WO2006090760A1 - 容量制御弁 - Google Patents
容量制御弁 Download PDFInfo
- Publication number
- WO2006090760A1 WO2006090760A1 PCT/JP2006/303231 JP2006303231W WO2006090760A1 WO 2006090760 A1 WO2006090760 A1 WO 2006090760A1 JP 2006303231 W JP2006303231 W JP 2006303231W WO 2006090760 A1 WO2006090760 A1 WO 2006090760A1
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- WO
- WIPO (PCT)
- Prior art keywords
- valve
- chamber
- valve portion
- side passage
- pressure
- Prior art date
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Classifications
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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
- 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
- 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
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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
- F04B27/14—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
- F04B2027/1822—Valve-controlled fluid connection
- F04B2027/1831—Valve-controlled fluid connection between crankcase and suction 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
- F04B2027/1854—External parameters
-
- 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
-
- 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
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/8593—Systems
- Y10T137/86493—Multi-way valve unit
- Y10T137/86574—Supply and exhaust
- Y10T137/86622—Motor-operated
Definitions
- the present invention relates to a displacement control valve that variably controls a displacement or pressure of a working fluid, and in particular, controls a discharge amount of a variable displacement compressor used in an air conditioning system such as an automobile according to a pressure load. It relates to a displacement control valve.
- a swash plate type variable capacity compressor used in an air conditioning system of an automobile or the like is a rotary shaft that is rotationally driven by the rotational force of an engine, a swash plate that is variably connected to the rotational shaft, A compression piston or the like connected to the plate is provided, and by changing the inclination angle of the swash plate, the stroke of the piston is changed to control the discharge amount of the refrigerant gas.
- the inclination angle of the swash plate depends on the suction pressure of the suction chamber that sucks refrigerant gas, the discharge pressure of the discharge chamber that discharges the refrigerant gas pressurized by the piston, and the control chamber pressure of the control chamber (crank chamber) containing the swash plate Using a capacity control valve that is driven to open and close by electromagnetic force, the pressure in the control chamber can be controlled as appropriate, and the balance of pressure acting on both sides of the piston can be adjusted to change continuously. It's like! /
- Such a capacity control valve includes a discharge side passage for communicating the discharge chamber and the control chamber, a first valve chamber formed in the middle of the discharge side passage, and a suction side for communicating the suction chamber and the control chamber.
- the second valve part that opens and closes the valve body is designed to reciprocate and reciprocate at the same time, and to open and close in the opposite direction.
- the third valve chamber (capacitance chamber), a pressure sensitive body (bellows) that is placed in the third valve chamber and exerts an urging force in the direction of expansion (expansion) and contracts as the surrounding pressure increases.
- a valve seat body (engagement part) provided at the free end in the telescopic direction and having an annular seating surface. It is known that a third valve portion (valve opening connecting portion) that can open and close the suction side passage by engagement and disengagement with the valve seat body, a solenoid that exerts electromagnetic driving force on the valve body, and the like (for example, Patent text (See Appendix 1).
- control chamber pressure can be adjusted by communicating with the chamber.
- the third valve part valve connection part
- valve seat engagement part
- the suction chamber and the control chamber are configured to communicate with each other.
- Patent Document 1 Japanese Unexamined Patent Application Publication No. 2003-332086
- the present invention has been made in view of the above circumstances, and its object is to improve the performance of discharging liquid refrigerant from the control chamber, particularly immediately after the start of the variable displacement compressor. It is an object of the present invention to provide a capacity control valve capable of quickly performing desired capacity control, enabling stable capacity control, and reducing the overall size and cost.
- the capacity control valve of the present invention that achieves the above object is formed in the middle of the discharge side passage and the discharge side passage for communicating the discharge chamber for discharging the fluid and the control chamber for controlling the discharge amount of the fluid.
- the first valve chamber, the suction side passage for connecting the suction chamber for sucking fluid and the control chamber, the suction side passage A second valve chamber formed in the middle of the valve, a first valve portion for opening and closing the discharge side passage in the first valve chamber, and a second valve portion for opening and closing the suction side passage in the second valve chamber.
- a valve body that opens and closes in the opposite direction by the reciprocating movement, and is disposed in the third valve chamber and the third valve chamber formed closer to the control chamber than the second valve chamber in the middle of the suction side passage.
- the third valve portion having an annular engagement surface that moves integrally with the valve body in the third valve chamber and opens and closes the suction side passage by engagement and disengagement with the seat surface of the valve seat body
- a solenoid that exerts an electromagnetic driving force in the direction in which the first valve portion is closed, and one of the engagement surface of the third valve portion and the seat surface of the valve seat body.
- the other of the engagement surface of the third valve portion and the seat surface of the valve seat body is formed in a tapered surface shape having a central angle a satisfying 120 ° ⁇ ⁇ 160 °.
- variable displacement compressor when the variable displacement compressor is left in a stopped state for a long time with the solenoid turned off and the second valve portion blocking the suction side passage, liquid refrigerant accumulates in the control chamber and the control chamber.
- the solenoid is turned on and the valve body starts to start, the first valve portion moves in the valve closing direction and at the same time the second valve portion moves in the valve opening direction.
- the suction side passage is open, the liquid refrigerant in the control chamber is discharged from the suction side passage to the suction chamber.
- the other of the engaging surface of the third valve portion and the seating surface of the valve seat body is formed in a tapered surface shape having a central angle ⁇ satisfying the above conditions, so that the liquid refrigerant can be discharged efficiently.
- the third valve portion engages with the valve seat and closes, a centering action is obtained and a reliable closed state is obtained.
- one of the engagement surface of the third valve portion and the seat surface of the valve seat body is formed in a spherical shape with a radius of curvature of 9 mm ⁇ R ⁇ 11 mm. Can do.
- the other of the engaging surface of the third valve portion and the seating surface of the valve seat body is formed in a tapered surface shape having a central angle ⁇ satisfying the above condition, and the third valve portion
- One of the engagement surface and the seat surface of the valve seat body is formed in a spherical shape having a radius of curvature R that satisfies the above conditions, so that the liquid refrigerant can be discharged more efficiently and more quickly. It is possible to shift to capacity control.
- the third valve chamber is formed closer to the control chamber than the first valve chamber in the middle of the discharge side passage, and the third valve portion is inserted to the first valve chamber force to the third valve chamber.
- the valve body is provided on the opposite side of the second valve portion with the first valve portion interposed therebetween, and the valve body forms a part of the suction side passage so as to penetrate from the second valve portion to the third valve portion in the axial direction thereof.
- the suction side passage from the third valve chamber to the control chamber and the discharge side passage from the third valve chamber to the control chamber may be formed as the same passage.
- the first valve chamber in which the first valve portion is arranged, the second valve chamber in which the second valve portion is arranged, and the third valve chamber in which the third valve portion is arranged are changed to the third valve portion, It can be easily arranged along the longitudinal direction (reciprocating direction) of the valve body having the first valve portion and the second valve portion, and the overall integration, the simplification of the structure, and the miniaturization can be achieved.
- the third valve portion is formed in a divergent shape from the state in which the first valve chamber force is also reduced in diameter toward the third valve chamber, and has an annular engagement surface on the outer peripheral edge thereof.
- the valve seat body may have a concave shape and an annular seat surface on the outer periphery thereof.
- the pressure receiving area of the third valve portion is set larger than the pressure receiving area of the first valve portion. It is possible to adopt the configuration.
- the third valve portion becomes the first valve portion. Since the pressure is received in the direction in which the valve is closed, it is possible to suppress a sudden increase in the pressure in the control room and to obtain a gradual pressure change characteristic. Therefore, when the existing capacity control valve has such a gentle and strong pressure change characteristic, the capacity control valve of the present invention can be replaced with the existing capacity control valve without requiring any other changes.
- the effective diameter ⁇ b of the pressure-sensitive body and the seal diameter ⁇ rl of the third valve portion are formed so as to satisfy 0.8 ⁇ rl / b ⁇ l.0. Can be adopted. According to this configuration, at the time of start-up, the differential pressure between the control chamber and the suction chamber effectively acts in the direction of opening the third valve portion, and the valve opening amount of the third valve portion can be maximized. it can. Therefore, the liquid refrigerant accumulated in the control chamber is discharged more efficiently.
- the liquid refrigerant accumulated in the control chamber can be quickly discharged immediately after the variable capacity compressor is started, so that a desired capacity control can be performed.
- a displacement control valve that can perform the operation quickly and reliably, can perform stable displacement control, and can achieve overall downsizing and low cost.
- FIG. 1 is a schematic configuration diagram showing a swash plate type variable capacity compressor provided with a capacity control valve according to the present invention.
- FIG. 2 is a cross-sectional view showing an embodiment of a capacity control valve according to the present invention.
- FIG. 3 is a partially enlarged sectional view in which a part of the capacity control valve is enlarged.
- FIG. 4 is a partially enlarged sectional view in which a part of the capacity control valve is enlarged.
- FIG. 5 is a partially enlarged sectional view in which a part of the capacity control valve is enlarged.
- FIG. 6 is a partially enlarged cross-sectional view in which a third valve portion and a valve seat body in the capacity control valve are enlarged.
- FIG. 7 is a diagram showing the relationship between the radius of curvature R of the spherically formed surface and the flow path area in the relationship between the engagement surface of the third valve portion and the seating surface of the valve seat body in the capacity control valve. is there.
- the pressure receiving area of the third valve in the displacement control valve is larger than the pressure receiving area of the first valve It is a figure which shows the pressure characteristic in a case.
- FIG. 9 is a graph showing characteristics relating to the opening area of the third valve portion in the capacity control valve. Explanation of symbols
- this swash plate type variable capacity compressor ⁇ has a discharge chamber 11, a control chamber (also referred to as a crank chamber) 12, a suction chamber 13, a plurality of cylinders 14, a cylinder 14 and a discharge chamber 11.
- Port l ib opened / closed by discharge valve 11a
- port 13b opened / closed by suction valve 13a by connecting cylinder 14 and suction chamber 13, discharge port 11c and suction port 13c connected to an external cooling circuit
- a communication passage 15 serving as a discharge side passage for communicating the discharge chamber 11 and the control chamber 12, a communication functioning as the above-described discharge side passage and also serving as a suction side passage for communicating the control chamber 12 and the suction chamber 13.
- Casing 10 defining passage 16, communication passage 17 as a suction side passage, etc., rotating shaft 20 that protrudes from the inside of the control chamber (crank chamber) 12 to the outside, and is rotatable with the rotating shaft 20. Rotation and tilt angle is variable with respect to the rotation axis 20 Attached to the connected swash plate 21, a plurality of pistons 22 reciprocally fitted in each cylinder 14, a plurality of connecting members 23 connecting the swash plate 21 and each piston 22, and a rotary shaft 20.
- the driven pulley 24 and the capacity control valve V of the present invention incorporated in the casing 10 are provided.
- a cooling circuit is connected to the discharge port 11c and the suction port 13c in the variable capacity compressor M of the swash plate, and this cooling circuit includes a condenser (condenser) 25, an expansion valve 26, an evaporator (evaporation). Machine) 27 are arranged in sequence.
- the capacity control valve V includes a body 30 made of a metal material or a resin material, a valve body 40 reciprocally disposed in the body 30, and a valve body 40.
- Pressure sensing element 50 biased in the direction, solenoid 60 connected to body 30 and exerting electromagnetic driving force on valve body 40, etc. It has.
- the body 30 includes communication passages 31, 32, 33 that function as discharge-side passages, and communication passages 33 that function as suction-side passages together with communication passages 44 of a valve body 40 described later.
- 34 first valve chamber 35 formed in the middle of the discharge side passage, second valve chamber 36 formed in the middle of the suction side passage, guide passage 37 for guiding the valve element 40, discharge side passage and suction side passage
- a third valve chamber 38, etc. formed near the control chamber 12 is provided.
- a closing member 39 that defines a third valve chamber 38 and forms a part of the body 30 is attached to the body 30 by screwing.
- the communication passage 33 and the third valve chamber 38 are formed so as to also serve as a part of the discharge side passage and the suction side passage, and the communication passage 32 includes the first valve chamber 35 and the third valve chamber 38. And a valve hole through which the valve body 40 is inserted (passing through the valve body 40 while ensuring a gap through which fluid flows) is formed.
- the communication paths 31, 33, and 34 are formed in a plurality (for example, four with an interval of 90 degrees) arranged radially in the circumferential direction.
- a seat surface 35 a on which a first valve portion 41 of a valve body 40 described later is seated is formed at the edge of the communication passage (valve hole) 32, and the second valve chamber 36
- a seat surface 36a on which a second valve portion 42 of a valve body 40 described later is seated is formed at an end portion of the fixed iron core 64 described later.
- the suction side passage from the control chamber 12 to the third valve chamber 38 and the discharge side passage from the third valve chamber 38 to the control chamber 12 are formed as the same communication passage 33, the first valve The chamber 35, the second valve chamber 36, and the third valve chamber 38 can be easily arranged along the longitudinal direction (reciprocating direction) of the valve body 40, thereby consolidating the whole, simplifying the structure, and reducing the size. Can be achieved.
- the valve body 40 is formed in a substantially cylindrical shape, and includes a first valve portion 41 on one end side, a second valve portion 42 on the other end side, and a first valve portion 41.
- the third valve part 43 is connected by retrofitting on the opposite side of the second valve part 42, and extends in the axial direction from the second valve part 42 to the third valve part 43 and functions as a suction side passage. It has a communication passage 44 etc.
- the third valve portion 43 is formed in a state in which the state force reduced in diameter from the first valve chamber 35 to the third valve chamber 38 is also widened so as to pass through the communication passage (valve hole) 32 and to the outer peripheral edge of the third valve portion 43.
- the engagement surface 43a of the third valve portion 43 is formed in a spherical shape having an outward convex shape and a curvature radius R, and the value of the curvature radius R is 9 mm. ⁇ R ⁇ l lmm is formed.
- the pressure-sensitive body 50 includes a bellows 51, a coil spring 52 that is compressed in the bellows 51, a valve seat 53, and the like.
- One end of the bellows 51 is fixed to the closing member 39, and the valve seat 53 is held at the other end (free end).
- the valve seat body 53 includes an annular seat surface 53a that engages and disengages in the outer peripheral edge of the valve seat body 53 so as to face and engage with the engagement surface 43a of the third valve portion 43.
- the seat surface 53a of the valve seat body 53 is formed in a tapered surface shape having a concave shape outwardly (direction facing the third valve portion 43) and a central angle ⁇ .
- the central angle ex is formed so that the value of 120 ° ⁇ ⁇ 160 ° is satisfied.
- the pressure-sensitive body 50 is disposed in the third valve chamber 38 and exerts an urging force in the direction of opening the first valve portion 41 due to its expansion (expansion), and the surroundings (the third valve chamber 38 and the valve). It operates so as to weaken the urging force exerted on the first valve portion 41 by contracting as the pressure in the communication passage 44 of the body 40 increases.
- the radius of curvature R of the spherical engagement surface 43a is 9 mm ⁇
- the effective diameter ⁇ b of the bellows 51 (which defines the effective pressure receiving area) is about ⁇ 8 mm.
- the solenoid 60 has a solenoid body 61 connected to the body 30, a casing 62 that surrounds the entire body, a sleeve 63 that is closed at one end, a solenoid body 61, and a sleeve 63.
- the movable iron core 66 fixed to the coil, the coil spring 67 that urges the movable iron core 66 in the direction to open the first valve portion 41, and the exciting coil wound around the outside of the sleeve 63 via a bobbin. It has 68 mag.
- the valve body 40 is driven by the electromagnetic driving force (biasing force) of the solenoid 60 acting in the opposite direction to the urging force of the pressure sensing body 50 and the coil spring 67. Moves to the left side in FIG. 5 and the first valve part 41 is seated on the seat surface 35a and closes the communication passages (discharge side passages) 31, 32, and at the same time the second valve part 42 moves away from the seat surface 36a. Open communication passage (suction side passage) 34, 44. Immediately after this start-up, when the control chamber pressure Pc is above a predetermined level, as shown in FIG.
- the state force that the valve seat 53 is released from the third valve part 43 and opens the suction side passage is also applied to the third valve. Until the portion 43 is seated on the valve seat 53, the liquid refrigerant or the like accumulated in the control chamber 12 is discharged to the suction chamber 13 through the communication passages (suction side passages) 44, 34.
- the pressure receiving area of the pressure sensitive body 50 (the bellows 51) with the effective diameter ⁇ !) Is Ab
- the seal diameter ⁇ ⁇ : 1 of the third valve portion 43 is
- the pressure receiving area at the seal diameter of the first valve part 41 is As
- the pressure receiving area at the seal diameter of the second valve part 42 is Ar2
- the biasing force of 50 is Fb
- the biasing force of the coil spring 67 is Fs
- the biasing force due to the electromagnetic driving force of the solenoid 60 is Fsol
- the discharge pressure of the discharge chamber 11 is Pd
- the suction pressure of the suction chamber 13 is Ps
- the pressure receiving area Ab of the pressure sensing body 50 and the pressure receiving area Arl of the third valve portion 43 are formed to be the same, and the pressure receiving area As of the first valve portion 41 is equal to the first pressure receiving area As.
- the pressure receiving area Ar 2 of the two valve sections 42 is formed to be the same, and the pressure receiving area Arl of the third valve section 43 is formed to be larger than the pressure receiving area As of the first valve section 41.
- the discharge pressure Pd acting on the valve body 40 is offset and the influence can be prevented, and the operation of the valve body 40 is not affected by the discharge pressure Pd. This makes it possible to perform stable capacity control.
- the third valve part 43 receives the discharge pressure Pd in the direction to close the first valve part 41 by an amount corresponding to the difference in pressure receiving area (Arl-As).
- the control chamber pressure Pc can be prevented from abruptly rising so that the characteristic indicated by the solid line is changed from the characteristic indicated by the two-point difference line, and a gradual pressure change characteristic can be obtained. Therefore, when the existing capacity control valve has such a gentle pressure change characteristic, it is possible to replace the capacity control valve V of the present invention with the existing capacity control valve without changing other configurations such as control software. it can.
- the discharge amount of the refrigerant gas is determined by the stroke of the piston 22, and the stroke of the piston 22 is determined by the inclination angle of the swash plate 21 controlled by the pressure in the control chamber 12 (control chamber pressure Pc). .
- the engagement surface 43a of the third valve portion 43 is formed in a spherical shape having a radius of curvature R (9 mm ⁇ R ⁇ 11 mm), and the seat surface 53a of the valve seat body 53 has a central angle ⁇ ( 120 ° ⁇ a and 160 °), the liquid refrigerant is discharged efficiently, and the desired capacity control can be quickly performed.
- the solenoid 60 (coil 68) is de-energized, and the movable iron core 66 and the drive rod 65 are retracted by the urging force of the coil springs 52 and 67.
- the first valve portion 41 is separated from the seat surface 35a to open the communication passages (discharge side passages) 31, 32, and the second valve portion 42 is seated on the seat surface 36a to enter the communication passage (suction).
- the valve body 40 moves to a position where the side passages 34 and 44 are closed.
- the discharge fluid discharge pressure Pd
- the inclination angle of the swash plate 21 is controlled to be the smallest, and the stroke of the piston 22 is minimized.
- the refrigerant gas discharge amount is minimized.
- the solenoid 60 (coil 68) is energized at a predetermined current value (I), and the movable iron core 66 and the drive rod 65 are connected to the pressure sensitive body 50 and the coil spring 67.
- the first valve part 41 is seated on the seating surface 35a against the urging force of the valve, closing the communication passages (discharge side passages) 31, 32, and the second valve part 42 moving away from the seating surface 36a. (Suction side passage)
- the valve element 40 moves to a position where the 34, 44 is opened.
- the pressure sensing body 50 receives the pressure and contracts, and the valve seat body 53 disengages from the third valve portion 43.
- the fluid (refrigerant gas, blowby gas, etc.) accumulated in the control chamber 12 passes through the communication passages (suction side passages) 33, 44, 34 to the suction chamber. Discharged to 13.
- the inclination angle of the swash plate 21 is controlled to be the largest, and the stroke of the piston 22 is maximized. As a result, the discharge amount of the refrigerant gas is maximized.
- the electromagnetic driving force biasing force
- the position of the valve body 40 is appropriately adjusted by the electromagnetic driving force, and the valve opening amount of the first valve portion 41 and the valve opening amount of the second valve portion 42 are controlled so as to obtain a desired discharge amount.
- the third valve chamber 38 in which the pressure sensitive body 50 (valve seat 53) and the third valve portion 43 are arranged is provided in the middle of the communication path that also serves as the discharge side passage and the suction side passage.
- it may be provided in the middle of the inhalation-side passage formed as a separate route that is not limited to this.
- the force shown in the case where the pressure receiving area Ab of the pressure sensing body 50 is formed to be the same as the pressure receiving area Ar1 of the third valve portion 43 is not limited to this.
- One of the mating surface 43a and the seating surface 53a of the valve seat body 54 is formed in a spherical shape, and the other of the engagement surface 43a of the third valve portion 43 and the seating surface 53a of the valve seat body 54 is 120 ° ⁇ A center angle ⁇ satisfying ⁇ ⁇ 160 °
- the relationship between the effective diameter ⁇ b of the pressure sensing body 50 and the seal diameter ⁇ rl of the third valve part 43 is
- the differential pressure (Pc —Ps) effectively acts in the direction of opening the third valve portion 43, and as shown in FIG. 9, the valve opening amount (opening area) of the third valve portion 43 can be maximized. Therefore, the liquid refrigerant accumulated in the control chamber 12 is discharged more efficiently.
- the engagement surface 43a of the third valve portion 43 is formed in a spherical shape with a radius of curvature R that satisfies 9mm ⁇ R ⁇ 11mm, and the seat surface 53a of the valve seat 53 is 120. °
- the figure shows the case where it is formed in a tapered surface with a central angle ⁇ satisfying 160 °, but this is not limited to this, and conversely the engagement surface 43a of the third valve part 43 is 120 ° ⁇
- a configuration is adopted in which the seat surface 53a of the valve seat 53 is formed into a spherical surface with a radius of curvature R that satisfies 9mm ⁇ R ⁇ 11mm.
- one of the engagement surface 43a of the third valve portion 43 and the seat surface 53a of the valve seat body 53 is formed in a spherical shape, and the engagement surface 43a of the third valve portion 43 and the valve seat body are formed.
- the other of the 53 seating surfaces 53a may be formed in a tapered surface shape having a central angle OC satisfying 120 ° ⁇ ⁇ 160 °.
- the relationship between the central angle ⁇ and the radius of curvature R is not limited to the above, but the same effect can be obtained for each combination of 9 mm ⁇ R ⁇ 11 mm and 120 ° ⁇ ⁇ 160 °. Play.
- the capacity control valve of the present invention quickly and reliably performs desired capacity control by quickly discharging the liquid refrigerant accumulated in the control chamber immediately after the start of the variable capacity compressor.
- it can be applied to a variable displacement compressor used in an air conditioning system of an automobile or the like, and the capacity of other fluids can be achieved. It is also useful as a capacity control valve that controls the capacity of a machine that variably controls the engine.
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- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2007504759A JP4700048B2 (ja) | 2005-02-24 | 2006-02-23 | 容量制御弁 |
EP20060714371 EP1852606B1 (en) | 2005-02-24 | 2006-02-23 | Capacity control valve |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2005-049575 | 2005-02-24 | ||
JP2005049575 | 2005-02-24 |
Publications (1)
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WO2006090760A1 true WO2006090760A1 (ja) | 2006-08-31 |
Family
ID=36927398
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2006/303231 WO2006090760A1 (ja) | 2005-02-24 | 2006-02-23 | 容量制御弁 |
Country Status (6)
Country | Link |
---|---|
US (1) | US8021124B2 (ja) |
EP (1) | EP1852606B1 (ja) |
JP (1) | JP4700048B2 (ja) |
KR (1) | KR101175201B1 (ja) |
CN (1) | CN100516516C (ja) |
WO (1) | WO2006090760A1 (ja) |
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Also Published As
Publication number | Publication date |
---|---|
JP4700048B2 (ja) | 2011-06-15 |
EP1852606A4 (en) | 2010-03-17 |
CN101124405A (zh) | 2008-02-13 |
EP1852606A1 (en) | 2007-11-07 |
KR101175201B1 (ko) | 2012-08-20 |
EP1852606B1 (en) | 2012-06-20 |
CN100516516C (zh) | 2009-07-22 |
JPWO2006090760A1 (ja) | 2008-07-24 |
KR20070103737A (ko) | 2007-10-24 |
US20080138213A1 (en) | 2008-06-12 |
US8021124B2 (en) | 2011-09-20 |
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