EP1262663A2 - Rotor pour un compresseur à plateau en biais à capacité variable - Google Patents

Rotor pour un compresseur à plateau en biais à capacité variable Download PDF

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Publication number
EP1262663A2
EP1262663A2 EP02011606A EP02011606A EP1262663A2 EP 1262663 A2 EP1262663 A2 EP 1262663A2 EP 02011606 A EP02011606 A EP 02011606A EP 02011606 A EP02011606 A EP 02011606A EP 1262663 A2 EP1262663 A2 EP 1262663A2
Authority
EP
European Patent Office
Prior art keywords
rotor
base portion
swash plate
drive shaft
variable displacement
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Withdrawn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
EP02011606A
Other languages
German (de)
English (en)
Other versions
EP1262663A3 (fr
Inventor
Hajime Kurita
Tomoji Tarutani
Takenori Sawa
Hirohiko Tanaka
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 EP1262663A2 publication Critical patent/EP1262663A2/fr
Publication of EP1262663A3 publication Critical patent/EP1262663A3/fr
Withdrawn legal-status Critical Current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
    • 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

Definitions

  • the present invention relates to variable displacement compressors that may be used for vehicle air conditioning systems.
  • the present invention also relates to methods for manufacturing such compressors.
  • Japanese Laid-open Patent Publication No. 11-264371 which corresponds to US Patent No. 6,276,904, teaches a variable displacement compressor 100 having one-head pistons.
  • the compressor 100 includes a drive shaft 101 that is rotatably driven by a vehicle engine (not shown) via a clutch (not shown).
  • a swash plate 102 is slidably mounted on the drive shaft 101 and is inclined relative to the drive shaft 101. Rotation of the drive shaft 101 is transmitted to the swash plate 102 via a rotor 103 and a hinge mechanism 104.
  • the rotor 103 is fixedly mounted on the drive shaft 101.
  • a piston 106 is connected to the swash plate 102 via a shoe 105, so that the piston 106 can reciprocate within a cylinder bore 107 in order to draw a refrigerant gas into the cylinder bore 107 and then compress and discharge the refrigerant gas.
  • the inclination angle of the swash plate 102 can be changed by sliding or pivoting about the drive shaft 101, so that the stroke length of the piston 106 can be varied in order to adjust the intake and discharge volume of the refrigerant gas.
  • the rotor 103 includes a base 108, supporting arms 109 and a counterweight 110. These parts are manufactured as a single, integral piece using a casting process.
  • the base 108 is mounted on the drive shaft 101.
  • the supporting arms 109 are included within the hinge mechanism 104 that also serves as a torque transmission mechanism.
  • the counterweight 110 serves to balance the weight of the rotor 103 such that the center of gravity of the rotor 103 is positioned on the rotational axis of the drive shaft 101.
  • the hinge mechanism 104 further includes a hinge pin 111 that is mounted on the swash plate 102.
  • variable replacement compressors that can reduce material costs and manufacturing costs. It is another object of the present teachings to provide an alternative design for the above-described known compressor.
  • variable displacement compressors include a rotor that has been press-formed from a plate or plate material.
  • the rotor may be fixedly mounted on a drive shaft and may be coupled to a swash plate via a hinge device.
  • the rotor optionally may define a portion of the hinge device.
  • the hinge device preferably permits the swash plate to rotate with the rotor as well as the drive shaft.
  • the hinge device also may permit the swash plate to change its inclination angle relative to the rotor as well as the drive shaft.
  • the swash plate may be coupled to a piston that slidably disposed within a cylinder bore.
  • Such compressors may include a plurality of pistons coupled to the swash plate and each piston may be reciprocally disposed in a respective cylinder bore.
  • the piston(s) may reciprocate within the cylinder bore(s) in order to compress a refrigerant gas (cooling medium).
  • the rotor may be formed from a flat plate, e.g., a cold-rolled steel plate or a plate made of SC steel, e.g., S35C and S45C.
  • the rotor may be formed from such a plate by punching (and/or perforating), bending and squeezing the plate.
  • the plate may be punched to form an intermediate product that has a predetermined outer contour.
  • the intermediate product may, e.g., include a base portion, a counterweight and support arms (link portion) that are formed integrally with each other.
  • the intermediate product may be perforated at the same time or before the punching operation so as to provide perforations and an axial hole.
  • the intermediate product may then be further processed to obtain a finished rotor.
  • the support arms may be bent to have a suitable configuration for connecting to the swash plate.
  • the hinge device may preferably include the support arms and the support arms may cooperate with a hinge pin.
  • the hinge pin may be mounted on the swash plate.
  • the peripheral portion of the axial hole may be squeezed to form a boss portion having an insertion hole and the drive shaft may be fixedly fitted within the insertion hole.
  • the counterweight and the perforations may serve to adjust the center of gravity of the entire rotor such that the center of gravity is positioned on the rotational axis of the rotor.
  • the rotational axis of the rotor preferably aligned with the rotational axis of the drive shaft.
  • the rotor may have improved strength and may be lightweight in comparison with the above-described cast-formed rotor.
  • a cast-formed rotor may include excess projections that are typically formed due to the casting process.
  • the press-formed rotor naturally will not include such excess projections, thereby ensuring that the rotor has the correct (desired) weight.
  • no cutting operations or only minimal cutting operations
  • variable displacement compressors may include press-forming a plate in order to form a rotor.
  • the press-forming operation may include punching (and/or perforating), bending and squeezing the plate.
  • lightweight, one-piece rotors can be manufactured at lower costs.
  • variable displacement compressors may include a swash plate that is mounted on a drive shaft in an inclined position relative to the drive shaft.
  • a piston may be coupled to the swash plate, so that the piston reciprocates within a cylinder bore as the swash plate rotates.
  • a rotor may be fixed to the drive shaft.
  • a hinge device may be disposed between the rotor and the swash plate.
  • the rotor may define a portion of the hinge device.
  • the hinge device preferably connects the rotor to the swash plate in order to permit the swash plate to change its inclination angle relative to the drive shaft when the rotor causes the swash plate to rotate.
  • the stroke length of the piston may be varied in response to changes in the inclination angle of the swash plate.
  • the rotor may be press-formed from a plate and may include a base portion and support arms formed integrally with the base portion. Further, the base portion may be fixed to the drive shaft and the support arms may constitute an element of the hinge device.
  • the rotor may have increased strength and may be lighter in weight than known rotors.
  • the press-formed rotor also may be formed to have the correct weight during the press-forming step, because it will not be necessary to remove excess projections that are typically formed using a casting process.
  • the rotor is press-formed from a plate, post-pressing cutting operations can be reduced or eliminated, as compared to cast-formed rotors, thereby reducing manufacturing time and manufacturing costs.
  • production efficiency may be improved.
  • a counterbalancing device may adjust the center of gravity of the rotor so as to position the center of gravity at the rotational axis of the rotor.
  • the counterweight device may be utilized in order to ensure that the rotor rotates in a stable manner.
  • the support arms may be bent by a predetermined angle relative to a flat surface of the base portion.
  • at least a portion of the support arms is positioned within a plane that projects from the base portion, which plane preferably is substantially perpendicular to the axial direction of the drive shaft. Therefore, the rotor may have a compact construction with respect to its diametrical direction.
  • the hinge device also includes a hinge pin that engages the support arms, the degree of freedom in determining the relative position between the support arms and the hinge pin may be improved.
  • the counterbalancing device may include at least one perforation formed in the base portion. Therefore, the center of gravity of the rotor can be easily adjusted by appropriately setting the position, configuration or the size of the perforation(s). In addition, the weight of the entire rotor can be reduced by providing the perforation(s).
  • the counterbalancing device may include a counterweight disposed on the base portion.
  • the counterweight may be positioned opposite to the support arms with respect to the rotational axis. Therefore, the center of gravity of the rotor can be easily adjusted by appropriately selecting the configuration, weight and/or the size of the counterweight.
  • a counterweight may be formed by various methods.
  • the counterweight optionally may be formed by extending the outer periphery of the base portion, by increasing the thickness of the outer peripheral portion of the base portion, or by folding the outer peripheral portion of the base portion.
  • methods for forming a variable displacement compressor may include press-forming a single plate or plate material in order to form the rotor.
  • the rotor preferably includes a base portion integrally attached to one or more support arms. The base portion may then be fixedly coupled to the drive shaft.
  • the support arms optionally may constitute an element of the hinge device.
  • the press forming step may include punching (including perforating), bending and squeezing the plate. Therefore, the rotor can be easily manufactured at lower costs as compared to cast-formed rotors.
  • the plate can be formed into a substantially finished rotor by the press-forming operation, post-pressing cutting operations can be reduced or eliminated.
  • the rotor may be formed as a one-piece element. Therefore, the number of steps for manufacturing the rotor can be reduced in comparison with known rotor manufacturing steps, in which parts of the rotor are formed separately from each other and thereafter are joined to each other.
  • variable displacement compressor 30 may comprise a housing and the housing generally may include, e.g., a front housing 1, a cylinder block 2 and a rear housing 3.
  • the front housing 1 may be joined to the front end (left end as viewed in FIG. 1) of the cylinder block 2.
  • the rear housing 3 may be joined to the rear end of the cylinder block 2 via a valve plate 4.
  • other housing configurations may be suitably utilized with the present teachings.
  • a crank housing 5 may be defined by and within the front housing 1 and the cylinder block 2.
  • a drive shaft 6 may extend through the crank housing 5.
  • the front portion of the drive shaft 6 may be rotatably supported by the front housing 1 and the rear portion of the drive shaft 6 may be rotatably supported by the cylinder block 2.
  • the drive shaft 6 may be coupled to an outside drive source, e.g., a vehicle engine (not shown), via a clutch mechanism, e.g., an electromagnetic clutch (not shown). Therefore, the drive shaft 6 may be rotatably driven by the drive source when the clutch is engaged.
  • a rotor 7 may be disposed within the crank chamber 5 and may be fixedly mounted on the drive shaft 6, so that the rotor 7 can rotate with the drive shaft 6.
  • a swash plate 8 also may be disposed within the crank chamber 5.
  • the swash plate 8 is slidably fitted onto the drive shaft 6 via an insertion hole 8a that is formed in the central portion of the swash plate 8.
  • a hinge mechanism 20 may be interposed between the rotor 7 and the swash plate 8, so as to couple the rotor 7 to the swash plate 8.
  • the hinge mechanism 20 may include support arms 23 and a hinge pin 9.
  • the support arms 23 may be integrally formed with the rotor 7, as shown more clearly in FIG. 2.
  • One or more slots or holes 26 may be defined within the support arms 23 and the hinge pin 9 may be disposed within the slot(s) 26.
  • the hinge pin 9 may be mounted on the swash plate 8.
  • a plurality of cylinder bores 2a may be defined within the cylinder block 2 and may be positioned at predetermined intervals around a rotational axis L of the drive shaft 6.
  • a rear side (right side portion as viewed in FIG. 1) of a piston 11 may be received within each of the cylinder bores 2a.
  • the front end of the piston 11 may be connected to the peripheral portion of the swash plate 8 via a pair of shoes 12.
  • the piston 11 can slide relative to the swash plate 8 in the rotational direction of the swash plate 8 but can move together with the swash plate 8 in the forward and rearward directions (i.e., left and right directions as viewed in FIG. 1). Therefore, the rotation of the drive shaft 6 may be transmitted to each piston 11 as reciprocating movement along the axial direction of the corresponding cylinder bore 2a, via the rotor 7, the hinge mechanism 20, the swash plate 8 and the corresponding shoes 12.
  • a suction chamber 3a and a plurality of discharge chambers 3b corresponding to the cylinder bores 2a may be defined within the rear housing 3 and may oppose the valve plate 4.
  • Each of the cylinder bores 2a may communicate with the suction chamber 3a and the corresponding discharge chamber 3b via a suction port 4a and a discharge port 4c that are respectively defined within the valve plate 4.
  • a suction valve 4b may be attached to the valve plate 4 and may serve to open and close the suction ports 4a.
  • a discharge valve 4d also may be attached to the valve plate 4 and may serve to open and close the discharge ports 4c.
  • a bleed gas port 15 may be defined within the valve plate 4 and may permit the crank chamber 5 to communicate with the suction chamber 3a.
  • a gas supply channel 16 may be defined through the cylinder block 2, the valve plate 4 and the rear housing 3. The gas supply channel 16 may permit the crank chamber 5 to communicate with the discharge chambers 3b.
  • a displacement control valve 17 may be located within a portion of the gas supply channel 16. The displacement control valve 17 may preferably be an electromagnetic valve. The displacement control valve 17 may control the flow rate of the refrigerant gas flowing through the gas supply channel 16, so that the pressure within the crank chamber 5 can vary or change (i.e., increase or decrease).
  • the pressure within the crank chamber 5 is thus varied or changed, the difference between the pressure within the crank chamber 5 and the pressure within the cylinder bores 2a that may be applied to the front side and the rear side of each piston 11, respectively.
  • the inclination angle of the swash plate 8 can be varied to effect a change in the stroke length of the pistons 11. In this manner, the discharge rate of the refrigerant gas can be adjusted during operation of the compressor.
  • the rotor 7 may include a base portion 22 and a counterweight 24.
  • the base portion 22 may be fixed to the drive shaft 6 and the counterweight 24 may serve to counterbalance the weight of the support arms 23.
  • These portions 22, 23 and 24 may be formed integrally with each other by press-forming a cold-rolled steel plate or a plate made of SC steel, e.g., S35C and S45C in order to manufacture the rotor 7.
  • the base portion 22 may have a substantially disk-like configuration.
  • a through-hole 22a may be formed in a central portion of the base portion 22.
  • the drive shaft 6 may be inserted into the through-hole 22a and may be fixed in position relative to the base portion 22, so that the base portion 22 will rotate together with the drive shaft 6.
  • the through-hole 22a may be formed within a boss portion 22c that is disposed at the central portion of the base portion 22 and extends rearward (rightward in FIG. 1) along the drive shaft 6.
  • a thrust bearing 25 may be interposed between the front surface of the base portion 22 and the inner wall of the front housing 1.
  • the thrust bearing 25 may be arranged so as to surround, or substantially surround, the drive shaft 6. Therefore, when a reaction force is applied to the piston 11 during the compression operation, which force is caused by the reciprocating movement of the piston 11, the front housing 1 may receive this reaction force via the shoes 12, the swash plate 8, the hinge mechanism 20 and the thrust bearing 25.
  • the support arms 23 may be disposed at an uppermost position of the rear surface of the base portion 22, which position opposes to an upper dead center position D of the swash plate 8 that defines the top clearance of the piston 11.
  • the support arms 23 may be positioned on the right and left sides of the rotational axis L of the drive shaft 6, as shown in FIG. 2.
  • the support arms 23 may be bent substantially perpendicular to and from right and left edges of the upper peripheral portion of the base portion 22, respectively.
  • rear ends of the support arms 23 may extend obliquely downward from the respective support arms 23, so that the support arms 23 may have substantially inverted V-shaped configurations.
  • the support arms 23 may be positioned within a plane that projects from the base portion 22, which plane preferably is substantially perpendicular to the axial or longitudinal direction of the drive shaft 6. Therefore, the relative position between the support arms 23 and the hinge pin 9 can be easily set.
  • the rotor 7 may have a compact size with regard to the diametrical direction.
  • elongated slots 26 may be defined within the rear ends of the support arms 23.
  • the counterweight 24 may be formed integrally with the lower portion of the rear side of the base portion 22. Because the support arms 23 are disposed on the upper side of the rotor 7, the center of gravity of the rotor 7 may be upwardly offset from the rotational axis L of the drive shaft 6. Therefore, the counterweight 24 may be positioned on the lower side of the rotor 7 that is the opposite side to the support arms 23 with respect to the rotational axis L.
  • the center of gravity of the rotor 7 may be suitably adjusted, e.g., by modifying the outer configuration, by forming appropriate perforations and/or by changing the thickness of the rotor 7.
  • the peripheral portion of the rotor 7 may be bent.
  • three perforations 27 are formed in the base portion 22 on the side adjacent to the support arms 23 of the base portion 22. Because no perforations are formed in the opposite side, the opposite side will have a greater weight. Naturally, the number, sizes, positions or other properties of the perforations 27 may be suitably determined in order to impart appropriate properties to the counterweight 24.
  • the counterweight 24 and the perforations 27 of the rotor 7 may cooperate to provide a counterbalancing function. Therefore, the center of gravity of the rotor 7 may be positioned at the rotational axis of the rotor 7 (i.e., the rotational axis L of the drive shaft 6).
  • the swash plate 8 may have a substantially disk-like configuration with the central insertion hole 8a.
  • the insertion hole 8a may be configured such that the swash plate 8 can incline relative to the drive shaft 6.
  • a projection 8b may be formed on the front surface of the swash plate 8 and may extend forwardly of the swash plate 8 toward the rotor 7.
  • the hinge pin 9 may be mounted on the front end of the projection 8b and may extend substantially horizontally. The ends of the hinge pin 9 may slidably engage the respective slots 26 of the support arms 23.
  • a slide guide for the swash plate 8 may be defined by the hinge pin 9 and the slots 26 of the support arms 23 and an axial slide support on the drive shaft 6 provided by the insertion hole 8a. Therefore, the swash plate 8 can incline relative to the drive shaft 6 while also sliding along the direction of the rotational axis L of the drive shaft 6.
  • a flat plate W as shown in FIG. 3(A) may be prepared with a predetermined size and configuration, e.g. a square configuration.
  • the plate W may be made of cold-rolled steel or SC steel, e.g., S35C and S45C.
  • the intermediate product S may include, e.g., the base portion 22, the support arms 23 and the counterweight 24.
  • a central, circular hole 22b may be defined within the base portion 22.
  • the support arms 23 may extend substantially horizontally from the right and left sides of the upper portion of the base portion 22.
  • the counterweight 24 may extend over substantially an angle of 180 along the lower portion of the base portion 22.
  • the perforations 27 may be formed within base portion 22 in the upper portion on the side of the support arms 23.
  • this second step may be performed in a single step or may be a two-stage step in which the plate W is first formed with the predetermined outer contour and then the hole 22b and perforations 27 are separately formed.
  • a third step may be performed to squeeze (and expand) the peripheral portion of the central circular hole in order to form the boss portion 22c having the through hole 22a, as shown in FIGS. 3(D) and 3(E).
  • the boss portion 22c will extend or project from the rear side of the base portion 22 by a predetermined distance, as shown in FIG. 3(E).
  • a fourth step may be performed to bend the support arms 23 in the direction toward the rear side of the base portion 22, as shown in FIGS. 3(F) and 3(G).
  • this four-step press-forming operation is merely one representative method for forming the rotor 7 and these steps may be augmented, eliminated or modified as appropriate.
  • the counterweight 24 may be formed to have a substantially semi-circular configuration around the rotational axis of the base portion 22.
  • the support arms 23 extend outside beyond the arc line (indicated by chain lines) that is an extension of the outer contour of the counterweight 24.
  • Cutouts S1 may be formed in the intermediate product S and may extend from predetermined peripheral points to a position adjacent to the base of the respective support arms 23. Therefore, the folding lines of the support arms 23 may be defined to extend adjacent to the extension line of the outer contour of the counterweight 24, so that the support arms 23 can be easily bent.
  • the support arms 23 are configured to have inverted V-shaped configurations, the support arms 23 may extend toward the central portion of the base portion 22 and within the plane that projects from the base portion 22 and is substantially perpendicular to the rotational axis of the drive shaft 6. As a result, the required length of the support arms 23 for engaging the hinge pin 9 can be easily ensured.
  • the sliding surfaces of the rotor 7, e.g., the inner surfaces of the slots 26 of the support arms 23 and the through hole 22a, and a contact surface 22b of the thrust bearing 25, optionally may be treated by a high-frequency hardening process or other processes in order to increase the strength and wear resistance of the rotor 7.
  • the rotor 7 (which may include the base portion 22, support arms 23 and the counterweight 24) may be integrally press-formed from a cold-rolled steel plate or a plate made of SC steel. Therefore, the rotor 7 may have improved strength and may be lightweight. In addition, the rotor 7 will not include excess projection(s) that result when a rotor is integrally formed using a casting process. This feature also ensures that the rotor 7 will be relatively lightweight.
  • the use of the plate as a material for the rotor 7 and the incorporation of the press-forming operation may reduce cutting operations and may reduce manufacturing time. Thus, manufacturing costs can be reduced.
  • the rotor 7 may be formed with a substantially finished configuration by press-forming and without the need for any additional operations, the number of cutting steps can be reduced. Furthermore, because the rotor 7 (e.g., the base portion 22, the support arms 23 and the counterweight 24) are formed into one piece, the number of rotor parts may be reduced to only one. Moreover, the number of manufacturing steps also may be reduced and it is not necessary to perform a joining or attaching step in order to manufacture a rotor having a plurality of parts.
  • a hinge mechanism 20A that corresponds to the hinge mechanism 20 of the above representative embodiment may include substantially C-shaped support arms 23A that correspond to the support arms 23.
  • a pair of hinge pins 9A may correspond to the hinge pin 9 mounted on the swash plate 8 and may include spherical ends 9A1 that slidably engage the respective support arms 23A.
  • the chain lines in FIGS. 4 and 5 indicate the configuration of the support arms 23A before they are bent to have the C-shaped configurations. According to this arrangement, substantially the same operation and effects as the representative embodiment may be attained.
  • FIGS. 6 and 7. may be further modified as shown in FIGS. 6 and 7.
  • cylindrical holes may be defined within support arms 23B and the cylindrical holes may slidably receive the spherical ends 9A1 of the hinge pins 9A.
  • the support arms 23B may be positioned on the upper side of the base portion 22 as indicated by chain lines in FIG. 6. According to this arrangement as well, substantially the same operation and effects as the representative embodiment may be attained.
  • the combination of the counterweight 24 on the lower side of the base portion 22 and the perforations 27 formed in the base portion 22 performs the function of adjusting the center of gravity of the rotor 7.
  • the counterweight 24 or the perforations 27 may be eliminated.
  • the counterweight 24 and the perforations 27 are not required to be disposed at a predetermined section of the rotor 7.
  • the center of gravity of the entire rotor is preferably adjusted so as to be positioned at the rotational axis L.
  • support arms 23 may be suitably modified.
  • support arms 23 may be formed by cutting lines, and then bending the cut portions.
  • the cutting lines may be disposed inside of an imaginary arc line that is an extension of the outer contour of the counterweight 24 and the cutting lines preferably correspond to the contour of support arms 23.

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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)
EP02011606A 2001-05-28 2002-05-28 Rotor pour un compresseur à plateau en biais à capacité variable Withdrawn EP1262663A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2001159356 2001-05-28
JP2001159356A JP2002349429A (ja) 2001-05-28 2001-05-28 可変容量型圧縮機及びその製造方法

Publications (2)

Publication Number Publication Date
EP1262663A2 true EP1262663A2 (fr) 2002-12-04
EP1262663A3 EP1262663A3 (fr) 2003-11-19

Family

ID=19002954

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EP02011606A Withdrawn EP1262663A3 (fr) 2001-05-28 2002-05-28 Rotor pour un compresseur à plateau en biais à capacité variable

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US (1) US20030007877A1 (fr)
EP (1) EP1262663A3 (fr)
JP (1) JP2002349429A (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20020067964A (ko) * 2001-02-19 2002-08-24 가부시키가이샤 도요다 지도숏키 압축기용 밸브 플레이트의 제조방법
US7455009B2 (en) * 2006-06-09 2008-11-25 Visteon Global Technologies, Inc. Hinge for a variable displacement compressor
CN100578619C (zh) * 2007-11-05 2010-01-06 华为技术有限公司 编码方法和编码器

Citations (3)

* 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
US6139282A (en) * 1997-02-28 2000-10-31 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Variable capacity refrigerant compressor with an aluminum cam plate means

Patent Citations (3)

* 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
US6139282A (en) * 1997-02-28 2000-10-31 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Variable capacity refrigerant compressor with an aluminum cam plate means

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Publication number Publication date
US20030007877A1 (en) 2003-01-09
JP2002349429A (ja) 2002-12-04
EP1262663A3 (fr) 2003-11-19

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