WO2010110537A2 - Soupape de commande de déplacement de compresseur volumétrique variable et procédé d'assemblage - Google Patents

Soupape de commande de déplacement de compresseur volumétrique variable et procédé d'assemblage Download PDF

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Publication number
WO2010110537A2
WO2010110537A2 PCT/KR2010/001308 KR2010001308W WO2010110537A2 WO 2010110537 A2 WO2010110537 A2 WO 2010110537A2 KR 2010001308 W KR2010001308 W KR 2010001308W WO 2010110537 A2 WO2010110537 A2 WO 2010110537A2
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WO
WIPO (PCT)
Prior art keywords
valve
control valve
variable displacement
displacement compressor
capacity control
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PCT/KR2010/001308
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English (en)
Korean (ko)
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WO2010110537A3 (fr
Inventor
한영창
이용주
이건호
Original Assignee
두원공과대학교
주식회사 두원전자
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Publication of WO2010110537A2 publication Critical patent/WO2010110537A2/fr
Publication of WO2010110537A3 publication Critical patent/WO2010110537A3/fr

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    • 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
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • 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
    • F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
    • F16B5/00—Joining sheets or plates, e.g. panels, to one another or to strips or bars parallel to them
    • F16B5/02—Joining sheets or plates, e.g. panels, to one another or to strips or bars parallel to them by means of fastening members using screw-thread
    • 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
    • F04B2027/1809—Controlled pressure
    • F04B2027/1818—Suction pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • 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
    • 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
    • F04B2027/184—Valve controlling parameter
    • F04B2027/1845—Crankcase pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • 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
    • F04B2027/184—Valve controlling parameter
    • F04B2027/1859—Suction pressure
    • 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
    • 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 capacity control valve and a method for assembling a variable displacement compressor, and more particularly, a variable displacement compressor configured to maintain a constant value of the suction pressure Ps even when the discharge pressure Pd is increased. Relates to a capacity control valve and an assembly method.
  • variable capacity compressor that can change the discharge amount of the refrigerant to obtain a cooling capacity without being regulated by the rotational speed of the engine has been used a lot.
  • variable displacement compressors such as swash plate type, rotary type and scroll type.
  • the swash plate type compressor In the swash plate type compressor, the swash plate provided so that the inclination angle is variable in the crank chamber rotates according to the rotational motion of the rotating shaft, and the piston reciprocates by the rotational motion of the swash plate.
  • the refrigerant in the suction chamber is sucked into the cylinder by the reciprocating motion of the piston, compressed and discharged into the discharge chamber.
  • the inclination angle of the swash plate is changed according to the pressure difference in the crank chamber and the pressure in the suction chamber, and the discharge amount of the refrigerant is Will be controlled.
  • Patent Document 1 A representative example of a capacity control valve of such a variable displacement compressor is disclosed in Patent Document 1 (hereinafter referred to as "prior art"), and a schematic configuration thereof will be described with reference to FIGS. .
  • the capacity control valve 5 has a shaft portion 15c, a valve body having a diameter smaller than the middle small diameter portion 15b and a diameter larger than the shaft portion 15c than the shaft portion 15c.
  • a valve rod 15 having a portion 15a, a guide hole 19 into which the shaft portion 15c of the valve rod 15 is inserted so as to be free to slide, and a valve body portion 15a are provided at their lower ends (valve).
  • a discharge pressure refrigerant inlet port 25 with a plurality of filters 25A for introducing a refrigerant of refrigerant is provided, and the refrigerant continuously passes through the crank chamber of the compressor at the lower side (downstream side) of the valve port 22.
  • the valve body 20 and the electronic actuator 30 provided with the outlet 26 are provided.
  • the electromagnetic actuator 30 includes a coil 32 having a connector portion 31 for power transmission, a cylindrical stator 33 disposed on an inner circumferential side of the coil 32, and a stator 33.
  • a pipe having a concave aspirator 34 having a concave end face press-fitted to the lower end inner circumference and a flange-shaped portion 35a whose upper end is joined to the outer circumference (step difference) of the stator 33 by TIG welding ( 35 and the plunger 37 and the bottom disposed to cover the outer circumference of the coil 32 are arranged on the inner circumferential side of the pipe 35 so as to be free to slide up and down on the inner circumferential side of the suction 34.
  • a cylindrical housing 60 having a hole therein is provided.
  • the adjustment screw 65 which has a hexagonal hole is screwed on the upper part of the said stator 33, and is between the said adjustment screw 65 and the aspirator 34 in the inner peripheral side of the stator 33.
  • the decompression chamber 45 is formed in which the suction pressure Ps of the compressor is introduced, and the decompression chamber 45 is provided with a bellows 41 as a member moving in accordance with the decompression, and has an inverted convex upper stopper 42. ),
  • a bellows main body 40 composed of an inverted lower stopper 43 and a compression coil spring 44 is disposed.
  • the compression coil spring 46 which presses in the direction which contracts the bellows main body 40 (the direction compressed to the adjustment screw 65 side) is arrange
  • an operating rod 14 penetrating the suction member 34 is disposed.
  • a valve comprising a compression coil spring for pressing the valve rod 15 downward (valve opening direction) through the plunger 37.
  • An opening spring 47 is arranged.
  • a guide hole 19 into which the valve rod 15 is inserted so as to slide freely is formed.
  • a plurality of suction pressure refrigerant inlets 27 are formed on the outer circumferential side thereof, and the refrigerant at the suction pressure Ps introduced into the suction pressure refrigerant introduction chamber 23 from the suction pressure refrigerant inlet 27 is a plunger.
  • the decompression chamber 45 through the vertical grooves 37a, 37a, ... formed on the outer circumference of the 37 and the continuous passage hole 37d protruding from the center portion, the continuous passage hole 39 formed in the aspirator 34, and the like. Is introduced.
  • valve closing spring 48 which consists of a conical compression coil spring which presses the said valve rod 15 upward is arrange
  • a lower flange portion 35a of the pipe 35 is placed on the upper end portion of the valve body 20 through an O-ring 57, and between the flange portion 35a and the coil 32.
  • a short cylindrical pipe holder 56 with a flanged portion 56a is fitted therein, and the flanged portions 35a and 56a are all fastened by the upper outer circumferential caulking portion 29 of the valve body 20. It is fixed.
  • the upper end portion of the pipe holder 56 is press-fitted and fixed with a bottom portion 61 having a hole in the housing 60, and the upper end portion 62 of the housing 60 has a flange shape of the connector portion 31.
  • a caulking is fixed on the portion 31c, and a zero ring 66 is fitted between the housing 60 and the connector portion 31 and the coil 32.
  • the recessed part 31a in which the convex part 31b which fits in the hexagonal hole of the said adjustment screw 65 protrudes is formed in the center lower part of the connector part 31, and this recessed part 31a is provided. The upper part of the stator 33 and the adjustment screw 65 is inserted into the.
  • valve rod 15 can move upward (valve closing direction) by the pressing force of the valve closing spring 48.
  • the refrigerant of the suction pressure Ps introduced from the compressor to the suction pressure inlet 27 is formed in the longitudinal grooves 37a, 37a, ... and suction formed on the outer circumference of the plunger 37 from the introduction chamber 23.
  • the bellows main body 40 internal vacuum pressure
  • the bellows main body 40 is introduced into the decompression chamber 45 through the continuous passage hole 39 formed in the 39, and the pressure (suction pressure Ps) of the decompression chamber 45. Expansion and contraction (shrinkage when the suction pressure Ps is high and elongate when the suction pressure Ps is high), the displacement is transmitted to the valve rod 15 through the operating rod 14 and the plunger 37, thereby opening the valve. (The lift amount of the valve body part 15a from the valve seat part 22a of the valve port 22) is adjusted.
  • the valve opening degree is the suction force of the plunger 37 by the solenoid part which consists of the coil 32, the stator 33, and the suction 34, the pressing force of the bellows main body 40, and the valve opening spring ( 47) and the pressing force by the valve closing spring 48, the valve opening direction load by the discharge pressure Pd with respect to the valve shaft 15, and the valve closing direction load, and are discharged according to the valve opening degree.
  • the amount of condensation of the refrigerant of the discharge pressure Pd introduced into the valve chamber 21 from the pressurized refrigerant introduction port 25, that is, the amount of condensation (condensation amount) into the crank chamber is adjusted.
  • the pressure Pc on the refrigerant outlet 26 side is controlled in accordance with the valve opening degree, thereby adjusting the inclination angle of the inclined plate of the compressor and the stroke of the piston, thereby increasing and decreasing the discharge amount.
  • the capacity control valve 5 for the variable displacement compressor according to the prior art has a problem to be improved as follows.
  • the discharge pressure refrigerant inlet 21 is provided upstream of the valve port 22, and the refrigerant outlet 26 is provided downstream of the valve port 22, and the valve main body is provided.
  • the portion 15a is provided at the lower end of the shaft portion 15c of the valve rod 15 to open and close the valve opening 22 from the lower side thereof, and the discharge pressure Pd acts on the valve rod 15. have.
  • the valve port 22 moves the shaft portion 15c of the valve rod 15 to its lower portion.
  • the aperture Da is made slightly larger than the outer diameter Db of the shaft portion 15c so as to pass through from the lower side, and to open and close the valve port 22 in the valve body portion 15a from the lower side thereof (
  • the outer diameter Dc of the valve main body 15a is larger than the diameter Da of the valve port 22 so that the valve main body 15a is in contact with the valve seat 22a provided at the lower end of the valve port 22. It becomes large (Db ⁇ Da ⁇ Dc).
  • valve closing direction load (pushing force) A by the discharge pressure Pd acting on the valve rod 15 depends on the hydraulic pressure area (outer diameter Db) of the shaft portion 15c.
  • the opening direction load (pushing force) B is applied to the load Ba along the diameter Da of the valve port 22 (valve seat portion 22a) to the outer diameter Dc (Dc-Da) of the valve body portion 15a.
  • the load Bb according to this is added magnitude.
  • the valve opening direction load (pushing force) due to the discharge pressure Pd to the valve rod 15 is greater than the valve closing direction load (pushing force).
  • Bb is large. Therefore, if the current value I supplied to the coil 32 of the electronic actuator 30 is made constant, the discharge pressure Pd is increased by the (Pd)-(Ps) characteristics shown in FIG. Pc) Furthermore, the suction pressure Ps (on the use of the compressor, the outlet pressure Pc and the suction pressure Ps are approximately equal) also tends to be high (upper right), which adversely affects the control (control There is a problem).
  • Patent Document 1 Japanese Unexamined Patent Publication No. 2006-291867
  • the present invention has been made to solve the above-mentioned conventional problems, the object of the present invention is configured to maintain a constant value of the suction pressure (Ps) even if the discharge pressure (Pd) is increased capacity variable deformation improved control accuracy To provide a capacity control valve and an assembly method of the compressor.
  • Another object of the present invention is to provide a capacity control valve and a method for assembling a variable displacement compressor that adjusts the discharge capacity by using a balance between the pressure difference between the discharge chamber and the suction chamber, and the force of the bellows and the solenoid.
  • the capacity control valve of the variable displacement compressor of the present invention for achieving the above object is, in the capacity control valve of the variable displacement compressor, the crankcase connecting hole which receives the crank chamber pressure, the discharge chamber pressure and the suction chamber pressure of the compressor, respectively;
  • a valve housing having a discharge chamber connecting hole and a suction chamber connecting hole respectively formed therein and having a first guide hole passing through the discharge chamber connecting hole and the crank chamber connecting hole;
  • a valve body composed of a large diameter portion and a small diameter portion to open and close the first guide hole entrance while reciprocating;
  • a sleeve member having a diameter larger than that of the small diameter portion, wherein the sleeve member connects the small diameter portion of the valve body to the solenoid of the valve body.
  • the cross-sectional area with respect to the diameter of the sleeve is preferably greater than or equal to the sum of the cross-sectional area with respect to the diameter of the first guide hole and the cross-sectional area with respect to the diameter of the large diameter portion divided by two.
  • valve housing is preferably formed with a sleeve bore corresponding to the sleeve.
  • the sleeve member is provided with a receiving portion, it is preferable that the receiving portion is provided with a bellows.
  • the electromagnetic solenoid is preferably composed of a movable iron core connected to the sleeve member, an electromagnetic coil disposed around the movable iron core, a rod connected to the bellows, and a fixed iron core fixing the rod.
  • an insertion groove is formed in the bellows, and an insertion hole corresponding to the insertion groove is formed in the rod, and is preferably fixed to prevent relative movement.
  • the rod is preferably screwed to the fixed iron core.
  • the rod is formed with a ring groove, it is preferable that the O-ring is inserted into the ring groove.
  • the guide groove is formed in the movable core to communicate with the suction chamber connecting hole.
  • the movable iron core is preferably formed with a second guide hole for guiding the movement of the rod.
  • the sleeve and the valve body is preferably fixed to prevent relative movement.
  • the first support spring is built in the bellows.
  • the opposite end is not formed the insertion groove of the bellows is preferably fixed to the sleeve member.
  • valve housing is provided with a cap screwed in the direction facing the end of the valve body, it is preferred that the second support spring is provided between the valve body and the cap.
  • a filter is installed in the discharge chamber connecting hole.
  • the rod is screwed to the electromagnetic solenoid
  • the bellows is coupled to the protruding end of the rod
  • the bellows Coupling the electronic solenoid and the sleeve member so as to surround the, and coupling the electronic solenoid and the valve housing, engaging the small diameter portion of the sleeve and the valve body of the sleeve member, fixing the cap to cover the open end of the valve housing It is characterized by.
  • the opening amount of the valve body is limited by the sleeve member, even if the discharge pressure (Pd) is increased, the suction pressure (Ps) maintains a constant value so that the control precision is increased. There is an effect to be improved.
  • the magnitude of the current acting on the electromagnetic solenoid is proportional to the difference between the discharge pressure and the suction pressure, so that the discharge capacity and the torque can be easily adjusted.
  • the sealing is improved by preventing the outflow of the refrigerant by the O-ring.
  • FIG. 1 is a longitudinal sectional view showing a capacity control valve of a variable displacement compressor according to the prior art.
  • FIG. 2 is an enlarged longitudinal sectional view (a) and an operation explanatory view (b) of an essential part of a capacity control valve according to the prior art.
  • FIG. 3 is a graph showing Pd-Ps characteristics of the displacement control valve of FIG.
  • FIG. 4 is a longitudinal sectional view showing the structure of a variable displacement compressor according to the present invention.
  • FIG. 5 is a longitudinal sectional view showing the structure of the displacement control valve in FIG. 4.
  • FIG. 6 is a longitudinal cross-sectional view showing a balance of forces between components in the displacement control valve of FIG. 4.
  • Figure 4 is a longitudinal sectional view showing a structure of a variable displacement compressor according to the present invention
  • Figure 5 is a longitudinal sectional view showing the structure of a capacity control valve in Figure 4
  • Figure 6 is a cross-sectional view between each component in the capacity control valve of Figure 4 Longitudinal cross-sectional view showing the balance of forces.
  • variable displacement swash plate type compressor provided with a capacity control valve according to the present invention will be described schematically.
  • variable displacement swash plate type compressor C has a cylinder block 10 having a plurality of cylinder bores 12 formed parallel to the inner circumferential surface in the longitudinal direction, and sealed in front of the cylinder block 10.
  • the front housing 16 is coupled, and the rear housing 18 is hermetically coupled to the rear of the cylinder block 10 via a valve plate 20.
  • the crank chamber 86 is provided inside the front housing 16, and one end of the drive shaft 44 is rotatably supported near the center of the front housing 16, while the other end of the drive shaft 44 is Passed through the crank chamber 86 is supported via a bearing provided in the cylinder block 10.
  • the lug plate 54 and the swash plate 50 are provided around the drive shaft 44.
  • a pair of power transmission support arms 62 each having a linearly perforated guide hole 64 formed at the center thereof are formed to protrude integrally on one surface, and one surface of the swash plate 50 has a ball.
  • the ball 66 of the swash plate 50 slides in the guide hole 64 of the lug plate 54 so that the swash plate 50 can be rotated.
  • the inclination angle is variable.
  • the outer circumferential surface of the swash plate 50 is fitted to the piston 14 so as to be able to slide through the shoe 76.
  • a suction chamber 22 and a discharge chamber 24 are formed in the rear housing 18, and each cylinder bore is provided in the valve plate 20 interposed between the rear housing 18 and the cylinder block 10.
  • a suction port 32 and a discharge port 36 are respectively formed in a position corresponding to (12).
  • the refrigerant in the suction chamber 22 is sucked into the cylinder bore 12, compressed, and discharged to the discharge chamber 24.
  • the pressure in the crank chamber 86 and the suction chamber ( The inclination angle of the swash plate 50 is changed according to the pressure difference in the 22 to adjust the discharge amount of the refrigerant.
  • variable displacement compressor adopted in the embodiment of the present invention adopts the electromagnetic solenoid type capacity control valve 100 to adjust the pressure of the crank chamber 86 by opening and closing the valve by energization, through which the swash plate 50 It is designed to adjust the discharge capacity by adjusting the inclination angle of), and can be applied to all compressors of this characteristic.
  • the capacity control valve 100 is installed to be movable in the valve housing 110, the electromagnetic solenoid 130, and the valve housing 110 in which some connection holes are formed.
  • the valve body 120 is included.
  • a first guide hole 117 is formed in the valve housing 110 to guide the movement of the valve body 120.
  • the valve body 120 is configured to open and close the first guide hole 117 formed in the valve housing 110 while reciprocating.
  • the valve housing 110 is formed with a crank chamber connecting hole 112 and a discharge chamber connecting hole 113 in which the pressure Pc of the crank chamber 86 and the pressure Pd of the discharge chamber 24 respectively work. have.
  • the discharge chamber connecting hole 113 and the crank chamber connecting hole 112 have a structure in communication with each other through the first guide hole 117.
  • valve housing 110 has a suction chamber connecting hole 111 formed at a lower end of the discharge chamber connecting hole 113.
  • the discharge chamber connecting hole 113 and the suction chamber connecting hole 111 are formed in a direction orthogonal to the crank chamber connecting hole 112, respectively, but the direction may be arbitrarily determined.
  • the valve body 120 is divided into a large diameter portion 122 and a small diameter portion 123 with the jaw portion 121 as a boundary.
  • the crankcase connecting hole 112 is formed around the jaw portion 121 as the large diameter portion 122 and the suction chamber connecting hole 111 is formed as the small diameter portion 123.
  • the jaw portion 121 is capable of opening and closing the inlet of the first guide hole 117 connecting the discharge chamber connecting hole 113 and the crank chamber connecting hole 112.
  • suction pressure Ps of the compressor C or the pressure Pc of the crank chamber 86 act on both ends of the valve body 120.
  • a sleeve member 140 is provided at an end of the small diameter portion 123 of the valve body 120 to connect the small diameter portion 123 of the valve body 120 to the solenoid 130.
  • a sleeve bore 119 is formed in the valve housing 110 in which the sleeve member 140 is installed, and a sleeve 141 corresponding to the sleeve bore 119 is formed in the sleeve member 140.
  • the sleeve 141 is preferably larger in diameter than the small diameter portion 123.
  • the cross sectional area with respect to the diameter of the sleeve 141 is greater than or equal to the sum of the cross sectional area with respect to the diameter of the first guide hole 117 and the cross sectional area with respect to the diameter of the large diameter portion 122 divided by two. It is preferable to form so that a detailed description thereof will be described later.
  • the sleeve member 140 is preferably configured to be pressed against each other and the small diameter portion 123 to prevent relative movement.
  • the electromagnetic solenoid 130 may include a movable core 131 connected to the sleeve member 140, an electromagnetic coil 132 disposed around the movable core 131, the electronic coil 132, and the like. Wrapping is composed of a solenoid housing 134, a fixed iron core 133 disposed inside the electromagnetic coil 132 and a rod 135 coupled to the fixed iron core 133 and fixed to the bellows 160 to be described later. .
  • the solenoid housing 134 corresponds to an injection molded product or an insulating case surrounding the electronic coil 132.
  • a second guide hole 131a for guiding the movement of the rod 135 is formed in the movable iron core 131.
  • the movable iron core 131, the sleeve member 140, and the valve body 120 reciprocate by energizing the electromagnetic solenoid 130, and are discharged by the jaw portion 121 of the valve body 120.
  • the inlet of the first guide hole 117 connecting between the thread connection hole 113 and the crankcase connection hole 112 is opened and closed.
  • an off-spring 125 is installed between the fixed iron core 133 and the movable iron core 131. In the absence of external force, the valve body 120 is raised to raise the first guide hole 117. Keep the inlet open.
  • the rod 135 may be screwed with the fixed iron core 133 to adjust an initial set value of the bellows 160 to be described later by the rotation of the rod 135.
  • the maximum opening amount of the valve body 120 is limited by the inner surface of the valve housing 110 in which one surface of the sleeve member 140 and the first guide hole 117 are formed.
  • the sleeve member 140 has an accommodating part 170 formed therein, and the accommodating part 170 is provided with a bellows 160.
  • the bellows 160 is a corrugated structure in which a certain amount of air is filled so that a predetermined pressure is applied when no external load is applied, and the bellows 160 exerts a force on a component connected thereto while performing expansion / contraction by external pressure. Component.
  • the receiving portion 170 is directly connected to the suction chamber 22, the suction chamber pressure (Ps) is applied.
  • an insertion groove 161 is formed in the bellows 160, and an insertion hole 135a corresponding to the insertion groove 161 is formed in the rod 135 to be fixedly coupled to prevent relative movement.
  • the opposite end is not formed the insertion groove 161 of the bellows 160 is preferably fixed to the inside of the sleeve member (140).
  • first support spring 162 may be built in the bellows 160 to maintain the expanded state.
  • valve housing 110 is provided with a cap 165 that is screwed in a direction facing the end of the valve body 120, a second support spring between the valve body 120 and the cap 165.
  • the expansion force of the bellows 160 and the expansion force of the first spring 162 installed therein are regulated.
  • the initial setting value of the second support spring 163 may be adjusted by the rotation of the cap 165.
  • the cap 165 is formed so that a part is open so that the pressure (Pc) of the crank chamber 86 is acting.
  • the movable iron core 131 is formed with a guide groove 131b to communicate with the suction chamber connecting hole 111.
  • the pressure Ps of the suction chamber 22 also acts on the solenoid housing 134.
  • the pressure Ps of the suction chamber 22 can also be applied to the movable iron core 131 and the sleeve member 140.
  • the suction solenoid gas having the pressure Ps of the suction chamber 22 passes through the solenoid housing 134 so that the electronic solenoid 130 portion can be effectively cooled. Accordingly, the reliability of the electronic solenoid 130 is increased, and the electronic solenoid 130 can accurately generate electromagnetic force proportional to the current without being affected by the generated heat.
  • a ring groove 136 is formed in the rod 135, an O-ring 137 is inserted into the ring groove 136 to prevent the leakage of the refrigerant introduced through the guide groove 131b.
  • a filter 180 is installed in the discharge chamber connecting hole 113 to serve to block foreign substances from entering the control valve.
  • the initial state is a state in which power supply to the capacity control valve 100 is cut off, and the valve body 120 is lifted by the off-spring 125 so that the jaw portion 121 of the valve body 120 is discharged. It is assumed that it is separated from the inlet of the first guide hole 117 connecting between the thread connection hole 113 and the crank chamber connection hole 112 to maintain an open state.
  • the engine speed, the indoor and outdoor temperature difference, the evaporator downstream temperature and pressure is detected and the signal is sent to the MCU, the calculation is performed with the thermal load set in the MCU, and the detected thermal load exceeds the set value.
  • the current signal for increasing the refrigerant discharge amount is sent to the power source.
  • the electric current flows through the solenoid 130 so that the movable core 131, the sleeve member 140, and the valve body 120 discharge the resistance of the off-spring 125 and the discharge chamber connecting hole 113.
  • the discharge chamber connecting hole 113 is closed by lowering the pressure Pd.
  • the suction pressure Ps is increased due to the external thermal load, that is, the indoor temperature is high, and the suction pressure Ps thus raised acts on the receiving unit 170.
  • the bellows 160 is reduced by the increased suction pressure Ps, and the valve body 120 fixed to the bellows 160 receives a descending force.
  • the valve body 120 can easily move downward even if the electric current acting on the electromagnetic solenoid 130 is small.
  • the amount of current acting on the electronic solenoid 130 decreases, the amount of heat generated from the electronic coil 132 also decreases, thereby minimizing the thermal effect of the electronic solenoid 130 and maintaining reliability.
  • the jaw portion 121 of the valve body 120 starts to be separated from the inlet of the first guide hole 117 connecting between the discharge chamber connecting hole 113 and the crank chamber connecting hole 112, and then Since the discharge pressure Pd acts on the crank chamber 86, the pressure of the crank chamber 86 is increased, and the inclination angle of the swash plate 50 and the discharge amount of the refrigerant are also drastically reduced.
  • the displacement control valve 100 of the present invention described above is formed so that the discharge pressure (Pd) acts on the jaw portion 121 of the valve body 120.
  • the cross-sectional area Ab for the diameter of the small-diameter portion 123 is a cross-sectional area for the diameter of the first guide hole 117 to facilitate the valve assembly and the discharge pressure Pd to move to the crank chamber 86 ( It is formed smaller than Ad), the cross-sectional area (Aa) with respect to the diameter of the large diameter portion 122 is formed larger than the cross-sectional area (Ad) of the first guide hole 117 to open and close the first guide hole (117). (Ab ⁇ Ad ⁇ Aa).
  • the cross-sectional area Ac of the sleeve 140 is greater than or equal to the sum of the cross-sectional area Ad of the first guide hole 117 and the cross-sectional area Aa of the large diameter part 122 divided by two.
  • the discharge pressure Pd applied to the large diameter portion 122 and the jaw portion 121 acts the same on the sleeve 140 so that the valve body 120 is stopped without moving due to the force balance. do.
  • the jaw portion 121 of the valve body 120 only shows the configuration of opening and closing the inlet, but the opening degree of the inlet of the first guide hole 117 can be adjusted according to the amount of energization. Of course it can.
  • the filter 180 is installed in the discharge chamber connecting hole 113, but the foreign matter is applied to the control valve by applying to both the suction chamber connecting hole 111 and the crank chamber connecting hole 112 into which the refrigerant is introduced. It can be configured to block the input.

Abstract

La présente invention a trait à une soupape de commande de déplacement de compresseur volumétrique variable. La soupape de commande de déplacement d'un compresseur volumétrique variable selon la présente invention comprend : un compartiment des soupapes doté d'un trou de connexion de chambre de manivelle, d'un trou de connexion de chambre de refoulement et d'un trou de connexion de chambre d'aspiration recevant respectivement une pression de chambre de manivelle, une pression de chambre de refoulement et une pression de chambre d'aspiration du compresseur formé à l'intérieur, et un premier trou de guidage passant par le trou de connexion de chambre de refoulement et le trou de connexion de chambre de manivelle ; un corps de soupapes constitué d'une partie de grand diamètre et d'une partie de petit diamètre permettant d'ouvrir ou de fermer l'entrée du premier trou de guidage, tout en effectuant un mouvement de va-et-vient ; un solénoïde électromagnétique permettant de déplacer selon un mouvement de va-et-vient le corps de soupapes à l'aide de l'électricité ; et un élément de manchon pourvu d'un manchon dont le diamètre est supérieur à celui de la partie de petit diamètre, l'élément de manchon étant connecté entre la partie de petit diamètre du corps de soupapes et le solénoïde électromagnétique. Par conséquent, dans la mesure où le degré d'ouverture du corps de soupapes est restreint par l'élément de manchon, une pression d'aspiration (Ps) est maintenue à une valeur constante, indépendamment de toute augmentation de pression de refoulement (Pd) et ainsi il est possible d'améliorer la précision de commande.
PCT/KR2010/001308 2009-03-25 2010-03-03 Soupape de commande de déplacement de compresseur volumétrique variable et procédé d'assemblage WO2010110537A2 (fr)

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KR10-2009-0025334 2009-03-25
KR1020090025334A KR101028874B1 (ko) 2009-03-25 2009-03-25 용량가변형 압축기의 용량제어밸브 및 조립방법

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110017395A (zh) * 2019-05-12 2019-07-16 苏州新智机电工业有限公司 一种可变排量压缩机用外控阀

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5699259B2 (ja) 2011-01-07 2015-04-08 株式会社テージーケー 可変容量圧縮機用制御弁
CN103890391B (zh) * 2011-10-20 2016-05-04 学校法人斗源学院 用于压缩机的控制阀
KR101298722B1 (ko) 2012-07-26 2013-08-21 동일기계공업 주식회사 가변 용량 압축기용 제어밸브

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20060043852A (ko) * 2004-03-12 2006-05-15 가부시키가이샤 티지케이 가변 용량 압축기용 제어 밸브
KR20060044873A (ko) * 2004-03-30 2006-05-16 가부시키가이샤 티지케이 가변 용량 압축기용 제어 밸브
JP2008157031A (ja) * 2006-12-20 2008-07-10 Toyota Industries Corp クラッチレス可変容量型圧縮機における電磁式容量制御弁

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR19990075818A (ko) * 1998-03-25 1999-10-15 윤종용 위치 검출 기능을 갖는 전자팽창밸브

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20060043852A (ko) * 2004-03-12 2006-05-15 가부시키가이샤 티지케이 가변 용량 압축기용 제어 밸브
KR20060044873A (ko) * 2004-03-30 2006-05-16 가부시키가이샤 티지케이 가변 용량 압축기용 제어 밸브
JP2008157031A (ja) * 2006-12-20 2008-07-10 Toyota Industries Corp クラッチレス可変容量型圧縮機における電磁式容量制御弁

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110017395A (zh) * 2019-05-12 2019-07-16 苏州新智机电工业有限公司 一种可变排量压缩机用外控阀
CN110017395B (zh) * 2019-05-12 2024-02-06 苏州新智机电工业有限公司 一种可变排量压缩机用外控阀

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WO2010110537A3 (fr) 2010-12-09
KR20100107178A (ko) 2010-10-05

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