WO2011016589A1 - Vanne de commande de cylindrée d’un compresseur à cylindrée variable - Google Patents

Vanne de commande de cylindrée d’un compresseur à cylindrée variable Download PDF

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Publication number
WO2011016589A1
WO2011016589A1 PCT/KR2009/004340 KR2009004340W WO2011016589A1 WO 2011016589 A1 WO2011016589 A1 WO 2011016589A1 KR 2009004340 W KR2009004340 W KR 2009004340W WO 2011016589 A1 WO2011016589 A1 WO 2011016589A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve body
iron core
discharge chamber
connecting hole
valve
Prior art date
Application number
PCT/KR2009/004340
Other languages
English (en)
Korean (ko)
Inventor
이건호
김학수
남동림
이석기
김성용
이용주
장영일
Original Assignee
두원공과대학교
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
Application filed by 두원공과대학교, 두원전자 filed Critical 두원공과대학교
Priority to KR1020127002954A priority Critical patent/KR101580266B1/ko
Priority to PCT/KR2009/004340 priority patent/WO2011016589A1/fr
Publication of WO2011016589A1 publication Critical patent/WO2011016589A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/1054—Actuating elements
    • F04B27/1072—Pivot mechanisms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • 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
    • F04B25/00—Multi-stage pumps
    • F04B25/04—Multi-stage pumps having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • 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

Definitions

  • the present invention relates to a displacement control valve of a variable displacement compressor, and more particularly to a displacement control valve of a variable displacement compressor with improved control accuracy.
  • 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 a comparative example.
  • 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 20, 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 comprised from the large diameter part 12a and the small diameter part 12b.
  • the large diameter portion 12a of the valve body 12 opens and closes the first guide hole 14 formed in the valve housing 11 while the valve body 12 reciprocates as the electromagnetic solenoid 20 is energized. It is composed.
  • 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 connection hole 17 formed at an upper end of the crank chamber connection hole 16.
  • the electromagnetic solenoid 20 is coupled to the valve body 12, the movable iron core 21 to reciprocate, the electromagnetic coil 22 disposed around the movable core 21, and the electromagnetic coil ( It consists of a solenoid housing 23 surrounding the 22 and a fixed iron core 24 disposed inside the electromagnetic coil 22.
  • the discharge chamber pressure Pd acts on the large diameter portion 12a of the valve body 12 and loses control characteristics of the control valve due to unstable behavior, thereby deteriorating control accuracy. There was a problem.
  • valve body 12 is vibrated by the pulsation of the refrigerant and the driving of the solenoid 20, and the valve body 12 is rotated by the pressure fluctuation of the refrigerant gas.
  • valve body 12 fixed to the movable core 21 and vertically moving has a problem in that the concentric relationship with the inside of the fixed iron core or the valve housing 11 is distorted or the valve body 12 is inclined.
  • 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 in which the control accuracy is improved by canceling the discharge chamber pressure acting on the valve body. .
  • another object of the present invention is to provide a capacity control valve of a variable displacement compressor that reduces the vibration of the valve body by the pulsation of the refrigerant and the driving of the electromagnetic solenoid and prevents rotation of the valve body.
  • another object of the present invention is configured to prevent the inclination of the valve body while maintaining the concentric relationship between the valve body and the site in which the valve body is installed by blocking the vibration generated from the movable core directly to the valve body control valve To provide a capacity control valve of a variable displacement compressor that can improve the operability of the.
  • the capacity control valve of the variable displacement compressor of the present invention for achieving the above object, the capacity control valve of the variable displacement compressor, the crank chamber connecting hole and the discharge chamber connecting hole which receives the crank chamber pressure and the discharge chamber pressure of the compressor inside A valve housing formed at each of the valve housings to allow the first guide hole to pass through the discharge chamber connecting hole and the crank chamber connecting hole; A valve body which opens and closes the first guide hole inlet while reciprocating; An electromagnetic solenoid composed of a movable iron core for reciprocating the valve body, an electromagnetic coil disposed around the movable iron core, a solenoid housing surrounding the electromagnetic coil, and a fixed iron core disposed inside the electromagnetic coil; And a sleeve generated by the fluid flow from the discharge chamber connection hole to the crank chamber connection hole to cancel the force acting on the discharge chamber connection hole side.
  • a damping spring for elastically supporting the movable iron core in the direction of the fixed iron core.
  • a rod supporting the lower end of the valve body and fixed to the movable iron core it is preferable to include a rod supporting the lower end of the valve body and fixed to the movable iron core.
  • the rounding part is formed in the site
  • the cross-sectional area with respect to the diameter of the said sleeve is larger than the cross-sectional area with respect to the diameter of the said valve body.
  • a locking step is formed in the valve body, and an off spring is installed between the locking step and the fixed core.
  • the sleeve is preferably installed detachably to the valve body.
  • FIG. 1 is a longitudinal sectional view showing a capacity control valve of a variable displacement compressor according to a comparative example.
  • 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 cross-sectional view showing the structure of the displacement control valve in FIG.
  • Figure 4 is a longitudinal cross-sectional view showing a coupling structure of the sleeve according to the present invention.
  • valve body 120 120 .
  • Figure 2 is a longitudinal sectional view showing a structure of a variable displacement compressor according to the present invention
  • Figure 3 is a longitudinal sectional view showing the structure of a capacity control valve in Figure 2
  • Figure 4 is a longitudinal sectional view showing a coupling structure of the sleeve according to the present invention. It is also.
  • 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 present invention, the valve housing 110, the electromagnetic solenoid 130, a plurality of connection holes are formed in the interior of the valve housing 110 It includes the valve body 120 which is installed possibly.
  • a first guide hole 117 is formed in the valve housing 110 to guide the movement of the valve body 120.
  • valve body 120 is divided into a large diameter portion 120a and a small diameter portion 120b.
  • 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 an upper end of the discharge chamber connecting hole 113.
  • the discharge chamber connecting hole 113 and the crank chamber connecting hole 112 are formed in a direction orthogonal to the suction chamber connecting hole 111, 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.
  • the end of the valve body 120 is provided with a sleeve 140, the sleeve 140 is generated by the fluid flow from the discharge chamber connecting hole 113 to the crank chamber connecting hole 112 The force acting on the discharge chamber connecting hole 113 side is canceled out.
  • a sleeve bore 119 is formed in the valve housing 110 in which the sleeve 140 is installed, and the sleeve 140 is formed to be larger than the diameter of the valve body 120.
  • the cross-sectional area (a) with respect to the diameter of the sleeve 140 is preferably formed larger than the cross-sectional area (b) with respect to the diameter of the valve body 120, which is a dynamic oil generated in the valve body 120 It is to offset the stamina.
  • the dynamic fluid force is formed of a large diameter portion 120a and a small diameter portion 120b through which the refrigerant flowing from the discharge chamber connection hole 113 to the crank chamber connection hole 112 opens and closes the first guide hole 117. Due to the shape of the valve body 120, some refrigerant generates vortex.
  • the vortex generated refrigerant acts a force to move the valve body 120 toward the discharge chamber connecting hole 112 side and cancels the abnormal operation by the sleeve 140 larger than the cross-sectional area of the large diameter portion (120a). prevent.
  • the sleeve 140 cancels the dynamic fluid force generated in the valve body 120 and at the same time offsets the discharge chamber pressure Pd acting on the valve body 120 to improve control accuracy.
  • the sleeve 140 is preferably fixed to the valve body 120 to prevent relative movement.
  • the electromagnetic solenoid 130 includes a movable iron core 131 for reciprocating the valve body 120, an electromagnetic coil 132 disposed around the movable iron core 131, and the electromagnetic coil 132. It consists of a solenoid housing 134 surrounding the back, and a fixed iron core 133 disposed inside the electromagnetic coil 132.
  • the solenoid housing 134 corresponds to an injection molded product or an insulating case surrounding the electronic coil 132.
  • a second guide hole 133a for guiding the movement of the valve body 120 is formed in the fixed iron core 133.
  • the movable iron core 131 and the valve body 120 reciprocate by energization of the electromagnetic solenoid 130, and the discharge chamber connecting hole 113 and the crank chamber connecting hole by the valve body 120.
  • the inlet of the first guide hole 117 connecting between the 112 is opened and closed.
  • a damping spring 135 for elastically supporting the movable iron core 131 in the direction of the fixed iron core 133 is further provided.
  • the damping spring 135 reduces vibration of the valve body 120 due to pulsation of the refrigerant and driving of the solenoid 130, and prevents rotation of the valve body 120.
  • the movable iron core 131 is further provided with a rod 136 for supporting the lower end of the valve body 120, a rounding portion 136a is provided at a portion facing the valve body 120 of the rod 136 Is formed.
  • the movable iron core 131 can accurately move the valve body 120 even in a concentric twisted state.
  • the vibration generated in the movable iron core 131 is reduced by the damping spring 135 described above, and the reduced vibration is prevented from being directly transmitted to the valve body 120 by the rod 136.
  • valve body 120 is maintained by maintaining the concentric relationship between the valve body 120 and the site where the valve body 120 is installed (valve housing; 110, fixed core; 133) and preventing the valve body 120 from tilting. 120 is to be smoothly driven by minimizing the resistance of the reciprocating movement.
  • the rod 136 may be fixed to the movable iron core 131 as a separate component, or may be integrally formed with the movable iron core 131.
  • a locking jaw 121 is formed in the valve body 120, and an off-spring 125 is installed between the locking jaw 121 and the fixed iron core 133, so that there is no external force.
  • the valve body 120 is lowered to maintain the inlet of the first guide hole 117 is open.
  • the fixed iron core 133 is formed with a guide groove 133b into which the refrigerant in the suction chamber 22 of the compressor flows.
  • 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 valve body 120.
  • 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.
  • the sleeve 140, the valve body 120 is fixedly installed through the center of the sleeve 140, as shown in Figure 4 (a), or as shown in Figure 4 (b) of the valve body 120 Grooves 122 are formed, and the protrusions 141 are formed in the sleeve 140 to be fitted to each other to be fixed.
  • 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 may be adjusted according to the amount of energization. .
  • the damping spring reduces vibration of the valve body caused by pulsation of the refrigerant and driving of the electromagnetic solenoid, and prevents rotation of the valve body.
  • the vibration generated from the movable core is prevented from being directly transmitted to the valve body by the rod, thereby maintaining the concentric relationship between the valve body and the site where the valve body is installed, and preventing the valve body from tilting.

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

Abstract

Cette invention concerne un compresseur à cylindrée variable dont la vanne de commande de cylindrée comprend les éléments suivants : boîtier de vanne comportant un trou de connexion de chambre d’amorçage et un trou de connexion de chambre de décharge formés respectivement à l’intérieur, auxquels sont appliquées la pression de la chambre de d’amorçage et à la pression de la chambre de décharge du compresseur, et premier trou de guidage traversant le trou de connexion de la chambre de décharge et le trou de connexion de la chambre de démarrage en pénétrant dans ces derniers ; corps de vanne assurant l’ouverture et la fermeture du premier trou de guidage selon un mouvement de va-et-vient ; solénoïde dont le noyau de fer mobile permet d’imprimer un mouvement alternatif au corps de vanne ; bobine électronique disposée à la périphérie du noyau de fer mobile de vanne, et noyau de fer fixe disposé dans la bobine électronique ; et manchon destiné à compenser la force générée par le flux du fluide entre le trou de connexion de la chambre de décharge et le trou de connexion de la chambre de démarrage, et qui est appliqué vers le trou de connexion de la chambre de décharge. Ainsi, la pression de la chambre de décharge appliquée au corps de vanne est compensée par le manchon, ce qui permet d’améliorer la précision de commande.
PCT/KR2009/004340 2009-08-03 2009-08-03 Vanne de commande de cylindrée d’un compresseur à cylindrée variable WO2011016589A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
KR1020127002954A KR101580266B1 (ko) 2009-08-03 2009-08-03 용량가변형 압축기의 용량제어밸브
PCT/KR2009/004340 WO2011016589A1 (fr) 2009-08-03 2009-08-03 Vanne de commande de cylindrée d’un compresseur à cylindrée variable

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/KR2009/004340 WO2011016589A1 (fr) 2009-08-03 2009-08-03 Vanne de commande de cylindrée d’un compresseur à cylindrée variable

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WO2011016589A1 true WO2011016589A1 (fr) 2011-02-10

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003301772A (ja) * 2002-04-09 2003-10-24 Sanden Corp 可変容量圧縮機
KR20040036578A (ko) * 2002-10-23 2004-04-30 가부시키가이샤 티지케이 가변 용량 압축기용 제어 밸브
JP2007298041A (ja) * 2007-06-21 2007-11-15 Sanden Corp 容量制御弁機構及びそれを備えた可変容量圧縮機
JP2008025388A (ja) * 2006-07-19 2008-02-07 Sanden Corp 可変容量圧縮機の容量制御弁

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4331667B2 (ja) * 2004-10-22 2009-09-16 株式会社テージーケー 可変容量圧縮機用制御弁

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003301772A (ja) * 2002-04-09 2003-10-24 Sanden Corp 可変容量圧縮機
KR20040036578A (ko) * 2002-10-23 2004-04-30 가부시키가이샤 티지케이 가변 용량 압축기용 제어 밸브
JP2008025388A (ja) * 2006-07-19 2008-02-07 Sanden Corp 可変容量圧縮機の容量制御弁
JP2007298041A (ja) * 2007-06-21 2007-11-15 Sanden Corp 容量制御弁機構及びそれを備えた可変容量圧縮機

Also Published As

Publication number Publication date
KR20120095843A (ko) 2012-08-29
KR101580266B1 (ko) 2015-12-28

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