WO2011065693A2 - Vanne de commande de cylindrée pour compresseur à cylindrée variable - Google Patents

Vanne de commande de cylindrée pour compresseur à cylindrée variable Download PDF

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Publication number
WO2011065693A2
WO2011065693A2 PCT/KR2010/007938 KR2010007938W WO2011065693A2 WO 2011065693 A2 WO2011065693 A2 WO 2011065693A2 KR 2010007938 W KR2010007938 W KR 2010007938W WO 2011065693 A2 WO2011065693 A2 WO 2011065693A2
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WO
WIPO (PCT)
Prior art keywords
valve
guide hole
valve body
sleeve
hole
Prior art date
Application number
PCT/KR2010/007938
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English (en)
Korean (ko)
Other versions
WO2011065693A3 (fr
Inventor
이건호
이용주
곽용석
Original Assignee
두원공과대학교
주식회사 두원전자
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
Priority claimed from KR1020090113692A external-priority patent/KR101631217B1/ko
Priority claimed from KR1020090113696A external-priority patent/KR101083671B1/ko
Priority claimed from KR1020090113694A external-priority patent/KR101083678B1/ko
Application filed by 두원공과대학교, 주식회사 두원전자 filed Critical 두원공과대학교
Priority to CN201080058095.2A priority Critical patent/CN102667154B/zh
Publication of WO2011065693A2 publication Critical patent/WO2011065693A2/fr
Publication of WO2011065693A3 publication Critical patent/WO2011065693A3/fr

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Classifications

    • 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
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0603—Multiple-way valves
    • F16K31/0624—Lift valves
    • F16K31/0634—Lift valves with fixed seats positioned between movable valve 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
    • F04B27/14—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
    • F04B2027/1813—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
    • F04B2027/1822—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
    • F04B2027/1854—External parameters

Definitions

  • the present invention relates to a capacity control valve of a variable displacement compressor, and more particularly, to a capacity control valve of a variable displacement compressor that can be quickly discharged when the crankcase pressure of the compressor rapidly increases.
  • 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 changed. Will be controlled.
  • FIG. 1 is a longitudinal sectional view showing a capacity control valve of a variable displacement compressor according to the prior art.
  • the capacity control valve 10 As shown in FIG. 1, the capacity control valve 10 according to the related art is installed to be movable in the valve housing 11, the electromagnetic solenoid 13, and the valve housing 11 in which some connection holes are formed.
  • the valve body 12 is included.
  • the valve housing 11 is formed with a first guide hole 14 for guiding the movement of the valve body 12.
  • valve body 12 is reciprocated to open and close the first guide hole 14 formed in the valve housing 11.
  • the valve housing 11 has a crank chamber connecting hole 15 and a discharge chamber connecting hole 16 in which the pressure Pc of the crank chamber and the pressure Pd of the discharge chamber respectively act.
  • the discharge chamber connecting hole 16 and the crank chamber connecting hole 15 are configured to communicate with each other through the first guide hole 14.
  • valve housing 11 has a suction chamber connecting hole 17 formed at a lower end of the discharge chamber connecting hole 16.
  • a sleeve member 18 is provided at the end of the valve body 12 to be configured to connect between the valve body 12 and the solenoid 13.
  • a sleeve bore 19 is formed in the valve housing 11 in which the sleeve member 18 is installed, and a sleeve 20 corresponding to the sleeve bore 19 is formed in the sleeve member 18.
  • the sleeve member 18 is provided with an accommodating portion 21 therein, and the accommodating portion 21 is provided with a bellows 22.
  • the valve housing 11 is provided with a cap 23 which is screwed in a direction facing the end of the valve body 12, and a support spring 24 between the valve body 12 and the cap 23. ) Is provided to regulate the expansion force of the bellows 22 and the expansion force of the first spring 25 installed therein.
  • the cap 23 is formed so that a part is open is configured to act on the pressure (Pc) of the crank chamber.
  • the present invention has been made to solve the above-mentioned conventional problems, and an object of the present invention is to provide a capacity control valve of a variable displacement compressor capable of quickly discharging when the pressure of the crankcase rapidly increases. .
  • 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 crank chamber connection hole and the discharged crank chamber pressure and discharge chamber pressure and suction chamber pressure of the compressor
  • a valve housing having a seal 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 that opens and closes the first guide hole inlet while reciprocating;
  • An electromagnetic solenoid for reciprocating the valve body by energization;
  • a sleeve connecting the solenoid and the valve body; And a bleed valve for controlling communication between the crank chamber and the suction chamber by the movement of the sleeve.
  • the bleed valve preferably includes a second guide hole formed inside the valve housing and an auxiliary valve body for opening and closing the inlet of the second guide hole while reciprocating.
  • an inflow passage connecting the crank chamber connecting hole and the second guide hole is formed inside the valve housing, and a discharge passage connecting the second guide hole and the suction chamber connecting hole is preferably formed.
  • valve body for opening and closing the first guide hole and the auxiliary valve body for opening and closing the second guide hole is preferably formed in a direction facing each other.
  • the valve housing may further include a cap facing the end of the valve body so as to open and close the bleed valve by the movement of the valve body.
  • the bleed valve, the large diameter portion and the sleeve formed in the valve body to open and close the inlet of the second guide hole and the second guide hole formed on the inner circumferential surface of the cap so as to be connected to the crankcase connecting hole It is preferable to include a discharge groove formed in.
  • valve body is preferably formed with a small diameter portion having a smaller outer circumferential diameter than the inner circumferential surface diameter of the second guide hole to form a connection flow path between the second guide hole and the small diameter portion.
  • the inlet flow passage connecting the connection flow path and the discharge groove is formed in the sleeve, it is preferable that the discharge passage for connecting the discharge groove and the suction chamber connecting hole is formed in the valve housing.
  • discharge passage is preferably formed between the valve housing and the sleeve.
  • the relief valve is preferably opened if the pressure of the crank chamber or the difference between the crank chamber pressure and the suction chamber pressure is more than the set value.
  • the relief valve may include a relief valve body having a through hole formed therein and inserted into the sleeve, a valve bushing for opening and closing the through hole while reciprocating, and a discharge passage formed at an outer circumference of the valve bushing. desirable.
  • the bellows is formed at the lower end of the valve bushing.
  • the bellows has a first support spring is embedded, it is preferable to be located inside the sleeve.
  • a biasing means is provided between the valve bushing and the inside of the sleeve to apply a biasing force in a direction of opening the through hole of the relief valve, and one end of which is supported inside the sleeve.
  • the relief valve preferably comprises a relief valve body for opening and closing the third guide hole and the third guide hole formed in the sleeve and reciprocating movement.
  • a bellows is formed at a lower end of the relief valve body.
  • the bellows has a first support spring is embedded, it is preferable to be located inside the sleeve.
  • a biasing means for supporting one end is provided inside the sleeve.
  • the relief valve is formed with a notch having a flat outer circumferential surface.
  • the discharge passage is formed between the cutout and the inside of the sleeve.
  • the bleed valve, the second guide hole formed on the inner circumferential surface of the cap to be connected to the crankcase connecting hole and the large diameter portion formed in the valve body to open and close the inlet of the second guide hole while reciprocating desirable.
  • valve body has a small diameter portion having a smaller outer circumferential diameter than the inner circumferential surface diameter of the second guide hole so that a connection flow path is formed between the second guide hole and the small diameter portion.
  • the liquid refrigerant evaporated from the crank chamber during the initial operation of the compressor smoothly discharged to the suction chamber to prevent the operation delay of the compressor and at the same time easy to move to the maximum inclination angle of the swash plate.
  • 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 a longitudinal sectional view showing the structure of a variable displacement compressor according to the present invention.
  • FIG. 3 is a longitudinal sectional view showing a structure of a capacity control valve according to a first embodiment of the present invention of FIG.
  • FIG. 4 is a longitudinal sectional view showing the structure of the displacement control valve of FIG.
  • FIG. 5 is a longitudinal sectional view showing a structure of a capacity control valve according to a second embodiment of the present invention of FIG.
  • FIG. 6 is an enlarged vertical cross-sectional view of a portion of the capacity control valve of FIG. 5.
  • FIG. 7 is a longitudinal sectional view showing a structure of a capacity control valve according to a third embodiment of the present invention of FIG.
  • FIG. 8 is an enlarged longitudinal sectional view of a portion of the capacity control valve of FIG. 7.
  • FIG. 9 is a longitudinal sectional view showing a structure of a capacity control valve according to another embodiment of FIG. 7.
  • FIG. 10 is an enlarged vertical cross-sectional view of a portion of the capacity control valve of FIG. 9.
  • FIG. 2 is a longitudinal sectional view showing the structure of a variable displacement compressor according to the present invention
  • Figure 3 is a longitudinal sectional view showing the structure of a displacement control valve according to a first embodiment of the present invention of Figure 2
  • Figure 4 is a 5 is an enlarged longitudinal sectional view of a part of the capacity control valve
  • FIG. 5 is a longitudinal sectional view showing the structure of the capacity control valve according to the second embodiment of the present invention of FIG. 2
  • FIG. 6 is a part of the capacity control valve of FIG. 7 is an enlarged vertical cross-sectional view
  • FIG. 7 is a vertical cross-sectional view illustrating a structure of a capacity control valve according to another embodiment of FIG. 5, and FIG.
  • FIG. 8 is an enlarged vertical cross-sectional view of a portion of the capacity control valve of FIG. 7.
  • 9 is a longitudinal sectional view showing the structure of the displacement control valve according to the third embodiment of the present invention of FIG. 2, and
  • FIG. 10 is a longitudinal sectional view showing the structure of the displacement control valve of FIG.
  • 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 includes a cylinder block 10 having a plurality of cylinder bores 12 formed on an inner circumferential surface in parallel in a longitudinal direction thereof, and a cylinder block 10 of the cylinder block 10.
  • the front housing 16 is hermetically coupled to the front, and the rear housing 18 hermetically coupled via a valve plate 20 to the rear of the cylinder block 10.
  • 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 according to the first embodiment of the present invention, the valve housing 110, the electromagnetic solenoid 130, the valve housing 110 is formed with a plurality of connection holes It includes a valve body 120 that is installed to be movable in the interior.
  • 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.
  • 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 140 is provided at an end of the valve body 120 to be configured to connect between the valve body 120 and the solenoid 130.
  • a sleeve bore 119 is formed in the valve housing 110 in which the sleeve 140 is installed, and a needle 141 corresponding to the sleeve bore 119 is formed in the sleeve 140.
  • the needle 141 is preferably formed larger than the diameter of the valve body 120.
  • the needle 141 penetrates through the valve body 120 and is preferably fixed to prevent relative movement.
  • a bleed valve 150 for connecting the crank chamber 86 and the suction chamber 32 by the movement of the sleeve 140 is further provided.
  • the bleed valve 150 is a secondary valve formed in the sleeve 140 to open and close the inlet of the second guide hole 151 and the second guide hole 151 formed in the valve housing 110 and reciprocating. Sieve 152.
  • valve body 120 for opening and closing the first guide hole 117 and the auxiliary valve body 152 for opening and closing the second guide hole 151 are formed in directions facing each other.
  • valve housing 110 is formed with an inflow passage 153 for connecting the crank chamber connecting hole 112 and the second guide hole 151, between the valve housing 110 and the sleeve 140 A discharge passage 154 connecting the second guide hole 151 and the suction chamber connecting hole 111 is formed.
  • the discharge passage 154 is preferably connected to the suction chamber (22).
  • the auxiliary valve body 152 opens the second guide hole 151 to open the second guide hole 151 at the time of initial driving of the compressor in which the crank chamber 86 pressure Pc of the compressor is rapidly increased by the bleed valve 150 configured as described above.
  • the chamber 86 pressure Pc is quickly discharged to the suction chamber 22.
  • the auxiliary valve body 152 formed in the sleeve 140 moves downward to open the second guide hole 151, and when the current is blocked in the solenoid 130.
  • the auxiliary valve body 152 moves upward to close the second guide hole 151.
  • the liquid refrigerant evaporated from the crank chamber 86 during the initial driving of the compressor is smoothly discharged to the suction chamber 22 to prevent the operation delay of the compressor and at the same time the swash plate ( It is easy to move to the maximum inclination angle of 50).
  • the electromagnetic solenoid 130 surrounds the movable iron core 131 connected to the sleeve 140, the electromagnetic coil 132 disposed around the movable iron core 131, the electronic coil 132, and the like. It 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 third 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 140, and the valve body 120 reciprocate by energizing the electromagnetic solenoid 130, and the discharge chamber connecting hole 113 by the valve body 120. And the inlet of the first guide hole 117 connecting between the crank chamber connecting hole 112 is opened and closed.
  • an off-spring 125 is installed between the fixed iron core 133 and the movable iron core 131.
  • the valve body 120 In the absence of external force, the valve body 120 is raised to raise the first guide hole 117.
  • the inlet is maintained in an open state, while the second guide hole 151 maintains a state in which the second valve body 152 is lifted up.
  • 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 140 and the first guide hole 117 are formed.
  • an accommodating part 170 is formed inside the sleeve 140, and a bellows 160 is installed in the accommodating part 170.
  • 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 (140).
  • first support spring 162 may be built in the bellows 160 to maintain the expanded state.
  • 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 an electromagnetic force proportional to the current without being affected by the generated heat.
  • a ring groove 136 is formed in the rod 135, and 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 capacity control valve 100 according to the second embodiment of the present invention, the valve housing 110, the electromagnetic solenoid 130, the valve housing 110 is formed with a plurality of connection holes It includes a valve body 120 that is installed to be movable in the interior.
  • 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.
  • 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 140 is provided at an end of the valve body 120 to be configured to connect between the valve body 120 and the solenoid 130.
  • a sleeve bore 119 is formed in the valve housing 110 in which the sleeve 140 is installed, and a needle 141 corresponding to the sleeve bore 119 is formed in the sleeve 140.
  • the needle 141 is preferably formed larger than the diameter of the valve body 120.
  • the needle 141 penetrates the valve body 120 and is preferably fixed to prevent relative movement.
  • valve housing 110 is provided with a cap 165 that is screwed in a direction facing the end of the valve body 120, the cap 165 is formed so that part of the crank chamber 86 Is configured to act.
  • a bleed valve 150 for connecting the crank chamber 86 and the suction chamber 32 by the movement of the sleeve 120 is further provided.
  • the bleed valve 150 is the second guide hole 151 formed on the inner circumferential surface of the cap 165 to be connected to the crankcase connecting hole 112 and the inlet of the second guide hole 151 while reciprocating It includes a large diameter portion 152 formed in the valve body 120 and the discharge groove 153 formed in the sleeve 140 to be connected to the second guide hole 151 to open and close. At this time, the discharge groove 153 is preferably connected to the suction chamber connecting hole (111).
  • a small diameter portion 154 having a smaller outer circumferential diameter than an inner circumferential surface diameter of the second guide hole 151 is formed in the valve body 120 to connect the flow path between the second guide hole 151 and the small diameter portion 154 ( 155 is formed.
  • an inflow passage 156 is formed in the sleeve 140 to connect the connection passage 155 and the discharge groove 153, and the discharge groove 153 is formed between the valve housing 110 and the sleeve 140.
  • a discharge passage 157 is formed to connect the suction chamber connecting hole 122.
  • the large diameter portion 152 of the valve body 120 is the second guide hole 151 at the time of initial driving of the compressor in which the crank chamber 86 pressure Pc of the compressor is rapidly increased by the bleed valve 150 configured as described above. ), The crank chamber 86 pressure Pc is quickly discharged into the suction chamber 22.
  • the liquid refrigerant evaporated from the crank chamber 86 during the initial driving of the compressor is smoothly discharged to the suction chamber 22 to prevent the operation delay of the compressor and at the same time the swash plate ( It is easy to move to the maximum inclination angle of 50).
  • the electromagnetic solenoid 130 surrounds the movable iron core 131 connected to the sleeve 140, the electromagnetic coil 132 disposed around the movable iron core 131, the electronic coil 132, and the like. It 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 third 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 140, and the valve body 120 reciprocate by energizing the electromagnetic solenoid 130, and the discharge chamber connecting hole 113 by the valve body 120. And the inlet of the first guide hole 117 connecting between the crank chamber connecting hole 112 is opened and closed.
  • an off-spring 125 is installed between the fixed iron core 133 and the movable iron core 131.
  • the valve body 120 In the absence of external force, the valve body 120 is raised to raise the first guide hole 117. The inlet of the to maintain the open state, while the second guide hole 151 maintains the closed state by the large diameter portion 152 of the valve body 120 is raised.
  • 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 140 and the first guide hole 117 are formed.
  • an accommodating part 170 is formed inside the sleeve 140, and a bellows 160 is installed in the accommodating part 170.
  • 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 (140).
  • first support spring 162 may be built in the bellows 160 to maintain the expanded state.
  • 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 an electromagnetic force proportional to the current without being affected by the generated heat.
  • a ring groove 136 is formed in the rod 135, and 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 capacity control valve 100 may include a valve housing 110, an electronic solenoid 130, and the valve housing 110 in which a plurality of connection holes are formed. It includes a valve body 120 that is installed to be movable in the interior.
  • 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.
  • 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 140 is provided at an end of the valve body 120 to be configured to connect between the valve body 120 and the solenoid 130.
  • a sleeve bore 119 is formed in the valve housing 110 in which the sleeve 140 is installed, and a needle 141 corresponding to the sleeve bore 119 is formed in the sleeve 140.
  • the needle 141 is preferably formed larger than the diameter of the valve body 120.
  • the needle 141 penetrates through the valve body 120 and is preferably fixed to prevent relative movement.
  • valve housing 110 is provided with a cap 165 that is screwed in a direction facing the end of the valve body 120, the cap 165 is formed so that part of the crank chamber 86 Is configured to act.
  • a bleed valve 150 for connecting the crank chamber 86 and the suction chamber 32 by the movement of the sleeve 120 is further provided.
  • the bleed valve 150 is the second guide hole 151 formed on the inner circumferential surface of the cap 165 to be connected to the crankcase connecting hole 112 and the inlet of the second guide hole 151 while reciprocating It includes a large diameter portion 152 formed in the valve body 120 to open and close. At this time, the second guide hole 151 is preferably connected to the suction chamber connecting hole 111.
  • valve body 120 is formed with a small diameter portion 153 having a smaller outer circumferential surface diameter than the inner circumferential surface diameter of the second guide hole 151 to connect the flow path between the second guide hole 151 and the small diameter portion 153 ( 154 is formed.
  • the relief valve 190 is opened to connect the crank chamber 86 and the suction chamber 22. It is provided.
  • the relief valve 190 according to the exemplary embodiment illustrated in FIGS. 7 to 8 has a through hole 191 formed therein and is reciprocated with the Rarif valve body 192 which is press-fitted into the sleeve 140.
  • a valve bushing 193 installed between the sleeve 140 and the relief valve body 192 to open and close the through hole 191, and a discharge passage formed between the valve bushing 193 and the sleeve 140. (194).
  • the valve bushing 193 is to open and close the through hole 191 by the pressure (Pc) of the crank chamber 86 directly acts.
  • a bellows 160 having a first support spring 162 having elastic support for the valve bushing 193 is further provided, and the bellows 160 is disposed at a lower end of the valve bushing 193. 140). A detailed installation position of the bellows 160 will be described later.
  • a force is applied between the valve bushing 193 and the inside of the sleeve 140 in a direction of opening the through hole 191 of the relief valve 190, and one end is supported inside the sleeve 140.
  • the biasing means 181 is installed.
  • the valve bushing 193 maintains the through hole 191 in a closed state by the bellows 160 in which the first support spring 162 is built.
  • the set pressure of the relief valve 190 is adjusted by the elastic force of the bellows 160 in which the first support spring 162 is incorporated.
  • a first inflow passage 195 connected to the crank chamber 86 is formed in the sleeve 140, and a second inflow passage communicating with the first inflow passage 195 is formed in the relief valve body 192. 196 is formed.
  • a relief valve 190 ′ according to another embodiment illustrated in FIGS. 9 to 10 includes a third guide hole 191 ′ formed in the sleeve 140 and the third guide hole 191 ′ while reciprocating. It includes a relief valve body (192 ') for opening and closing the. In this case, the relief valve body 192 ′ opens and closes the third guide hole 191 ′ by acting directly on the pressure Pc of the crank chamber 86.
  • a bellows 160 having a built-in first support spring 162 for elastically supporting the relief valve body 192 ' is further provided, and the bellows 160 is disposed at a lower end of the relief valve body 192'. It is installed in the sleeve 140 to be located. A detailed installation position of the bellows 160 will be described later.
  • a force is applied between the relief valve 190 'and the inner side of the sleeve 140 in the direction of opening the third guide hole 191', and one end supported by the inner side of the sleeve 140.
  • Means 181 are installed.
  • the relief valve body 192 maintains the third guide hole 191' closed.
  • the set pressure of the relief valve 190 ' is adjusted by the elastic force of the bellows 160 in which the first support spring 162 is incorporated.
  • the relief valve body 192 ′ is formed with a cutout portion 193 ′ having a flat outer circumferential surface, and a discharge passage 194 ′ is formed between the cutout portion 193 ′ and the sleeve 140.
  • the cutouts 193 ' are formed in plural along the outer circumferential surface of the relief valve body 192'.
  • first inflow passage 195 ' is formed in the sleeve 140 to be connected to the crank chamber 86, and a second inflow passage 195' is connected to the relief valve body 192 '.
  • An inflow passage 196 ' is formed.
  • the electromagnetic solenoid 130 surrounds the movable iron core 131 connected to the sleeve 140, the electromagnetic coil 132 disposed around the movable iron core 131, the electronic coil 132, and the like. It 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 fourth 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 140, and the valve body 120 reciprocate by energizing the solenoid 130, and at the same time, the discharge chamber connecting hole 113 by the valve body 120. And the inlet of the first guide hole 117 connecting between the crank chamber connecting hole 112 is opened and closed.
  • an off-spring 125 is installed between the fixed iron core 133 and the movable iron core 131.
  • the valve body 120 In the absence of external force, the valve body 120 is raised to raise the first guide hole 117. The inlet of the to maintain the open state, while the second guide hole 151 maintains the closed state by the large diameter portion 152 of the valve body 120 is raised.
  • 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 140 and the first guide hole 117 are formed.
  • an accommodating part 170 is formed inside the sleeve 140, and a bellows 160 is installed in the accommodating part 170.
  • 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 (140).
  • first support spring 162 may be built in the bellows 160 to maintain the expanded state.
  • 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 an electromagnetic force proportional to the current without being affected by the generated heat.
  • a ring groove 136 is formed in the rod 135, and 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.

Abstract

La présente invention concerne une vanne de commande de cylindrée pour un compresseur à cylindrée variable. La vanne de commande de cylindrée comprend: un corps de vanne comportant un orifice de connexion pour une chambre de vilebrequin et un orifice de raccordement pour une chambre d'aspiration formé dans celui-ci, qui reçoivent respectivement la pression de la chambre de vilebrequin du compresseur, de la chambre de sortie et de la chambre d'aspiration et comportant également un premier orifice de guidage formé de manière à pénétrer dans ce dernier, qui est positionné entre l'orifice de raccordement de la chambre de sortie et l'orifice de raccordement de la chambre de vilebrequin; un corps de vanne qui, lorsqu'il est animé d'un mouvement de va-et-vient, ouvre et ferme l'ouverture du premier orifice de guidage; et un solénoïde électronique qui provoque le mouvement de va-et-vient de la vanne par application de courant électrique; un manchon qui relie le solénoïde électronique et le corps de vanne; ainsi qu'une vanne d'extraction d'air qui commande le couplage entre la chambre de vilebrequin et la chambre d'aspiration au moyen du mouvement du manchon. De cette manière, lorsque la pression dans la chambre de vilebrequin du compresseur augmente rapidement, la pression peut être rapidement relâchée par la chambre d'aspiration au moyen de la vanne d'extraction d'air.
PCT/KR2010/007938 2009-11-24 2010-11-11 Vanne de commande de cylindrée pour compresseur à cylindrée variable WO2011065693A2 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201080058095.2A CN102667154B (zh) 2009-11-24 2010-11-11 用于变排量压缩机的排量控制阀

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
KR1020090113692A KR101631217B1 (ko) 2009-11-24 2009-11-24 용량가변형 압축기의 용량제어밸브
KR10-2009-0113696 2009-11-24
KR10-2009-0113692 2009-11-24
KR1020090113696A KR101083671B1 (ko) 2009-11-24 2009-11-24 용량가변형 압축기의 용량제어밸브
KR10-2009-0113694 2009-11-24
KR1020090113694A KR101083678B1 (ko) 2009-11-24 2009-11-24 용량가변형 압축기의 용량제어밸브

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US11053933B2 (en) * 2018-12-13 2021-07-06 Eagle Industry Co., Ltd. Displacement control valve
EP3722603A4 (fr) * 2017-12-08 2021-07-14 Eagle Industry Co., Ltd. Soupape de régulation de capacité et procédé de régulation associé

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JP6064132B2 (ja) * 2012-10-09 2017-01-25 株式会社テージーケー 複合弁
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CN110005869B (zh) * 2019-04-17 2021-07-06 上海进纬仪器设备有限公司 一种波纹管及具有该波纹管的电磁阀

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JP2008157116A (ja) * 2006-12-25 2008-07-10 Saginomiya Seisakusho Inc 容量制御弁および容量可変型圧縮機並びに空気調和装置
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EP3722603A4 (fr) * 2017-12-08 2021-07-14 Eagle Industry Co., Ltd. Soupape de régulation de capacité et procédé de régulation associé
US11053933B2 (en) * 2018-12-13 2021-07-06 Eagle Industry Co., Ltd. Displacement control valve
CN113474553A (zh) * 2018-12-13 2021-10-01 伊格尔工业股份有限公司 排量控制阀

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CN102667154A (zh) 2012-09-12
CN102667154B (zh) 2015-01-21

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