EP1970566A2 - Compresseur à déplacement variable - Google Patents

Compresseur à déplacement variable Download PDF

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Publication number
EP1970566A2
EP1970566A2 EP08004480A EP08004480A EP1970566A2 EP 1970566 A2 EP1970566 A2 EP 1970566A2 EP 08004480 A EP08004480 A EP 08004480A EP 08004480 A EP08004480 A EP 08004480A EP 1970566 A2 EP1970566 A2 EP 1970566A2
Authority
EP
European Patent Office
Prior art keywords
swash plate
rotary support
rotation
balance weight
outer peripheral
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Withdrawn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
EP08004480A
Other languages
German (de)
English (en)
Inventor
Naoya Yokomachi
Motoaki Okuda
Hiroaki Kayudawa
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
Priority claimed from JP2008059227A external-priority patent/JP2008255985A/ja
Application filed by Toyota Industries Corp filed Critical Toyota Industries Corp
Publication of EP1970566A2 publication Critical patent/EP1970566A2/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Withdrawn legal-status Critical Current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
    • 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
    • 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
    • F04B27/109—Lubrication

Definitions

  • the present invention relates to a variable displacement compressor, in which the pressure in a control pressure chamber accommodating a swash plate is adjusted to control the inclination angle of the swash plate so that the displacement is controlled.
  • a swash plate is tiltably accommodated in a crank chamber (control pressure chamber).
  • the control pressure chamber is supplied with refrigerant of a discharge chamber (discharge pressure zone), and the refrigerant in the crank chamber is discharged to a suction pressure zone, so that the pressure in the crank chamber is adjusted.
  • the inclination angle of the swash plate decreases. This decreases the displacement.
  • the inclination angle of the swash plate increases. This increases the displacement.
  • Lubricant is provided in the crank chamber.
  • Lubricant stored in a bottom portion of the crank chamber is sheared (agitated) by a thrust flange (rotary support), which rotates integrally with the rotary shaft, and the swash plate, which splashes the lubricant.
  • the splashed lubricant lubricates the parts that need lubrication in the crank chamber.
  • the swash plate is linked to the thrust flange by means of a link mechanism, which rotates integrally with the thrust flange.
  • a counterweight that corresponds to the link mechanism is provided to the thrust flange or the swash plate.
  • the thrust flange and the swash plate shear lubricant stored in the bottom portion of the crank chamber.
  • the temperature of the lubricant is excessively raised. This can degrade the lubrication performance of the lubricant.
  • the greater the rotational resistance the greater the power loss becomes.
  • a variable displacement compressor having a swash plate tiltably accommodated in a control pressure chamber. Refrigerant is supplied from a discharge pressure zone to the control pressure chamber, and is discharged therefrom to a suction pressure zone, so that the pressure in the control pressure chamber is adjusted to change an inclination angle of the swash plate, so that the displacement is controlled.
  • the compressor includes a rotary shaft having a rotation axis, a rotary support that rotates integrally with the rotary shaft, a link mechanism, a first balance weight, and a second balance weight. The link mechanism links the swash plate to the rotary support such that the inclination angle of the swash plate is changeable.
  • the link mechanism includes a first appendage attached to the rotary support and a second appendage attached to the swash plate.
  • the first balance weight is provided on the rotary support and corresponds to the link mechanism.
  • the second balance weight is provided on the swash plate and corresponds to the link mechanism.
  • At least one of the first balance weight, the second balance weight, the first appendage, and the second appendage has a slope on a leading side in the rotation direction of the rotary shaft. The slope has a leading end in the rotation direction and is shaped to descend in the direction of the rotation axis toward the leading end.
  • a variable displacement compressor having a swash plate tiltably accommodated in a control pressure chamber. Refrigerant is supplied from a discharge pressure zone to the control pressure chamber, and is discharged therefrom to a suction pressure zone, so that the pressure in the control pressure chamber is adjusted to change an inclination angle of the swash plate, so that the displacement is controlled.
  • the compressor includes a rotary shaft having a rotation axis, a rotary support that rotates integrally with the rotary shaft, a link mechanism, a first balance weight, and a second balance weight. The link mechanism links the swash plate to the rotary support such that the inclination angle of the swash plate is changeable.
  • the link mechanism includes a first appendage attached to the rotary support and a second appendage attached to the swash plate.
  • the first balance weight is provided on the rotary support and corresponds to the link mechanism.
  • the second balance weight is provided on the swash plate and corresponds to the link mechanism.
  • At least one of the first balance weight, the second balance weight, the first appendage, and the second appendage has a step on a leading side in the rotation direction of the rotary shaft, and the step is covered with a cover so as to suppress rotational resistance generated as the lubricant in the control pressure chamber is sheared by rotation of the rotary support or the swash plate.
  • a variable displacement compressor having a swash plate tiltably accommodated in a control pressure chamber. Refrigerant is supplied from a discharge pressure zone to the control pressure chamber, and is discharged therefrom to a suction pressure zone, so that the pressure in the control pressure chamber is adjusted to change an inclination angle of the swash plate, so that the displacement is controlled.
  • the compressor includes a rotary shaft having a rotation axis, a rotary support that rotates integrally with the rotary shaft, a link mechanism, a first balance weight, and a second balance weight. The link mechanism links the swash plate to the rotary support such that the inclination angle of the swash plate is changeable.
  • the link mechanism includes a first appendage attached to the rotary support and a second appendage attached to the swash plate.
  • a first appendage attached to the rotary support and a second appendage attached to the swash plate When at least one of the rotary support and the swash plate is defined as a body of revolution, the body of revolution having, on a surface of a part of the body of revolution except a portion on which the appendage is formed, a plane of rotation that is formed all around the rotation axis.
  • a recess is formed in the plane of rotation, and wherein the recess is located on the same side as the appendage with respect to the axis.
  • a front housing member 12 is coupled to the front end of a cylinder 11.
  • a rear housing member 13 is coupled to the rear end of the cylinder 11.
  • the cylinder 11, the front housing member 12, and the rear housing member 13 form a whole housing of a variable displacement compressor 10.
  • the front housing member 12 and the cylinder 11 define a control pressure chamber 121, and rotatably support a rotary shaft 14.
  • the rotary shaft 14 projects from the control pressure chamber 121 to the outside, and receives power from an external power source (for example, a vehicle engine).
  • a rotary support 17 is fixed to the rotary shaft 14, and a swash plate 18 is supported on the rotary shaft 14.
  • the swash plate 18 is permitted to slide in a direction of a rotation axis 141 of the rotary shaft 14 and to incline with respect to the rotary shaft 14.
  • an arm 19 is integrally formed with the rotary support 17 on a surface 171 opposed to the swash plate 18.
  • a pair of guide holes 191, 192 are formed in the arm 19.
  • a pair of support brackets 20 and a balance weight 34 are integrally formed with the swash plate 18 on a surface 181 opposed to the rotary support 17.
  • a guide pin 21 is fixed to each support bracket 20.
  • Each of the guide holes 191, 192 slidably receives the corresponding one of the guide pins 21.
  • the engagement of the guide holes 191, 192 with the guide pins 21 allows the swash plate 18 to move along the rotation axis 141 of the rotary shaft 14 while being inclined, and to rotate integrally with the rotary shaft 14.
  • the swash plate 18 is inclined by sliding the guide pins 21 with respect to the guide holes 191, 192, and sliding the swash plate 18 with respect to the rotary shaft 14.
  • the arm 19, the guide holes 191, 192, the support brackets 20, and the guide pins 21 form a link mechanism 22.
  • the link mechanism 22 links the swash plate 18 to the rotary support 17, which rotates integrally with the rotary shaft 14, in such a manner that the inclination angle of the swash plate 18 is changeable.
  • the arm 19 is an appendage attached to the rotary support 17 included in the link mechanism 22.
  • the support brackets 20 and the guide pins 21 are appendages attached to the swash plate 18 included in the link mechanism 22.
  • the maximum inclination angle of the swash plate 18 is defined by the contact between the rotary support 17 and the swash plate 18.
  • the swash plate 18 is at the maximum inclination position.
  • the swash plate 18 is at the minimum inclination position.
  • cylinder bores 111 are formed in and extend through the cylinder 11.
  • a piston 23 is retained in each cylinder bore 111.
  • the rotation of the swash plate 18 is converted to reciprocation of the pistons 23 by means of shoes 24.
  • each piston 23 reciprocates in the corresponding cylinder bore 111.
  • a suction chamber 131 and a discharge chamber 132 are defined in the rear housing member 13.
  • refrigerant in the suction chamber 131 which is a suction pressure zone, is drawn into the associated cylinder bore 111 through a suction port 15 while flexing a suction valve flap 151.
  • gaseous refrigerant in the corresponding cylinder bore 111 is discharged to the discharge chamber 132 through a discharge port 16 while flexing a discharge valve flap 161.
  • Refrigerant that is discharged to the discharge chamber 132 which is a discharge pressure zone, flows out to an external refrigerant circuit (not shown) located outside of the compressor 10. After being discharged to the external refrigerant circuit, the refrigerant is returned to the suction chamber 131.
  • the discharge chamber 132 is connected to the control pressure chamber 121 by a supply passage 25.
  • the control pressure chamber 121 is connected to the suction chamber 131 by a release passage 26. Refrigerant in the control pressure chamber 121 flows to the suction chamber 131 through the release passage 26.
  • An electromagnetic displacement control valve 27 is installed in the rear housing member 13. The electromagnetic displacement control valve 27 regulates the flow passage area of the supply passage 25. When the opening degree of the electromagnetic displacement control valve 27 is increased, the flow passage area of the supply passage 25 is increased. This increases the amount of refrigerant supplied from the discharge chamber 132 to the suction chamber 131, thereby increasing the pressure in the control pressure chamber 121. Accordingly, the inclination angle of the swash plate 18 is reduced.
  • the opening degree of the electromagnetic displacement control valve 27 When the opening degree of the electromagnetic displacement control valve 27 is decreased, the flow passage area of the supply passage 25 is decreased. This reduces the amount of refrigerant supplied from the discharge chamber 132 to the suction chamber 131, thereby lowering the pressure in the control pressure chamber 121. Accordingly, the inclination angle of the swash plate 18 is increased.
  • the balance weight 28 is integrally formed on the opposed surface 171 of the rotary support 17. To improve the rotation balance of the rotary support 17, the balance weight 28 is located in an opposite side of the arm 19 with respect to the rotation axis 141.
  • the balance weight 28 is formed as a projection having a shape of a circular arc about the rotation axis 141.
  • Each of an outer peripheral surface 282 and an inner peripheral surface 283 of the balance weight 28 is a part of an imaginary circumferential surface about the rotation axis 141.
  • the outer peripheral surface 282 and the inner peripheral surface 283 are planes of rotation created by rotation trajectories when lines parallel to the rotation axis 141 are rotated about the rotation axis 141. No step is formed in the outer peripheral surface 282 or the inner peripheral surface 283 along the circumferential direction.
  • An outer peripheral surface 174 of the rotary support 17 is a circumferential surface about the rotation axis 141.
  • the radius of the outer peripheral surface 174 is substantially equal to the radius of the outer peripheral surface 282.
  • the outer peripheral surface 174 is a plane of rotation created by rotation trajectory when a line parallel to the rotation axis 141 is rotated about the rotation axis 141. No step is formed in the outer peripheral surface 174 along the circumferential direction.
  • the rotary support 17 rotates about the rotation axis 141 in a rotation direction indicated by arrow R.
  • a step of the balance weight 28 on a leading side in the rotation direction R of the rotary support 17 forms a slope 281.
  • the leading side has a leading end.
  • the slope 281 is shaped to descend in the direction of the rotation axis 141 toward the opposed surface 171 in the rotation direction R. In other words, the slope 281 is shaped to descend in the direction of the rotation axis 141 toward the leading end.
  • the arm 19 is substantially shaped like a circular arc projection about the rotation axis 141.
  • An outer peripheral surface 194 of the arm 19 is a part of an imaginary circumferential surface about the rotation axis 141.
  • the outer peripheral surface 194 is a plane of rotation created by rotation trajectory when a line parallel to the rotation axis 141 is rotated about the rotation axis 141. No step is formed in the outer peripheral surface 194 along the circumferential direction.
  • a step of the arm 19 on a leading side in the rotation direction R of the rotary support 17 forms a slope 193.
  • the leading side has a leading end.
  • the slope 193 is shaped to descend in the direction of the rotation axis 141 toward the opposed surface 171 in the rotation direction R. In other words, the slope 193 is shaped to descend in the direction of the rotation axis 141 toward the leading end.
  • lubricant Y is stored in the control pressure chamber 121.
  • the lubricant Y stored in a bottom portion of the control pressure chamber 121 is sheared and splashed so that the lubricant Y lubricates parts in the control pressure chamber 121 that need lubrication.
  • the first embodiment provides the following advantages.
  • an outer peripheral surface 174 of a rotary support 17 is a circumferential surface about a rotation axis 141.
  • An arm 19 is formed on an opposite surface 171 of the rotary support 17.
  • a surface of the rotary support 17 that is opposite to the surface on which an arm 19 is formed (the opposed surface 171 shown in Fig. 4A ) is referred to as a back surface 172.
  • the back surface 172 is perpendicular to the rotation axis 141.
  • the back surface 172 is a surface of a part of the rotary support 17 except a portion on which the arm 19, which is an appendage of the rotary support 17, is formed.
  • the back surface 172 is also a plane created by rotation trajectory when a line perpendicular to the rotation axis 141 is rotated about the rotation axis 141. That is, the back surface 172 is a plane of rotation formed all around the rotation axis 141.
  • Recesses 173 are formed in the back surface 172.
  • the recesses 173 are located on the same side as the arm 19 with respect to the rotation axis 141.
  • a portion opposite to the arm 19 with respect to the rotation axis 141 is solid.
  • This structure offers a disk-shaped outer peripheral shape that has no step intersecting the circumferential direction, and a function of a balance weight. This improves the rotation balance of the rotary support 17.
  • no step is provided in any given circumferential section spaced from the rotation axis 141 by a constant distance.
  • the recesses 173 create steps on the back surface 172, which is a plane of rotation.
  • the rotational resistance at the recesses 173 generated when lubricant is sheared by the rotary support 17 is smaller than the rotational resistance generated at a projection formed on a plane of rotation.
  • the recesses 173 in the flat back surface 172 are easily formed.
  • the recesses 173 formed in the back surface 172 which is a plane of rotation, has a simple structure as a rotational resistance suppressing portion that suppresses rotational resistance related to lubricant.
  • the second embodiment has the same advantage as the advantage (5) of the first embodiment.
  • an arm 19A is integrally formed with a rotary support 17A on an opposed surface 171.
  • a guide hole 195 is formed in the arm 19A.
  • a pair of support brackets 29 are attached to an opposed surface 181 of a swash plate 18.
  • a guide pin 30 extends between and is supported by the support brackets 29.
  • the guide pin 30 is fitted in the guide hole 195.
  • the arm 19A, the guide hole 195, the support brackets 29, and the guide pin 30 form a link mechanism 22A.
  • the link mechanism 22A links the swash plate 18 to the rotary support 17A, which rotates integrally with the rotary shaft 14, in such a manner that the inclination angle of the swash plate 18 is changeable.
  • the arm 19A is an appendage attached to the rotary support 17A included in the link mechanism 22A.
  • the support brackets 29 and the guide pin 30 are appendages attached to the swash plate 18 included in the link mechanism 22A.
  • a balance weight 28A is formed on the rotary support 17A.
  • the balance weight 28A is formed as a circular arc about the rotation axis 141.
  • the radius of an outer peripheral surface 282 of the balance weight 28A is greater than the radius of the outer peripheral surface 175 of the rotary support 17A.
  • a rotational resistance suppressing cover 31 made of synthetic resin is attached to the outer periphery of the rotary support 17A on the same side as the arm 19A with respect to the rotation axis 141.
  • the rotational resistance suppressing cover 31 is attached to the rotary support 17A, for example, by adhesive.
  • the rotational resistance suppressing cover 31 is substantially formed as a circular arc.
  • An outer peripheral surface 311 of the rotational resistance suppressing cover 31 is a part of an imaginary circumferential surface having the same radius as the outer peripheral surface 282 of the balance weight 28A.
  • the outer peripheral surface 311 and the outer peripheral surface 282 are planes of rotation created by rotation trajectories when lines parallel to the rotation axis 141 are rotated about the rotation axis 141.
  • the outer peripheral surface 311 of the rotational resistance suppressing cover 31 attached to the rotary support 17A smoothly continuous to the outer peripheral surface 282 of the balance weight 28A.
  • the outer peripheral surface 282 of the balance weight 28A and the outer peripheral surface 311 of the rotational resistance suppressing cover 31 each form a plane of rotation that is formed all around the rotation axis 141. No step is formed in the outer peripheral surface 311 or the outer peripheral surface 282 along the circumferential direction.
  • a front surface 312 of the rotational resistance suppressing cover 31 is flat and attached to the rotary support 17 A. Also, the front surface 312 is flush with a flat front surface 286 of the balance weight 28A.
  • the rotational resistance suppressing cover 31 covers the step between the outer peripheral surface 282 of the balance weight 28A and outer peripheral surface 175 of the rotary support 17A, and the step between the front surface 286 of the balance weight 28A and the opposed surface 171 of the rotary support 17A. That is, the rotational resistance suppressing cover 31 covers an end face 284, which is a step of the balance weight 28 A, and an end face 285, which is a step of an leading end portion of the balance weight 28A in the rotation direction R.
  • the rotational resistance generated as lubricant is sheared by the rotary support 17A is suppressed.
  • an outer peripheral surface 174 of a rotary support 17B is a circumferential surface about the rotation axis 141.
  • the radius of an outer peripheral surface 282 of a balance weight 28B is equal to the radius of the outer peripheral surface 174 of the rotary support 17B.
  • a metal ring 32 shown in Fig. 7B is press fitted to the outer peripheral surface 174 of the rotary support 17B and the outer peripheral surface 282 of the balance weight 28B.
  • the ring 32 which is a rotational resistance suppressing cover, covers the outer peripheral surface 174 of the rotary support 17B and the outer peripheral surface 282 of the balance weight 28B, and end faces (steps) 287, 288 of the balance weight 28B are located inside the ring 32.
  • An outer peripheral surface 321 of the ring 32 is a circumferential surface about the rotation axis 141.
  • the outer peripheral surface 321 is a plane of rotation created by rotation trajectory when a line parallel to the rotation axis 141 is rotated about the rotation axis 141. No step is formed in the outer peripheral surface 321 along the circumferential direction.
  • the structure in which the end faces 287, 288 of the balance weight 28B are located inside the ring 32 generates less rotational resistance due to shearing of lubricant by the rotary support 17B compared to a structure in which the end faces 287, 288 of the balance weight 28B are located outside of the ring 32.
  • the fourth embodiment has the same advantage as the advantage (5) of the first embodiment.
  • a base plate 33 is fixed to the opposed surface 181 of the swash plate 18.
  • a balance weight 34A and a pair of support brackets are formed integrally on a surface of the base plate 33 that is opposed to the rotary support 17.
  • the balance weight 34A is formed as a circular.
  • a synthetic resin cover 35 is fixed to the opposed surface 331 of the base plate 33.
  • a recess 36 is formed on a contact surface 332 of the base plate 33 that contacts the opposed surface 181 of the swash plate 18.
  • the recess 36 faces the support brackets 20.
  • a recess 37 which faces the recess 36, is formed in the opposed surface 181 of the swash plate 18.
  • the recesses 36, 37 reduce the size (weight) of the balance weight 34A.
  • the cover 35 which is a rotational resistance suppressing cover, covers most of the opposed surface 331 of the base plate 33, and an outer peripheral surface 351 of the cover 35 is a circumferential surface about the rotation axis 141.
  • the height of the cover 35 is substantially equal to the height of the balance weight 34A, and most of the balance weight 34A and many portions of the support brackets 20 are located inside the cover 35. Rotational resistance in this structure due to shearing of lubricant is less than that in a structure without the cover 35.
  • each support bracket 20 of the swash plate 18 may form a slope 203 similarly to the slope 193 provided on the arm 19 of the rotary support 17 shown in Fig. 2 .
  • a slope 341 may be provided on the balance weight 34 of the swash plate 18 as shown in Fig. 10A similarly to the slope 281 provided on the balance weight 28 of the rotary support 17 shown in Fig. 2 .
  • recesses 183 may be provided on the back surface 182 of the swash plate 18 similarly to the recesses 173 provided on the back surface 172 of the rotary support 17 shown in Fig. 4B .
  • the rotary support 17A may be placed in the mold for molding the rotational resistance suppressing cover 31, so that the rotational resistance suppressing cover 31 is formed through insert molding.
  • the rotary support 17A is fixed to the rotational resistance suppressing cover 31 at the same time as the molding of the rotary support 17A, which facilitates the manufacture.
  • the rotational resistance suppressing cover 31 may be integrally formed with the rotary support 17A as a single member. Specifically, the rotational resistance suppressing cover 31, the arm 19A as the appendage, and the balance weight 28A are integrally formed with the rotary support 17A. Such configuration allows the strength of the arm 19A to be easily increased and facilitates the manufacture of the rotary support 17A.
  • the rotational resistance suppressing cover 31 may have any structure as long as it covers steps, thereby reducing the steps.
  • the outer peripheral surface 174 of the rotary support 17 may be a conical plane of rotation or a plane of rotation created by rotation trajectory when a curve is rotated about the rotation axis 141.
  • the outer peripheral surface 321 of the ring 32 may be a conical plane of rotation or a plane of rotation created by rotation trajectory when a curve is rotated about the rotation axis 141.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
EP08004480A 2007-03-12 2008-03-11 Compresseur à déplacement variable Withdrawn EP1970566A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2007062027 2007-03-12
JP2008059227A JP2008255985A (ja) 2007-03-12 2008-03-10 可変容量型圧縮機

Publications (1)

Publication Number Publication Date
EP1970566A2 true EP1970566A2 (fr) 2008-09-17

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP08004480A Withdrawn EP1970566A2 (fr) 2007-03-12 2008-03-11 Compresseur à déplacement variable

Country Status (2)

Country Link
US (1) US20080226471A1 (fr)
EP (1) EP1970566A2 (fr)

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CN105863998A (zh) * 2016-06-03 2016-08-17 江苏盈科汽车空调有限公司 一种汽车空调转臂

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Publication number Priority date Publication date Assignee Title
EP2298586A1 (fr) 2009-09-09 2011-03-23 FERRARI S.p.A. Véhicule Hybride

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