WO2007046580A1 - Variable capacity swash plate type compressor - Google Patents

Variable capacity swash plate type compressor Download PDF

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Publication number
WO2007046580A1
WO2007046580A1 PCT/KR2006/003190 KR2006003190W WO2007046580A1 WO 2007046580 A1 WO2007046580 A1 WO 2007046580A1 KR 2006003190 W KR2006003190 W KR 2006003190W WO 2007046580 A1 WO2007046580 A1 WO 2007046580A1
Authority
WO
WIPO (PCT)
Prior art keywords
swash plate
inclination angle
hub
stopper
driving shaft
Prior art date
Application number
PCT/KR2006/003190
Other languages
French (fr)
Inventor
Hewnam Ahn
Original Assignee
Halla Climate Control Corporation
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 Halla Climate Control Corporation filed Critical Halla Climate Control Corporation
Priority to US11/989,405 priority Critical patent/US20090148312A1/en
Priority to CN2006800332941A priority patent/CN101278124B/en
Publication of WO2007046580A1 publication Critical patent/WO2007046580A1/en

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/1054—Actuating elements
    • F04B27/1072—Pivot mechanisms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/1045—Cylinders
    • 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
    • F04B27/0873—Component parts, e.g. sealings; Manufacturing or assembly thereof
    • F04B27/0878—Pistons
    • 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
    • F04B27/1018—Cylindrical 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
    • 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
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F1/00—Springs
    • F16F1/02—Springs made of steel or other material having low internal friction; Wound, torsion, leaf, cup, ring or the like springs, the material of the spring not being relevant
    • F16F1/04—Wound springs
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/12—Kind or type gaseous, i.e. compressible
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/14—Refrigerants with particular properties, e.g. HFC-134a
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S417/00—Pumps

Definitions

  • the present invention relates to a variable capacity swash plate type compressor, and more particularly, to a variable capacity swash plate type compressor, which has a stopper protruding from the inner surface of a hub and being in contact with a sleeve when a swash plate is at the maximum inclination angle to shorten a stroke distance of the stopper for supporting the maximum inclination angle of the swash plate, thereby reducing a hitting noise when the stopper is moved at the maximum inclination angle and when an air conditioner is turned off.
  • a compressor constituting an air conditioning system for an automobile is a device to selectively receive driving power from a power source by a restricting action of an electromagnetic clutch, compress refrigerant gas by a straight reciprocating motion of pistons after absorbing the refrigerant gas from an evaporator, and discharge it toward a condenser.
  • Such a compressor is classified into various kinds according to compression methods and structures, and out of the compressors of the various kinds, a variable capacity compressor, which can vary a compression volume, has been widely used.
  • the variable capacity swash plate type compressor 1 includes: a cylinder block 10 having a plurality of cylinder bores 11 axially formed inside the cylinder block 10 along a concentric circle; a front housing 20 mounted on the front of the cylinder block 10 and having a crank chamber 21 formed therein; a rear housing 30 mounted on the rear of the cylinder block 10 and having a suction chamber 31 and a discharge chamber 32 formed therein; a plurality of pistons 40 reciprocatingly inserted into each of the cylinder bores 11 of the cylinder block 10 and having a bridge 41 at the rear end portion thereof; a driving shaft 50 having an end portion rotatably passing through the front housing 20 and the other end portion inserted and rotatably mounted into the center of the cylinder block 10; a rotor 60 combined to the driving shaft 50 and rotating with the driving shaft 50 inside the crank chamber 21; a swash plate 70 mounted on the circumference of the driving shaft 50 by slidably combining a sleeve 65, having an edge rotat
  • the inclination angle of the swash plate 70 against the driving shaft 50 can be adjusted according to a pressure change inside the crank chamber 21 by a control valve 90 mounted in the rear housing 30.
  • the rotor 60 has a slot 62 formed on the hinge arm 61 thereof, and a connection hinge arm 73 having a hinge pin 74 is formed on a hub 71 of the swash plate 70, which is faced to the hinge arm 61 of the rotor 60.
  • the connection hinge arm 73 protrudes toward both sides of the hinge arm 61 and is movably combined to the slot 62 of the hinge arm 61.
  • variable capacity swash plate type compressor 1 a plurality of the pistons 40 arranged along the concentric circle of the cylinder block 10 perform the forward and backward reciprocating motion in order by the rotation of the swash plate 70.
  • a suction valve (not shown) of the valve unit 80 is opened by a drop of pressure inside the cylinder bore 11, whereby the cylinder bore 11 and the suction chamber 31 are fluidically communicated with each other and the refrigerant is induced from the suction chamber 31 into the cylinder bore 11.
  • valve unit 80 is opened while the refrigerant is compressed by a rise of pressure inside the cylinder bore 11, whereby the cylinder bore 11 and the discharge chamber 32 are fluidically communicated with each other and the compressed refrigerant is discharged from the cylinder bore 11 into the discharge chamber 32.
  • the swash plate 70 adjusts its inclination angle in correspondence to a difference between pressure inside the crank chamber 21 and suction pressure inside the cylinder bores 11, whereby a discharge volume of the compressor 1 is varied.
  • the hub 71 of the swash plate 70 has a stopper 72 formed oppositely to the connection hinge arm 73 to support the maximum inclination angle of the swash plate 70.
  • variable capacity swash plate type compressor which has a stopper protruding from the inner surface of a hub and being in contact with a sleeve when a swash plate is at the maximum inclination angle to shorten a stroke distance of the stopper for supporting the maximum inclination angle of the swash plate, thereby reducing a hitting noise when the stopper is moved at the maximum inclination angle and when an air conditioner is turned off.
  • the present invention provides a variable capacity swash plate type compressor including: a cylinder block having a plurality of cylinder bores therein; a front housing mounted on the front of the cylinder block and having a crank chamber therein, and a rear housing mounted on the rear of the cylinder block and having a suction chamber and a discharge chamber therein; a driving shaft rotatably mounted on the cylinder block and the front housing; a rotor combined to the driving shaft and rotating together with the driving shaft inside the crank chamber; a swash plate having a hub movably connected to a hinge arm of the rotor and a swash plate board combined to the hub, the hub being rotatably combined to a sleeve which is slidably combined to the driving shaft, the swash plate varying its inclination angle in correspondence to a pressure change of the crank chamber; and a spring mounted on the driving shaft located between the rotor and the swash plate for returning the swash plate to the initial
  • FIG. 1 is a sectional view of a prior art variable capacity swash plate type compressor.
  • FIG. 2 is a sectional view of a variable capacity swash plate type compressor according to the present invention.
  • FIG. 3 is a perspective view showing a state where a swash plate and a rotor are disassembled from the compressor of FIG. 2.
  • FIG. 4 is a sectional view showing a state when an inclination angle of the swash plate is at the minimum angle in the variable capacity swash plate type compressor according to the present invention.
  • FIG. 5 is a sectional view showing a state when an inclination angle of the swash plate is at the maximum angle in the variable capacity swash plate type compressor according to the present invention.
  • FIG. 6 is a view for explaining a formed position of a stopper in the variable capacity swash plate type compressor according to the present invention.
  • FIG. 2 is a sectional view of a variable capacity swash plate type compressor according to the present invention
  • FIG. 3 is a perspective view showing a state where a swash plate and a rotor are disassembled from the compressor of FIG. 2
  • FIG. 4 is a sectional view showing a state when an inclination angle of the swash plate is at the minimum angle in the variable capacity swash plate type compressor according to the present invention
  • FIG. 5 is a sectional view showing a state when an inclination angle of the swash plate is at the maximum angle in the variable capacity swash plate type compressor according to the present invention
  • FIG. 6 is a view for explaining a formed position of a stopper in the variable capacity swash plate type compressor according to the present invention.
  • variable capacity swash plate type compressor 100 includes: a cylinder block 110 having a plurality of cylinder bores 11 axially formed on a concentric circle thereof; a front housing 120 mounted on the front of the cylinder block 110 and having a crank chamber 121 formed therein; and a rear housing 130 mounted on the rear of the cylinder block 110 and having a suction chamber 131 and a discharge chamber 132 therein.
  • a plurality of pistons 140 having a bridge 141 at the rear end thereof are recip- rocatingly inserted and mounted to each of the cylinder bores 111 of the cylinder block 110.
  • a driving shaft 150 has an end portion rotatably passing through the front housing 120 and the other end portion inserted into the center of the cylinder block 110 in such a way as to be rotatably supported on the center of the cylinder block 110.
  • a rotor 160 is combined to the driving shaft 150 and rotated together with the driving shaft 150 inside the crank chamber 121.
  • a swash plate 170 is rotatably mounted on a sleeve 165 which is slidably combined to the driving shaft 150 inside the crank chamber 121, has an edge rotatably mounted to an insertion space of the piston bridge 141 by interposing a shoe 145 between the insertion space and the swash plate, and is movably connected to a hinge arm 161 of the rotor 160, whereby the swash plate 170 adjusts its inclination angle against the driving shaft 150 while being rotated together with the rotor 160.
  • the swash plate 170 includes a hub 171 movably connected to the hinge arm
  • the rotor 160 has a slot 162 formed on the hinge arm 161 thereof, and a connection hinge arm 173 having a hinge pin 174 is formed on the hub 171 of the swash plate 170, which is faced to the hinge arm 161 of the rotor 160.
  • the connection hinge arm 173 protrudes toward both sides of the hinge arm 161 and is movably combined to the slot 162 of the hinge arm 161.
  • the hinge pin 174 supports an inclination motion of the swash plate 170 while sliding along the slot 162.
  • a valve unit 180 is mounted between the cylinder block 110 and the rear housing 130 to inhale refrigerant from the suction chamber 131 into the cylinder bores 111 during a suction stroke and discharge compressed refrigerant from the cylinder bores 111 into the discharge chamber 132 during a compression stroke.
  • a control valve 190 is mounted in the rear housing 130 to operationally fluidically communicate the discharge chamber 132 and the crank chamber 121 with each other, whereby pressure difference between refrigerant suction pressure inside the cylinder bore 111 and gas pressure inside the crank chamber 121 is varied to adjust the inclination angle of the swash plate 170.
  • a compression coil spring 155 is mounted on the driving shaft 150 located between the rotor 160 and the swash plate 170 to return the swash plate 170 to the initial position.
  • maximum inclination angle supporting means 175 is mounted between the hub 171 and the sleeve 165 to reduce the hitting noise by supporting the maximum inclination angle of the swash plate 170 when the air conditioner is turned off.
  • the maximum inclination angle supporting means 175 has a stopper 176 protruding on the inner surface of the hub 171 or the outer surface of the sleeve 165, so that the stopper 176 is in contact with the outer surface of the sleeve 165 or the inner surface of the hub 171 when the swash plate 170 is at the maximum inclination angle.
  • the stopper 176 is formed on the inner surface of the hub 171, but may be formed on the outer surface of the sleeve 165.
  • the stopper 176 is formed on a connection line (LC) passing a position (Pl) of the swash plate 170 corresponding with the center of the cylinder bore 111, which is in the maximum compression stroke state, and a center (P2) of the driving shaft 150.
  • LC connection line
  • the stopper 176 is axially eccentric on the inner surface of the hub 171.
  • the stopper 176 is formed on the upper portion of the inner surface of the hub 171 in the drawing, but may be formed on the lower portion of the hub 171.
  • the stopper 176 has an end portion spaced apart at a predetermined distance from the outer surface of the sleeve 165, and is in contact with the sleeve 165 only when the swash plate 170 is at the maximum inclination angle to restrict and support the maximum inclination angle of the swash plate 170.
  • the stopper 176 can be integrally or detachably formed on the inner surface of the hub 171.
  • the stopper 176 is formed on the inner surface of the hub 171 facing to the outer surface of the sleeve 165, whereby the inclination angle of the swash plate 170 is increased and the compression coil spring 155 is gradually compressed when the compressor 100 is in a condition of the maximum inclination angle.
  • the stopper 176 formed on the inner surface of the hub 171 is in contact with the outer surface of the sleeve 165 to support the maximum inclination angle of the swash plate 170 and to prevent a further increase of the inclination angle of the swash plate 170.
  • the present invention can reduce a hitting noise when the stopper is moved at the maximum inclination angle and when an air conditioner is turned off, since the stopper is formed on the inner surface of the hub and is in contact with the sleeve when the swash plate is at the maximum inclination angle to shorten the stroke distance of the stopper for supporting the maximum inclination angle of the swash plate.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Manufacturing & Machinery (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Abstract

The present invention relates to a variable capacity swash plate type compressor, which has a stopper protruding from the inner surface of a hub and being in contact with a sleeve when a swash plate is at the maximum inclination angle to shorten a stroke distance of the stopper for supporting the maximum inclination angle of the swash plate, thereby reducing a hitting noise when the stopper is moved at the maximum inclination angle and when an air conditioner is turned off.

Description

Description VARIABLE CAPACITY SWASH PLATE TYPE COMPRESSOR
Technical Field
[1] The present invention relates to a variable capacity swash plate type compressor, and more particularly, to a variable capacity swash plate type compressor, which has a stopper protruding from the inner surface of a hub and being in contact with a sleeve when a swash plate is at the maximum inclination angle to shorten a stroke distance of the stopper for supporting the maximum inclination angle of the swash plate, thereby reducing a hitting noise when the stopper is moved at the maximum inclination angle and when an air conditioner is turned off. Background Art
[2] In general, a compressor constituting an air conditioning system for an automobile is a device to selectively receive driving power from a power source by a restricting action of an electromagnetic clutch, compress refrigerant gas by a straight reciprocating motion of pistons after absorbing the refrigerant gas from an evaporator, and discharge it toward a condenser. Such a compressor is classified into various kinds according to compression methods and structures, and out of the compressors of the various kinds, a variable capacity compressor, which can vary a compression volume, has been widely used.
[3] Hereinafter, referring to FIG. 1, a prior art variable capacity swash plate type compressor will be described as an example.
[4] The variable capacity swash plate type compressor 1 includes: a cylinder block 10 having a plurality of cylinder bores 11 axially formed inside the cylinder block 10 along a concentric circle; a front housing 20 mounted on the front of the cylinder block 10 and having a crank chamber 21 formed therein; a rear housing 30 mounted on the rear of the cylinder block 10 and having a suction chamber 31 and a discharge chamber 32 formed therein; a plurality of pistons 40 reciprocatingly inserted into each of the cylinder bores 11 of the cylinder block 10 and having a bridge 41 at the rear end portion thereof; a driving shaft 50 having an end portion rotatably passing through the front housing 20 and the other end portion inserted and rotatably mounted into the center of the cylinder block 10; a rotor 60 combined to the driving shaft 50 and rotating with the driving shaft 50 inside the crank chamber 21; a swash plate 70 mounted on the circumference of the driving shaft 50 by slidably combining a sleeve 65, having an edge rotatably mounted to an insertion space of the piston bridge 41 by interposing a shoe 45 between the insertion space and the edge of the swash plate 70, and movably connected to a hinge arm 61 of the rotor 60 so as to be rotated together with the rotor 60 and adjust its inclination angle against the driving shaft 50; and a valve unit 80 mounted between the cylinder block 10 and the rear housing 30 to inhale refrigerant from the suction chamber 31 into the cylinder bore 11 during a suction stroke and discharge compressed refrigerant from the cylinder bore 11 into the discharge chamber 32 during a compression stroke.
[5] In addition, the inclination angle of the swash plate 70 against the driving shaft 50 can be adjusted according to a pressure change inside the crank chamber 21 by a control valve 90 mounted in the rear housing 30.
[6] Furthermore, a compression coil spring 55 interposed on the driving shaft 50 located between the rotor 60 and the swash plate 70 elastically supports the sleeve 65, to which the swash plate 70 is rotatably combined, against the rotor 60, so that the swash plate 70 can be returned to its original position.
[7] Meanwhile, the rotor 60 has a slot 62 formed on the hinge arm 61 thereof, and a connection hinge arm 73 having a hinge pin 74 is formed on a hub 71 of the swash plate 70, which is faced to the hinge arm 61 of the rotor 60. The connection hinge arm 73 protrudes toward both sides of the hinge arm 61 and is movably combined to the slot 62 of the hinge arm 61.
[8] As described above, in the variable capacity swash plate type compressor 1, a plurality of the pistons 40 arranged along the concentric circle of the cylinder block 10 perform the forward and backward reciprocating motion in order by the rotation of the swash plate 70.
[9] Here, during the suction stroke of the pistons 40, a suction valve (not shown) of the valve unit 80 is opened by a drop of pressure inside the cylinder bore 11, whereby the cylinder bore 11 and the suction chamber 31 are fluidically communicated with each other and the refrigerant is induced from the suction chamber 31 into the cylinder bore 11.
[10] Additionally, during the compression stroke of the pistons 40, a discharge valve
(not shown) of the valve unit 80 is opened while the refrigerant is compressed by a rise of pressure inside the cylinder bore 11, whereby the cylinder bore 11 and the discharge chamber 32 are fluidically communicated with each other and the compressed refrigerant is discharged from the cylinder bore 11 into the discharge chamber 32.
[11] In addition, the swash plate 70 adjusts its inclination angle in correspondence to a difference between pressure inside the crank chamber 21 and suction pressure inside the cylinder bores 11, whereby a discharge volume of the compressor 1 is varied.
[12] Meanwhile, the hub 71 of the swash plate 70 has a stopper 72 formed oppositely to the connection hinge arm 73 to support the maximum inclination angle of the swash plate 70.
[13] Therefore, when the compressor 1 is at the maximum angle, the inclination angle of the swash plate 70 is changed into the maximum angle, and in this instance, the compression coil spring 55 is compressed and at the same time the stopper 72 is in contact with a side surface of the rotor 60 to support the maximum inclination angle of the swash plate 70.
[14] However, when the swash plate 70 is changed into the maximum inclination angle, it may cause noise due to a hitting noise generated while the stopper 72 is in contact with the rotor 60.
[15] In addition, the prior art may cause a great hitting noise due to expansion of refrigerant inside the crank chamber 21 when the air conditioner is turned off.
[16] That is, a stroke distance of the stopper 72 is enlarged while the stopper 72 is gradually spaced apart from the hinge arms 61 and 73 connecting the swash plate 70 and the rotor 60 with each other, and thereby, it causes more severe hitting noise. Disclosure of Invention Technical Problem
[17] Accordingly, it is an object of the present invention to provide a variable capacity swash plate type compressor, which has a stopper protruding from the inner surface of a hub and being in contact with a sleeve when a swash plate is at the maximum inclination angle to shorten a stroke distance of the stopper for supporting the maximum inclination angle of the swash plate, thereby reducing a hitting noise when the stopper is moved at the maximum inclination angle and when an air conditioner is turned off. Technical Solution
[18] To achieve the above objects, the present invention provides a variable capacity swash plate type compressor including: a cylinder block having a plurality of cylinder bores therein; a front housing mounted on the front of the cylinder block and having a crank chamber therein, and a rear housing mounted on the rear of the cylinder block and having a suction chamber and a discharge chamber therein; a driving shaft rotatably mounted on the cylinder block and the front housing; a rotor combined to the driving shaft and rotating together with the driving shaft inside the crank chamber; a swash plate having a hub movably connected to a hinge arm of the rotor and a swash plate board combined to the hub, the hub being rotatably combined to a sleeve which is slidably combined to the driving shaft, the swash plate varying its inclination angle in correspondence to a pressure change of the crank chamber; and a spring mounted on the driving shaft located between the rotor and the swash plate for returning the swash plate to the initial position, wherein maximum inclination angle supporting means is provided between the hub and the sleeve. Brief Description of the Drawings
[19] FIG. 1 is a sectional view of a prior art variable capacity swash plate type compressor.
[20] FIG. 2 is a sectional view of a variable capacity swash plate type compressor according to the present invention.
[21] FIG. 3 is a perspective view showing a state where a swash plate and a rotor are disassembled from the compressor of FIG. 2.
[22] FIG. 4 is a sectional view showing a state when an inclination angle of the swash plate is at the minimum angle in the variable capacity swash plate type compressor according to the present invention.
[23] FIG. 5 is a sectional view showing a state when an inclination angle of the swash plate is at the maximum angle in the variable capacity swash plate type compressor according to the present invention.
[24] FIG. 6 is a view for explaining a formed position of a stopper in the variable capacity swash plate type compressor according to the present invention. Mode for the Invention
[25] Reference will now be made in detail to the preferred embodiments of the present invention, examples of which are illustrated in the accompanying drawings.
[26] FIG. 2 is a sectional view of a variable capacity swash plate type compressor according to the present invention, FIG. 3 is a perspective view showing a state where a swash plate and a rotor are disassembled from the compressor of FIG. 2, FIG. 4 is a sectional view showing a state when an inclination angle of the swash plate is at the minimum angle in the variable capacity swash plate type compressor according to the present invention, FIG. 5 is a sectional view showing a state when an inclination angle of the swash plate is at the maximum angle in the variable capacity swash plate type compressor according to the present invention, and FIG. 6 is a view for explaining a formed position of a stopper in the variable capacity swash plate type compressor according to the present invention.
[27] As shown in the drawings, the variable capacity swash plate type compressor 100 includes: a cylinder block 110 having a plurality of cylinder bores 11 axially formed on a concentric circle thereof; a front housing 120 mounted on the front of the cylinder block 110 and having a crank chamber 121 formed therein; and a rear housing 130 mounted on the rear of the cylinder block 110 and having a suction chamber 131 and a discharge chamber 132 therein.
[28] A plurality of pistons 140 having a bridge 141 at the rear end thereof are recip- rocatingly inserted and mounted to each of the cylinder bores 111 of the cylinder block 110.
[29] In addition, a driving shaft 150 has an end portion rotatably passing through the front housing 120 and the other end portion inserted into the center of the cylinder block 110 in such a way as to be rotatably supported on the center of the cylinder block 110.
[30] Moreover, a rotor 160 is combined to the driving shaft 150 and rotated together with the driving shaft 150 inside the crank chamber 121.
[31] Furthermore, a swash plate 170 is rotatably mounted on a sleeve 165 which is slidably combined to the driving shaft 150 inside the crank chamber 121, has an edge rotatably mounted to an insertion space of the piston bridge 141 by interposing a shoe 145 between the insertion space and the swash plate, and is movably connected to a hinge arm 161 of the rotor 160, whereby the swash plate 170 adjusts its inclination angle against the driving shaft 150 while being rotated together with the rotor 160.
[32] Here, the swash plate 170 includes a hub 171 movably connected to the hinge arm
161 of the rotor and rotatably combined to the sleeve 165, which is slidably combined to the driving shaft 150, via a hub pin 166, and a swash plate board 172 combined to the outer peripheral surface of the hub 171.
[33] In addition, the rotor 160 has a slot 162 formed on the hinge arm 161 thereof, and a connection hinge arm 173 having a hinge pin 174 is formed on the hub 171 of the swash plate 170, which is faced to the hinge arm 161 of the rotor 160. The connection hinge arm 173 protrudes toward both sides of the hinge arm 161 and is movably combined to the slot 162 of the hinge arm 161.
[34] Therefore, during displacement of the inclination angle of the swash plate 170, the hinge pin 174 supports an inclination motion of the swash plate 170 while sliding along the slot 162.
[35] In addition, a valve unit 180 is mounted between the cylinder block 110 and the rear housing 130 to inhale refrigerant from the suction chamber 131 into the cylinder bores 111 during a suction stroke and discharge compressed refrigerant from the cylinder bores 111 into the discharge chamber 132 during a compression stroke.
[36] Meanwhile, a control valve 190 is mounted in the rear housing 130 to operationally fluidically communicate the discharge chamber 132 and the crank chamber 121 with each other, whereby pressure difference between refrigerant suction pressure inside the cylinder bore 111 and gas pressure inside the crank chamber 121 is varied to adjust the inclination angle of the swash plate 170.
[37] Moreover, a compression coil spring 155 is mounted on the driving shaft 150 located between the rotor 160 and the swash plate 170 to return the swash plate 170 to the initial position.
[38] In addition, maximum inclination angle supporting means 175 is mounted between the hub 171 and the sleeve 165 to reduce the hitting noise by supporting the maximum inclination angle of the swash plate 170 when the air conditioner is turned off.
[39] The maximum inclination angle supporting means 175 has a stopper 176 protruding on the inner surface of the hub 171 or the outer surface of the sleeve 165, so that the stopper 176 is in contact with the outer surface of the sleeve 165 or the inner surface of the hub 171 when the swash plate 170 is at the maximum inclination angle.
[40] In the drawing, the stopper 176 is formed on the inner surface of the hub 171, but may be formed on the outer surface of the sleeve 165.
[41] As shown in FIG. 6, it is preferable that the stopper 176 is formed on a connection line (LC) passing a position (Pl) of the swash plate 170 corresponding with the center of the cylinder bore 111, which is in the maximum compression stroke state, and a center (P2) of the driving shaft 150.
[42] As described above, in a state where the stopper 176 is formed at the correct position, it is preferable that the stopper 176 is axially eccentric on the inner surface of the hub 171. The stopper 176 is formed on the upper portion of the inner surface of the hub 171 in the drawing, but may be formed on the lower portion of the hub 171.
[43] The stopper 176 has an end portion spaced apart at a predetermined distance from the outer surface of the sleeve 165, and is in contact with the sleeve 165 only when the swash plate 170 is at the maximum inclination angle to restrict and support the maximum inclination angle of the swash plate 170.
[44] As described above, when the swash plate 170 is displaced into the maximum inclination angle, the hub 171 is rotated on the hub pin 166 combined to the sleeve 165, and in this instance, the stopper 176 is in contact with the outer surface of the sleeve 165 to support the maximum inclination angle of the swash plate 170, whereby the hitting noise generated while the stopper 72 (in the prior art) is in contact with the rotor 60 (in the prior art) can be decreased more since the stroke distance of the stopper 176 is shorter than that of the prior art stopper 72 (in the prior art).
[45] Meanwhile, the stopper 176 can be integrally or detachably formed on the inner surface of the hub 171.
[46] As described above, the stopper 176 is formed on the inner surface of the hub 171 facing to the outer surface of the sleeve 165, whereby the inclination angle of the swash plate 170 is increased and the compression coil spring 155 is gradually compressed when the compressor 100 is in a condition of the maximum inclination angle. In this instance, when the swash plate 170 reaches the maximum inclination angle, the stopper 176 formed on the inner surface of the hub 171 is in contact with the outer surface of the sleeve 165 to support the maximum inclination angle of the swash plate 170 and to prevent a further increase of the inclination angle of the swash plate 170.
[47] Meanwhile, when the compressor 100 is in a condition of the minimum inclination angle, the inclination angle of the swash plate 170 is decreased by restoring force of the compression coil spring 155. Industrial Applicability
[48] As described above, the present invention can reduce a hitting noise when the stopper is moved at the maximum inclination angle and when an air conditioner is turned off, since the stopper is formed on the inner surface of the hub and is in contact with the sleeve when the swash plate is at the maximum inclination angle to shorten the stroke distance of the stopper for supporting the maximum inclination angle of the swash plate.

Claims

Claims
[1] A variable capacity swash plate type compressor, which includes: a cylinder block (110) having a plurality of cylinder bores (111) therein; a front housing (120) mounted on the front of the cylinder block (110) and having a crank chamber (121) therein, and a rear housing (130) mounted on the rear of the cylinder block (110) and having a suction chamber (131) and a discharge chamber (132) therein; a driving shaft (150) rotatably mounted on the cylinder block (110) and the front housing (120); a rotor (160) combined to the driving shaft (150) and rotating together with the driving shaft (150) inside the crank chamber (121); a swash plate (170) having a hub (171) movably connected to a hinge arm (161) of the rotor (160) and a swash plate board (172) combined to the hub (171), the hub (171) being rotatably combined to a sleeve (165) which is slidably combined to the driving shaft (150), the swash plate (170) varying its inclination angle in correspondence to a pressure change of the crank chamber (121); and a spring (155) mounted on the driving shaft (150) located between the rotor (160) and the swash plate (170) for returning the swash plate (170) to the initial position, wherein maximum inclination angle supporting means is provided between the hub (171) and the sleeve (165).
[2] The variable capacity swash plate type compressor according to claim 1, wherein the maximum inclination angle supporting means is provided with a stopper (176) protruding from the inner surface of the hub (171) or the outer surface of the sleeve (165), whereby the stopper (176) is in contact with the outer surface of the sleeve (165) or the inner surface of the hub (171) is at the maximum inclination angle.
[3] The variable capacity swash plate type compressor according to claim 2, wherein the stopper (176) is formed on a connection line (LC) passing a position (Pl) of the swash plate (170) corresponding with the center of the cylinder bore (111), which is in the maximum compression stroke state, and a center (P2) of the driving shaft (150).
PCT/KR2006/003190 2005-10-20 2006-08-16 Variable capacity swash plate type compressor WO2007046580A1 (en)

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US11/989,405 US20090148312A1 (en) 2005-10-20 2006-08-16 Variable Capacity Swash Plate Type Compressor
CN2006800332941A CN101278124B (en) 2005-10-20 2006-08-16 Variable capacity swash plate type compressor

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KR1020050098999A KR101104282B1 (en) 2005-10-20 2005-10-20 Variable capacity type swash plate type compressor
KR10-2005-0098999 2005-10-20

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Publication number Priority date Publication date Assignee Title
KR101193399B1 (en) * 2012-06-22 2012-10-26 주식회사 두원전자 Variable displacement swash plate type compressor
KR101421961B1 (en) 2013-08-27 2014-07-22 현대자동차주식회사 Structure of variable swash plate type compressor

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US5941161A (en) * 1996-12-06 1999-08-24 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Piston type compressor
JP2001304107A (en) * 2001-03-30 2001-10-31 Zexel Valeo Climate Control Corp Variable displacement compressor
US6382927B1 (en) * 1999-04-01 2002-05-07 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Valve plate assembly positioning structure for compressor
US6416297B1 (en) * 1998-10-02 2002-07-09 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Stopping means for preventing movement of the drive shaft of a variable displacement compressor

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US2256079A (en) * 1940-12-03 1941-09-16 Watson Stillman Co Swash plate mechanism
JPH08326655A (en) * 1995-06-05 1996-12-10 Calsonic Corp Swash plate compressor
JPH1162824A (en) * 1997-08-08 1999-03-05 Sanden Corp Variable capacity compressor

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Publication number Priority date Publication date Assignee Title
US5941161A (en) * 1996-12-06 1999-08-24 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Piston type compressor
US6416297B1 (en) * 1998-10-02 2002-07-09 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Stopping means for preventing movement of the drive shaft of a variable displacement compressor
US6382927B1 (en) * 1999-04-01 2002-05-07 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Valve plate assembly positioning structure for compressor
JP2001304107A (en) * 2001-03-30 2001-10-31 Zexel Valeo Climate Control Corp Variable displacement compressor

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US20090148312A1 (en) 2009-06-11
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KR20070043118A (en) 2007-04-25
KR101104282B1 (en) 2012-01-11

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