EP1388668A2 - Hinge mechanism for a variable displacement compressor - Google Patents

Hinge mechanism for a variable displacement compressor Download PDF

Info

Publication number
EP1388668A2
EP1388668A2 EP03018032A EP03018032A EP1388668A2 EP 1388668 A2 EP1388668 A2 EP 1388668A2 EP 03018032 A EP03018032 A EP 03018032A EP 03018032 A EP03018032 A EP 03018032A EP 1388668 A2 EP1388668 A2 EP 1388668A2
Authority
EP
European Patent Office
Prior art keywords
hinge
rotor
hinge element
cam plate
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Withdrawn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
EP03018032A
Other languages
German (de)
English (en)
French (fr)
Inventor
Hajime Kurita
Hiroshi Uneyama
Tetsuhiko Fukanuma
Hiroaki Kayukawa
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Toyota Industries Corp
Original Assignee
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 EP1388668A2 publication Critical patent/EP1388668A2/en
Withdrawn legal-status Critical Current

Links

Images

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

Definitions

  • the present invention relates to a variable displacement piston type compressor for use in a vehicle air conditioner.
  • FIG. 14 illustrates a partially longitudinal cross-sectional view of a variable displacement compressor according to a prior art.
  • a housing 101 of the compressor defines a cylinder bore 101 a that accommodates a piston 102.
  • a drive shaft 103 is rotatably supported by the housing 101.
  • a rotor 104 is connected to the drive shaft 103 so as to rotate integrally therewith.
  • a swash plate 105 is supported by the drive shaft 103 so that it slides and inclines relative to the drive shaft 103.
  • the piston 102 engages the periphery of the swash plate 105 through a pair of shoes 107.
  • a hinge mechanism 108 is interposed between the rotor 104 and the swash plate 105.
  • the rotation of the drive shaft 103 is converted to the reciprocation of the piston 102 through the rotor 104, the hinge mechanism 108 and the swash plate 105, while the swash plate 105 is guided by the hinge mechanism 108 to slide on the drive shaft 103 in accordance with the inclination of the swash plate 105.
  • the displacement volume of the compressor is varied.
  • the hinge mechanism 108 includes a pair of first protrusions 108a (only one is shown in FIG. 14), a second protrusion 108b and a cam surface 108c.
  • the first protrusions 108a extend from the rotor 104 toward the swash plate 105.
  • the second protrusion 108b extends from the swash plate 105 toward the rotor 104.
  • the distal end of the second protrusion 108b is inserted between the first protrusions 108a.
  • the cam surface 108c is formed at the proximal portion of the first protrusions 108a.
  • the first protrusions 108a and the second protrusion 108b contact with a certain amount of area to engage each other so that the rotation of the rotor 104 is transmitted to the swash plate 105 through the hinge mechanism 108.
  • the distal end of the second protrusion 108b slidably contacts the cam surface 108c so that axial load that acts on the swash plate 105 due to compression reactive force is received by the cam surface 108c through the second protrusion 108b.
  • the first protrusions 108a and the second protrusion 108b are integrally formed with the rotor 104 and the swash plate 105, respectively.
  • An unwanted feature is that as the swash plate 105 inclines to twist the second protrusion 108b by the pair of first protrusions 108b due to offset axial load based upon the compression reactive force, sliding resistances increase between the side surfaces of the first protrusions 108a and the second protrusion 108b and between the distal end of the second protrusion 108b and the cam surface 108c due to the contact of the edge. This leads to early abrasion of each sliding surface.
  • a variable displacement compressor has a housing, a piston, a drive shaft, a rotor, a cam plate and a hinge mechanism.
  • the housing defines a cylinder bore.
  • the piston is accommodated in the cylinder bore.
  • the drive shaft is rotatably supported by the housing.
  • the rotor is connected to the drive shaft so as to rotate integrally with.
  • the cam plate is supported by the drive shaft so as to slide and incline relative to the drive shaft and is operatively connected to the piston.
  • the hinge mechanism is interposed between the rotor and the cam plate and guides the cam plate to incline and slide relative to the drive shaft.
  • the rotation of the drive shaft is converted to the reciprocation of the piston through the rotor, the hinge mechanism and the cam plate.
  • the hinge mechanism includes a first hinge element and a second hinge element.
  • the first hinge element is provided on the rotor.
  • the second hinge element is provided on the cam plate and is engaged with the first hinge element.
  • At least one of the first and second hinge elements has a degree of freedom for motion against the rotor and/or the cam plate to which the hinge element having the degree of freedom for motion belongs.
  • FIGs. 1 through 4 A first preferred embodiment of the present invention will now be described with reference to FIGs. 1 through 4.
  • the present invention is applied to a variable displacement compressor for a refrigerant circuit of a vehicle air conditioner in the first preferred embodiment.
  • the left side and the right side respectively correspond to the front side and the rear side of the compressor in FIG. 1.
  • FIG. 1 illustrates a longitudinal cross-sectional view of the variable displacement compressor according to the first preferred embodiment of the present invention.
  • a housing of the compressor includes a cylinder block 11, a front housing 12 and a rear housing 14.
  • the front housing 12 is fixedly connected to the front end of the cylinder block 11.
  • the rear housing 14 is fixedly connected to the rear end of the cylinder block 11 through a valve plate assembly 13.
  • a crank chamber 15 is defined between the cylinder block 11 and the front housing 12.
  • a drive shaft 16 is rotatably supported by the housing and extends through the crank chamber 15 from the front housing 12 to the cylinder block 11. The drive shaft 16 is rotated by the power transmitted from an engine (not shown) for traveling a vehicle.
  • a rotor 17 made of cast iron is fixedly connected to the drive shaft 16 so as to rotate integrally therewith.
  • the front end surface of the rotor 17 and the facing inner wall surface of the front housing 12 interpose a thrust bearing 35.
  • the crank chamber 15 accommodates a swash plate or a cam plate 18.
  • the swash plate 18 is made of iron series metal, such as iron and iron alloy.
  • the swash plate 18 is formed by forging.
  • a through hole 20 is formed at the center of the swash plate 18.
  • the drive shaft 16 extends through the through hole 20.
  • the swash plate 18 is supported by the drive shaft 16 through an inner surface 20a of the through hole 20 in such a manner that the swash plate 18 inclines and slides relative to the drive shaft 16.
  • a circular clip 32 is fitted on the drive shaft 16 on the rear side to the swash plate 18.
  • a coil spring 33 for increasing inclination angle of the swash plate 18 is arranged between the circular clip 32 and the swash plate 18 so as to urge the middle portion of the swash plate 18 forward.
  • a hinge mechanism 19 is interposed between the rotor 17 and the swash plate 18.
  • the hinge mechanism 19 includes a first hinge element 52 provided on the rotor 17 and a second hinge element 51 provided on the swash plate 18.
  • the swash plate 18 is coupled to the rotor 17 through the hinge mechanism 19 and is supported by the drive shaft 16 through the inner surface 20a of the though hole 20. Accordingly, the swash plate 18 is integrally rotatable with the rotor 17 and the drive shaft 16, while it is inclinable relative to the drive shaft 16 in accordance with sliding movement in the direction of the axis L of the drive shaft 16.
  • the inner surface 20a of the through hole 20 is treated by induction hardening for improving sliding performance against the drive shaft 16 and for improving abrasion resistance.
  • a plurality of cylinder bores 22 extends through the cylinder block 11 and is arranged around the axis L of the drive shaft 16 at equiangular positions.
  • Each of the cylinder bores 22 accommodates a single-headed piston 23 so as to be reciprocated therein.
  • the front and rear openings of each cylinder bore 22 are respectively closed by the top end surface of the piston 23 and the front end surface of the valve port assembly 13.
  • a compression chamber 24 is defined in each of the cylinder bores 22 and varies its volume in accordance with the reciprocation of the respective piston 23.
  • Each of the pistons 23 engages the outer periphery of the swash plate 18 through a pair of semispherical shoes 25. Accordingly, the rotation of the swash plate 18 in accordance with the rotation of the drive shaft 16 is converted to the reciprocation of the piston 23 through the shoes 25.
  • sliding surfaces 18b against the respective shoes 25 are treated by induction hardening for improving sliding performance against the shoes 25 and for improving abrasion resistance.
  • a suction chamber 26 and a discharge chamber 27 are defined between the valve plate assembly 13 and the rear housing 14.
  • the refrigerant gas in the suction chamber 26 is introduced into the compression chamber 24 through a suction port 28 and a suction valve 29 as each piston 23 moves from its top dead center to its bottom dead center.
  • the suction port 28 and the suction valve 29 are formed in the valve plate assembly 13.
  • the refrigerant gas in the compression chamber 24 is compressed to a predetermined pressure value as the piston 23 moves from the bottom dead center to the top dead center.
  • the compressed refrigerant gas is discharged to the discharge chamber 27 through a discharge port 30 and a discharge valve 31, which are formed in the valve plate assembly 13.
  • the compressor optionally varies its displacement volume and regulates its displacement volume in such a manner that a control valve 21 adjusts pressure in the crank chamber 15.
  • pressure differential between the crank chamber 15 and the compression chambers 24 is varied by the control valve 21 in response to variation of the pressure in the crank chamber 15.
  • the inclination angle of the swash plate 18 is varied, and the stroke of the piston 23 is adjusted.
  • the front end surface of the swash plate 18 has a portion 18a for regulating maximum inclination angle.
  • the portion 18a also serves as a balance weight.
  • the maximum inclination angle of the swash plate 18 is regulated in such a manner that the portion 18a contacts the rear end surface of the rotor 17, as shown in FIG. 1.
  • the swash plate 18 resists against the coil spring 33 to decrease its inclination angle.
  • the strokes of the pistons 23 decrease, and the displacement volume of the compressor decreases.
  • the minimum inclination angle of the swash plate 18 is regulated by the circular clip 32 and the coil spring 33.
  • FIG. 2 illustrates a side view of the hinge mechanism 19 according to the first preferred embodiment of the present invention.
  • FIG. 3 illustrates a plan view of the hinge mechanism 19 according to the first preferred embodiment of the present invention.
  • an engaging recess 41 is formed at the rear end of the rotor 17 and faces a point TDC of the swash plate 18.
  • the point TDC is a center of the hypothetical spherical surface of the shoes 25 when the piston 23 is positioned at a top dead center.
  • the engaging recess 41 is defined by a pair of first protrusions 43 that extend toward the swash plate 18.
  • the first protrusions 43 are respectively disposed at the rear end on a preceding side and on a following side in the rotational direction of the rotor 17.
  • a pair of second protrusions 44 extends toward the rotor 17 and is arranged at the front end of the swash plate 18 so as to face the engaging recess 41.
  • the second protrusions 44 are respectively disposed on a preceding side and on a following side in the rotational direction of the drive shaft 16 so as to interpose a hypothetical plane including the axis L and the point TDC.
  • Each of the distal ends of the second protrusions 44 fits into the engaging recess 41.
  • Each of the second protrusions 44 includes a side surface 44a that faces away from each other.
  • Each of the side surfaces 44a contacts a side surface 43a of the first protrusion 43 with a certain amount of area.
  • the side surfaces 43a partially form the inner surface of the engaging recess 41. Accordingly, the rotational power of the rotor 17 is transmitted to the swash plate 18 through one of the first protrusions 43 (the side surfaces 43a) and one of the second protrusions 44 (the side surfaces
  • the hinge mechanism 19 is symmetrically formed relative to the the hypothetical plane including TDC and the axis L along the rotational direction of the drive shaft 16 so as to appropriately respond either rotational direction of the drive shaft 16, even if a mounted engine rotates in either direction.
  • a cam portion 45 for receiving axial load is formed on the proximal portion of each first protrusion 43 in the engaging recess 41.
  • the cam portions 45 and the first protrusions 43 constitute the first hinge element 52 on the side of the rotor 17.
  • the rear end surface of each cam portion 45 facing the swash plate 18 forms a cam surface 45a that protrudes toward the rear side as it approaches the drive shaft 16.
  • Each of the second protrusions 44 forms a convex circular arc surface 44b and slidably contacts the cam surface 45a of the corresponding cam portion 45 by the circular arc surface 44b. Accordingly, the axial load that acts on the swash plate 18 due to the compression reactive force is received by the cam surfaces 45a of the cam portions 45 through the circular arc surfaces 44b of the second protrusions 44, respectively.
  • the hinge mechanism 108 includes the single and relatively large-scaled second protrusion 108b.
  • the second protrusion 108b of the prior art is divided into the two second protrusions 44.
  • the above structure ensures the same width for receiving axial load as that of the second protrusion 108b of the prior art and lightens the swash plate assembly 18, 51 by changing the structure of the second protrusion 108b of the prior art to a hollow structure.
  • the hinge mechanism 19 guides to increase the inclination angle of the swash plate 18.
  • the distal ends of the second protrusions 44 rotate around the central axis S of the circular arc surfaces 44b in the counterclockwise direction in FIG. 1, while they move on the cam surfaces 45a of the cam portions 45 to approach the drive shaft 16.
  • the hinge mechanism 19 guides to reduce the inclination angle of the swash plate 18.
  • first hinge element 52 and the second hinge element 51 slide on each other at sliding surfaces, such as the side surfaces 43a, 44a of the respective first and second protrusions 43, 44, the circular arc surfaces 44b of the respective second protrusions 44, and the cam surfaces 45a of the respective cam portions 45.
  • the above sliding surfaces are treated by induction hardening for improving their sliding performance and abrasion resistance.
  • the induction hardening may exclusively be treated at a portion including the side surfaces 44a and the circular arc surfaces 44b or may entirely be treated.
  • the former treatment restrains the distortion and crack of the second hinge element 51 of the swash plate 18 due to heat affection of the hardening.
  • the induction hardening may be treated only at portions including the side surfaces 43a and the cam surfaces 45a or may be treated at the entire first hinge element 52.
  • the former treatment restrains the distortion and crack of the first hinge element 52 due to heat affection of the hardening.
  • the second hinge element 51 is separately formed from the swash plate 18.
  • the second hinge element 51 includes a base plate or a base 47 and a pair of second protrusions 44 that extend from the front end surface of the base plate 47.
  • the swash plate 18 is made of iron series metal and is formed by forging.
  • the second hinge element 51 is made of aluminum series metal, such as aluminum and aluminum alloy. That is, the second hinge element 51 is made of different material from that of the swash plate 18, and the second protrusions 44 and the base plate 47 are integrally formed by forging or by molding.
  • the sliding surfaces 18b against the shoes 25 and the inner surface 20a of the through hole 20 are polished and treated by induction hardening before the second hinge element 51 is assembled to the swash plate 18.
  • a shaft 48 is integrally formed at the center of the rear end surface of the base plate 47 and extends vertically relative to the base plate 47.
  • a shaft hole 18c is recessed inwardly from the sliding surfaces 18b against the shoes 25 and extends in thickness of the swash plate 18.
  • the second hinge element 51 is loosely fitted into the shaft hole 18c of the swash plate 18 by the shaft 48.
  • the diagram illustrates the second hinge element 51 according to the first preferred embodiment of the present invention.
  • the second hinge element 51 is rotatable on the swash plate 18 relative to an axis M of the shaft 48 (or the shaft hole 18c).
  • the second hinge element 51 has the degree of freedom for rotation against the swash plate 18 to which the second hinge element 51 belongs.
  • the rotation of the second hinge element 51 is regulated in a predetermined angular range in such a manner that an end surface 47a of the base plate 47 near the drive shaft 16 contacts the wall surface of a step or a regulating means 18d formed on the front end surface of the swash plate 18.
  • a lightening recess 48a is formed at the distal end of the shaft 48 on the side near the drive shaft 16 so that the swash plate 18 avoids interfering with the coil spring 33 when positioned at the maximum inclination angle.
  • FIG. 5 A second preferred embodiment of the present invention will now be described with reference to FIG. 5.
  • the components that are different from those of the first preferred embodiment are only described.
  • the same reference numerals denote the substantially identical components to those of the first preferred embodiment, and the description is omitted.
  • FIG. 5 illustrates an enlarged longitudinal cross-sectional view of the hinge mechanism 19 according to the second preferred embodiment of the present invention.
  • the second hinge element 51 is integrally formed with the swash plate 18, while the first hinge element 52 is separately formed from the rotor 17.
  • the first hinge element 52 integrally forms a base plate 56, a pair of the first protrusions 43 and a pair of the cam portions 45.
  • the first protrusions 43 extend from the rear end surface of the base plate 56.
  • the cam portions 45 are formed on the proximal portions of the respective first protrusions 43.
  • the rotor 17 that is separately formed from the first hinge element 52 is simple and may apply forging as a manufacturing procedure.
  • the first hinge element 52 is loosely fitted into a shaft hole 17a at a shaft 55 thereof.
  • the shaft 55 extends from the front end surface of the base plate 56.
  • the shaft hole 17a is formed through the rotor 17. Accordingly, the first hinge element 52 is rotatable on the rotor 17 around the axis M of the shaft 55 (or the shaft hole 17a) that is parallel with the axis L of the drive shaft 16. Namely, the first hinge element 52 has the degree of freedom for rotation against the rotor 17.
  • the rotation of the first hinge element 52 is regulated in a predetermined angular range on the rotor 17 in such a manner that an end surface 56a facing the drive shaft 16 contacts the wall surface of the step 17b that is formed on the rotor 17.
  • the first hinge element 52 is rotatable on the rotor 17. Accordingly, even if the swash plate 18 inclines to twist the second protrusions 44 in the engaging recess 41 by the axial load due to the compression reactive force, stress due to the inclination rotates the first hinge element 52 around the axis M on the rotor 17 so as to prevent the swash plate 18 from twisting the second protrusions 44.
  • a third preferred embodiment of the present invention will now be described with reference to FIG. 6.
  • the components that are different from those of the first preferred embodiment are only described.
  • the same reference numerals denote the substantially identical components to those of the first preferred embodiment, and the description is omitted.
  • FIG. 6 illustrates a plan view of the hinge mechanism 19 according to the third preferred embodiment of the present invention.
  • the engaging recess 41 is formed between a pair of the second protrusions 44 in the second hinge element 51.
  • the rotor 17 includes the single first protrusion 43 at its rear end surface facing the engaging recess 41.
  • the first protrusion 43 extends toward the swash plate 18.
  • the distal end of the first protrusion 43 is inserted in the engaging recess 41.
  • the first protrusion 43 has a pair of side surfaces 43b, while each of the second protrusions 44 has a side surface 44c that is a part of the inner surface of the engaging recess 41.
  • the side surfaces 43b of the first protrusion 43 contact the side surfaces 44c with a certain amount of area. Accordingly, the rotational power of the rotor 17 is transmitted to the swash plate 18 through one of the side surfaces 43b of the first protrusion 43 and one of the side surfaces 44c of the respective second protrusions 44.
  • the second hinge element 51 includes the cam portion 45 at the proximal portions of the second protrusions 44 in the engaging recess 41.
  • the distal end of the first protrusion 43 forms a convex circular arc surface 43d and slidably contacts a cam surface 45c of the cam portion 45. Accordingly, the axial load that acts on the swash plate 18 due to the compression reactive force is received by the cam surface 45c of the cam portion 45.
  • a fourth preferred embodiment of the present invention will now be described with reference to FIG. 7.
  • the components that are different from those of the first preferred embodiment are only described.
  • the same reference numerals denote the substantially identical components to those of the first preferred embodiment, and the description is omitted.
  • FIG. 7 illustrates an enlarged side view of the hinge mechanism 19 according to the fourth preferred embodiment of the present invention.
  • the side surface 43a of the first protrusion 43 includes a guide groove 43c that extends along the direction of the cam surface 45a of the cam portion 45.
  • the side surface 44a of the second protrusion 44 includes a guide protrusion 44d on the central axis S of the circular arc surface 44b, and the guide protrusion 44d is engagedly inserted in the guide groove 43c for guiding the swash plate 18 to incline and slide relative to the drive shaft 16.
  • the swash plate assembly 18, 51 engages the rotor 17 by the engagement between the guide groove 43c and the guide protrusion 44d. As a result, the swash plate assembly 18, 51 is prevented from rattling due to vibration of a vehicle, with a consequence of preventing noise generated on the compressor.
  • a fifth preferred embodiment of the present invention will now be described with reference to FIG. 8.
  • the components that are different from those of the first preferred embodiment are only described.
  • the same reference numerals denote the substantially identical components to those of the first preferred embodiment, and the description is omitted.
  • FIG. 8 illustrates an enlarged longitudinal cross-sectional view of the hinge mechanism 19 according to the fifth preferred embodiment of the present invention.
  • a slider 57 is interposed between the circular arc surface 44b of the second protrusion 44 and the cam surface 45a of the cam portion 45. Namely, the second protrusion 44 (the circular arc surface 44b) and the cam portion 45 (the cam surface 45a) slidably contact each other through the slider 57.
  • the slider 57 includes a concave circular arc surface 57a and a planar surface 57b.
  • the concave circular arc surface 57a slides on the circular arc surface 44b of the second protrusion 44.
  • the planar surface 57b slides on the cam surface 45a. Accordingly, the cam portion 45 and the slider 57 contact each other with a certain amount of area, and the second protrusion 44 and the slider 57 contact each other with a certain amount of area.
  • the areal contacts reduce abrasion of the cam surface 45a and the circular arc surface 44b. That is, the areal contacts contribute to improved durability of the hinge mechanism 19.
  • FIG. 9 A sixth preferred embodiment of the present invention will now be described with reference to FIG. 9.
  • the components that are different from those of the first preferred embodiment are only described.
  • the same reference numerals denote the substantially identical components to those of the first preferred embodiment, and the description is omitted.
  • FIG. 9 illustrates a plan view of the hinge mechanism 19 according to the sixth preferred embodiment of the present invention.
  • the drive shaft 16 rotates in the direction of an arrow R
  • the hinge mechanism 19 is particularly configured to appropriately handle a state when the drive shaft 16 rotates in the direction of the arrow R.
  • a cam portion 45A and a second protrusion 44A shown in the lower side of FIG. 9 in a compression cycle mainly receive the axial load that acts on the swash plate 18 based upon the compression reactive force, while the first protrusion 43 and another second protrusion 44B shown in the upper side of FIG. 9 in a suction cycle transmit power from the rotor 17 to the swash plate 18. Then, with respect to the second protrusions 44A, 44B, when absolute amount of load, variation of the load and its variation rate are considered, the second protrusion 44A for receiving the axial load is hard in strength than the second protrusion 44B for power transmission.
  • the cam surface 45a of the cam portion 45A for receiving the axial load is widened than the cam surface 45a of the cam portion 45B for power transmission, while the second protrusion 44A for receiving the axial load is thicker than the second protrusion 44B for power transmission.
  • the width of the circular arc surface 44b of the second protrusion 44A is predetermined to be wide. Accordingly, the strength of the second protrusion 44A for receiving the axial load is improved. In comparison to the thickened second protrusions 44A, 44B, an increase in weight is relatively small, while durability of the hinge mechanism 19 is ensured at equivalent level in the sixth preferred embodiment.
  • a seventh preferred embodiment of the present invention will now be described with reference to FIGs. 10 and 11.
  • the components that are different from those of the first preferred embodiment are only described.
  • the same reference numerals denote the substantially identical components to those of the first preferred embodiment, and the description is omitted.
  • FIG. 10 illustrates an enlarged longitudinal cross-sectional view of the hinge mechanism 19 according to the seventh preferred embodiment of the present invention.
  • FIG. 11 illustrates an enlarged perspective view of the hinge mechanism 19 according to the seventh preferred embodiment of the present invention.
  • a slider 60 is supported by the drive shaft 16 so as to slide in the direction of the axis L.
  • a fulcrum shaft 60a is formed with the slider 60 and inclinably supports the swash plate 18.
  • the cam portion 45 is omitted from the first hinge element 52, and the first and second hinge elements 52, 51 engage each other through link arms 61.
  • the second hinge element 51 includes the single second protrusion 44.
  • An insertion hole 44e is formed through the distal end of the second protrusion 44 in the direction perpendicular to the axis L of the drive shaft 16.
  • the first hinge element 52 includes the single first protrusion 43 that radially extends from the outer periphery of the rotor 17.
  • An insertion hole 43e is formed through the distal end of the first protrusion 43 in the direction perpendicular to the axis L of the drive shaft 16.
  • a pair of the link arms 61 is arranged on each side of the distal ends of the first and second protrusions 43, 44 and each of the link arms 61 has through holes 61 a, 61b at both ends.
  • One end of each link arm 61 is pivotally supported through the through hole 61a by a pin 62 that is inserted into the through hole 43e of the first protrusion 43.
  • the other end of each link arm 61 is pivotally supported through the through hole 61b by another pin 63 that is inserted through the through hole 44e of the second protrusion 44. Accordingly, the swash plate 18 inclines around the pins 62, 63 in accordance with slide on the drive shaft 16.
  • the second hinge element 51 is rotatable on the swash plate 18. Accordingly, even if the swash plate 18 inclines to twist the second protrusion 44 between the link arms 61 by the axial load due to the compression reactive force, stress due to the inclination rotates the second hinge element 51 around the axis M on the swash plate 18 so as to prevent the second protrusion 44 from twisting between the link arms 61.
  • FIGs. 12 and 13 An eighth preferred embodiment of the present invention will now be described with reference to FIGs. 12 and 13. The components that are different from those of the first preferred embodiment are only described. The same reference numerals denote the substantially identical components to those of the first preferred embodiment, and the description is omitted.
  • FIG. 12 illustrates a longitudinal cross-sectional view of the hinge mechanism 19 according to the eighth preferred embodiment of the present invention.
  • FIG. 13 illustrates a plan view of the hinge mechanism 19 according to the eighth preferred embodiment of the present invention.
  • the second hinge element 51 includes the single second protrusion 44.
  • a through hole 44f is formed through the distal end of the second protrusion 44.
  • a pin 65 is fixedly inserted into the through hole 44f in the direction perpendicular to the axis L of the drive shaft 16.
  • a cam groove 43f is formed in each of the first protrusions 43.
  • the second protrusion 44 is inserted in between the first protrusions 43 so as to permit power transmission from the rotor 17 to the swash plate 18 by contacting the side surfaces 43a, 44a through a washer 67 and to slidably contact the inner surface of the cam groove 43f by a cylindrical surface 65a of both sides of the pin 65 that is inserted into the cam groove 43f.
  • the hinge mechanism 19 guides to increase the inclination angle of the swash plate 18 in such a manner that the pin 65 (the cylindrical surface 65a) moves away from the drive shaft 16 along the inner surface of the cam groove 43f on the side of the rotor 17, while the distal end of the second protrusion 44 rotates around a central axis of the pin 65.
  • the second hinge element 51 is rotatable on the swash plate 18. Accordingly, even if the swash plate 18 inclines to twist the second protrusion 44 between the first protrusions 43 and also inclines to twist the pin 65 in the cam groove 43f by the axial load due to the compression reactive force, stress due to the inclination rotates the second hinge element 51 around the axis M on the swash plate 18 so as to avoid their twisting.
  • the second hinge element 51 is made of iron series sintered metal.
  • the first hinge element 52 is made of iron series sintered metal. Accordingly, the sintered metal effectively holds lubricating oil so that sliding performance and seizure resistance improve between the first and second hinge elements 52, 51. Incidentally, the lubricating oil is supplied to the crank chamber 15 with its mist contained in the refrigerant gas.
  • the second hinge element 51 is rotatable on the swash plate 18, while the first hinge element 52 is rotatable on the rotor 17.
  • the first protrusion 43 is only rotatable on the rotor 17 in the components 43, 45 of the first hinge element 52, while the cam portion 45 is fixed to the rotor 17.
  • the second protrusion 44 is only rotatable on the swash plate 18 in the components 44, 45 of the second hinge element 51, while the cam portion 45 is fixed to the swash plate 18.
  • a plurality of the second protrusions 44 is separately formed, and each of the second protrusions 44 is individually rotatable on the swash plate 18.
  • a plane bearing or a rolling bearing is interposed between the shaft portion 48 or 55 and the shaft hole 18c or 17a, respectively.
  • solid lubricant such as fluororesin and molybdenum disulfide is applied on at least one of the outer circumferential surface of the shaft portion 48 or 55 and the inner circumferential surface of the shaft hole 18c or 17a, respectively.
  • At least one of the first and second hinge elements 52, 51 includes a shaft hole, while the rotor 17 or the swash plate 18 on which the hinge element is arranged includes a shaft portion. Also, a pair of the first hinge element 52 and the rotor 17 or a pair of the second hinge element 51 and the swash plate 18 respectively includes shaft holes, and a shaft member is interposed between the shaft holes by inserting the shaft member into the shaft holes.
  • the first hinge element 52 or the second hinge element 51 has the degree of freedom for slide relative to the rotor 17 or the swash plate 18, respectively.
  • At least one of the first and second hinge elements 52, 51 has two dimensional degree of freedom for motion against the rotor 17 or the swash plate 18 on which the hinge element is arranged.
  • one of the first and second hinge elements 52, 51 has the degree of freedom for rotation and for slide relative to the rotor 17 or the swash plate 18, respectively.
  • an engaging groove is recessed in a merely disc-shaped rotor (for example, the shape from which the first and second hinge elements 52, 51 are omitted in the above preferred embodiments) or a disc of a swash plate.
  • the compressor is a variable displacement compressor that has a double-headed piston.
  • the compressor is a wobble type variable displacement compressor that has a wobble plate or a cam plate.
  • a variable displacement compressor has a housing, a piston, a drive shaft, a rotor, a cam plate and a hinge mechanism.
  • the hinge mechanism between the rotor and the cam plate guides the cam plate to incline and slide relative to the drive shaft.
  • the rotation of the drive shaft is converted to the reciprocation of the piston through the rotor, the hinge mechanism and the cam plate.
  • the hinge mechanism includes first and second hinge elements that are respectively provided on the rotor and on the cam plate and engage each other. At least one of the first and second hinge elements has a degree of freedom for motion against the rotor and/or the cam plate to which it belongs.
EP03018032A 2002-08-08 2003-08-07 Hinge mechanism for a variable displacement compressor Withdrawn EP1388668A2 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2002231651 2002-08-08
JP2002231651A JP2004068757A (ja) 2002-08-08 2002-08-08 容量可変型圧縮機

Publications (1)

Publication Number Publication Date
EP1388668A2 true EP1388668A2 (en) 2004-02-11

Family

ID=30437775

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03018032A Withdrawn EP1388668A2 (en) 2002-08-08 2003-08-07 Hinge mechanism for a variable displacement compressor

Country Status (3)

Country Link
US (1) US20040055456A1 (ja)
EP (1) EP1388668A2 (ja)
JP (1) JP2004068757A (ja)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1607630A1 (de) * 2004-06-14 2005-12-21 Obrist Engineering GmbH Hubkolbenkompressor

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2005299516A (ja) * 2004-04-12 2005-10-27 Calsonic Kansei Corp リンク機構およびこれを用いた可変容量圧縮機
JP2006105007A (ja) * 2004-10-04 2006-04-20 Toyota Industries Corp 可変容量型圧縮機における容量制御機構
JP2006242120A (ja) * 2005-03-04 2006-09-14 Toyota Industries Corp 容量可変型斜板式圧縮機
US7455009B2 (en) * 2006-06-09 2008-11-25 Visteon Global Technologies, Inc. Hinge for a variable displacement compressor
JP2009068358A (ja) * 2007-09-11 2009-04-02 Toyota Industries Corp 容量可変型斜板式圧縮機
US8196506B2 (en) * 2009-08-17 2012-06-12 Delphi Technologies, Inc. Variable stroke compressor design
KR101907696B1 (ko) * 2012-06-22 2018-10-15 학교법인 두원학원 용량가변형 사판식 압축기
WO2016013558A1 (ja) * 2014-07-23 2016-01-28 Ntn株式会社 斜板式コンプレッサの半球シューおよび斜板式コンプレッサ
KR20200080821A (ko) * 2018-12-27 2020-07-07 한온시스템 주식회사 사판식 압축기

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0261588U (ja) * 1988-10-24 1990-05-08
US5228841A (en) * 1991-03-28 1993-07-20 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Variable capacity single headed piston swash plate type compressor having piston abrasion preventing means
JP3422186B2 (ja) * 1995-11-24 2003-06-30 株式会社豊田自動織機 可変容量圧縮機
JPH10196539A (ja) * 1997-01-17 1998-07-31 Zexel Corp 往復式圧縮機
JPH11201032A (ja) * 1998-01-13 1999-07-27 Toyota Autom Loom Works Ltd 可変容量型圧縮機
JP2000320454A (ja) * 1999-05-13 2000-11-21 Toyota Autom Loom Works Ltd 可変容量圧縮機
JP4332294B2 (ja) * 2000-12-18 2009-09-16 サンデン株式会社 片頭斜板式圧縮機の製造方法

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1607630A1 (de) * 2004-06-14 2005-12-21 Obrist Engineering GmbH Hubkolbenkompressor
KR100700861B1 (ko) 2004-06-14 2007-03-29 오브리스트 엔지니어링 게엠베하 왕복 운동하는 피스톤 압축기

Also Published As

Publication number Publication date
US20040055456A1 (en) 2004-03-25
JP2004068757A (ja) 2004-03-04

Similar Documents

Publication Publication Date Title
EP0775824A1 (en) Variable displacement compressor
US5644968A (en) Variable capacity swash plate type compressor with an improved hinge unit for inclinably supporting a swash plate
US6932582B2 (en) Vibration damping mechanism for piston type compressor
KR100660666B1 (ko) 가변용량 압축기
US6116145A (en) Variable displacement compressor
EP1394411B1 (en) Swash plate type variable displacement compressor
EP1388668A2 (en) Hinge mechanism for a variable displacement compressor
US6786705B2 (en) Variable displacement compressor
US6276904B1 (en) Variable capacity refrigerant compressor having an inclination limiting means to interrupt compressive forces on a hinge mechanism
US5882179A (en) Compressor with bearing between the drive shaft and the swash-plate boss
US6446540B1 (en) Bearing for swash plate compressor
KR20090052867A (ko) 가변 용량 압축기
US5771775A (en) Device for guiding a piston
EP1531266B1 (en) Variable displacement compressor
US20040202551A1 (en) Variable displacement compressor
JP2004068756A (ja) 容量可変型圧縮機
US20060222513A1 (en) Swash plate type variable displacement compressor
KR100519745B1 (ko) 용량가변형 사판식 압축기
JPH02267371A (ja) 可変容量型斜板式圧縮機
US20010042438A1 (en) Piston for swash plate type compressor
KR100196246B1 (ko) 용량 가변형 경사판식 압축기
JPH08109875A (ja) 斜板式コンプレッサ
EP1039128A2 (en) Swash plate type compressor
US6386090B2 (en) Piston type compressor
US6979182B2 (en) Vibration damping mechanism for piston type compressor

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20030807

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LI LU MC NL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL LT LV MK

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION HAS BEEN WITHDRAWN

18W Application withdrawn

Effective date: 20050128