WO2010151019A2 - Clapet anti-retour et compresseur muni de celui-ci - Google Patents

Clapet anti-retour et compresseur muni de celui-ci Download PDF

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Publication number
WO2010151019A2
WO2010151019A2 PCT/KR2010/004019 KR2010004019W WO2010151019A2 WO 2010151019 A2 WO2010151019 A2 WO 2010151019A2 KR 2010004019 W KR2010004019 W KR 2010004019W WO 2010151019 A2 WO2010151019 A2 WO 2010151019A2
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant
oil
check valve
valve body
inlet
Prior art date
Application number
PCT/KR2010/004019
Other languages
English (en)
Korean (ko)
Other versions
WO2010151019A3 (fr
Inventor
이건호
김기범
박재석
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 WO2010151019A2 publication Critical patent/WO2010151019A2/fr
Publication of WO2010151019A3 publication Critical patent/WO2010151019A3/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
    • F04B27/1009—Distribution members
    • F04B27/1018—Cylindrical distribution members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—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
    • F04B27/109—Lubrication
    • 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
    • F04B39/04—Measures to avoid lubricant contaminating the pumped fluid
    • 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
    • F04B39/10—Adaptations or arrangements of distribution members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • 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
    • F04B39/14—Provisions for readily assembling or disassembling
    • 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
    • F16K15/00—Check valves
    • F16K15/02—Check valves with guided rigid valve members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/02—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat for separating lubricants from the refrigerant
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/12—Kind or type gaseous, i.e. compressible
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/14—Refrigerants with particular properties, e.g. HFC-134a

Definitions

  • the present invention relates to a check valve and a compressor having the same, and more particularly, to a check valve and a compressor having the same, which maximize the oil separation performance by naturally separating and discharging the oil contained in the refrigerant. It is about.
  • variable capacity compressor that can change the discharge amount of the refrigerant to obtain a cooling capacity without being regulated by the rotational speed of the engine has been used a lot.
  • variable displacement compressors such as swash plate type, rotary type and scroll type.
  • the swash plate type compressor In the swash plate type compressor, the swash plate provided so that the inclination angle is variable in the crank chamber rotates according to the rotational motion of the rotating shaft, and the piston reciprocates by the rotational motion of the swash plate.
  • the refrigerant in the suction chamber is sucked into the cylinder by the reciprocating motion of the piston, compressed and discharged into the discharge chamber.
  • the inclination angle of the swash plate is changed according to the pressure difference in the crank chamber and the pressure in the suction chamber, and the discharge amount of the refrigerant is Will be controlled.
  • the operation of the capacity control valve is calculated by a control unit in which a signal such as the detected engine speed, the temperature inside or outside the vehicle, the evaporator temperature, or the like is incorporated by the CPU, and based on the result of the calculation, the current By sending it to an electromagnetic coil.
  • an oil separator for separating the gas refrigerant and oil may be provided.
  • a check valve is provided in the discharge port communicating with the discharge chamber to prevent the backflow of the refrigerant during the minimum capacity operation of the compressor.
  • the oil separator separating the refrigerant and the oil and the check valve preventing the backflow of the refrigerant are separately provided, so that a separate space is required for the design and assembly. .
  • the present invention has been made to solve the above-mentioned conventional problems, an object of the present invention is to naturally separate the discharge of the oil contained in the refrigerant to maximize the oil separation performance and at the same time to prevent the back flow of the refrigerant and this It is to provide a compressor provided.
  • the check valve of the present invention for achieving the above object, the hollow body having an inlet through which the oil-mixed refrigerant is introduced, the outlet and the drain hole is formed and a communication path connecting the inlet and the outlet; A valve body moving inside the main body and controlling a flow of the refrigerant from the inlet to the outlet; A cap covering an open portion of the main body; And pressurizing means for pressurizing the valve body in a direction of blocking the flow of the refrigerant, wherein the refrigerant separated from the communication path pressurizes the valve body to allow the refrigerant to flow from the inlet to the outlet. do.
  • the communication path is hollow and the hollow cross-sectional area is changed stepwise or continuously.
  • the cross-sectional area of the communication path hollow decreases in the flow direction of the refrigerant step by step.
  • the drain hole is preferably formed through the inner peripheral surface of the communication path.
  • valve body is formed of a large diameter portion and a small diameter portion, it is preferable that the refrigerant groove is formed in the small diameter portion.
  • the coolant groove may be formed by cutting a portion of the outer circumferential surface of the small diameter part.
  • the valve body when the refrigerant in which the oil is separated from the communication passage pressurizes the valve body, the valve body is moved, and the refrigerant groove preferably communicates with the communication passage and the discharge port.
  • valve body is formed of a large diameter portion and a small diameter portion, it is preferable that the oil groove is formed in the small diameter portion.
  • the discharge chamber and the suction chamber is formed;
  • a check valve as described above installed in the discharge chamber and separating oil contained in the refrigerant;
  • a drain flow path formed in the housing to guide the oil separated from the check valve to the crank chamber, wherein the coolant in the discharge chamber flows in a tangential direction (check valve side) in the inner circumferential surface of the check valve.
  • the O-ring is preferably provided on the outer circumferential surface of the check valve body.
  • the oil separation function and the check valve function to prevent the back flow of the refrigerant is integrally formed to facilitate the internal space of the compressor, thereby improving design and assembly.
  • FIG. 1 is a longitudinal sectional view showing the structure of a swash plate compressor according to the present invention.
  • FIG. 2 is a side view illustrating the rear housing of FIG. 1.
  • FIG. 2 is a side view illustrating the rear housing of FIG. 1.
  • FIG. 3 is a sectional view taken along the line 'a-a' of FIG. 2.
  • Figure 4 is an exploded perspective view of the check valve according to the present invention.
  • Figure 1 is a longitudinal sectional view showing the structure of a swash plate compressor according to the present invention
  • Figure 2 is a side view showing the rear housing of Figure 1
  • Figure 3 is a cross-sectional view 'a-a' of Figure 2
  • Figure 4 Is a perspective view showing an exploded view of the check valve according to the present invention.
  • the swash plate type compressor C includes a cylinder block 10 having a plurality of cylinder bores 12 formed in an inner circumferential surface in parallel in a longitudinal direction, and the cylinder block 10.
  • the front housing 16 is hermetically coupled to the front of the, and the rear housing 18 is hermetically coupled via a valve plate 20 in 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 a central portion thereof are formed to protrude integrally on one surface, and a pin is formed on one surface of the swash plate 50.
  • the pin 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.
  • the swash plate compressor (C) of the present invention adopts an electromagnetic solenoid type capacity control valve 100 to adjust the pressure of the crank chamber 86 by opening and closing the valve by energization, thereby adjusting the pressure of the crank chamber 86.
  • an electromagnetic solenoid type capacity control valve 100 to adjust the pressure of the crank chamber 86 by opening and closing the valve by energization, thereby adjusting the pressure of the crank chamber 86.
  • the discharge chamber 24 is provided with a check valve 200 that separates oil from the discharged refrigerant and prevents backflow of the discharged refrigerant.
  • the check valve 200 serves to prevent the compressor from falling in efficiency by separating oil from the refrigerant passing through the discharge chamber 24 so that only the gas refrigerant is directed to the condenser (not shown). Will be described later.
  • the oil separated by the check valve 200 is re-introduced into the crank chamber 86 through the drain passage 19 formed in the rear housing 18 to maintain excellent lubrication performance.
  • the check valve 200 includes a hollow main body 210 having an inlet 215 and an outlet 211 formed therein, and an inside of the main body 210.
  • a valve body 220 which moves and controls the flow of the refrigerant from the inlet 215 to the outlet 211, and a cap 230 and the valve body 220 to close the open end of the body 210. It consists of a pressurizing means 240 for pressurizing in a direction to block the flow of the refrigerant.
  • a communication path 212 connecting the inlet 215 and the outlet 211 is formed in the main body 210, and a drain hole 213 is formed in the communication path 212.
  • the communication path 212 is a hollow shape, the cross-sectional area of the communication path 212 is formed to be changed stepwise or continuously, or the cross-sectional area of the communication path 212 is formed to be reduced step by step in the flow direction of the refrigerant Can be.
  • the drain hole 213 is formed through the inner peripheral surface of the communication path 212, the drain hole 213 is in communication with the above-described drain flow path (19).
  • the outlet 211 is formed along the outer circumferential surface of the main body 210.
  • the refrigerant containing oil flows in the tangential direction (check valve side) of the inner circumferential surface of the communication path 212 through the inlet 215 as shown in Figures 2 to 3 and rotates along the inner circumferential surface of the communication path 212.
  • the refrigerant including the oil enters the inlet 215 and at the same time a collision occurs so that the oil is separated first, and then the refrigerant separated by the primary oil rotates along the inner circumferential surface of the communication path 212 so that the oil has 2 Separated by car.
  • the jaw portion 214 is formed while the cross-sectional area is reduced in the direction of the valve body 220 of the communication passage 212, so that the refrigerant having secondary oil separated by rotating the inner circumferential surface of the inlet 215 is the jaw portion 214. ), The oil is separated in 3rd order. Thereafter, the refrigerant rotates again in the communication path 212 having a reduced cross-sectional area, and finally oil is separated.
  • the oil contained in the refrigerant is separated several times and sent to the crank chamber 86 through the drain hole 213 and the drain flow path 19.
  • valve body 220 is formed of a large diameter portion 220a and a small diameter portion 220b, an oil groove 221 is formed in the small diameter portion 220b, and the oil groove 221 is the inlet ( The oil not separated at 215 and at the jaw 214 is once again separated from the refrigerant.
  • the inner end of the oil groove 221 is formed to be inclined in the center direction.
  • the small diameter portion 220b is formed with a coolant groove 222 having a portion of an outer circumferential surface thereof cut out, and the coolant groove 222 discharges the refrigerant from which oil is separated through the discharge port 211.
  • valve body 220 moves so that the refrigerant groove 222 is connected to the communication path 212 and the discharge port ( 211).
  • the refrigerant from which the oil is separated exerts a discharge pressure on the small diameter portion 220b of the valve body 220 and the valve body 220 moves while compressing the pressurizing means 240 having excellent restoring force by the discharge pressure.
  • a coolant flows through the coolant groove 222 and the outlet 211 to form a flow path to discharge the coolant.
  • At least one O-ring 219 is preferably installed on the outer circumferential surface of the main body 210.
  • the above-described check valve 200 can perform all the roles of separating the oil from the refrigerant and at the same time, the role of the check valve to prevent the reverse flow of the discharged refrigerant.
  • the check valve is applied to the swash plate compressor, but the present invention is not limited thereto, and the present invention may be applied to both a scroll compressor and a rotary compressor, including a general anchoring compressor.
  • check valve of the present invention is applicable to any device having a function of separating gas and liquid.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Power Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Compressor (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Check Valves (AREA)

Abstract

La présente invention concerne un clapet anti-retour comportant : un corps principal présentant une forme creuse et doté d’une entrée à travers laquelle est introduit un agent frigorigène mélangé à de l’huile, d’une sortie et d’un trou de purge qui définissent un conduit de communication reliant l’entrée à la sortie ; un corps de soupape, mobile à l’intérieur du corps principal et régulant l’écoulement d’agent frigorigène de l’entrée à la sortie ; un capuchon servant à recouvrir une partie ouverte du corps principal ; et un moyen de pression servant à appuyer sur le corps de soupape dans le sens d’un blocage de l’écoulement d’agent frigorigène, le corps de soupape poussant de l’agent frigorigène exempt d’huile dans le conduit de communication pour permettre à l’agent frigorigène de s’écouler de l’entrée à la sortie. Il en découle entre autres avantages la séparation naturelle et l’évacuation de l’huile contenue dans l’agent frigorigène par la partie inférieure de l’entrée d’agent frigorigène, maximisant ainsi les performances de séparation d’huile, tandis que le reflux de l’agent frigorigène est empêché par le corps de soupape. En outre, la combinaison de la fonction de séparation d’huile et des fonctions de clapet anti-retour capable d’empêcher le reflux de l’agent frigorigène facilite la création d’un espace intérieur plus important à l’intérieur d’un compresseur, améliorant ainsi les processus de conception et de montage.
PCT/KR2010/004019 2009-06-26 2010-06-22 Clapet anti-retour et compresseur muni de celui-ci WO2010151019A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
KR10-2009-0057574 2009-06-26
KR1020090057574A KR101099117B1 (ko) 2009-06-26 2009-06-26 체크 밸브 및 이를 구비하는 압축기

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WO2010151019A2 true WO2010151019A2 (fr) 2010-12-29
WO2010151019A3 WO2010151019A3 (fr) 2011-04-21

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WO (1) WO2010151019A2 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101877261B1 (ko) * 2012-07-26 2018-07-11 한온시스템 주식회사 가변 용량형 사판식 압축기
KR102302329B1 (ko) * 2019-04-02 2021-09-15 엘지전자 주식회사 압축기
KR102717006B1 (ko) * 2020-02-21 2024-10-15 한온시스템 주식회사 압축기용 토출 체크 밸브

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2004218610A (ja) * 2003-01-17 2004-08-05 Toyota Industries Corp 圧縮機
JP2005023847A (ja) * 2003-07-02 2005-01-27 Zexel Valeo Climate Control Corp 圧縮機
WO2007111194A1 (fr) * 2006-03-29 2007-10-04 Kabushiki Kaisha Toyota Jidoshokki Compresseur
JP2007321688A (ja) * 2006-06-02 2007-12-13 Toyota Industries Corp 圧縮機

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2004218610A (ja) * 2003-01-17 2004-08-05 Toyota Industries Corp 圧縮機
JP2005023847A (ja) * 2003-07-02 2005-01-27 Zexel Valeo Climate Control Corp 圧縮機
WO2007111194A1 (fr) * 2006-03-29 2007-10-04 Kabushiki Kaisha Toyota Jidoshokki Compresseur
JP2007321688A (ja) * 2006-06-02 2007-12-13 Toyota Industries Corp 圧縮機

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Publication number Publication date
WO2010151019A3 (fr) 2011-04-21
KR20110000180A (ko) 2011-01-03
KR101099117B1 (ko) 2011-12-27

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