EP3477104A1 - Compresseur à déplacement variable, en particulier pour un circuit de réfrigérant d'un système de conditionnement d'air pour véhicule - Google Patents

Compresseur à déplacement variable, en particulier pour un circuit de réfrigérant d'un système de conditionnement d'air pour véhicule Download PDF

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Publication number
EP3477104A1
EP3477104A1 EP17198578.1A EP17198578A EP3477104A1 EP 3477104 A1 EP3477104 A1 EP 3477104A1 EP 17198578 A EP17198578 A EP 17198578A EP 3477104 A1 EP3477104 A1 EP 3477104A1
Authority
EP
European Patent Office
Prior art keywords
swash plate
variable displacement
displacement compressor
projections
axial contact
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Withdrawn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
EP17198578.1A
Other languages
German (de)
English (en)
Inventor
Peter VITAZKA
Hiroshi Kanai
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.)
Valeo Japan Co Ltd
Original Assignee
Valeo Japan Co Ltd
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 Valeo Japan Co Ltd filed Critical Valeo Japan Co Ltd
Priority to EP17198578.1A priority Critical patent/EP3477104A1/fr
Publication of EP3477104A1 publication Critical patent/EP3477104A1/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Withdrawn legal-status Critical Current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
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • 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
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/14—Provisions for readily assembling or disassembling
    • 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
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/1822—Valve-controlled fluid connection
    • F04B2027/1827—Valve-controlled fluid connection between crankcase and discharge chamber

Definitions

  • the invention relates to a variable displacement compressor having a housing enclosing a crank chamber, a suction chamber, and a discharge chamber; a plurality of cylinders provided in the housing; a drive shaft rotatably supported in the housing and having a driving flange connected thereto; a swash plate arranged on the drive shaft so as to have an adjustable inclination angle relative to a plane perpendicular to the drive shaft; a plurality of pistons, each of which is slidably disposed within one each of the cylinders; the pistons being coupled to the swash plate so as to reciprocate within the cylinders with a stroke depending from the inclination of the swash plate; and an engagement structure for connecting the swash plate to the driving flange.
  • Variable displacement compressors of this type are a well-known component in an air conditioning system, in particular for vehicles.
  • the reciprocating motion of the pistons serves for sucking refrigerant gas into the cylinders, compressing the refrigerant and discharging it towards the discharge chamber.
  • the displacement of the cylinders is adjusted by controlling the pressure within the crank chamber of the housing, thereby changing the inclination of the swash plate.
  • the function of the engagement structure is to allow the swash plate to assume the respective inclination angle depending from the pressure within the crank chamber, while at the same time transmitting the rotary motion from the driving flange to a hub carrying the swash plate.
  • the object of the invention is to provide an engagement structure which on the one hand is very compact and consists of a few components only while at the other hand ensures a reliable connection between the driving flange and the swash plate.
  • the invention provides a variable displacement compressor as outlined above, characterized in that the engagement structure comprises at least one groove and two projections, the projections being formed integrally with at least one male arm associated with the swash plate or the driving flange and engaging into the at least one groove associated with the driving flange or the swash plate.
  • the invention is based on the concept of reducing the number of parts of the engagement structure to a minimum, which is achieved by engaging the male arm(s) directly (via the projections) into the groove of the engagement structure.
  • no additional parts such as pins known from the prior art have to be mounted.
  • small tolerances and a low weight can be achieved.
  • the entire structure is very compact.
  • each of the projections is provided on one male arm, the male arms being spaced from each other.
  • the male arms being spaced from each other. Using two arms spaced from each other allows obtaining a high rigidity of the engagement structure in case forces act on the swash plate which generate a torque around an axis perpendicular to the drive shaft and located in a central plane of the engagement structure, while at the same time reducing the weight of the engagement structure.
  • the projections are arranged at a distal end of the male arm(s).
  • the projections are formed integrally with the male arm(s), they can be arranged at the very end of the arm(s) at a position where for example a pin known from prior art engagement structures cannot be arranged.
  • the engagement structure is very compact in an axial direction.
  • each of the grooves being provided in one female arm, the female arm being spaced from each other.
  • a high rigidity of the engagement structure can be achieved while at the same time the weight of the engagement structure can be kept low.
  • the female arms are arranged at the driving flange.
  • they can be formed integrally with the driving flange so that no mounting steps are necessary.
  • the grooves are delimited by parallel side walls. This structure allows manufacturing the grooves with little effort as a milling cutter can be used for machining the grooves with a simple translational movement.
  • the grooves extend at an angle with respect to the drive shaft which is between 60° and 70°.
  • the grooves are facing each other while the projections are facing away from each other.
  • the male arms are arranged between the female arms which thus reliably prevent the projections from disengaging from the grooves.
  • each of the projections has two distinct rounded contact surfaces for axial engagement with the side walls of the grooves, one of the axial contact surfaces facing the swash plate and the other of the axial contact surfaces facing away from that swash plate.
  • the axial contact surfaces have different radii, with the radius of the axial contact surface facing that swash plate preferably being smaller than the radius of the axial contact surface facing away from the swash plate.
  • the larger radius allows transmitting higher axial loads while the smaller radius is advantageous during the mounting process.
  • the axial contact surface facing the swash plate is concentric with the axial contact surface facing away from that swash plate. This configuration ensures that the axial play of the projections within the grooves is the same irrespective of the inclination angle of the swash plate.
  • the projections have flat contact surfaces for lateral engagement with a bottom wall of the grooves, the flat contact surfaces facing away from each other.
  • the lateral contact surfaces are very effective for transmitting loads in a circumferential direction between the driving flange and the swash plate.
  • the compressor has a housing which consists of three parts, namely a front housing 10, a cylinder block 12 and a rear head 14.
  • cylinder block 12 a plurality of cylinders 16 is provided. Within each cylinder, a piston 18 is slidably accommodated.
  • the compressed refrigerant gas then circulates from the discharge chamber through a condenser, an expansion device and a vaporizer so as to again arrive as the suction chamber 20.
  • variable displacement compressor the condenser, the expansion device and the vaporizer are the main components of an air conditioning system which allows removing heat from air to be admitted into the cabin of a vehicle.
  • the reciprocating motion of pistons 18 is generated by means of a swash plate 24 to which each piston 18 is connected by means of a pair of sliding shoes 26.
  • the swash plate 24 is fixed to a hub 28 which is connected via an engagement structure 30 with a driving flange 32.
  • the driving flange in turn is mounted non-rotationally on a drive shaft 34.
  • Drive shaft 34 is rotatably mounted within housing by means of bearings 35.
  • Drive shaft 34 is driven from a motor of the vehicle in which the air condition system is arranged.
  • the motor can be a combustion engine to which drive shaft 34 is connected via pulleys and a drive belt.
  • a separate driving motor for the compressor can be provided.
  • Engagement structure 30 transmits a rotary motion of driving flange 32 to hub 28.
  • engagement structure 30 allows hub 28 and thereby swash plate 24 to assume different angles of inclination with respect to a plane which is perpendicular to drive shaft 34. This can be seen by comparing Figures 1 and 2 .
  • swash plate 24 is shown with a maximum inclination angle ⁇ .
  • swash plate 24 has a minimum inclination angle which here is slightly greater than 0.
  • each piston When the inclination angle is at the minimum inclination angle, the stroke of pistons 18 within cylinders is very small. Thus, the discharge volume of the compressor is very small as well.
  • each piston For any inclination angle different from 0, each piston, during one revolution of drive shaft 34, performs one stroke. Looking at Figure 1 , each piston travels from a position in which the remaining volume within cylinder 16 is minimum (please see piston 18 shown in the upper half of Figure 1 ) to a position in which the volume within cylinder 16 is maximum (please see piston 18 shown in the lower half of Figure 1 ) and back to the first position.
  • crank chamber The pressure in the space in which swash plate 24 is arranged (referred to as "crank chamber” and denominated with reference numeral 36).
  • the pressure within crank chamber 36 is controlled via a solenoid valve 37 controlling the flow connection between discharge chamber 22 and crank chamber 36. Details of this way of controlling the inclination angle of swash plate 24 are well-known from the prior art.
  • a stroking spring 38 and a destroking spring 38a help in controlling movement of hub 28 in response to changes of the pressures within crank chamber 36.
  • Hub 28 is provided with a through hole 37 through which drive shaft 34 extends.
  • Through hole 37 has an inner wall which is formed by two cylindrical holes crossing each other, namely one cylindrical hole which extends through the hub in an orientation which corresponds to a slightly negative inclination angle, and one cylindrical hole which extends through the hub in an orientation which corresponds to the maximum inclination angle.
  • the contour of through hole 37 approximates the outer surfaces of drive shaft 34 at a lower left side and an upper right side for the maximum inclination of the hub (visible in Figure 1 and 8 , with reference to "right”, “left”, “upper” and “lower” being made to the orientation shown in the drawings), and at an upper left side and a lower right side (please see Figure 2 ).
  • engagement structure 30 With reference to Figures 3 to 6 , engagement structure 30 will now be described in detail.
  • engagement structure 30 consists of two female arms 40 of which each is provided with a groove 42, and two male arms 44 of which each is provided with a projection 46 which is an integral part of the respective male arm, with each projection 46 engaging into an associated one of grooves 42.
  • the projections being integrally formed with the male arms, no mounting step is necessary.
  • female arms 40 are formed integrally with and extend generally in an axial direction from driving flange 32.
  • Female arms 40 have a distance from each other which is in the order of twice the diameter of drive shaft 34.
  • Each groove 42 is provided in the respective female arm 40 on its side facing the other female arm 40.
  • two grooves 42 are provided which are arranged symmetrically opposite each other with respect to a center plane C.
  • Each groove 42 is delimited by a bottom wall 48 and two side walls 50, 52.
  • Side walls 50, 52 are arranged parallel to each other. Further, they are arranged perpendicular with respect to bottom wall 48. Furthermore, the side walls 50 of both grooves 42 extend in the same plane as well as side walls 52 of opposite grooves 42 extend in one and the same plane. Thus, grooves 42 define a (virtual) cubic space.
  • grooves 42 Because of the cubic nature of the space defined by grooves 42, they can be milled with a single milling cutter which is advanced along a straight path between the two female arms 40.
  • Driving flange 32 is provided with a counter weight 54 so that driving flange 32 is balanced with respect to centrifugal loads.
  • male arms 44 are formed integrally with hub 28 on which swash plate 24 is mounted.
  • the space between the two male arms 40 corresponds approximately to the diameter of drive shaft 34.
  • Each projection 46 is provided with two axial contact surfaces 56, 58 and with one lateral contact surface 60.
  • Axial contact surface 56 is arranged on the side of protrusion 46 which, in a completely mounted condition of the compressor, faces swash plate 24. Conversely, axial contact surface 58 is arranged such that it faces away from swash plate 24.
  • axial contact surfaces 56 cooperate with side walls 52 of grooves 42 and axial contact surfaces 58 cooperate with side walls 50 of grooves 42.
  • Lateral contact surfaces 60 are arranged on protrusions 46 such that they face away from each other. They cooperate, in a mounted condition, with bottom walls 48 of grooves 42.
  • a counterweight 61 is provided for balancing hub 28 .
  • Axial contact surfaces 58, 56 have the shape of a portion of a cylinder.
  • each point of an axial contact surface has the same distance ("radius") from an axis (schematically shown in Figures 6b and 6c and denominated with reference numeral K) at which all the centers of curvature of the axial contact surfaces are located.
  • K is the center of curvature of the contour of the contact surface.
  • both contact surfaces 56, 58 have one and the same axis of curvature K.
  • the axis of curvature K is not located centrally between the axial contact surfaces 56, 58 but is arranged closer to axial contact surface 56.
  • the radius RY of axial contact surface 56 is smaller than the radius RX of axial contact surface 58.
  • a smaller radius for axial contact surface 56 allows using a larger radius for axial contact surface 58 which is beneficial in that axial contact surface 58 typically is exposed to larger forces than axial contact surface 56.
  • a larger radius results in a lower specific surface pressure.
  • the radius for axial contact surface 56 is chosen to be 2 mm while the radius for axial contact surface 58 is chosen to be 6 mm. Accordingly, the width of groove 42 (the distance between side walls 50, 52) is 8 mm.
  • protrusion 46 When the orientation of the swash plate is being changed (and thus the inclination angle is changed from a maximum inclination angle to a minimum inclination angle), protrusion 46 is displaced within groove 42 from an upper end (please see Figure 11a ) towards the lower end (please see Figure 11c ). At the same time, protrusion 46 is rotated within groove in a counterclockwise direction (with reference to Figures 11a to 11c ). Nevertheless, the effective diameter of protrusion 46 remains to be 8 mm.
  • Grooves 42 are arranged such that their longitudinal axis (schematically shown in Figure 7 and denominated with reference numeral B) extends with an angle ⁇ with respect to the drive shaft 34, with the angle ⁇ being between 60° and 70°.
  • Swash plate 24 together with hub 28 and male arms 44 is advanced in axial direction towards driving flange 32.
  • swash plate 24 together with hub 28 has to be tilted in a negative orientation (please see Figure 12b ).
  • This tilting in a counterclockwise direction is critical as it requires a larger clearance between drive shaft 34 and through hole 37 of hub 28 which is not necessary during normal operation of the compressor.
  • Using a small radius for axial contact surfaces 56 is advantageous in this regard as a smaller radius results in less necessary tilting in the negative direction (and thus requires a smaller clearance within the hub of swash plate 24).
  • the swash plate is returned into a neutral orientation (please see Figure 12c ), and stroking spring 38 can be mounted and fixed with a circlip 39. Then, mounting of the swash plate on drive shaft 34 is completed.
  • the smaller radius for the axial contact surface facing the swash plate has shown to reduce the negative tilt angle by nearly 40% (the exact value is 38%) as compared to a structure with identical radii on both sides.
  • the reduced negative angle additionally has shown to reduce the minimum clearance between the hub and the shaft in a vertical direction by nearly 50% (the exact value is 47%) as compared to a structure with identical radii on both sides.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
EP17198578.1A 2017-10-26 2017-10-26 Compresseur à déplacement variable, en particulier pour un circuit de réfrigérant d'un système de conditionnement d'air pour véhicule Withdrawn EP3477104A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP17198578.1A EP3477104A1 (fr) 2017-10-26 2017-10-26 Compresseur à déplacement variable, en particulier pour un circuit de réfrigérant d'un système de conditionnement d'air pour véhicule

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP17198578.1A EP3477104A1 (fr) 2017-10-26 2017-10-26 Compresseur à déplacement variable, en particulier pour un circuit de réfrigérant d'un système de conditionnement d'air pour véhicule

Publications (1)

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EP3477104A1 true EP3477104A1 (fr) 2019-05-01

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EP17198578.1A Withdrawn EP3477104A1 (fr) 2017-10-26 2017-10-26 Compresseur à déplacement variable, en particulier pour un circuit de réfrigérant d'un système de conditionnement d'air pour véhicule

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5364232A (en) * 1992-03-03 1994-11-15 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Variable displacement compressor
DE10011173A1 (de) * 1999-03-11 2000-09-21 Sanden Corp Schrägscheibenkompressor variabler Verdrängung
EP1041281A2 (fr) * 1999-04-02 2000-10-04 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Compresseur à capacité variable
JP2001041153A (ja) * 1999-07-23 2001-02-13 Zexel Valeo Climate Control Corp 可変容量型圧縮機

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5364232A (en) * 1992-03-03 1994-11-15 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Variable displacement compressor
DE10011173A1 (de) * 1999-03-11 2000-09-21 Sanden Corp Schrägscheibenkompressor variabler Verdrängung
EP1041281A2 (fr) * 1999-04-02 2000-10-04 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Compresseur à capacité variable
JP2001041153A (ja) * 1999-07-23 2001-02-13 Zexel Valeo Climate Control Corp 可変容量型圧縮機

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