US20020031434A1 - Swash plate for compresser - Google Patents

Swash plate for compresser Download PDF

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Publication number
US20020031434A1
US20020031434A1 US09/808,292 US80829201A US2002031434A1 US 20020031434 A1 US20020031434 A1 US 20020031434A1 US 80829201 A US80829201 A US 80829201A US 2002031434 A1 US2002031434 A1 US 2002031434A1
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US
United States
Prior art keywords
swash plate
contact surface
coating
shoe
layer
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.)
Abandoned
Application number
US09/808,292
Other languages
English (en)
Inventor
Manabu Sugiura
Kazuaki Iwama
Naohiki Isomura
Shigeki Kawachi
Hiroaki Kayukawa
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Toyota Industries Corp
Original Assignee
Toyoda Jidoshokki Seisakusho KK
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 Toyoda Jidoshokki Seisakusho KK filed Critical Toyoda Jidoshokki Seisakusho KK
Assigned to KABUSHIKI KAISHA TOYODA JIDOSHOKKI SEISAKUSHO reassignment KABUSHIKI KAISHA TOYODA JIDOSHOKKI SEISAKUSHO ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ISOMURA, NAOHIKO, IWAMA, KAZUAKI, KAWACHI, SHIGEKI, KAYUKAWA, HIROAKI, SUGIURA, MANABU
Publication of US20020031434A1 publication Critical patent/US20020031434A1/en
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • 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
    • 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
    • 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
    • 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
    • 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
    • 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]
    • 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
    • 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.
  • 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.
  • FIG. 5 is a view schematically showing a coating apparatus of a second embodiment.
  • 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 1 a (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 1 a.
  • 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 1 a.
  • 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 10 a extends in the middle of the swash plate 10 .
  • the drive shaft 9 extends through the through hole 10 a.
  • 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 20 A and a head side shoe 20 B. The shoes 20 A, 20 B slide along the periphery of the swash plate 10 .
  • each piston 8 moves in the associated cylinder bore 1 a 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 1 a.
  • the gas is then compressed in the cylinder bore 1 a 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 10 b is provided on the swash plate 10 . The counterweight 10 b abuts against a restricting portion 11 a 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 1 a 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 30 A 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 30 B is formed on a side of the swash plate that is closer to the piston head.
  • the skirt side shoes 20 A slide on the skirt side contact surface 30 A
  • the head side shoes 20 B slide the head side contact surface 30 B.
  • 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 20 A, 20 B 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 20 A, 20 B) slide against each other under severe conditions, seizure may occur. Accordingly, in the first embodiment, skirt side coating 31 A and had side coating 31 B are formed at least on the associated contact surfaces 30 A, 30 B.
  • the coatings 31 A, 31 B allow the shoes 20 A, 20 B to slide smoothly along the contact surfaces 30 A, 30 B. That is, the procedure of the present invention is performed on the contact surfaces 30 A, 30 B of the swash plate 10 .
  • the skirt side coating 31 A which is formed on the skirt side contact surface 30 A, is made of solid lubricant.
  • the thickness of the skirt side coating 31 A is for example 0.5 to 10 82 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.
  • a liquid paint that includes the solid lubricant is applied to the skirt side contact surface 30 A through spray coating, roll coating or screen printing.
  • the head side coating 31 B which is formed on the head side contact surface 30 B, has a two-layer structure.
  • a first layer 31 B- 1 of the head side coating 31 B is formed of metal different from that forming the body of the swash plate 10 and the bodies of the shoes 20 A, 20 B.
  • the material of the first layer 31 B- 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 31 B- 2 of the head side coating 31 B covers the first layer 31 B- 1 .
  • the second layer 31 B- 2 is formed of solid lubricant and the thickness is between 0.5 and 10 ⁇ m.
  • the coatings 31 A, 31 B prevent seizure from occurring between the shoes 20 A, 20 B and the contact surfaces 30 A, 30 B.
  • the coatings 31 A, 31 B also allow the shoes 20 A, 20 B to slide smoothly along the contact surfaces 30 A, 30 B of the swash plate 10 . In other words, even when the lubricant oil supply to the compressor is insufficient, the coatings 31 A, 31 B ensure a certain level of lubrication between the swash plate 10 and the shoes 20 A, 20 B.
  • the head side contact surface 30 B 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 30 B of the swash plate 10 (the difference between the outer radius and the inner radius of the head side contact surface 30 B).
  • 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 M 1 .
  • the swash plate 10 is rotated about an axis L.
  • the head side contact surface 30 B is centered on the axis L and is perpendicular to axis L. In this state, a portion of the head side contact surface 30 B 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 M 2 .
  • 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 30 B 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 M 2 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 30 B, 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 30 B of the swash plate 10 , one point on the circumference of the end 41 touches the outer circumference of the head side contact surface 30 B, and a diametrically opposite point on the end 41 touches the inner circumference of the head side contact surface 30 B (as indicated by broken lines in FIG. 3).
  • the second motor M 2 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 30 B of the swash plate 10 , the supplier 40 is pressed against the head side contact surface 30 B until the pressure reaches a predetermined level (for example, 18 MPa).
  • the first motor Ml 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 30 B move relative to each other along the circumferential direction of the head side contact surface 30 B.
  • Heat which is caused by friction, is generated between the end 41 of the supplier 40 and the head side contact surface 30 B.
  • 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 30 B. Accordingly, while the supplier 40 is moving relative to the head side contact surface 30 B, molten metal is continuously supplied from the supplier 40 to the head side contact surface 30 B along the annular path of the surface 30 B.
  • molten metal is supplied to the entire head side contact surface 30 B.
  • the thickness of the head side coating 31 B 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 31 B- 1 is machined through cutting or grinding to adjust the thickness of the first layer 31 B- 1 as desired.
  • the surface of the first layer 31 B- 1 is roughened through, for example, shot blasting.
  • Liquid paint containing solid lubricant is applied to the roughened surface of the first layer 31 B- 1 in the same manner as the procedure for forming the skirt side coating 31 A. Thereafter, the applied liquid paint is baked for forming the second layer 31 B- 2 . Afterwards, the surface of the second layer 31 B- 2 is machined through cutting or grinding to adjust the thickness of the first layer 31 B- 1 , or the thickness of the head side coating 31 B, as desired.
  • the first embodiment has the following advantages.
  • the first layer 31 B- 1 is formed only on the head side contact surface 30 B, which need to have high wear resistance.
  • the skirt side contact surface 30 A which need to have relatively low wear resistance, is coated with the solid lubricant skirt side coating 31 A. Solid liquid is inexpensive. Therefore, the swash plate 10 has sufficient level of lubrication for a minimized cost.
  • the first layer 31 B- 1 is hard and therefore is easy to crack if the first layer 31 B- 1 directly contacts the head side shoes 20 B.
  • the relatively soft second layer 31 B- 2 is formed on the first layer 31 B- 1 , which prevents the first layer 31 B- 1 from directly contacting the head side shoes 20 B. Cracking of the first layer 31 B- 1 is thus prevented.
  • the head side contact surface 30 B is roughened before applying the first layer 31 B- 1 . This increases the contact area between the head side contact surface 30 B and the first layer 31 B- 1 and thus improves the adherence.
  • the first layer 31 B- 1 is formed on the head side contact surface 30 B by pressing the metal supplier 40 against the head side contact surface 30 B. Therefore, unlike thermal spraying, no spraying noise is produced. Also, metal powder is not spread, which improves yield and working conditions.
  • the supplier 40 which is a solid metal cylinder, is pressed against the head side contact surface 30 B for forming the first layer 31 B- 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.
  • the first layer 31 B- 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 54 b on a core 54 a, 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 30 B.
  • 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 30 B.
  • the second embodiment has the advantages (1)-(5) and (7) of the first embodiment.
  • the first layer 31 B- 1 may be formed through thermal spraying.
  • thermal spraying metal powder is molten and sprayed on to the head side contact surface 30 B with flame.
  • the first layer 31 B- 1 may be formed through sintering. In sintering, metal powder is sintered on to the head side contact surface 30 B with flame.
  • the skirt side coating 31 A may be formed of tin through electroplating or through electroless plating.
  • the first layer 31 B- 1 is formed through arc welding by using the coated electrode 54 .
  • the first layer 31 B- 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.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Lubricants (AREA)
  • Coating By Spraying Or Casting (AREA)
  • Compressor (AREA)
US09/808,292 2000-03-17 2001-03-14 Swash plate for compresser Abandoned US20020031434A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2000-075537 2000-03-17
JP2000075537A JP2001263226A (ja) 2000-03-17 2000-03-17 斜板式圧縮機に用いられる斜板

Publications (1)

Publication Number Publication Date
US20020031434A1 true US20020031434A1 (en) 2002-03-14

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ID=18593417

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US09/808,292 Abandoned US20020031434A1 (en) 2000-03-17 2001-03-14 Swash plate for compresser

Country Status (6)

Country Link
US (1) US20020031434A1 (fr)
EP (1) EP1134413A3 (fr)
JP (1) JP2001263226A (fr)
KR (1) KR20010091888A (fr)
CN (1) CN1314549A (fr)
BR (1) BR0101095A (fr)

Cited By (2)

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Publication number Priority date Publication date Assignee Title
US20060018730A1 (en) * 2003-10-10 2006-01-26 Ernst Richard J Drywall fastener
US20090061073A1 (en) * 2005-07-02 2009-03-05 M-Real Oyi Cast coating device

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JP4846670B2 (ja) * 2001-10-26 2011-12-28 カルソニックカンセイ株式会社 フッ素系樹脂コーティング方法およびこの方法を用いた摺動部材、気体圧縮機
JP4846669B2 (ja) * 2001-10-26 2011-12-28 カルソニックカンセイ株式会社 フッ素系樹脂コーティング方法およびこの方法を用いた摺動部材、気体圧縮機
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CN100451332C (zh) * 2004-11-11 2009-01-14 大丰工业株式会社 滑动装置
JP2006291881A (ja) * 2005-04-13 2006-10-26 Toyota Industries Corp 斜板式圧縮機
EP1877663B1 (fr) * 2005-04-23 2009-01-28 ixetic MAC GmbH Machine a pistons axiaux
JP2007270994A (ja) * 2006-03-31 2007-10-18 Daido Metal Co Ltd 摺動部材
CN101598121B (zh) * 2009-07-09 2011-04-13 南京奥特佳冷机有限公司 斜盘式双头活塞式压缩机
CN103629074A (zh) * 2012-08-24 2014-03-12 苏州轩昌机电科技有限公司 压缩机斜盘及其制造方法和工装模具
CN103470475A (zh) * 2013-09-26 2013-12-25 常熟市淼泉压缩机配件有限公司 一种旋转斜盘式空调压缩机的斜盘

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20060018730A1 (en) * 2003-10-10 2006-01-26 Ernst Richard J Drywall fastener
US20090061073A1 (en) * 2005-07-02 2009-03-05 M-Real Oyi Cast coating device

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Publication number Publication date
EP1134413A3 (fr) 2004-01-02
CN1314549A (zh) 2001-09-26
JP2001263226A (ja) 2001-09-26
KR20010091888A (ko) 2001-10-23
BR0101095A (pt) 2001-11-06
EP1134413A2 (fr) 2001-09-19

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