US20010029837A1 - Hinge mechanism for variable displacement compressor - Google Patents

Hinge mechanism for variable displacement compressor Download PDF

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Publication number
US20010029837A1
US20010029837A1 US09/829,853 US82985301A US2001029837A1 US 20010029837 A1 US20010029837 A1 US 20010029837A1 US 82985301 A US82985301 A US 82985301A US 2001029837 A1 US2001029837 A1 US 2001029837A1
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US
United States
Prior art keywords
guide pin
cam plate
guide
swash plate
compressor
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.)
Abandoned
Application number
US09/829,853
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English (en)
Inventor
Hiroaki Kayukawa
Kiyohiro Yamada
Masanobu Tomita
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
Toyoda Jidoshokki Seisakusho KK
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 Toyoda Jidoshokki Seisakusho KK filed Critical Toyoda Jidoshokki Seisakusho KK
Assigned to KABUSHIKI KAISHA TOYODA JIDOSHOKKI SEISAKUSHO reassignment KABUSHIKI KAISHA TOYODA JIDOSHOKKI SEISAKUSHO ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: KAYUKAWA, HIROAKI, TOMITA, MASANOBU, YAMADA, KIYOHIRO
Publication of US20010029837A1 publication Critical patent/US20010029837A1/en
Abandoned 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
    • F04B27/1009—Distribution members
    • 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
    • F04B27/1081—Casings, housings
    • 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
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/06—Mobile combinations

Definitions

  • the present invention relates to a hinge mechanism in a variable displacement compressor suitable for vehicle air-conditioners and a guide pin used in such a hinge mechanism.
  • a typical variable displacement compressor includes a housing, which includes a cylinder block, and a drive shaft, which is supported by the housing.
  • a housing which includes a cylinder block, and a drive shaft, which is supported by the housing.
  • a plurality of bores are formed to surround the drive shaft, and a piston is located in each bore.
  • a swash plate is driven by on the drive shaft through a special hinge mechanism such that the swash plate rotates integrally with the drive shaft and inclines with respect to the drive shaft. When the inclination of the swash plate changes, the swash plate slides along the surface of the drive shaft in the axial direction.
  • Each piston is connected to the outer periphery of the swash plate. Rotation of the drive shaft is converted to reciprocating movement of the pistons, and suction and compression are performed in each of the cylinder bores.
  • the pressure in a crank chamber, in which the swash plate is located the inclination angle of the swash plate is controlled, and the stroke of the pistons and the discharge displacement are changed accordingly.
  • FIG. 9 shows one example of a hinge mechanism between a swash plate and a drive shaft.
  • the mechanism of FIG. 9 is from Japanese Unexamined Patent Publication No. Hei 11-93833.
  • a drive shaft 61 is fixed to a rotor 63 in a crank chamber 62 , and a pair of support arms 64 projects from the rotor 63 .
  • Guide holes 65 are formed in the support arms 64 , respectively.
  • a swash plate 66 is supported by the drive shaft 61 .
  • the swash plate 66 includes an aluminum based swash plate body 67 and an iron based swash plate guide 68 .
  • the swash plate body 67 is press fitted into the swash plate guide 68 .
  • the swash plate body 67 is connected to the pistons 70 via the shoes 69 , which slide on the periphery of the swash plate body 67 .
  • a pair of guide pins 71 extend from the swash plate 68 .
  • Each guide pins 71 includes a spherical portion 71 a , which is received by one of the guide holes 65 .
  • the support arms 64 , the guide holes 65 and the guide pins 71 form a hinge mechanism.
  • FIG. 9 A vibration axis of the swash plate 66 is represented by z, and the axis of the drive shaft 61 , which is perpendicular to the vibration axis z, is represented by y. An axis that is perpendicular to both the y and z axes is represented by x. The point of intersection of the axes is shown by an origin 0 .
  • the centrifugal force moment is obtained by multiplying the product of inertia Ixy of the swash plate 66 with respect to the xz plane and the yz plane by the square of the angular velocity with respect to the drive shaft 61 (refer to U.S. Pat. No. 5,573,379, which is incorporated herein by reference).
  • the dm represents mass of a minute component which forms the swash plate.
  • the swash plate 67 is made of an aluminum-based metal and is fitted into an iron based guide 68 , the distance from the plane of the swash plate body 67 to the spherical portion 71 a of the guide pin 71 in the axial direction increases by about 20% compared to a compressor where the entire swash plate 66 is formed of an iron-based metal, to ensure the press-fit strength of the swash plate 66 . As a result, the influence of the moment increases.
  • An object of the present invention is to provide a hinge mechanism of a variable displacement compressor capable of reducing pressure in a crank chamber which is necessary for changing displacement at a high speed rotation, capable of suppressing the occurrence of hunting and capable of reducing the power dissipation in a clutchless type compressor, and a guide pin suitable for the hinge mechanism.
  • a variable displacement compressor includes a housing including a cylinder bore, a piston accommodated in the cylinder bore, a drive shaft supported by the housing, a rotating support integrally fixed to the drive shaft, a cam plate and a hinge mechanism.
  • the cam plate is connected to the piston for converting rotational motion of the drive shaft to reciprocation of the piston.
  • the cam plate inclines with respect to the drive shaft.
  • the stroke of the piston changes to vary the discharge displacement of the compressor when the inclination of the cam plate changes.
  • the hinge mechanism is positioned between the rotating support and the cam plate.
  • the hinge mechanism includes a guide pin for transferring rotation of the rotating support to the cam plate and for permitting the inclination of the cam plate, wherein a part of the guide pin is hollow.
  • FIG. 1 is a cross-sectional view of a first embodiment of the present invention
  • FIGS. 2 ( a ), 2 ( b ), and 2 ( c ) are cross-sectional views of various guide pins
  • FIGS. 3 ( a ) and 3 ( b ) are schematic cross-sectional views illustrating swash plates
  • FIG. 4 is a graph showing a relationship between an inclination angle of the swash plate and moment
  • FIG. 5 is a partial cross-sectional view showing a hinge mechanism of a second embodiment
  • FIG. 6 is a partial plan view of the hinge mechanism of FIG. 5;
  • FIGS. 7 ( a ) and 7 ( b ) are cross-sectional views showing other embodiments of guide pins used in the compressor of the first embodiment, and FIG. 7( c ) is a perspective view of another embodiment of a guide pin;
  • FIG. 8( a ) is a cross-sectional view showing another embodiment of a guide pin used in a compressor of the second embodiment
  • FIG. 8( b ) is a perspective view showing a guide pin of still another embodiment
  • FIG. 9 is a partial cross-sectional view of a prior art variable displacement compressor.
  • variable displacement compressor of a vehicle air-conditioner of a first embodiment of the invention will be described with reference to FIGS. 1, 2, and 3 .
  • a compressor 10 includes a cylinder block 11 , a front housing member 12 , which is fixed to the front end of the cylinder block 11 , and a rear housing member 14 , which is fixed to the rear end of the cylinder block 11 through a valve plate 13 .
  • the housing members 12 , 14 , the valve plate 13 and the cylinder block 11 are secured to each other with a plurality of bolts 10 a (only one shown).
  • a crank chamber 15 is defined between the cylinder block 11 and the front housing member 12 .
  • a drive shaft 16 is supported in the cylinder block 11 and the front housing member 12 with bearings.
  • a lug plate 17 is fixed to the drive shaft 16 in the crank chamber 15 .
  • the lug plate 17 transmits thrust to an internal wall surface of the front housing member 12 through a thrust bearing 18 .
  • a swash plate 19 or cam plate, includes an aluminum-based swash plate body 20 and an iron-based swash plate guide 21 , and the swash plate body 20 is press fitted into the swash plate guide 21 .
  • burning between the swash plate 19 and an iron-based shoe 23 a is inhibited.
  • the weight of the swash plate 19 is limited.
  • the swash plate guide 21 is provided with a through hole 21 a , and the drive shaft 16 passes through the through hole 21 a .
  • a hinge mechanism 22 is located between the lug plate 17 and the swash plate 19 . Therefore, the swash plate 19 rotates in synchronization with the lug plate 17 and the drive shaft 16 , and the swash plate 19 can incline with respect to the drive shaft 16 while sliding on the drive shaft 16 in the axial direction.
  • the swash plate 21 includes a counterweight 21 b at a location that is opposite to the hinge mechanism 22 with respect to the drive shaft 16 .
  • a spring 16 a is fitted around the drive shaft 16 .
  • the spring 16 a urges the swash plate 19 toward the cylinder block 11 , that is, in the direction in which the inclination angle decreases.
  • a plurality of cylinder bores 11 a (only one shown in FIG. 1) is provided in the cylinder block 11 such that the bores 11 a are positioned at equal angular intervals.
  • a single-headed piston 23 is fitted in each of the cylinder bores 11 a .
  • the front openings of the cylinder bores 11 a are closed by the valve plate 13 , and a compressor chamber 11 b is defined in each cylinder bore 11 a .
  • the volume of the compressor 11 b varies depending on the position of the corresponding piston 23 .
  • Each piston 23 is connected to the periphery of the swash plate 19 through a pair of the shoes 23 a . Accordingly, the rotational motion of the swash plate 19 , which is produced by the rotation of the drive shaft 16 , is converted to reciprocating motion of the pistons 23 .
  • the drive shaft 16 is connected to an engine 25 through a power transmission mechanism 24 .
  • the power transmission mechanism 24 may be a clutch mechanism (for example, an electromagnetic clutch), which connects and disconnects power transmission and is externally controlled.
  • the power transmission mechanism 24 may be a clutchless (for example, the combination of a belt and a pulley).
  • the present embodiment has a clutchless type power transmission mechanism 24 .
  • a suction port 28 , a suction valve 29 , which opens and closes the suction port 28 , a discharge port 30 , and a discharge valve 31 , which opens and closes the discharge port 30 are formed in correspondence with each cylinder bore 11 a .
  • the suction chamber 26 and the discharge chamber 27 are connected to each other by an external refrigerant circuit 32 .
  • the cylinder block 11 , the valve plate 13 and the rear housing member 14 are provided with an air-supply passage 33 , which connects the crank chamber 15 and the discharge chamber 27 , and a bleed passage 34 , which connects the crank chamber 15 and the suction chamber 26 .
  • a control valve 35 is installed on the way of the supply passage 33 .
  • the control valve 35 is similar to the control valve disclosed in Japanese Unexamined Patent Publication No. Hei 9-268973, and includes a bellows, which moves in response to changes in the suction pressure, a solenoid, which produces electromagnetic force, and a valve mechanism, which controls the degree of opening of the supply passage 33 according to the displacement of the bellows and the electromagnetic force of the solenoid.
  • the parts of the control valve 35 are not shown.
  • the bellows are displaced so that the supply passage 33 is opened, and when the pressure in the suction chamber 26 is a predetermined value or more, the supply passage 33 is held in a closed state.
  • the discharge displacement of the compressor is adjusted by controlling the pressure (crank pressure) Pc in the crank chamber with the control valve 35 . That is, when the pressure in the suction chamber 26 is relatively low, the degree of opening of the control valve 35 is increased so that the crank pressure Pc is increased.
  • the inclination angle (angle formed by a plane perpendicular to the drive shaft 16 and the swash plate 19 ) of the swash plate 19 is decreased so that the stroke of each piston 23 is decreased and the discharge displacement is reduced.
  • the degree of opening of the control valve 35 is decreased so that the crank pressure Pc is lowered. Accordingly, the inclination angle of the swash plate 19 is increased so that the stroke of each piston 23 is increased and the discharge displacement is increased.
  • the hinge mechanism 22 has two supporting arms 36 (only one is shown), which extend from a rear surface of the lug plate 17 , a guide hole 37 formed in each of the supporting arms 36 , and two guide pins 38 , which are fixed to the swash plate 19 .
  • Each guide hole 37 is cylindrical.
  • the guide pins 38 are parallel, and an imaginary plane that includes the axis of the drive shaft 16 lies between the pins 38 .
  • One pin 38 corresponds to each supporting arm 36 .
  • the guide pins 38 are identical in shape and size, and are symmetrical with respect to the previously mentioned imaginary plane.
  • Each of the guide pins 38 includes a shaft portion 38 a attached to the swash plate 19 and a spherical portion 38 b formed at the distal end of the shaft portion 38 a .
  • the spherical portions 38 b engage the guide holes 37 .
  • Each spherical portion 38 b has a larger outer diameter than the shaft portion 38 a , and the distal end of each spherical portion 38 b is truncated along a plane. At least a portion of each spherical portion 38 b is hollow.
  • Each guide pin 38 is forged by use of, for example, a header or a former.
  • a hollow chamber 38 c in each guide pin 38 is opened at the distal end of the spherical portion 38 b .
  • the shape of the hollow chamber 38 c can be appropriately selected. For example, any one of many shapes such as a first shape, in which the hollow chamber 38 c extends to approximately the center of the spherical portion 38 b as shown in FIG. 2( a ), a second shape, in which the hollow chamber 38 c extends to the shaft portion 38 a as shown in FIG. 2( b ), and a third shape, in which the hollow chamber 38 c extends to the vicinity of the location where the shaft portion 38 a joins with the swash plate guide 21 as shown in FIG. 2( c ), can be selected.
  • FIGS. 2 ( a ), 2 ( b ) and 2 ( c ) decreases as indicated by the following inequality: FIG. 2( a )>FIG. 2( b )>FIG. 2( c ).
  • FIGS. 3 ( a ) and 3 ( b ) employ an xyz coordinate system. Additionally, a vibration axis of the swash plate 19 is represented by S. The axis of the drive shaft 16 , is represented by y. A z-axis is perpendicular to the plane of the sheet of FIG. 3( a ) and is parallel to the vibration axis S. An x-axis is perpendicular to both the y and z axes.
  • a point of intersection the x, y and z axes is defined as an origin point O.
  • the degree of opening of the control valve 35 is adjusted according to the cooling load.
  • the opening degree of the control valve 35 is reduced, and the pressure (crank pressure Pc) in the crank chamber 15 is decreased as a result, which increases the inclination angle of the swash plate 19 .
  • the stroke of each piston 23 is increased accordingly, and the compressor 10 operates with a large displacement.
  • the opening degree of the control valve 35 is increased and the pressure (crank pressure Pc) in the crank chamber 15 is increased so that the inclination angle of the swash plate 19 is decreased.
  • the stroke of the piston 23 is decreased, and the compressor 10 operates with a small displacement.
  • the moment that is generated by rotation of the swash plate 19 (the moment due to centrifugal force) is the product of inertia Ixy of the swash plate 19 with respect to the xz plane and the yz plane in the right-angled coordinate system (x, y, z) multiplied by the square of the angular velocity ⁇ of the drive shaft 16 .
  • y axis coincides with the axis of the drive shaft 16
  • the z axis is parallel to the vibration shaft S
  • the x axis is perpendicular to the y axis and the z axis.
  • the distance L is increased by about 20%, as shown in FIG. 3( a ), as compared with the swash plate 19 shown in FIG. 3( b ), which is an entirely iron-based swash plate.
  • the product of inertia Ixy of the swash plate 19 of FIG. 3( a ) is significantly increased compared with the swash plate 19 of FIG. 3( b ).
  • the hollow chambers 38 c are formed so that the masses of the front spherical portions 38 b of the guide pins 38 are decreased, even if the mass of the guide pins 38 are the same, the product of inertia Ixy is smaller than that of a swash plate lacking the hollow chambers 38 c . Further, the moment M based on the rotation of the swash plate 19 is smaller than the moment Mo of a conventional swash plate, as shown in FIG. 4. Thus, the crank pressure Pc necessary for changing the inclination angle of the swash plate 19 is reduced.
  • This embodiment has the following effects.
  • At least a part of the guide pin 38 is hollow.
  • the product of inertia of a portion of the guide pin 38 that influences the rotational moment rotation of the drive shaft 16 and the swash plate 19 is decreased.
  • the crank pressure Pc that is necessary for changing the displacement of a compressor can be reduced at a high rotation speeds, and hunting can be inhibitted.
  • the crank pressure Pc that is necessary for changing the displacement of a compressor can be reduced at a high rotation speeds, and hunting can be inhibitted.
  • the crank pressure Pc that is necessary for changing the displacement of a compressor can be reduced at a high rotation speeds, and hunting can be inhibitted.
  • the crank pressure Pc that is necessary for changing the displacement of a compressor can be reduced at a high rotation speeds, and hunting can be inhibitted.
  • the power of engine is transferred to the compressor.
  • the inclination angle of the swash plate 19 approaches zero degree so that power dissipation can be decreased.
  • a check valve is provided downstream of the discharge port of the compressor, the valve
  • the hollow chamber 38 c is opened at the distal end.
  • the product of inertia Ixy can be easily changed.
  • machining of the hollow chamber 38 c is relatively simple.
  • the guide pin is formed by forging. Therefore, the guide pin is stronger than a pin in which the hollow chamber 38 c of the guide pin 38 is formed by a cutting operation. In addition, if the guide pin is manufactured by a header or a former, productivity is higher.
  • the swash plate 19 is made of an aluminum based metallic swash plate body 20 and an iron based metallic swash plate guide 21 . Therefore, the entire swash plate 19 is lighter than an iron-based swash plate 19 .
  • the swash plate 19 is directly supported on the drive shaft 16 by the wall of the through hole 21 a .
  • the number of parts is low.
  • FIGS. 5 and 6 A second embodiment of the present invention will be described with reference to FIGS. 5 and 6.
  • the hinge mechanism 22 is different from that of the first embodiment.
  • the second embodiment is basically the same as the first embodiment. Therefore, parts that are the same are denoted by the same reference numerals, and only the differences will be explained.
  • a sleeve 39 is fitted on the drive shaft 16 and is permitted to slide on the drive shaft 16 .
  • a swash plate guide 21 is pivotally supported by a pair of supporting shafts 40 (only one shown) to the sleeve 39 .
  • the supporting shafts 40 extend perpendicular to the drive shaft 16 .
  • the hinge mechanism 22 includes two swing arms 41 that extend from the swash plate guide 21 toward the lug plate 17 .
  • a supporting arm 42 extends from on the lug plate 17 , and a guide pin 43 connects the swing arms 41 to the supporting arm 42 .
  • the swing arms 41 surrounds the supporting arm 42 as shown in FIG. 6.
  • a guide hole 44 is formed in the supporting arm 42 .
  • Each of the swing arms 41 has a mounting hole 45 , the axes of which are parallel to the supporting shaft 40 .
  • the guide pin 43 is press fitted into the mounting holes 45 and fitted into the guide hole 44 .
  • the guide hole 44 is elongated so that, even if the inclination angle of the swash plate is changed, the top dead center position, of the pistons 23 do not substantially change. That is, the guide hole 44 extends so that the closer the guide hole 44 is to the swash plate 19 , the further it is from the drive shaft 16 .
  • the guide pin 43 is a hollow cylinder.
  • this embodiment has the following effects in addition to the effects (1) to (7) described in the first embodiment.
  • the guide pin 43 which is part of the hinge mechanism 22 , moves along the guide hole 44 , and the sliding motion and inclination of the swash plate 19 are guided. Therefore, the guide pin 43 can have a simple linear shape, which further simplifies manufacturing.
  • the guide hole 44 is formed in the supporting arm 42 , and mounting holes 45 are formed in the swing arms 41 . Therefore, the structure of the swash plate 19 is simple as compared to a swash plate where the guide hole 44 is formed in the swing arm 41 .
  • the second embodiment is not limited to the structure described above, and may be constructed as follows for example.
  • the hollow chamber 38 c of the guide pin 38 may be formed in the shaft 38 a of the guide pin 38 , as shown in FIGS. 7 ( a ) and 7 ( b ).
  • a hollow chamber 38 c may be formed in the guide pin 38 and a slit 38 d may be formed in the shaft portion 38 a , as shown in FIG. 7( c ).
  • the outer diameter tolerance of the shaft portion 38 a may be increased.
  • the guide pin 43 may be formed such that a partition is formed in the hollow portion 43 a as shown in FIG. 8( a ).
  • the ends of the pin 43 may be formed by solid bodies, as shown in FIG. 8( b ), instead of the simple pipe shape of FIG. 5. The force on the guide pin 43 acts strongly on the ends of the guide pin 43 . However, when the ends of the guide pin 43 are solid, the strength of the guide pin 43 is improved.
  • the swash plate 19 may be pivotally connected to a sleeve 39 that is fitted on the drive shaft 16 , as in the second embodiment, through the supporting shafts 40 .
  • the swash plate 19 may be supported on the drive shaft 16 as in the first embodiment.
  • a spherical sleeve may be fitted on the drive shaft 16 , and the swash plate 19 may be pivotally supported on the outer surface of the spherical sleeve.
  • the hinge mechanisms of FIG. 1 and 6 have two joints. That is, two pins 38 couple with two holes 37 in FIG. 1, and two arms 41 form joints in FIG. 6. Alternatively, each hinge may have just one joint. However, two sets are preferable from the viewpoints of rotational balance and stability in the driving power transmission.
  • the swash plate 19 may be made of only one kind of metal, such as an iron based metal or the like. In this case, a press-fit margin is not needed, and the distance between the guide pin 38 and the xz plane can be decreased. Accordingly, the product of inertia Ixy can be further decreased by forming the guide pin 38 in a hollow shape.
  • a surface treatment for example, aluminum spray coating
  • the guide hole 44 may be formed in the swing arm 41
  • the mounting holes 45 may be formed in the supporting arm 42 .
  • the guide pin 38 may be manufactured by cutting or casting.
  • the present invention may be applied to a wobble type variable displacement compressor.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Rotary Pumps (AREA)
US09/829,853 2000-04-17 2001-04-10 Hinge mechanism for variable displacement compressor Abandoned US20010029837A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2000114806A JP2001295755A (ja) 2000-04-17 2000-04-17 可変容量圧縮機のガイドピン及び可変容量圧縮機
JP2000-114806 2000-04-17

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US20010029837A1 true US20010029837A1 (en) 2001-10-18

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US09/829,853 Abandoned US20010029837A1 (en) 2000-04-17 2001-04-10 Hinge mechanism for variable displacement compressor

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US (1) US20010029837A1 (ja)
EP (1) EP1148239A3 (ja)
JP (1) JP2001295755A (ja)
KR (1) KR20010096580A (ja)
CN (1) CN1318691A (ja)
BR (1) BR0101494A (ja)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6508634B2 (en) * 2000-07-17 2003-01-21 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Compressor utilizing spaces between cylinder bores
US20110164994A1 (en) * 2004-06-16 2011-07-07 Otfried Schwarzkopf Axial piston compressor, in particular a compressor for the air conditioning system of a motor vehicle
US9765764B2 (en) 2014-04-07 2017-09-19 Hanon Systems Hinge mechanism for a variable displacement compressor

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004027321A1 (de) * 2004-06-04 2005-12-22 Zexel Valeo Compressor Europe Gmbh Axialkolbenverdichter
JP5324936B2 (ja) * 2009-01-21 2013-10-23 サンデン株式会社 可変容量圧縮機及びその斜板最小傾角設定方法
JP6013768B2 (ja) * 2012-04-25 2016-10-25 サンデンホールディングス株式会社 可変容量圧縮機及びその製造方法
KR102112214B1 (ko) * 2017-09-14 2020-05-19 한온시스템 주식회사 가변 사판식 압축기

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3060670B2 (ja) * 1991-11-29 2000-07-10 株式会社豊田自動織機製作所 可変容量型揺動斜板式圧縮機
JP3082993B2 (ja) * 1992-05-12 2000-09-04 株式会社豊田自動織機製作所 容量可変型斜板式圧縮機
JP3182951B2 (ja) * 1992-12-28 2001-07-03 株式会社豊田自動織機製作所 クラッチレス揺動斜板式可変容量圧縮機

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6508634B2 (en) * 2000-07-17 2003-01-21 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Compressor utilizing spaces between cylinder bores
US20110164994A1 (en) * 2004-06-16 2011-07-07 Otfried Schwarzkopf Axial piston compressor, in particular a compressor for the air conditioning system of a motor vehicle
US8230773B2 (en) * 2004-06-16 2012-07-31 Valeo Compressor Europe Gmbh Axial piston compressor, in particular a compressor for the air conditioning system of a motor vehicle
US9765764B2 (en) 2014-04-07 2017-09-19 Hanon Systems Hinge mechanism for a variable displacement compressor

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BR0101494A (pt) 2001-11-13
JP2001295755A (ja) 2001-10-26
CN1318691A (zh) 2001-10-24
KR20010096580A (ko) 2001-11-07
EP1148239A2 (en) 2001-10-24
EP1148239A3 (en) 2004-02-25

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