawn
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B27/1036—Component parts, details, e.g. sealings, lubrication
- F04B27/1054—Actuating elements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
- F05C2201/00—Metals
- F05C2201/90—Alloys not otherwise provided for
- F05C2201/903—Aluminium alloy, e.g. AlCuMgPb F34,37
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
- F05C2203/00—Non-metallic inorganic materials
- F05C2203/08—Ceramics; Oxides
- F05C2203/0804—Non-oxide ceramics
- F05C2203/0856—Sulfides
- F05C2203/086—Sulfides of molybdenum
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
- F05C2203/00—Non-metallic inorganic materials
- F05C2203/08—Ceramics; Oxides
- F05C2203/0865—Oxide ceramics
- F05C2203/0882—Carbon, e.g. graphite
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
- F05C2225/00—Synthetic polymers, e.g. plastics; Rubber
- F05C2225/04—PTFE [PolyTetraFluorEthylene]
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
- F05C2251/00—Material properties
- F05C2251/14—Self lubricating materials; Solid lubricants
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
- F05C2253/00—Other material characteristics; Treatment of material
- F05C2253/12—Coating
Definitions
- the present invention relates to a swash plate that is used in a compressor, for example, in a refrigerant circuit of an air conditioner, and is coupled to single headed pistons by pairs of shoes.
- Each pair of the shoes has a head side shoes and a skirt side shoes.
- the head side shoes contacts a head side face of the swash plate, or the face that is closer to the piston heads.
- the skirt side shoes contacts the other side of the swash plate, or the skirt side face, which is closer to the end of the piston skirts.
- the shoes and the swash plate in a swash plate type compressor are lubricated by lubricant oil retained in the compressor. Specifically, the lubricant oil is converted into mist by gas circulating in the compressor. The oil mist is then supplied to the joint between the shoes and the swash plate.
- Load applied to the head side face of a swash plate by the head side shoes is different from load applied to the skirt side face of the swash plate by the skirt side shoes. That is, when gas is drawn into the associated cylinder bore, the piston is pulled outward by the swash plate and the reaction force of the suction mainly acts on the skirt side face of the swash plate. When the gas is compressed in each cylinder bore, the associated piston is pressed into the cylinder bore and the reaction force of the compression mainly acts on the head side face of the swash plate.
- the load based on the compression reaction force is generally greater than the load based on the suction reaction force.
- the head side face, which contacts the head side shoess need to have relatively high wear resistance.
- the wear resistance of the skirt side face, which contacts the skirt side shoess is not as high as the level required for the head side face, the lubrication between the skirt side face and the skirt side shoess is maintained for an extended period.
- the skirt side face is treated to have the same coating as that of the head side face. In other words, the skirt side face has been given an excessive wear resistance, which increases the cost for coating the swash plate.
- a swash plate used in a compressor is provided.
- the swash plate is mounted on a drive shaft and coupled to a single-headed piston to convert a rotational movement of the drive shaft to a linearly reciprocal movement of the piston.
- the piston has a head portion compressing gas and receiving reaction force from the gas and a skirt portion accommodating a first shoe and a second shoe opposed to each other.
- the first shoe is disposed closer to the piston head than the second shoe.
- the first shoe and the second shoe are respectively kept in a slidable contact with a first contact surface and a second contact surface opposed to each other in the swash plate.
- the swash plate includes a first coating formed on the first contact surface.
- the first coating is made of an aluminum based material.
- the swash plate also includes a second coating formed on the second contact surface.
- the second coating material is made of a material simpler for production than the aluminum based material.
- the compressor includes a cylinder block 1, a front housing member 2, a valve plate 3, and a rear housing member 4.
- the front housing member 2 is coupled to a front end of the cylinder block 1. The front end is to the left in Fig. 1.
- the rear housing member 4 is connected to the rear end of the cylinder block 1 through the valve plate 3.
- the cylinder block 1, the front housing member 2, the valve plate 3, and the rear housing member 4 are fastened together with through bolts (not shown) to define a compressor housing.
- a crank chamber 5, a suction chamber 6 and a discharge chamber 7 are defined in the housing.
- Cylinder bores la (only one is shown in Fig. 1) are defined in the cylinder block 1.
- a single-headed piston 8 is reciprocally accommodated in each cylinder bore la.
- each piston 8 is made of aluminum based material.
- Valve flaps are provided in the valve plate 3 for selectively connecting the suction chamber 6 and the discharge chamber 7 with each cylinder bore la.
- a drive shaft 9 is rotationally supported in the crank chamber 5.
- a swash plate 10 is fitted around the drive shaft 9.
- a through hole 10a extends in the middle of the swash plate 10.
- the drive shaft 9 extends through the through hole 10a.
- the swash plate 10 is connected with the drive shaft 9 through a hinge mechanism 13 and a lug plate 11 to rotate integrally with the drive shaft 9.
- the swash plate 10 inclines with respect to the drive shaft 9 while axially sliding along the surface of the drive shaft 9.
- the skirt of each piston 8 is connected with the swash plate 10 by a skirt side shoe 20A and a head side shoe 20B.
- the shoes 20A, 20B slide along the periphery of the swash plate 10.
- each piston 8 moves in the associated cylinder bore la by a stroke corresponding to the inclination angle.
- Refrigerant gas is drawn from the suction chamber 6 (the zone in which suction pressure Ps acts) to the cylinder bore la.
- the gas is then compressed in the cylinder bore la and is discharged to the discharge chamber 7 (the zone in which discharge pressure Pd acts). This series of steps is repeated.
- a spring 14 urges the swash plate 10 toward the cylinder block 1 (to decrease the inclination of the swash plate 10).
- a snap ring 15 is secured to the drive shaft 9 for determining the minimum angle of inclination ⁇ min (for example, three to five degrees) of the swash plate 10.
- a counterweight 10b is provided on the swash plate 10. The counterweight 10b abuts against a restricting portion lla of the lug plate 11. This determines the maximum inclined angle ⁇ max of the swash plate 10.
- the inclination angle of the swash plate 10 is determined according to various moments acting on the swash plate 10.
- the moments include a rotational moment, which is based on the centrifugal force of the rotating swash plate 10, a spring force moment, which is based on the force of the spring 14, a moment of inertia of the piston reciprocation, and a gas pressure moment.
- the gas pressure moment is generated by the force of the pressure in the cylinder bores la and the pressure in the crank chamber 5 (crank pressure Pc). Depending on the crank pressure Pc, the gas pressure moment acts either to increase or decrease the inclination angle of the swash plate 10.
- the swash plate type compressor of Fig. 1 has a control valve 16 that adjusts the crank pressure Pc to alter the moment of the gas pressure as necessary. The control valve 16 thus selects the inclination angle of the swash plate 10 within a range between the minimum angle of inclination ⁇ min and the maximum angle of inclination ⁇ max.
- annular skirt side contact surface 30A is formed on a side of the swash plate 10 that is closer to the ends of the piston skirts
- annular head side contact surface 30B is formed on a side of the swash plate that is closer to the piston head.
- the skirt side shoes 20A slide on the skirt side contact surface 30A
- the head side shoes 20B slide the head side contact surface 30B.
- the swash plate 10 is formed of relatively heavy, iron-based material (for example, cast iron FCD700) to optimize the moment of rotation due to centrifugal force caused by rotation of the swash plate 10.
- the shoes 20A, 20B are also formed of iron-based material (bearing steel) to increase their mechanical strength. If two different components formed of the same material (in this case, the swash plate 10 and the shoes 20A, 20B) slide against each other under severe conditions, seizure may occur. Accordingly, in the first embodiment, skirt side coating 31A and had side coating 31B are formed at least on the associated contact surfaces 30A, 30B.
- the coatings 31A, 31B allow the shoes 20A, 20B to slide smoothly along the contact surfaces 30A, 30B. That is, the procedure of the present invention is performed on the contact surfaces 30A, 30B of the swash plate 10.
- the skirt side coating 31A which is formed on the skirt side contact surface 30A, is made of solid lubricant.
- the thickness of the skirt side coating 31A is for example 0.5 to 10 ⁇ m.
- the solid lubricant includes at least one of molybdenum disulfide, tungsten disulfide, graphite, boron nitride, antimony oxide, lead oxide, indium, tin and fluorocarbon resin.
- the head side coating 31B which is formed on the head side contact surface 30B, has a two-layer structure.
- a first layer 31B-1 of the head side coating 31B is formed of metal different from that forming the body of the swash plate 10 and the bodies of the shoes 20A, 20B.
- the material of the first layer 31B-1 may be Al-Si based material including, for example, silicon containing aluminum alloys and intermetallic compounds consisting of aluminum and silicon.
- the physical properties such as hardness and melting point of the Al-Si based material, or aluminum based material, vary in accordance with the silicon content of the material.
- the Al-Si based material contains 10 to 20 weight percent (preferably, from 15 to 18 percent) silicon.
- a second layer 31B-2 of the head side coating 31B covers the first layer 31B-1.
- the second layer 31B-2 is formed of solid lubricant and the thickness is between 0.5 and 10 ⁇ m.
- the coatings 31A, 31B prevent seizure from occurring between the shoes 20A, 20B and the contact surfaces 30A, 30B.
- the coatings 31A, 31B also allow the shoes 20A, 20B to slide smoothly along the contact surfaces 30A, 30B of the swash plate 10. In other words, even when the lubricant oil supply to the compressor is insufficient, the coatings 31A, 31B ensure a certain level of lubrication between the swash plate 10 and the shoes 20A, 20B.
- the head side contact surface 30B is roughened through, for example, shot blasting.
- the procedure is performed with a cylindrical metal supplier 40.
- the supplier 40 is formed of Al-Si based material.
- the supplier 40 has a planer end 41 having a diameter substantially equal to a radial dimension of the head side contact surface 30B of the swash plate 10 (the difference between the outer radius and the inner radius of the head side contact surface 30B).
- the swash plate 10 is mounted to a first drive mechanism 51, and the supplier 40 is connected to a second drive mechanism 52.
- the first drive mechanism 51 is driven by a first motor M1.
- the swash plate 10 is rotated about an axis L.
- the head side contact surface 30B is centered on the axis L and is perpendicular to axis L. In this state, a portion of the head side contact surface 30B faces and is spaced from the end 41 of the supplier 40.
- the second drive mechanism 52 is operably connected to a linear mover 53 and a second motor M2.
- the linear mover 53 operates to move the supplier 40 axially. Specifically, the linear mover 53 enables the supplier 40 to contact the swash plate 10. The supplier 40 is then pressed against the head side contact surface 30B of the swash plate 10 by the linear mover 53. Afterwards, the linear mover 53 separates the supplier 40 from the swash plate 10.
- the second motor M2 rotates the supplier 40 about the axis L', which is the axis of the supplier 40.
- the end 41 of the supplier 40 is perpendicular to the axis L'.
- the end 41 is parallel to the head side contact surface 30B, and the rotation axis L' of the supplier 40 is offset from axis L. That is, when the supplier 40 is pressed against the head side contact surface 30B of the swash plate 10, one point on the circumference of the end 41 touches the outer circumference of the head side contact surface 30B, and a diametrically opposite point on the end 41 touches the inner circumference of the head side contact surface 30B (as indicated by broken lines in Fig. 3).
- the second motor M2 rotates the supplier 40 at a predetermined speed (for example, 1,500 rpm) about the axis L'.
- the linear mover 53 causes the supplier 40 and the second drive mechanism 52 to approach the swash plate 10.
- the supplier 40 contacts the head side contact surface 30B of the swash plate 10
- the supplier 40 is pressed against the head side contact surface 30B until the pressure reaches a predetermined level (for example, 18 MPa).
- the first motor M1 rotates the swash plate 10 by a predetermined rotation speed (for example, 1 rpm). That is, the supplier 40 and the head side contact surface 30B move relative to each other along the circumferential direction of the head side contact surface 30B.
- Heat which is caused by friction, is generated between the end 41 of the supplier 40 and the head side contact surface 30B.
- the heat is mainly caused by the relatively rapid rotation of the supplier 40.
- the heat softens a portion of the supplier 40 near its end 41.
- Molten metal is then supplied from the soft portion of the supplier 40 to a corresponding portion of the head side contact surface 30B. Accordingly, while the supplier 40 is moving relative to the head side contact surface 30B, molten metal is continuously supplied from the supplier 40 to the head side contact surface 30B along the annular path of the surface 30B.
- molten metal is supplied to the entire head side contact surface 30B.
- the thickness of the head side coating 31B is, for example, 70 to 100 micrometers. The thickness is determined by adding a finishing allowance (which is, for example, 20 to 50 micrometers) to the desired coating thickness (which is, for example, 50 micrometers).
- the surface of the first layer 31B-1 is machined through cutting or grinding to adjust the thickness of the first layer 31B-1 as desired.
- the surface of the first layer 31B-1 is roughened through, for example, shot blasting.
- Liquid paint containing solid lubricant is applied to the roughened surface of the first layer 31B-1 in the same manner as the procedure for forming the skirt side coating 31A. Thereafter, the applied liquid paint is baked for forming the second layer 31B-2. Afterwards, the surface of the second layer 31B-2 is machined through cutting or grinding to adjust the thickness of the first layer 31B-1, or the thickness of the head side coating 31B, as desired.
- the first embodiment has the following advantages.
- the first layer 31B-1 is formed through build up welding by using a coated electrode 54.
- Fig. 5 schematically shows an arc welding apparatus 60.
- a first drive mechanism 51 of the second embodiment is installed such that the axis L is perpendicular to the axis L in the embodiment of Figs. 1 to 4.
- the arc welding apparatus 60 includes an electrode 54 and a welding source 55, which applies voltage to the electrode 54 and the swash plate 10.
- the electrode 54 is formed by applying flux 54b on a core 54a, which is made of Al-Si based material.
- the electrode 54 is supported by a support 56, which is connected to a lift 57.
- the axis of the electrode 54 is offset from the axis L of the swash plate 10, which is placed on the first drive mechanism 51 and is located above the head side contact surface 30B.
- the support 56, together with the electrode 54, is moved vertically as viewed in the drawing by the lift 57, which permits the electrode 54 to approach and separate from a part of the head side contact surface 30B.
- molten metal is supplied to the entire head side contact surface 30B. This forms the first layer 31B-1 of Al-Si based material.
- the second embodiment has the advantages (1)-(5) and (7) of the first embodiment.
- the first layer 31B-1 may be formed through thermal spraying.
- thermal spraying metal powder is molten and sprayed on to the head side contact surface 30B with flame.
- the first layer 31B-1 may be formed through sintering.
- sintering metal powder is sintered on to the head side contact surface 30B with flame.
- the skirt side coating 31A may be formed of tin through electroplating or through electroless plating.
- the first layer 31B-1 is formed through arc welding by using the coated electrode 54.
- the first layer 31B-1 may be formed through gas-shielded arc welding or submerged-arc welding.
- Gas-shielded arc welding includes metal inert gas (MIG) welding, metal active gas (MAG) welding and TIG welding.
- the procedures of the present invention may be applied to swash plates 10 formed of aluminum based material instead of iron based material.
- a swash plate used in a compressor A side of the swash plate that contacts head side shoes is coated with two layers. The first layer is formed of aluminum material and the second layer is formed with solid lubricant. A side of the swash plate that contacts skirt side shoes is coated with a single layer of solid lubricant. Accordingly, the swash plate has a sufficiently wear resistance on both sides for the minimized cost.
Abstract
Description
- The present invention relates to a swash plate that is used in a compressor, for example, in a refrigerant circuit of an air conditioner, and is coupled to single headed pistons by pairs of shoes. Each pair of the shoes has a head side shoes and a skirt side shoes. The head side shoes contacts a head side face of the swash plate, or the face that is closer to the piston heads. The skirt side shoes contacts the other side of the swash plate, or the skirt side face, which is closer to the end of the piston skirts.
- The shoes and the swash plate in a swash plate type compressor are lubricated by lubricant oil retained in the compressor. Specifically, the lubricant oil is converted into mist by gas circulating in the compressor. The oil mist is then supplied to the joint between the shoes and the swash plate.
- However, if the compressor is de-activated for a relatively long time, the lubricant oil that has been applied to the joint between the shoes and the swash plate is removed by refrigerant gas when the compressor is re-started. Thus, when the compressor is re-started, the lubrication between the shoes and the swash plate is insufficient until refrigerant returns to the compressor and convert the lubricant oil into mist.
- Accordingly, to ensure minimum lubrication even when the lubricant supply is insufficient, various procedures for coating part of a swash plate that contacts shoes have been proposed.
- Load applied to the head side face of a swash plate by the head side shoes is different from load applied to the skirt side face of the swash plate by the skirt side shoes. That is, when gas is drawn into the associated cylinder bore, the piston is pulled outward by the swash plate and the reaction force of the suction mainly acts on the skirt side face of the swash plate. When the gas is compressed in each cylinder bore, the associated piston is pressed into the cylinder bore and the reaction force of the compression mainly acts on the head side face of the swash plate. The load based on the compression reaction force is generally greater than the load based on the suction reaction force.
- Therefore, the head side face, which contacts the head side shoess, need to have relatively high wear resistance. On the other hand, even if the wear resistance of the skirt side face, which contacts the skirt side shoess, is not as high as the level required for the head side face, the lubrication between the skirt side face and the skirt side shoess is maintained for an extended period.
- Since the difference of the load acting on both sides of a swash plates has never been considered in prior art, the skirt side face is treated to have the same coating as that of the head side face. In other words, the skirt side face has been given an excessive wear resistance, which increases the cost for coating the swash plate.
- Accordingly, it is an objective of the present invention to provide a swash plate the head and skirt side faces of which are appropriately coated for reduced cost such that necessary reliability is obtained.
- To achieve the foregoing and other objectives and in accordance with the purpose of the present invention, a swash plate used in a compressor is provided. The swash plate is mounted on a drive shaft and coupled to a single-headed piston to convert a rotational movement of the drive shaft to a linearly reciprocal movement of the piston. The piston has a head portion compressing gas and receiving reaction force from the gas and a skirt portion accommodating a first shoe and a second shoe opposed to each other. The first shoe is disposed closer to the piston head than the second shoe. The first shoe and the second shoe are respectively kept in a slidable contact with a first contact surface and a second contact surface opposed to each other in the swash plate. The swash plate includes a first coating formed on the first contact surface. The first coating is made of an aluminum based material. The swash plate also includes a second coating formed on the second contact surface. The second coating material is made of a material simpler for production than the aluminum based material.
- Other aspects and advantages of the invention will become apparent from the following description, taken in conjunction with the accompanying drawings, illustrating by way of example the principles of the invention.
- The invention, together with objects and advantages thereof, may best be understood by reference to the following description of the presently preferred embodiments together with the accompanying drawings in which:
- Fig. 1 is a cross-sectional view illustrating a swash plate type variable displacement compressor according to a first embodiment of the present invention;
- Fig. 2 is a partial cross-sectional view illustrating the swash plate and a pair of the shoes of the compressor shown in Fig. 1;
- Fig. 3 is a rear view showing the swash plate of the compressor shown in Fig. 1, with a metal supplier shown in perspective;
- Fig. 4 is a view schematically showing a coating apparatus of the first embodiment; and
- Fig. 5 is a view schematically showing a coating apparatus of a second embodiment.
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- First and second embodiments of the present invention will now be described with reference to the attached drawings. In describing the second embodiment, only the differences from the first embodiment will be discussed. Same or like reference numerals are given to parts in the second embodiment that are the same as or like corresponding parts of the first embodiment.
- First, the compressor will be described.
- As shown in Fig. 1, the compressor includes a
cylinder block 1, afront housing member 2, avalve plate 3, and a rear housing member 4. Thefront housing member 2 is coupled to a front end of thecylinder block 1. The front end is to the left in Fig. 1. The rear housing member 4 is connected to the rear end of thecylinder block 1 through thevalve plate 3. Thecylinder block 1, thefront housing member 2, thevalve plate 3, and the rear housing member 4 are fastened together with through bolts (not shown) to define a compressor housing. - A
crank chamber 5, asuction chamber 6 and adischarge chamber 7 are defined in the housing. Cylinder bores la (only one is shown in Fig. 1) are defined in thecylinder block 1. A single-headed piston 8 is reciprocally accommodated in each cylinder bore la. To reduce the weight, eachpiston 8 is made of aluminum based material. Valve flaps are provided in thevalve plate 3 for selectively connecting thesuction chamber 6 and thedischarge chamber 7 with each cylinder bore la. - A
drive shaft 9 is rotationally supported in thecrank chamber 5. Aswash plate 10 is fitted around thedrive shaft 9. A throughhole 10a extends in the middle of theswash plate 10. Thedrive shaft 9 extends through the throughhole 10a. Theswash plate 10 is connected with thedrive shaft 9 through ahinge mechanism 13 and alug plate 11 to rotate integrally with thedrive shaft 9. Theswash plate 10 inclines with respect to thedrive shaft 9 while axially sliding along the surface of thedrive shaft 9. The skirt of eachpiston 8 is connected with theswash plate 10 by askirt side shoe 20A and ahead side shoe 20B. Theshoes swash plate 10. - When the
swash plate 10 rotates integrally with thedrive shaft 9 while inclined with respect to thedrive shaft 9, eachpiston 8 moves in the associated cylinder bore la by a stroke corresponding to the inclination angle. Refrigerant gas is drawn from the suction chamber 6 (the zone in which suction pressure Ps acts) to the cylinder bore la. The gas is then compressed in the cylinder bore la and is discharged to the discharge chamber 7 (the zone in which discharge pressure Pd acts). This series of steps is repeated. - A
spring 14 urges theswash plate 10 toward the cylinder block 1 (to decrease the inclination of the swash plate 10). Asnap ring 15 is secured to thedrive shaft 9 for determining the minimum angle of inclination min (for example, three to five degrees) of theswash plate 10. Acounterweight 10b is provided on theswash plate 10. Thecounterweight 10b abuts against a restricting portion lla of thelug plate 11. This determines the maximum inclined angle max of theswash plate 10. - The inclination angle of the
swash plate 10 is determined according to various moments acting on theswash plate 10. The moments include a rotational moment, which is based on the centrifugal force of therotating swash plate 10, a spring force moment, which is based on the force of thespring 14, a moment of inertia of the piston reciprocation, and a gas pressure moment. - The gas pressure moment is generated by the force of the pressure in the cylinder bores la and the pressure in the crank chamber 5 (crank pressure Pc). Depending on the crank pressure Pc, the gas pressure moment acts either to increase or decrease the inclination angle of the
swash plate 10. The swash plate type compressor of Fig. 1 has acontrol valve 16 that adjusts the crank pressure Pc to alter the moment of the gas pressure as necessary. Thecontrol valve 16 thus selects the inclination angle of theswash plate 10 within a range between the minimum angle of inclination min and the maximum angle of inclination max. - The
swash plate 10 will now be described. - As shown in Figs. 1 to 3, an annular skirt
side contact surface 30A is formed on a side of theswash plate 10 that is closer to the ends of the piston skirts, and an annular headside contact surface 30B is formed on a side of the swash plate that is closer to the piston head. Theskirt side shoes 20A slide on the skirtside contact surface 30A, and the head side shoes 20B slide the headside contact surface 30B. - The
swash plate 10 is formed of relatively heavy, iron-based material (for example, cast iron FCD700) to optimize the moment of rotation due to centrifugal force caused by rotation of theswash plate 10. Theshoes swash plate 10 and theshoes skirt side coating 31A and hadside coating 31B are formed at least on the associated contact surfaces 30A, 30B. Thecoatings shoes swash plate 10. - The
skirt side coating 31A, which is formed on the skirtside contact surface 30A, is made of solid lubricant. The thickness of theskirt side coating 31A is for example 0.5 to 10µm. The solid lubricant includes at least one of molybdenum disulfide, tungsten disulfide, graphite, boron nitride, antimony oxide, lead oxide, indium, tin and fluorocarbon resin. When forming theskirt side coating 31A, a liquid paint that includes the solid lubricant is applied to the skirtside contact surface 30A through spray coating, roll coating or screen printing. - The
head side coating 31B, which is formed on the headside contact surface 30B, has a two-layer structure. Afirst layer 31B-1 of thehead side coating 31B is formed of metal different from that forming the body of theswash plate 10 and the bodies of theshoes first layer 31B-1 may be Al-Si based material including, for example, silicon containing aluminum alloys and intermetallic compounds consisting of aluminum and silicon. The physical properties such as hardness and melting point of the Al-Si based material, or aluminum based material, vary in accordance with the silicon content of the material. In the first embodiment, the Al-Si based material contains 10 to 20 weight percent (preferably, from 15 to 18 percent) silicon. - A
second layer 31B-2 of thehead side coating 31B covers thefirst layer 31B-1. Like theskirt side coating 31A, thesecond layer 31B-2 is formed of solid lubricant and the thickness is between 0.5 and 10µm. - The
coatings shoes coatings shoes swash plate 10. In other words, even when the lubricant oil supply to the compressor is insufficient, thecoatings swash plate 10 and theshoes - A procedure for forming the
coatings side contact surface 30B is roughened through, for example, shot blasting. - As shown in Fig. 3, the procedure is performed with a
cylindrical metal supplier 40. Thesupplier 40 is formed of Al-Si based material. Thesupplier 40 has aplaner end 41 having a diameter substantially equal to a radial dimension of the headside contact surface 30B of the swash plate 10 (the difference between the outer radius and the inner radius of the headside contact surface 30B). - As shown in Fig. 4, the
swash plate 10 is mounted to afirst drive mechanism 51, and thesupplier 40 is connected to asecond drive mechanism 52. - The
first drive mechanism 51 is driven by a first motor M1. When the first motor M1 drives thefirst drive mechanism 51, theswash plate 10 is rotated about an axis L. Specifically, with theswash plate 10 mounted to thefirst drive mechanism 51, the headside contact surface 30B is centered on the axis L and is perpendicular to axis L. In this state, a portion of the headside contact surface 30B faces and is spaced from theend 41 of thesupplier 40. - The
second drive mechanism 52 is operably connected to alinear mover 53 and a second motor M2. Thelinear mover 53 operates to move thesupplier 40 axially. Specifically, thelinear mover 53 enables thesupplier 40 to contact theswash plate 10. Thesupplier 40 is then pressed against the headside contact surface 30B of theswash plate 10 by thelinear mover 53. Afterwards, thelinear mover 53 separates thesupplier 40 from theswash plate 10. When thelinear mover 53 moves thesupplier 40, the second motor M2 rotates thesupplier 40 about the axis L', which is the axis of thesupplier 40. - The
end 41 of thesupplier 40 is perpendicular to the axis L'. When thesupplier 40 is mounted to thesecond drive mechanism 52, theend 41 is parallel to the headside contact surface 30B, and the rotation axis L' of thesupplier 40 is offset from axis L. That is, when thesupplier 40 is pressed against the headside contact surface 30B of theswash plate 10, one point on the circumference of theend 41 touches the outer circumference of the headside contact surface 30B, and a diametrically opposite point on theend 41 touches the inner circumference of the headside contact surface 30B (as indicated by broken lines in Fig. 3). - After the
swash plate 10 and thesupplier 40 are mounted on the associateddrive mechanisms supplier 40 at a predetermined speed (for example, 1,500 rpm) about the axis L'. Thelinear mover 53 causes thesupplier 40 and thesecond drive mechanism 52 to approach theswash plate 10. After thesupplier 40 contacts the headside contact surface 30B of theswash plate 10, thesupplier 40 is pressed against the headside contact surface 30B until the pressure reaches a predetermined level (for example, 18 MPa). - When the
supplier 40 is pressed against the headside contact surface 30B, the first motor M1 rotates theswash plate 10 by a predetermined rotation speed (for example, 1 rpm). That is, thesupplier 40 and the headside contact surface 30B move relative to each other along the circumferential direction of the headside contact surface 30B. - Heat, which is caused by friction, is generated between the
end 41 of thesupplier 40 and the headside contact surface 30B. The heat is mainly caused by the relatively rapid rotation of thesupplier 40. The heat softens a portion of thesupplier 40 near itsend 41. Molten metal is then supplied from the soft portion of thesupplier 40 to a corresponding portion of the headside contact surface 30B. Accordingly, while thesupplier 40 is moving relative to the headside contact surface 30B, molten metal is continuously supplied from thesupplier 40 to the headside contact surface 30B along the annular path of thesurface 30B. - When at least one rotation cycle is completed by the
swash plate 10, molten metal is supplied to the entire headside contact surface 30B. This forms thefirst layer 31B-1 of Al-Si based material. The thickness of thehead side coating 31B is, for example, 70 to 100 micrometers. The thickness is determined by adding a finishing allowance (which is, for example, 20 to 50 micrometers) to the desired coating thickness (which is, for example, 50 micrometers). - Afterwards, the surface of the
first layer 31B-1 is machined through cutting or grinding to adjust the thickness of thefirst layer 31B-1 as desired. - The surface of the
first layer 31B-1 is roughened through, for example, shot blasting. Liquid paint containing solid lubricant is applied to the roughened surface of thefirst layer 31B-1 in the same manner as the procedure for forming theskirt side coating 31A. Thereafter, the applied liquid paint is baked for forming thesecond layer 31B-2. Afterwards, the surface of thesecond layer 31B-2 is machined through cutting or grinding to adjust the thickness of thefirst layer 31B-1, or the thickness of thehead side coating 31B, as desired. - The first embodiment has the following advantages.
- (1) The
first layer 31B-1 is formed only on the headside contact surface 30B, which need to have high wear resistance. The skirtside contact surface 30A, which need to have relatively low wear resistance, is coated with the solid lubricantskirt side coating 31A. Solid liquid is inexpensive. Therefore, theswash plate 10 has sufficient level of lubrication for a minimized cost. - (2) The
first layer 31B-1 is hard and therefore is easy to crack if thefirst layer 31B-1 directly contacts the head side shoes 20B. However, in the first embodiment, the relatively softsecond layer 31B-2 is formed on thefirst layer 31B-1, which prevents thefirst layer 31B-1 from directly contacting the head side shoes 20B. Cracking of thefirst layer 31B-1 is thus prevented. - (3) The head
side contact surface 30B is roughened before applying thefirst layer 31B-1. This increases the contact area between the headside contact surface 30B and thefirst layer 31B-1 and thus improves the adherence. - (4) The surface of the
first layer 31B-1 is roughed before applying thesecond layer 31B-2. This increases the contact area between thefirst layer 31B-1 and thesecond layer 31B-2 and thus improves the adherence. - (5) The
first layer 31B-1 is formed on the headside contact surface 30B by pressing themetal supplier 40 against the headside contact surface 30B. Therefore, unlike thermal spraying, no spraying noise is produced. Also, metal powder is not spread, which improves yield and working conditions. - (6) Molten metal is reliably separated from the
supplier 40 and is supplied to the headside contact surface 30B. That is, a predetermined amount of metal is reliably supplied from thesupplier 40 to the headside contact surface 30B. Thefirst layer 31B-1 thus has a desired uniform thickness along the entire headside contact surface 30B. - (7) The
supplier 40, which is a solid metal cylinder, is pressed against the headside contact surface 30B for forming thefirst layer 31B-1. Therefore, unlike thermal spraying, costly metal powder is not needed. Further, metal cylinders are easier to handle than metal powder, which improves the efficiency and the working conditions. -
- A second embodiment will now be described with reference to Fig. 5. In the second embodiment, the
first layer 31B-1 is formed through build up welding by using acoated electrode 54. - Fig. 5 schematically shows an
arc welding apparatus 60. Afirst drive mechanism 51 of the second embodiment is installed such that the axis L is perpendicular to the axis L in the embodiment of Figs. 1 to 4. Thearc welding apparatus 60 includes anelectrode 54 and a welding source 55, which applies voltage to theelectrode 54 and theswash plate 10. Theelectrode 54 is formed by applying flux 54b on acore 54a, which is made of Al-Si based material. Theelectrode 54 is supported by asupport 56, which is connected to alift 57. - The axis of the
electrode 54 is offset from the axis L of theswash plate 10, which is placed on thefirst drive mechanism 51 and is located above the headside contact surface 30B. Thesupport 56, together with theelectrode 54, is moved vertically as viewed in the drawing by thelift 57, which permits theelectrode 54 to approach and separate from a part of the headside contact surface 30B. - When the
lift 57 lowers theelectrode 54 toward a part of the headside contact surface 30B and the welding source 55 is activated, arc is generated between theelectrode 54 and theswash plate 10. The heat of the arc melts part of theelectrode core 54a. Molten metal is dropped onto the contact surface. The molten part of theelectrode 54 is fused with part of the headside contact surface 30B, which is also molten by the arc heat. The motor M1 rotates thefirst drive mechanism 51 with theswash plate 10, which continuously changes part of the headside contact surface 30B that is located below theelectrode 54. - When at least one rotation cycle is completed by the
swash plate 10, molten metal is supplied to the entire headside contact surface 30B. This forms thefirst layer 31B-1 of Al-Si based material. - The second embodiment has the advantages (1)-(5) and (7) of the first embodiment.
- It should be apparent to those skilled in the art that the present invention may be embodied in many other specific forms without departing from the spirit or scope of the invention. Particularly, it should be understood that the invention may be embodied in the following forms.
- The
first layer 31B-1 may be formed through thermal spraying. In thermal spraying, metal powder is molten and sprayed on to the headside contact surface 30B with flame. - The
first layer 31B-1 may be formed through sintering. In sintering, metal powder is sintered on to the headside contact surface 30B with flame. - The
skirt side coating 31A may be formed of tin through electroplating or through electroless plating. - In the second embodiment, the
first layer 31B-1 is formed through arc welding by using thecoated electrode 54. However, thefirst layer 31B-1 may be formed through gas-shielded arc welding or submerged-arc welding. Gas-shielded arc welding includes metal inert gas (MIG) welding, metal active gas (MAG) welding and TIG welding. - The procedures of the present invention may be applied to
swash plates 10 formed of aluminum based material instead of iron based material. - Therefore, the present examples and embodiments are to be considered as illustrative and not restrictive and the invention is not to be limited to the details given herein, but may be modified within the scope and equivalence of the appended claims.
- A swash plate used in a compressor. A side of the swash plate that contacts head side shoes is coated with two layers. The first layer is formed of aluminum material and the second layer is formed with solid lubricant. A side of the swash plate that contacts skirt side shoes is coated with a single layer of solid lubricant. Accordingly, the swash plate has a sufficiently wear resistance on both sides for the minimized cost.
Claims (9)
- A swash plate used in a compressor, the swash plate is mounted on a drive shaft and coupled to a single-head piston to convert a rotational movement of the drive shaft to a linearly reciprocal movement of the piston, the piston having a head portion compressing gas and receiving reaction force from the gas and a skirt portion accommodating a first shoe and a second shoe opposed to each other, the first shoe being disposed closer to the piston head than the second shoe, the first shoe and the second shoe being respectively kept in a slidable contact with a first contact surface and a second contact surface opposed to each other in the swash plate, the swash plate comprising:a first coating formed on the first contact surface, the first coating being made of an aluminum based material; anda second coating formed on the second contact surface, the second coating material being made of a material simpler for production than the aluminum based material.
- The swash plate as set forth in Claim 1, wherein the second coating is made of one of a rigid lubrication layer, a plating layer and a sinter.
- The swash plate as set forth in Claim 1, wherein the first coating is formed on the first contact surface by one selected from a group consisting of a pressure welding, a welding and a flame spraying.
- The swash plate as set forth in Claim 1, wherein the first contact surface is finished by roughening.
- The swash plate as set forth in Claim 1, wherein the first coating is coated by a rigid lubrication layer.
- The swash plate as set forth in Claim 5, wherein the first coating has a roughened surface.
- The swash plate as set forth in Claim 1, wherein the first coating is made of an aluminum alloy containing silicon.
- The swash plate as set forth in Claim 1, wherein the first coating includes a first layer made of an aluminum alloy containing silicon and a second layer formed on the first layer and made of a rigid lubrication agent.
- The swash plate as set forth in Claim 8, wherein the first layer is formed of the aluminum alloy containing 10 to 20 weight percent of the silicon.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2000075537 | 2000-03-17 | ||
JP2000075537A JP2001263226A (en) | 2000-03-17 | 2000-03-17 | Swash plate used for swash plate type compressor |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1134413A2 true EP1134413A2 (en) | 2001-09-19 |
EP1134413A3 EP1134413A3 (en) | 2004-01-02 |
Family
ID=18593417
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP01106655A Withdrawn EP1134413A3 (en) | 2000-03-17 | 2001-03-16 | Swash plate for compressor |
Country Status (6)
Country | Link |
---|---|
US (1) | US20020031434A1 (en) |
EP (1) | EP1134413A3 (en) |
JP (1) | JP2001263226A (en) |
KR (1) | KR20010091888A (en) |
CN (1) | CN1314549A (en) |
BR (1) | BR0101095A (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1584819A1 (en) * | 2002-12-26 | 2005-10-12 | Zexel Valeo Climate Control Corporation | Compressor |
Families Citing this family (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP4846670B2 (en) * | 2001-10-26 | 2011-12-28 | カルソニックカンセイ株式会社 | Fluorine resin coating method, sliding member using the method, and gas compressor |
JP4846669B2 (en) * | 2001-10-26 | 2011-12-28 | カルソニックカンセイ株式会社 | Fluorine resin coating method, sliding member using the method, and gas compressor |
JP4049082B2 (en) * | 2003-06-19 | 2008-02-20 | 株式会社豊田自動織機 | Compressor |
US20060018730A1 (en) * | 2003-10-10 | 2006-01-26 | Ernst Richard J | Drywall fastener |
CN100451332C (en) * | 2004-11-11 | 2009-01-14 | 大丰工业株式会社 | Slider |
JP2006291881A (en) * | 2005-04-13 | 2006-10-26 | Toyota Industries Corp | Swash plate type compressor |
DE502006002752D1 (en) * | 2005-04-23 | 2009-03-19 | Ixetic Mac Gmbh | axial piston |
EP1739231A1 (en) * | 2005-07-02 | 2007-01-03 | M-real Oyj | Cast coating device |
JP2007270994A (en) * | 2006-03-31 | 2007-10-18 | Daido Metal Co Ltd | Sliding member |
CN101598121B (en) * | 2009-07-09 | 2011-04-13 | 南京奥特佳冷机有限公司 | Swash plate double-headed piston compressor |
CN103629074A (en) * | 2012-08-24 | 2014-03-12 | 苏州轩昌机电科技有限公司 | Compressor swash plate, manufacturing method of compressor swash plate and tool die |
CN103470475A (en) * | 2013-09-26 | 2013-12-25 | 常熟市淼泉压缩机配件有限公司 | Swash plate of rotating swash plate type air conditioner compressor |
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JPS6022080A (en) * | 1983-07-15 | 1985-02-04 | Taiho Kogyo Co Ltd | Swash plate type compressor |
JPH08199327A (en) * | 1995-01-27 | 1996-08-06 | Taiho Kogyo Co Ltd | Swash plate for swash plate type compressor |
US5655432A (en) * | 1995-12-07 | 1997-08-12 | Ford Motor Company | Swash plate with polyfluoro elastomer coating |
EP0911517A2 (en) * | 1997-10-24 | 1999-04-28 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Swash plate type compressor |
EP0926340A2 (en) * | 1997-12-26 | 1999-06-30 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Coating of a swash plate bearing |
WO1999050556A1 (en) * | 1998-03-27 | 1999-10-07 | Taiho Kogyo Co., Ltd. | Swash plate of swash plate compressor |
-
2000
- 2000-03-17 JP JP2000075537A patent/JP2001263226A/en active Pending
-
2001
- 2001-02-02 KR KR1020010005176A patent/KR20010091888A/en not_active Application Discontinuation
- 2001-03-14 US US09/808,292 patent/US20020031434A1/en not_active Abandoned
- 2001-03-16 EP EP01106655A patent/EP1134413A3/en not_active Withdrawn
- 2001-03-17 CN CN01117225A patent/CN1314549A/en active Pending
- 2001-03-19 BR BR0101095-6A patent/BR0101095A/en not_active IP Right Cessation
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JPS6022080A (en) * | 1983-07-15 | 1985-02-04 | Taiho Kogyo Co Ltd | Swash plate type compressor |
JPH08199327A (en) * | 1995-01-27 | 1996-08-06 | Taiho Kogyo Co Ltd | Swash plate for swash plate type compressor |
US5655432A (en) * | 1995-12-07 | 1997-08-12 | Ford Motor Company | Swash plate with polyfluoro elastomer coating |
EP0911517A2 (en) * | 1997-10-24 | 1999-04-28 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Swash plate type compressor |
EP0926340A2 (en) * | 1997-12-26 | 1999-06-30 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Coating of a swash plate bearing |
WO1999050556A1 (en) * | 1998-03-27 | 1999-10-07 | Taiho Kogyo Co., Ltd. | Swash plate of swash plate compressor |
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Title |
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PATENT ABSTRACTS OF JAPAN vol. 009, no. 142 (M-388), 18 June 1985 (1985-06-18) & JP 60 022080 A (TAIHOU KOGYO KK;OTHERS: 01), 4 February 1985 (1985-02-04) * |
PATENT ABSTRACTS OF JAPAN vol. 1996, no. 12, 26 December 1996 (1996-12-26) & JP 08 199327 A (TAIHO KOGYO CO LTD;TOYOTA AUTOM LOOM WORKS LTD), 6 August 1996 (1996-08-06) * |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1584819A1 (en) * | 2002-12-26 | 2005-10-12 | Zexel Valeo Climate Control Corporation | Compressor |
EP1584819A4 (en) * | 2002-12-26 | 2006-08-23 | Zexel Valeo Climate Contr Corp | Compressor |
US7320273B2 (en) | 2002-12-26 | 2008-01-22 | Zexel Valeo Climate Control Corporation | Compressor |
Also Published As
Publication number | Publication date |
---|---|
BR0101095A (en) | 2001-11-06 |
US20020031434A1 (en) | 2002-03-14 |
KR20010091888A (en) | 2001-10-23 |
CN1314549A (en) | 2001-09-26 |
EP1134413A3 (en) | 2004-01-02 |
JP2001263226A (en) | 2001-09-26 |
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