WO2012008787A2 - Vanne de régulation de capacité pour compresseur à capacité variable - Google Patents

Vanne de régulation de capacité pour compresseur à capacité variable Download PDF

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Publication number
WO2012008787A2
WO2012008787A2 PCT/KR2011/005211 KR2011005211W WO2012008787A2 WO 2012008787 A2 WO2012008787 A2 WO 2012008787A2 KR 2011005211 W KR2011005211 W KR 2011005211W WO 2012008787 A2 WO2012008787 A2 WO 2012008787A2
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WO
WIPO (PCT)
Prior art keywords
damper
chamber
valve
iron core
valve body
Prior art date
Application number
PCT/KR2011/005211
Other languages
English (en)
Korean (ko)
Other versions
WO2012008787A3 (fr
Inventor
이용주
이건호
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
Application filed by 두원공과대학교, 주식회사 두원전자 filed Critical 두원공과대학교
Publication of WO2012008787A2 publication Critical patent/WO2012008787A2/fr
Publication of WO2012008787A3 publication Critical patent/WO2012008787A3/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
    • F04B27/14—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
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0027—Pulsation and noise damping means
    • 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
    • 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

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 that reduces vibration and noise caused by the contact of the valve body and the valve seat.
  • 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 cylinder, thereby controlling the discharge amount of the refrigerant. Will be.
  • PWM Pulse Width Modulation
  • the valve body is configured to open and close the valve seat while reciprocating.
  • the conventional capacity control valve shown in FIG. 1 has a problem that vibration and noise are generated due to the PWM frequency.
  • the frequency of the PWM is transmitted to the valve body 1, which causes the valve body 1 and the valve seat 2 to generate noise due to contact.
  • 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 that reduces the vibration and noise caused by the contact of the valve body and the valve seat.
  • 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 are respectively formed therein,
  • a valve housing formed to penetrate the guide hole crossing the discharge chamber connecting hole and the crank chamber connecting hole, and a valve seat formed at an inlet of the guide hole;
  • Valve body for opening and closing the guide hole while reciprocating;
  • an electromagnetic solenoid provided with a movable iron core for reciprocating the valve body by energization (PWM control), wherein the electromagnetic solenoid is provided with a plunger chamber in which a movable iron core is installed, and fluid is provided between the plunger chamber and the movable iron core. It is characterized by being filled.
  • the crank chamber connection hole and the discharge chamber connection hole which receive the crank chamber pressure and the discharge chamber pressure of the compressor are respectively formed therein, and the discharge chamber connection hole and the crank chamber are respectively formed.
  • a guide hole passing through the connection hole is formed therethrough, and a valve housing having a valve seat formed at an inlet of the guide hole; Valve body for opening and closing the guide hole while reciprocating;
  • an electromagnetic solenoid having a movable iron core for reciprocating the valve body by energization (PWM control) and a rod fixed by the fixed iron core, wherein the movable iron core is formed with a damper chamber in which fluid is filled.
  • a damper plate is attached to the rod inside the damper chamber.
  • the crank chamber connection hole and the discharge chamber connection hole which receive the crank chamber pressure and the discharge chamber pressure of the compressor are respectively formed therein, and the discharge chamber connection hole and the crank
  • a guide hole passing through the thread connecting hole is formed to pass through the valve housing, and a valve seat is formed at an inlet of the guide hole;
  • Valve body for opening and closing the guide hole while reciprocating and an electromagnetic solenoid provided with a movable iron core for reciprocating the valve body by energization (PWM control), wherein the electromagnetic solenoid is provided with a plunger chamber in which a movable iron core is installed, and fluid is provided between the plunger chamber and the movable iron core.
  • a damper chamber in which the fluid is filled in the movable iron core, and a damper plate is attached to the rod inside the damper chamber.
  • the damper plate is preferably formed to be spaced apart from the side wall surface of the damper chamber, a damper hole is formed between the damper chamber and the damper plate.
  • the damper plate is formed to be in close contact with the side wall surface of the damper chamber, the damper plate is preferably formed through the damper hole.
  • a contact portion is formed in one of the valve seat and the valve body, and a sliding part is formed in the other one of the valve seat and the valve body in which the contact portion is not formed to have a gap with the contact portion.
  • the damper plate is preferably formed to reduce the thickness in the direction of the side wall surface of the damper chamber in the rod.
  • the damper hole is preferably formed such that the cross-sectional area is reduced in the direction in which the valve body closes the guide hole.
  • the fluid is preferably a high viscosity oil.
  • a rod penetrating the movable iron core and a fixed iron core contacting the outer surface of the rod are formed.
  • one end of the rod is preferably provided with a protrusion contacting the inner circumferential surface of the fixed iron core.
  • the capacity control valve of the variable displacement compressor by inserting oil into the plunger chamber, the vibration and noise caused by the contact between the valve body and the valve seat by suppressing or attenuating the transmission of the vibration due to the movement of the movable core to the valve body. Has the effect of reducing
  • non-contact sliding section is formed between the valve body and the valve seat by the contact portion and the sliding portion having a gap therebetween to reduce vibration and noise caused by the contact between the valve body and the valve seat.
  • FIG. 1 is a longitudinal sectional view showing a conventional capacity control valve.
  • 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 the structure of the displacement control valve of FIG.
  • FIG. 4 is a longitudinal sectional view showing a structure of a capacity control valve according to another embodiment of FIG. 2.
  • FIG. 5 is an enlarged vertical cross-sectional view of a 'b' part of FIG. 4.
  • FIG. 6 is a longitudinal sectional view showing another embodiment of FIG.
  • FIG. 7 is an enlarged longitudinal sectional view of a portion 'a' of FIG. 3.
  • FIG. 8 is a longitudinal sectional view showing another embodiment of FIG.
  • 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 the capacity control valve of Figure 2
  • Figure 4 is a capacity control valve according to another embodiment of FIG.
  • Figure 5 is a longitudinal cross-sectional view showing the structure
  • Figure 5 is an enlarged longitudinal sectional view of the 'b' part of Figure 4
  • Figure 6 is a longitudinal sectional view showing another embodiment of Figure 5
  • Figure 7 is a 'a' section of FIG. It is an enlarged longitudinal cross-sectional view
  • FIG. 8 is a longitudinal cross-sectional view which shows another Example 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 cylinder bore ( 12, the inclination angle of the swash plate 50 is changed in accordance with the pressure difference in the inside, thereby controlling the discharge amount of the refrigerant.
  • variable displacement compressor adopted in the embodiment of the present invention adopts the electromagnetic solenoid type capacity control valve 100 to adjust the pressure of the crank chamber 86 by opening and closing the valve by energization, through which the swash plate 50 It is designed to adjust the discharge capacity by adjusting the inclination angle of), and can be applied to all compressors of this characteristic.
  • the capacity control valve 100 is installed to be movable in the valve housing 110, the electromagnetic solenoid 130, and the valve housing 110 in which some connection holes are formed.
  • the valve body 120 is included.
  • valve housing 110 is formed with a guide hole 140 for guiding the movement of the valve body 120.
  • valve body 120 is configured to open and close the guide hole 140 formed in the valve housing 110 while reciprocating.
  • the guide hole 140 is formed with a valve seat 300 in contact with the valve body 120.
  • the valve housing 110 has a crank chamber connecting hole 150 and a discharge chamber connecting hole 160 in which the pressure Pc of the crank chamber and the pressure Pd of the discharge chamber respectively act.
  • the discharge chamber connecting hole 160 and the crank chamber connecting hole 150 has a structure in communication with each other through the guide hole 140.
  • valve housing 110 has a suction chamber connecting hole 170 formed at a lower end of the discharge chamber connecting hole 160.
  • a sleeve member 180 is provided at an end of the valve body 120 to be configured to connect between the valve body 120 and the electromagnetic solenoid 130.
  • a sleeve bore 190 is formed in the valve housing 110 in which the sleeve member 180 is installed, and a sleeve 200 corresponding to the sleeve bore 190 is formed in the sleeve member 180. .
  • the sleeve member 180 is provided with an accommodating part 210 therein, and the receiving part 210 is provided with a bellows 220.
  • the valve housing 110 includes a cap 230 screwed in a direction facing the end of the valve body 120, and a support spring 240 between the valve body 120 and the cap 230. ) Is provided to regulate the expansion force of the bellows 220 and the expansion force of the first spring 250 installed therein.
  • cap 230 is configured to open a part so that the pressure (Pc) of the crankcase acts.
  • the electromagnetic solenoid 130 may include a movable core 131 connected to the sleeve member 180, an electronic coil 132 disposed around the movable core 131, the electronic coil 132, and the like. Wrapping is composed of a solenoid housing 134, a fixed iron core 133 disposed inside the electromagnetic coil 132 and a rod 135 inserted into the fixed iron core 133 and fixed to the bellows 220.
  • the solenoid housing 134 corresponds to an injection molded product or an insulating case surrounding the electronic coil 132.
  • a second guide hole 131a for guiding the movement of the rod 135 is formed in the movable iron core 131.
  • the movable iron core 131, the sleeve member 180, and the valve body 120 reciprocate by energizing the electromagnetic solenoid 130, and at the same time, the discharge chamber connecting hole 160 by the valve body 120. ) And the inlet of the guide hole 140 connecting between the crank chamber connecting hole 150 is opened and closed.
  • an off-spring 125 is installed between the fixed iron core 133 and the movable iron core 131. In the absence of an external force, the valve body 120 is raised to inlet the guide hole 140. Should remain open.
  • the solenoid 130 is configured to open and close the valve seat 300 while the valve body 120 is reciprocated as controlled by the PWM control signal. That is, the opening amount of the capacity control valve 100 is controlled by PWM.
  • the valve body 120 and the valve seat 300 generated noise due to contact. That is, the vibration by the PWM is transmitted to the movable core 131, the vibration transmitted to the movable core 131 is transmitted to the valve body 120 is in contact with the valve seat 300.
  • the electromagnetic solenoid 130 is formed with a plunger chamber 136, the movable core 131 is installed, the plunger chamber 136 And a fluid is inserted between the movable iron chamber 131 to suppress or attenuate the transmission of the PWM frequency to the valve body 120 via the movable iron core 131, and thus, the contact of the valve body 120 and the valve seat 300. This reduces vibration and noise.
  • the fluid is preferably a high viscosity oil.
  • the vibration of the PWM frequency by the oil having a high viscosity is suppressed to be transmitted to the movable core 131 to the maximum.
  • the oil is inserted into the plunger chamber 136 to optimize the insertion allowance to suppress the vibration according to the PWM frequency. This is because when a large amount of oil is inserted, the reciprocating motion of the movable core 131 may be prevented, and when the amount of oil is inserted too little, the vibration may not be reduced according to the PWM frequency transmitted to the movable core 131.
  • an O-ring 137 is installed between the plunger chamber 136 and the movable iron core 131 to prevent leakage of oil.
  • one end of the rod 135 is formed with a protrusion 135a in contact with the inner circumferential surface of the fixed iron core 133, and a plurality of protrusions 135a are formed.
  • an elastic member mounting part 135c on which the elastic member 135b is mounted is formed between the plurality of protrusions 135a.
  • a damper chamber 138 filled with oil such as grease is formed in the movable iron core 131, and a damper plate 139 is attached to the rod 135 inside the damper chamber 138. You can do that.
  • the oil in the damper chamber 138 moves the vibration according to the PWM frequency and suppresses or attenuates the vibration to thereby suppress the transmission to the movable iron core 131 as much as possible.
  • damper holes 138a and 139a are formed so that the oil of the damper chamber 138 does not affect the operation of the movable iron core 131.
  • the damper plate 139 is spaced apart from the side wall surface of the damper chamber 138 to form a damper hole 138a between the damper chamber 138 and the damper plate 139. do.
  • the damper plate 139 is a flow resistance is generated by the oil having a viscosity.
  • the damper plate 139 is formed to reduce the thickness in the direction of the side wall surface of the damper chamber 138 in the rod 135 to reduce the flow resistance.
  • the damper plate 139 is formed to be in close contact with the sidewall surface of the damper chamber 138, and a damper hole 139a is formed in the damper plate 139.
  • the damper hole (139a) is formed such that the cross-sectional area in the direction in which the valve body 120 closes the guide hole 140 in order to reduce the flow resistance by the oil having a viscosity as shown in Figure 6 (b) do.
  • the damper holes 138a and 139a may move oil before and after the damper plate 139, thereby preventing the operation of the movable core 131 by the oil.
  • the solenoid 130 is configured to open and close the valve seat 300 while the valve body 120 is reciprocated as it is controlled by an analog control signal. At this time, the noise due to the contact of the valve body 120 and the valve seat 300 is weak, but some may occur.
  • one of the valve seat 300 and the valve body 120 is formed with a contact portion 500, the contact with the valve seat 300 is not formed 500 and The other one of the valve body 120, the sliding portion 400 is formed to have a small gap 402 with the contact portion 500.
  • the gap 402 has a size such that the refrigerant does not pass by the oil film phenomenon due to the surface tension.
  • the lower end of the sliding part 400 is preferably configured to substantially coincide with the bottom dead center of the valve body 120.
  • the bottom dead center of the valve body 120 is configured not to exceed the sliding part 400 when controlled by PWM.
  • the non-slid sliding movement of the valve body 120 and the valve seat 300 occurs by the sliding part 400 and the contact part 500 to reduce vibration and noise due to contact. That is, the vibration of the capacity control valve 200 is reduced by preventing the vibration of the PMW from being transmitted to the valve seat 300 by the sliding part 400 and the contact part 500 in which the non-contact sliding movement occurs.
  • a rounding part 501 is formed in the contact part 500 to reduce the overlapping area of the contact part 500 and the sliding part 400.
  • the sliding portion 400 is preferably formed with an inclined surface 401 for limiting the downward movement (bottom dead center of the valve body) of the contact portion 500.
  • the inclined surface 401 and the contact portion 500 is to close the guide hole 140 for communicating the discharge chamber connecting hole 160 and the crank chamber connecting hole 150 with each other.

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

Abstract

Selon un mode de réalisation de l'invention, une vanne de régulation de capacité pour un compresseur à capacité variable comprend : un logement de vanne dans lequel sont formés un orifice de communication de chambre de vilebrequin et un orifice de communication de chambre de décharge respectivement destinés à recevoir la pression de la chambre de vilebrequin et la pression de la chambre de décharge du compresseur, et dans lequel un orifice de guidage croise l'orifice de communication de la chambre de décharge et celui de la chambre de vilebrequin pénètre dans le corps de vanne, un siège de vanne étant formé à l'entrée de l'orifice de guidage; un corps de vanne qui va et vient de manière à fermer/ouvrir l'orifice de guidage; et un solénoïde électronique prévu dans un noyau ferreux actif afin de permettre au corps de vanne d'aller et venir lorsqu'il est alimenté en électricité (commande PWM), et comprenant une chambre de piston dans laquelle le noyau ferreux actif est installé, l'espace formé entre la chambre de piston et le noyau ferreux actif étant rempli de fluide. La chambre de piston est donc remplie d'huile afin d'empêcher que les vibrations dues au mouvement du noyau ferreux actif soient transmises au corps de vanne ou d'atténuer leur transmission et de réduire ainsi les vibration et le bruit induits par le contact entre le corps de vanne et son siège.
PCT/KR2011/005211 2010-07-16 2011-07-15 Vanne de régulation de capacité pour compresseur à capacité variable WO2012008787A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
KR1020100069094A KR101781612B1 (ko) 2010-07-16 2010-07-16 용량가변형 압축기의 용량제어밸브
KR10-2010-0069094 2010-07-16

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WO2012008787A2 true WO2012008787A2 (fr) 2012-01-19
WO2012008787A3 WO2012008787A3 (fr) 2012-05-03

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2975266A1 (fr) * 2014-07-18 2016-01-20 TGK CO., Ltd. Soupape de contrôle pour compresseur à déplacement variable
EP3059445A1 (fr) * 2015-02-23 2016-08-24 TGK CO., Ltd. Vanne de contrôle électromagnétique d'un compresseur à déplacement variable

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05288150A (ja) * 1992-04-03 1993-11-02 Saginomiya Seisakusho Inc 電磁式制御弁
JP2000274351A (ja) * 1999-03-23 2000-10-03 Toyota Autom Loom Works Ltd 可変容量型圧縮機
JP2005098197A (ja) * 2003-09-04 2005-04-14 Tgk Co Ltd 可変容量圧縮機用容量制御弁

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05288150A (ja) * 1992-04-03 1993-11-02 Saginomiya Seisakusho Inc 電磁式制御弁
JP2000274351A (ja) * 1999-03-23 2000-10-03 Toyota Autom Loom Works Ltd 可変容量型圧縮機
JP2005098197A (ja) * 2003-09-04 2005-04-14 Tgk Co Ltd 可変容量圧縮機用容量制御弁

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2975266A1 (fr) * 2014-07-18 2016-01-20 TGK CO., Ltd. Soupape de contrôle pour compresseur à déplacement variable
EP3059445A1 (fr) * 2015-02-23 2016-08-24 TGK CO., Ltd. Vanne de contrôle électromagnétique d'un compresseur à déplacement variable
CN105909490A (zh) * 2015-02-23 2016-08-31 株式会社Tgk 控制阀

Also Published As

Publication number Publication date
KR101781612B1 (ko) 2017-09-26
WO2012008787A3 (fr) 2012-05-03
KR20120008309A (ko) 2012-01-30

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