EP1195519A1 - Variable displacement compressors - Google Patents

Variable displacement compressors Download PDF

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Publication number
EP1195519A1
EP1195519A1 EP01121683A EP01121683A EP1195519A1 EP 1195519 A1 EP1195519 A1 EP 1195519A1 EP 01121683 A EP01121683 A EP 01121683A EP 01121683 A EP01121683 A EP 01121683A EP 1195519 A1 EP1195519 A1 EP 1195519A1
Authority
EP
European Patent Office
Prior art keywords
rotary disk
rotor
swash plate
plate
drive shaft
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Withdrawn
Application number
EP01121683A
Other languages
German (de)
English (en)
French (fr)
Inventor
Takenori Sawa
Masahiro Kawaguchi
Masaki Ota
Osamu Hiramatsu
Hirohiko Tanaka
Naoki Usui
Yoshinori Inoue
Kiyoshi Narukawa
Tomoji Tarutani
Hidenori Iida
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
Toyota Industries Corp
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 Toyota Industries Corp filed Critical Toyota Industries Corp
Publication of EP1195519A1 publication Critical patent/EP1195519A1/en
Withdrawn legal-status Critical Current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
    • 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
    • F04B27/1072—Pivot mechanisms
    • 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

Definitions

  • the present invention relates to variable displacement compressors that utilize a rotating swash plate to the output discharge capacity of a compressed refrigerant. More particular, the present invention relates to compressors that may rotate the swash plate using a relatively simple and lightweight structure and to methods for making such compressors. Such compressors may be utilized in air conditioning systems and more preferably in automobile air conditioning systems.
  • variable displacement compressor is described in Japanese Laid-open Patent Publication No. 11-264371.
  • This known variable displacement compressor is reproduced herein in Fig. 15 and includes a swash plate 104 coupled to a driving shaft 102 that is disposed within a driving chamber 101b.
  • a compressor front housing 101 encloses the swash plate 104 and pistons 105 are slidably supported within respective cylinder bores 101a provided within a cylinder block 106.
  • a shoe 110 engages the end portion of each piston 105 with the swash plate 104.
  • a hinge mechanism 107 inclinably and slidably coupled the swash plate 104 to a rotor 103.
  • the rotor 103 is also coupled to the driving shaft 102.
  • the hinge mechanism 107 includes a guide 109 and a guide protrusion 108.
  • the guide 109 is provided on the rotor 103 and has a guide hole 109a.
  • the guide protrusion 108 is provided on the swash plate 104 and has a guide pin 108a.
  • the guide pin 108a is slidably engaged with the guide hole 109a.
  • a thrust bearing 112 is disposed between the rotor 103 and the front housing 101.
  • the rotor 103 also includes a rotary disk 103a.
  • a weight 111 is disposed on the rotary disk 103 to adjust the weight balance of the rotor 103.
  • the guide 109 is disposed on the rotary disk 103.
  • the weight 111 and the guide 109 are molded by simultaneously casting these parts together with the rotary disk 103.
  • the rotor 103 and hinge mechanism 107 rotate together with the drive shaft 102.
  • the rotor 103 and hinge mechanism 107 are required to be relatively light in view of the centrifugal force exerted to the rotor 103 and hinge mechanism 107 due to the rotation together with the drive shaft 102.
  • it is relatively difficult to mold a complicated and thin shape using casting techniques it has been difficult to reduce the weight of the rotor 103 and the hinge mechanism 107 using the known art.
  • variable displacement compressors that may utilize lighter weight parts for the torque transmitting structure disposed between the drive shaft and the swash plate. Methods of making such lighter weight parts are also described.
  • the functional parts of the rotor such as the rotary disk, the guide and the weight may preferably be manufactured by pressing and punching a piece of plate metal.
  • Each functional part may be separately manufactured in this manner or two or more parts may be preferably manufactured in an integral or seamless manner using these techniques.
  • the functional part(s) may be manufactured by pressing a plate, the thickness of the rotor can be reduced, as compared to known manufacturing techniques, without reducing the strength or integrity of the rotor.
  • the weight of the torque transmitting structure between the drive shaft and the swash plate can be reduced.
  • the functional part(s) actually have greater strength and integrity than rotors manufactured using known techniques.
  • Fig. 1 shows a variable displacement compressor according to the first representative embodiment.
  • Fig. 2 shows the torque transmitting structure of the first representative embodiment.
  • Fig. 3 schematically shows the hinge mechanism.
  • Fig. 4 shows a perspective view of the rotor.
  • Fig. 5 (A) to Fig. 5 (C) show a representative process for manufacturing the rotary disk by pressing a plate.
  • Fig. 6 (A) to Fig. 6 (C) show a representative process for manufacturing the guide by pressing a plate.
  • Fig. 7 (A) and Fig. 7 (B) show a representative process for manufacturing the weight by pressing a plate.
  • Fig. 8 shows the torque transmitting structure according to the second representative embodiment.
  • Fig. 9 shows the torque transmitting structure according to the third representative embodiment.
  • Fig. 10 shows a perspective view of the rotor manufactured using a press.
  • Fig. 11 (A) to Fig. 11 (C) show a representative process for manufacturing the rotary disk together with the weight.
  • Fig. 12 (A) to Fig. 12 (C) show a representative process for manufacturing the guide.
  • Fig. 13 shows a perspective view of the rotor manufactured by pressing a plate according to the third embodiment.
  • Fig. 14 (A) to Fig. 14 (C) show a representative process for manufacturing the guide by pressing a plate.
  • Fig. 15 shows the torque transmitting structure according to a known variable displacement compressor.
  • variable displacement compressors may include a drive shaft, a swash plate, a piston, a rotor and a hinge mechanism.
  • the swash plate may be inclinably coupled to the drive shaft.
  • the piston may be disposed within a cylinder bore and the end portion of the piston may be connected to a peripheral edge of the swash plate by utilizing a shoe.
  • the piston can reciprocate within the cylinder bore to compress the refrigerant in response to rotation of the inclined swash plate.
  • the inclination angle of the swash plate can be changed. When the inclination angle is changed, the compressor output discharge capacity can be changed.
  • the rotor may be coupled to the drive shaft and the rotor may rotate together with the rotating drive shaft.
  • the rotor may include functional parts, such as a rotary disk, a guide disposed on the rotary disk and a weight disposed on the rotary disk.
  • the weight may be utilized to adjust the weight balance of the rotating rotor.
  • at least one of the functional parts can be formed by pressing and punching a plate of metal.
  • the hinge mechanism may connect the swash plate with the rotor by means of the guide on the rotary disk of the rotor.
  • the hinge mechanism transmits torque from the driving shaft to the swash plate, regardless of the inclination angle of the swash plate. Because at least one of the functional parts is manufactured by pressing and punching a plate, the thickness of the rotor can be reduced and the weight of the torque transmitting structure between the drive shaft and the swash plate can be reduced.
  • each functional part may be separately manufacture by pressing and punching a plate
  • any two of the functional parts may be integrally or seamlessly manufactured by pressing and punching a plate.
  • the rotary disk and the weight, or the weight and the guide may be integrally manufactured by pressing and punching a plate.
  • a hinge mechanism may connect the swash plate with the rotor in order to transmit torque from the driving shaft to the swash plate.
  • a guide member may be engaged with a guide protrusion.
  • either the guide member or the guide protrusion may preferably be manufactured independent from the rotary disk and may then be integrally joined to the rotary disk.
  • the rotary disk and/or the guide may be manufactured by pressing and punching a plate in order to reduce the weight of the torque transmitting structure.
  • the representative compressor 1a includes a compressor housing defined by a front housing 1, a cylinder block 2 and a rear housing 3.
  • the front housing 1 is coupled to the front end of the cylinder block 2.
  • the rear housing 3 is coupled to the rear end of the cylinder block 2.
  • a valve plate 4 is provided between the cylinder block 2 and the rear housing 3.
  • a crank chamber 5 is defined by a space within the front housing 1.
  • a drive shaft 6 is rotatably supported within the crank chamber 5.
  • the drive shaft 6 is preferably connected to an automotive engine by an electromagnetic clutch. That is, the engine causes the drive shaft 6 to rotate when clutch mechanism couples the driving force of the engine to the drive shaft 6.
  • a rotating swash plate 8 is inclinably and slidably coupled to the drive shaft 6 via a rotor 7.
  • the rotor 7 is coupled to the drive shaft 6 and can rotate together with the drive shaft 6.
  • the drive shaft 6 extends through a penetration hole 8a formed in the center of the swash plate 8.
  • a hinge mechanism 20 is provided between the rotor 7 and the swash plate 8 in order to transmit torque from the drive shaft 6 to the swash plate 8, which swash plate 8 may rotate at various inclination angles.
  • the penetration hole 8a preferably has a support point 8b.
  • the hinge mechanism 20 preferably includes a guide member 23 disposed on the rotor 7 and a guide pin 9 disposed on the swash plate 8.
  • the guide member 23 corresponds to a "rotor-side member”. The guide member 23 and the guide pin 9 are mutually engaged to connect the swash plate 8 with the rotor 7.
  • the cylinder block 2 preferably includes six cylinder bores 2a that are disposed in six pistons 11. However, Fig. 1 only shows one piston for purposes of illustration. Each piston 11 is reciprocally and slidably supported each cylinder bore 2a. The piston 11 is coupled to the swash plate 8 via a shoe 12. The rotational movement of the swash plate 8 is converted into reciprocating movement of the pistons 11 via the shoe 12.
  • a suction chamber 3a and a discharge chamber 3b are respectively defined by spaces within the rear housing 3.
  • a suction port 4a, a suction valve 4b, a discharge port 4c, and a discharge valve 4d are preferably disposed on the valve plate 4.
  • the crank chamber 5 preferably communicates with the discharge chamber 3b via a capacity control passage 16.
  • the capacity control passage 16 is opened and closed by a capacity control valve 17.
  • the pressure state within the crank chamber 5 is controlled by opening and closing the capacity control passage 16.
  • a bleeding passage 15 preferably connects the crank chamber 5 and the suction chamber 3a.
  • the rotor 7 preferably includes functional parts, such as a rotary disk 22 coupled to the drive shaft 6, the guide member 23 and a weight 24.
  • the guide member 23 and the guide pin 9 together define the hinge mechanism 20.
  • the weight 24 offsets any weight imbalance of the rotor 7 caused by the guide member 23 when the rotor rotates together with the drive shaft 6.
  • each functional part is formed independently of the others.
  • the rotary disk 22 has a disk-like shape and an insertion hole 22a is defined substantially in the center of the rotary disk 22. Further, the rotary disk 22 is mounted to the drive shaft 6 by inserting the drive shaft 6 into the insertion hole 22a.
  • the insertion hole 22a is formed in a tube-like shape that extends toward the rear of the rotary disk 22 along the drive shaft 6.
  • a thrust bearing 25 is disposed between the front face of the rotary disk 22 and the front housing 1, which thrust bearing 25 circumferentially surrounds the drive shaft 6.
  • the thrust bearing 25 preferably includes a roller 25a that directly contacts the rotary disk 22.
  • Fig. 3 shows a plan view of the hinge mechanism 20, in which each end of the guide member 23 substantially has a curved shape that defines a support 23a for receiving the guide pin 9. Further, the guide member 23 has a plane that defines a connecting portion 23b that affixes the guide member 23 to the rotary disk 22.
  • the central axis S of the support 23a extends parallel to the plane that includes the rotational axis L of the drive shaft 6 and the position corresponding to the upper dead point D of the swash plate 8.
  • the guide member 23 is fixed to the rotary disk 22 by spot welding at a plurality points.
  • the weight 24 is fixed to the bottom part on the rear face of the rotary disc 22. Because the guide member 23 is fixed to the rotor 7, the center of gravity of the rotor 7 is shifted from the rotational axis L of the drive shaft 6. In order to rectify this weight imbalance, the weight 24 is provided on the lower rear edge of the rotor 7 at a position that is opposite to the guide member 23. Thus, the center of gravity of the rotor 7 is adjusted to correspond to the axis of rotation defined by the axis L of the drive shaft 6. In this embodiment, the weight 24 is preferably fixed to the rotary disk 22 by spot welding, although other attaching methods may naturally be utilized.
  • each part can be made of a different material that may be appropriate for the particular application, and each part can be manufactured differently in order to provide optimal properties for each of the functional parts.
  • Representative manufacturing methods for each functional part of the rotor 7 are respectively shown in Figs. 5 to 7.
  • Fig. 5 (A) to Fig. 5 (C) show a representative manufacturing process for the rotary disk 22.
  • a plate W is first prepared by pressing a cold-rolled steel plate or carbon steel, such as S35C or S45C, into an appropriate thickness (see Fig. 5 (A)).
  • the plate W is punched with an appropriate cutting device, e.g. a die, in order to form a disk A1 having a circular insertion hole defined in the center of the disk A1 (see Fig. 5 (B)).
  • an appropriate cutting device e.g. a die
  • the rotary disk 22 is manufactured by deeply drawing the disk A1 (see Fig. 5 (C)).
  • Figs. 6 (A) to Fig. 6 (C) show a representative manufacturing process for the guide member 23.
  • a plate W is prepared by pressing a cold-rolled steel plate or carbon steel, such as S35C or S45C, to an appropriate thickness (see Fig. 6 (A)).
  • the plate W is punched to form a rectangular plate B1 (see Fig. 6 (B)).
  • the guide member 23 is manufactured by utilizing a bending machine (see Fig. 6 (C)).
  • Figs. 7 (A) and (B) show a representative manufacturing process for the weight 24.
  • a plate W is pressed to an appropriate thickness (see Fig. 7 (A)) and then the plate W is punched provide the weight 24 having a semicircular shape (see Fig. 7 (B)).
  • any distortions are removed from the supports 23a and the supports 23a are surface-treated with induction hardening in order to improve the strength and wear-resistance of the supports 23a.
  • a thrust bearing receiver 22c of the rotary disk 22 is surface-treated with induction hardening. Because each functional part of the rotor 7 is individually manufactured, such surface-treating process can be easily performed.
  • the guide member 23 and the weight 24 are welded to the rotary disk 22 (see Fig.4) in order to provide the rotor 7.
  • the guide pin 9 corresponds to a "guide protrusion" as utilized herein. As shown in Fig. 2, a pair of guide pins 9 protrudes from the front face of the swash plate 8 toward the guide member 23. The guide pins 9 straddle the position corresponding to the upper dead point D of the swash plate 8. A spherical portion 9a is formed on the top of each guide pin 9. The spherical portion 9a is inserted into and engaged with the guide member 23. The radius of curvature of the spherical portion 9a is slightly less than the radius of curvature of the support 23a.
  • the swash plate 8 can slide while inclining toward the drive shaft 6 in the direction of the axis L of the drive shaft 6, due to the slide-guide relationship between the spherical portions 9a of the guide pins 9 and the supports 23a of the guide member 23, as well as due to the slide-support action by the drive shaft 6 by way of the insertion hole 8a.
  • the rotary disk 22, the rotor-side member 23, and the weight 24 are independently manufactured and each functional part is manufactured with a press and a punch. Therefore, each part may be hardened and lightened. Further, the thickness of the rotor can be reduced as compared to known rotors.
  • the roller 25a of the thrust bearing 25 can directly contact the rotary disk 22 during operation of the compressor. In other words, because it is not necessary to provide a race with the thrust bearing 25, a reduction in the number of parts can be achieved.
  • the second representative embodiment is shown in Fig. 8, in which the rotary disk 22 and the weight 22d are integrally formed as one part. That is, rotary disk 22 and the weight 22d are manufactured at the same time using a press machine and there are no seams between the rotary disk 22 and the weight 22d. As the result, the weight 22d is formed in a unitary manner on the lower rear face of the rotary disk 22.
  • the guide member 23 has a plate-like shape and includes an elongated hole 26.
  • the swash plate 8 includes a pin 27 that is engaged in the elongated hole 26.
  • the hinge mechanism is defined by a link-and-pin mechanism. All other features of the second representative embodiment are substantially identical to the corresponding features of the first representative embodiment. According to the second representative embodiment, because the functional parts of the rotor 7 are integrally (seamlessly) manufactured at the same time using a press, the number of parts of the torque transmitting structure can be reduced.
  • the third representative embodiment is shown in Figs. 9 to 13. As shown in Figs. 9 and 10, the rotary disk 22 and the weight 22d are manufactured at the same time using a press in the second representative embodiment.
  • the weight 22d is provided on the outer circumference of the lower rear face of the rotary disk 22. As described above, the weight 22d can correct the weight imbalance of the rotor 7 when the hinge mechanism 20 rotates together with the drive shaft 6.
  • a link-type hinge mechanism 20 is utilized.
  • an insertion hole 23c is defined within the guide member 23 and link parts 23d are disposed on the right and left sides of the guide member 23.
  • Each link part 23d includes an elongated hole 26.
  • the inner diameter of the insertion hole 23c is defined to correspond to the outer circumferential diameter of a cylindrical boss part 22f of the rotary disk 22.
  • the guide member 23 is coupled to the rotary disk 22.
  • a guide pin 27 is provided on the swash plate 8 and is engaged with the elongated hole 26. All other features of the third representative embodiment are substantially identical to the features of the first representative embodiment as described above.
  • a representative manufacturing process for the rotary disk 22 with the weight 22d is shown in Fig. 11 (A) to Fig. 11 (C).
  • a plate W is prepared by pressing a cold-rolled steel plate or carbon steel, such as S35C or S45C, into an appropriate thickness (see Fig. 11 (A)).
  • the plate W is punched to form a disk A2 having a circular insertion hole in the center of the disk A2 (see Fig. 11 (B)).
  • the rotary disk 22 with the weight 22d is manufactured by bending and drawing the disk A2 (see Fig. 11 (C)).
  • a representative manufacturing process for the guide member 23 is shown in Fig. 12 (A) to Fig. 12 (C).
  • a plate W is prepared by pressing a cold-rolled steel plate or carbon steel, such as S35C or S45C, to an appropriate thickness (see Fig. 12 (A)). Then, the plate W is punched to form a disk B2 having a insertion hole formed in the center of the disk B2 (see Fig. 11 (B)). Thereafter, link parts 23d are formed by bending the disk B2 (see Fig. 12 (C)).
  • the guide member 23 is fixed to the rotary disk 22 by joining the cylindrical boss part 22f of the rotary disk 22 to the insertion hole 23c of the guide member 23. After the joining, the guide member 23 is welded to the rotary disk 22.
  • a thrust bearing receiving portion 22c (see Fig. 9) and the inner circumferential surface of the elongated hole 26 are preferably treated by induction hardening in order to increase the strength and the wear resistance of these parts. All other features of the third representative embodiment are substantially identical to the features of the first representative embodiment as described above. According to the third representative embodiment, a relatively lightweight rotor 7 can be easily manufactured.
  • the fourth representative embodiment is shown in Figs. 13 and 14. According to the fourth embodiment, the guide member 23 and the weight 22d are integrally and seamlessly manufactured using a press. All other features of the fourth representative embodiment are substantially identical to the features of the first representative embodiment as described above.
  • FIG. 14 (A) to Fig. 14 (C) A representative manufacturing process for the guide member 23 with the weight 22d is shown in Fig. 14 (A) to Fig. 14 (C).
  • a plate W is prepared by pressing a cold-rolled steel plate or carbon steel, such as S35C or S45C, to an appropriate thickness (see Fig. 11 (A)).
  • the plate W is punched to form a disk B3 (see Fig. 14 (B)).
  • the guide member 23 with the weight 22d is manufactured by bending and drawing the disk B3 (see Fig. 14 (C)).
  • the joining of the guide member 23 (with the weight 22d) and the rotary disk 22 is completed by welding.
  • the support 23a of the guide member 23 may be formed to have a cylindrical shape.
  • the functional parts of the rotor 7 can be fixed with each other by utilizing a screw or rivet, instead of welding.
  • the guide member may be provided with the swash plate 8.
  • the guide protrusion (guide pin) may be provided with the rotor 7.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Compressor (AREA)
EP01121683A 2000-09-14 2001-09-14 Variable displacement compressors Withdrawn EP1195519A1 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2000279066 2000-09-14
JP2000279066 2000-09-14
JP2001159355 2001-05-28
JP2001159355A JP2002161852A (ja) 2000-09-14 2001-05-28 可変容量型圧縮機及びその製造方法

Publications (1)

Publication Number Publication Date
EP1195519A1 true EP1195519A1 (en) 2002-04-10

Family

ID=26599949

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01121683A Withdrawn EP1195519A1 (en) 2000-09-14 2001-09-14 Variable displacement compressors

Country Status (6)

Country Link
US (1) US20020031433A1 (zh)
EP (1) EP1195519A1 (zh)
JP (1) JP2002161852A (zh)
KR (1) KR20020021363A (zh)
CN (1) CN1342838A (zh)
BR (1) BR0105598A (zh)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4385516B2 (ja) * 2000-11-07 2009-12-16 株式会社豊田自動織機 ピストン式圧縮機
JP2009257150A (ja) * 2008-04-15 2009-11-05 Sanden Corp 流体機械のピンとピン挿入穴とから成る変角機構のピン挿入穴周壁を高周波焼入れする方法
DE102010015073A1 (de) * 2010-04-15 2011-10-20 Robert Bosch Gmbh Axialkolbenmaschine mit einer Rückzugplatte sowie Verfahren zu deren Herstellung

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4073603A (en) * 1976-02-06 1978-02-14 Borg-Warner Corporation Variable displacement compressor
US4175915A (en) * 1978-04-27 1979-11-27 General Motors Corporation Drive shaft lug for variable displacement compressor
EP0334634A1 (en) * 1988-03-23 1989-09-27 Sanden Corporation Slant plate type compressor
US5567124A (en) * 1992-12-21 1996-10-22 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Variable capacity swash-plate type compressor with an improved capacity control means
FR2760793A1 (fr) * 1997-02-28 1998-09-18 Toyoda Automatic Loom Works Compresseur a refrigerant pour conditionnement d'air de vehicule, a capacite variable
US5857402A (en) * 1996-08-05 1999-01-12 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Variable displacement compressor method and apparatus

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4073603A (en) * 1976-02-06 1978-02-14 Borg-Warner Corporation Variable displacement compressor
US4175915A (en) * 1978-04-27 1979-11-27 General Motors Corporation Drive shaft lug for variable displacement compressor
EP0334634A1 (en) * 1988-03-23 1989-09-27 Sanden Corporation Slant plate type compressor
US5567124A (en) * 1992-12-21 1996-10-22 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Variable capacity swash-plate type compressor with an improved capacity control means
US5857402A (en) * 1996-08-05 1999-01-12 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Variable displacement compressor method and apparatus
FR2760793A1 (fr) * 1997-02-28 1998-09-18 Toyoda Automatic Loom Works Compresseur a refrigerant pour conditionnement d'air de vehicule, a capacite variable

Also Published As

Publication number Publication date
BR0105598A (pt) 2002-04-30
US20020031433A1 (en) 2002-03-14
JP2002161852A (ja) 2002-06-07
CN1342838A (zh) 2002-04-03
KR20020021363A (ko) 2002-03-20

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