KR20200071518A - Oil control valve - Google Patents

Oil control valve Download PDF

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Publication number
KR20200071518A
KR20200071518A KR1020180159341A KR20180159341A KR20200071518A KR 20200071518 A KR20200071518 A KR 20200071518A KR 1020180159341 A KR1020180159341 A KR 1020180159341A KR 20180159341 A KR20180159341 A KR 20180159341A KR 20200071518 A KR20200071518 A KR 20200071518A
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KR
South Korea
Prior art keywords
pintle
control valve
valve
lower frame
oil control
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KR1020180159341A
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Korean (ko)
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최명식
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현대자동차주식회사
기아자동차주식회사
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Application filed by 현대자동차주식회사, 기아자동차주식회사 filed Critical 현대자동차주식회사
Priority to KR1020180159341A priority Critical patent/KR20200071518A/en
Priority to US16/514,211 priority patent/US20200182105A1/en
Priority to CN201910902276.1A priority patent/CN111306349A/en
Publication of KR20200071518A publication Critical patent/KR20200071518A/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • 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
    • F16K31/44—Mechanical actuating means
    • F16K31/52—Mechanical actuating means with crank, eccentric, or cam
    • F16K31/524—Mechanical actuating means with crank, eccentric, or cam with a cam
    • F16K31/52408—Mechanical actuating means with crank, eccentric, or cam with a cam comprising a lift valve
    • F01L9/023—
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
    • F01L9/11—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column
    • F01L9/12—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column with a liquid chamber between a piston actuated by a cam and a piston acting on a valve stem
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/26—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder
    • F01L1/267—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder with means for varying the timing or the lift of the valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L13/0036—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L13/0036—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction
    • F01L13/0042—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction with cams being profiled in axial and radial direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
    • F01L9/11—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
    • F01L9/11—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column
    • F01L9/12—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column with a liquid chamber between a piston actuated by a cam and a piston acting on a valve stem
    • F01L9/14—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column with a liquid chamber between a piston actuated by a cam and a piston acting on a valve stem the volume of the chamber being variable, e.g. for varying the lift or the timing of a valve
    • 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
    • F16K15/025—Check valves with guided rigid valve members the valve being loaded by a spring
    • 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
    • F16K31/04—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor
    • F16K31/046—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor with electric means, e.g. electric switches, to control the motor or to control a clutch between the valve and the motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34426—Oil control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34453—Locking means between driving and driven members
    • F01L2001/34459—Locking in multiple positions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34453—Locking means between driving and driven members
    • F01L2001/34469—Lock movement parallel to camshaft axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2820/00—Details on specific features characterising valve gear arrangements
    • F01L2820/01—Absolute values
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2820/00—Details on specific features characterising valve gear arrangements
    • F01L2820/03—Auxiliary actuators
    • F01L2820/033—Hydraulic engines

Abstract

An objective of the present invention is to provide an oil control valve which prevents a lift deviation between two valves. The oil control valve controls the oil pressure of a first hydraulic chamber and a second hydraulic chamber formed in a first electro-hydraulic valve (EHV) device and a second EHV device driven by a first cam and a second cam and provided with a first valve and a second valve connected to lower portions thereof. The oil control valve comprises: a body including a communication hole of which one end and the other end communicate with the first hydraulic chamber and the second hydraulic chamber; a hollow lower frame formed or fixed and mounted on a lower end of the body, wherein the height of an upper end thereof is positioned in an internal space of the communication hole to allow the communication hole and an upper portion thereof to communicate with each other, and a lower portion thereof communicates with an oil gallery which supplies oil; and a pin frame which is arranged between the lower frame and a vertically moving actuator to vertically penetrate the communication hole, and comes in contact with or is separated from the upper end of the lower frame. When the pin frame and the lower frame come in contact with each other, the one end and the other end of the communication hole do not communicate with each other.

Description

오일 제어 밸브{OIL CONTROL VALVE}Oil control valve {OIL CONTROL VALVE}

본 발명은 오일 제어 밸브(Oil Control Valve; OCV)에 관한 것으로, 더욱 상세하게는 같은 종류의 두 밸브들 간 리프트 편차의 발생을 방지하는 오일 제어 밸브에 관한 것이다.The present invention relates to an oil control valve (OCV), and more particularly, to an oil control valve preventing occurrence of lift deviation between two valves of the same type.

가변 밸브 제어 기술은 자동차 엔진의 효율 향상을 위한 하나의 영역을 담당하고 있다. Variable valve control technology is responsible for one area to improve the efficiency of automobile engines.

일반적으로, 캠의 형상과 캠들 간 위상 차에 의해 밸브들 간 개폐 시기를 조절함으로써 엔진의 흡기 및 배기가 제어된다.In general, the intake and exhaust of the engine are controlled by adjusting the opening and closing timing between the valves by the cam shape and the phase difference between the cams.

가변 밸브 타이밍(Variable Valve Timing; VVT) 방식은 밸브들 간 개폐 시기를 조절하여 흡기 밸브 및 배기 밸브가 동시에 열리는 오버랩 구간을 제어하고, 가변 밸브 리프트(Variable Valve Lift; VVL) 방식은 밸브 리프트를 조절하여 흡입 공기량을 제어한다.The Variable Valve Timing (VVT) method controls the opening and closing timing between valves to control the overlapping section where the intake and exhaust valves open simultaneously, and the Variable Valve Lift (VVL) method controls the valve lift. To control the intake air volume.

VVT 방식이 연속 가변 밸브 타이밍(Continuous VVT; CVVT) 방식으로 발전한 것과 같이, VVL 방식이 연속 가변 밸브 리프트(Continuous VVL; CVVL) 방식으로 발전하였고, 잇달아 기계 전기 유압 밸브 트레인(Mechanical Electro Hydraulic Valvetrain; MEHV) 방식까지 개발되어 자동차 엔진에 활발히 적용되고 있다.Just as the VVT method evolved into the Continuous VVT (CVVT) method, the VVL method developed into the Continuous VVL (CVVL) method, followed by the Mechanical Electro Hydraulic Valvetrain (MEHV). ) Method and it is actively applied to automobile engines.

MEHV 방식은 기계적 밸브 기구와 전기 유압 밸브(Electric Hydraulic Valve; EHV) 장치를 조합한 것이고, 오일 압력을 이용하여 밸브의 리프트를 조절한다.The MEHV method is a combination of a mechanical valve mechanism and an electric hydraulic valve (EHV) device, and controls the lift of the valve using oil pressure.

일반적으로, MEHV 시스템은 2개의 동일 구조를 갖는 전기유압밸브(Electro Hydraulic Valve; EHV) 장치들과 상기 장치들에 각기 연결된 동일 종류(흡기 또는 배기)의 2개의 밸브들을, 하나의 오일 제어 밸브(Oil Control Valve; OCV)를 이용함으로써, 작동시킨다.In general, the MEHV system includes two hydraulic hydraulic valves (EHV) devices having the same structure and two valves of the same type (intake or exhaust) respectively connected to the devices, one oil control valve ( It works by using Oil Control Valve (OCV).

EHV 장치는 일반적으로 기계식 캠에 의해 구동되며 EHV 장치 안에는 유압 챔버가 형성되는데, OCV를 통해 유압 챔버에 오일이 공급되거나, 유압 챔버로부터 오일이 빠져나감으로써, 캠에 의한 구동 효과가 제어된다. 즉, EHV 장치에 충분한 오일이 공급된 상태에서 캠이 EHV 장치를 구동하면, 상기 EHV 장치에 연결된 밸브가 작동함으로써 밸브 리프트가 발생하게 된다. 그러나, 상기 EHV 장치로부터 오일이 유출된 상태에서 캠이 상기 EHV 장치를 구동하면, 상기 EHV 장치에 연결된 밸브가 작동하지 않게 된다.The EHV device is generally driven by a mechanical cam, and a hydraulic chamber is formed in the EHV device. Oil is supplied to the hydraulic chamber through OCV or oil is discharged from the hydraulic chamber, thereby controlling the driving effect by the cam. That is, when sufficient oil is supplied to the EHV device and the cam drives the EHV device, a valve lift is generated by operating a valve connected to the EHV device. However, if the cam drives the EHV device in a state where oil is leaked from the EHV device, the valve connected to the EHV device does not operate.

종래의 MEHV 시스템은, 오일의 원활한 공급을 위해 2개의 EHV 장치들이 서로 연통되도록 구성된 OCV를 이용하였다. 따라서, 상기 2개의 EHV 장치들 간 오일 압력 차가 발생하는 경우 상기 2개의 EHV 장치들 사이에서 오일의 맥동이 발생할 수 있었고, 이에 따라 상기 2개의 EHV 장치들에 각기 연결된 2개의 밸브들 간에 리프트 편차가 발생하는 문제가 있었다.Conventional MEHV systems used OCV configured to allow two EHV devices to communicate with each other for a smooth supply of oil. Therefore, when an oil pressure difference between the two EHV devices occurred, pulsation of oil could occur between the two EHV devices, and thus a lift deviation between the two valves respectively connected to the two EHV devices There was a problem that occurred.

도5는 종래의 오일 제어 밸브가 적용된 경우 캠각도에 따른 밸브 리프트를 도시한 그래프이다.5 is a graph showing the valve lift according to the cam angle when the conventional oil control valve is applied.

도5를 참조하면, 좌우 밸브들 간에 리프트 편차가 나타나고 있다. 이러한 상태에서는 엔진 실린더들 간 연소의 불균형이 발생할 수 있으며, 연비, 에미션(emission), 또는 노킹 특성이 악화될 수 있다.Referring to Figure 5, the lift deviation between the left and right valves is shown. In this state, an imbalance of combustion between engine cylinders may occur, and fuel consumption, emission, or knocking characteristics may deteriorate.

본 발명의 목적은 상기한 문제점을 해결하기 위한 것으로, 두 밸브들 간의 리프트 편차의 발생을 방지하는 오일 제어 밸브를 제공하는 것이다.An object of the present invention is to solve the above problems, to provide an oil control valve that prevents the occurrence of lift deviation between the two valves.

본 발명의 하나 또는 다수의 실시 예에서는, 제1캠 및 제2캠에 의해 각기 구동되며, 하부들에는 각기 제1밸브 및 제2밸브가 연결된, 제1전기유압밸브(Electro Hydraulic Valve; EHV) 장치 및 제2EHV 장치의 내부들에 각기 형성된 제1유압 챔버 및 제2유압 챔버의 오일 압력을 제어하도록 된 오일 제어 밸브에 있어서, 일단과 타단이 상기 제1유압 챔버와 상기 제2유압 챔버에 각기 연통되는 연통홀을, 포함하는 바디, 상기 바디의 하단부에 형성되거나 고정 장착되며, 상단의 높이가 상기 연통홀의 내부 공간에 위치함으로써 상기 연통홀과 상부가 연통되고, 오일을 공급하는 오일 갤러리와 하부가 연통되는, 중공의 하부틀, 그리고 상하 운동을 하는 작동기와 상기 하부틀 사이에 배치됨으로써 상기 연통홀을 상하로 관통하며, 상기 하부틀의 상기 상단과 접촉하거나 분리되는 핀틀을 포함하되, 상기 핀틀과 상기 하부틀이 서로 접촉할 시, 상기 연통홀의 상기 일단과 상기 타단이 연통되지 않는 것을 특징으로 하는 오일 제어 밸브가 제공될 수 있다.In one or more embodiments of the present invention, the first and second valves are respectively driven by the first cam and the second cam, and the first valve and the second valve are respectively connected to the first electro-hydraulic valve (EHV). In the oil control valve configured to control the oil pressure of the first hydraulic chamber and the second hydraulic chamber respectively formed in the interiors of the device and the second EHV device, one end and the other end are respectively in the first hydraulic chamber and the second hydraulic chamber A body including a communicating hole, formed in the lower portion of the body, or fixedly mounted, and the height of the upper end is located in the inner space of the communicating hole, so that the communicating hole and the upper portion communicate with each other, and an oil gallery and a lower portion supplying oil It comprises a pintle that is in communication with, through the upper and lower parts of the lower frame, and the upper and lower movement through the communication hole by being disposed between the actuator and the lower frame, and is in contact with or separated from the top of the lower frame, the pintle When the and the lower frame are in contact with each other, an oil control valve may be provided, characterized in that the one end and the other end of the communication hole are not in communication.

상기 핀틀은 중공이며, 상기 오일 제어 밸브는, 상단은 상기 핀틀의 상부에 연결되고, 하단은 상기 하부틀의 내부 공간에 형성된 지지부에 연결됨으로써, 상기 핀틀에 복원력을 작용시키는 스프링을 더 포함할 수 있다.The pintle is hollow, the oil control valve, the upper end is connected to the upper portion of the pintle, the lower end is connected to a support formed in the inner space of the lower frame, and may further include a spring that exerts a restoring force on the pintle. have.

상기 작동기는 솔레노이드에 의해 상하로 작동할 수 있다.The actuator can be operated up and down by a solenoid.

상기 핀틀은 상기 작동기의 하단부와 일체로 형성될 수 있다.The pintle may be integrally formed with the lower end of the actuator.

상기 하부틀, 상기 연통홀, 그리고 상기 핀틀은 각기 실린더 모양을 가지고, 상기 하부틀 및 상기 핀틀의 직경은 상기 연통홀의 직경보다 클 수 있다. Each of the lower frame, the communication hole, and the pintle has a cylinder shape, and the diameter of the lower frame and the pintle may be larger than the diameter of the communication hole.

상기 핀틀에는 상기 핀틀 하단의 외주 면을 따라 챔퍼가 형성되고, 상기 하부틀의 상단에는, 상기 챔퍼와 만남으로써 고정 및 기밀 상태가 유지되도록, 챔퍼면이 형성될 수 있다.A chamfer may be formed on the pintle along the outer circumferential surface of the lower end of the pintle, and on the upper end of the lower frame, a fixed and airtight state is maintained by contacting the chamfer.

본 발명의 실시 예에 따른 오일 제어 밸브는, 상기 핀틀이 상기 하부틀과 분리될 때, 상기 제1EHV 장치 및 상기 제2EHV 장치로부터 오일이 유출됨으로써 상기 제1캠 및 제2캠의 작동에도 불구하고 상기 제1밸브 및 상기 제2밸브가 작동하지 않도록 될 수 있다.In the oil control valve according to the embodiment of the present invention, when the pintle is separated from the lower frame, the oil flows out from the first EHV device and the second EHV device, despite the operation of the first cam and the second cam. The first valve and the second valve may not be operated.

상기 오일 제어 밸브는, 상기 핀틀이 상기 하부틀과 접촉할 때, 상기 제1캠 및 제2캠의 작동에 의해 상기 제1밸브 및 상기 제2밸브가 작동하도록 될 수 있다.In the oil control valve, when the pintle contacts the lower frame, the first valve and the second valve may be operated by the operation of the first cam and the second cam.

상술한 바와 같이 본 발명에 따르면, 두 밸브들 간의 리프트 프로파일이 같아짐으로써 연비가 개선되고 에미션이 좋아지며 노킹 발생이 감소한다.As described above, according to the present invention, the lift profile between the two valves is the same, thereby improving fuel efficiency, improving emission, and reducing knocking.

도1은 본 발명의 실시 예에 따른 오일 제어 밸브가 장착된 밸브 트레인 구조의 개략도이다.
도2는 본 발명의 실시 예에 따른 오일 제어 밸브가 장착된 밸브 트레인 구조의 측면도이다.
도3은 본 발명의 실시 예에 따른 오일 제어 밸브의 A-A 단면도이다.
도4는 본 발명의 실시 예에 따른 오일 제어 밸브의 B-B 단면도이다.
도5는 종래의 오일 제어 밸브가 적용된 경우 캠각도에 따른 밸브 리프트를 도시한 그래프이다.
도6은 본 발명의 실시 예에 따른 오일 제어 밸브가 적용된 경우 캠각도에 따른 밸브 리프트를 도시한 그래프이다.1 is a schematic diagram of a valve train structure equipped with an oil control valve according to an embodiment of the present invention.
2 is a side view of a valve train structure equipped with an oil control valve according to an embodiment of the present invention.
3 is an AA sectional view of an oil control valve according to an embodiment of the present invention.
4 is a BB cross-sectional view of an oil control valve according to an embodiment of the present invention.
5 is a graph showing the valve lift according to the cam angle when the conventional oil control valve is applied.
6 is a graph showing the valve lift according to the cam angle when the oil control valve according to an embodiment of the present invention is applied.

이하, 본 발명의 바람직한 실시 예를 첨부한 도면에 의거하여 본 발명이 속하는 기술분야에서 통상의 지식을 가진 자가 용이하게 실시할 수 있도록 상세하게 설명하면 다음과 같다.Or less, on the basis of the accompanying drawings, preferred embodiments of the present invention will be described in detail so that those skilled in the art to which the present invention can easily implement.

이러한 실시 예는 본 발명에 따른 일 실시 예로서, 본 발명이 속하는 기술 분야에서 통상의 지식을 가진 자가 여러 가지 상이한 형태로 구현할 수 있으므로, 본 발명의 권리범위는 이하에서 설명하는 실시 예에 한정되지 않는다 할 것이다. Such an embodiment is an embodiment according to the present invention, since a person having ordinary knowledge in the technical field to which the present invention belongs can be implemented in various different forms, the scope of the present invention is not limited to the embodiments described below Will do.

명세서 전체에서, 어떤 부분이 어떤 구성요소를 "포함"한다고 할 때, 이는 특별히 반대되는 기재가 없는 한 다른 구성요소를 제외하는 것이 아니라 다른 구성요소를 더 포함할 수 있다는 것을 의미한다. 또한, 구성요소의 이름이 해당 구성요소의 기능을 한정하지 않는다.Throughout the specification, when a part “includes” a certain component, this means that other components may be further included rather than excluding other components unless specifically stated to the contrary. In addition, the name of the component does not limit the function of the component.

도1은 본 발명의 실시 예에 따른 오일 제어 밸브가 장착된 밸브 트레인 구조의 개략도이다.1 is a schematic diagram of a valve train structure equipped with an oil control valve according to an embodiment of the present invention.

도2는 본 발명의 실시 예에 따른 오일 제어 밸브가 장착된 밸브 트레인 구조의 측면도이다.2 is a side view of a valve train structure equipped with an oil control valve according to an embodiment of the present invention.

도1 및 도2를 참조하면, 본 발명의 실시 예에 따른 오일 제어 밸브(10)는, 제1전기유압밸브(Electro Hydraulic Valve; EHV) 장치(21) 및 제2EHV 장치(22)의 내부들에 각기 형성된 제1유압 챔버(21a) 및 제2유압 챔버(22a)의 오일 압력을 제어하도록 구성된다. 상기 제1EHV 장치(21) 및 제2EHV 장치(22)는 제1캠(1) 및 제2캠(2)에 의해 각기 구동되며, 그 하부들에는 각기 제1밸브(3) 및 제2밸브(4)가 연결된다. 따라서, 상기 오일 제어 밸브(10)에 의해 상기 제1밸브(3) 및 제2밸브(4)의 작동이 조절된다.1 and 2, the oil control valve 10 according to an embodiment of the present invention, the interior of the first electro-hydraulic valve (EHV) device 21 and the second EHV device 22 It is configured to control the oil pressure of the first hydraulic chamber (21a) and the second hydraulic chamber (22a) formed in each. The first EHV device 21 and the second EHV device 22 are driven by the first cam 1 and the second cam 2, respectively, and the first valve 3 and the second valve ( 4) is connected. Therefore, the operation of the first valve 3 and the second valve 4 is controlled by the oil control valve 10.

상기 오일 제어 밸브(10)는, 일단과 타단이 상기 제1유압 챔버(21a)와 상기 제2유압 챔버(22a)에 각기 연통되는 연통홀(32)을 포함하는 바디(30), 상기 바디(30)의 하단부에 형성되거나 고정 장착되며, 상단의 높이가 상기 연통홀(32)의 내부 공간에 위치함으로써 상기 연통홀(32)과 상부가 연통되고 오일을 공급하는 오일 갤러리(34)와 하부가 연통되는, 중공의 하부틀(40), 그리고 상하 운동을 하는 작동기(15)와 상기 하부틀(40) 사이에 배치됨으로써 상기 연통홀(32)을 상하로 관통하며, 상기 하부틀(40)의 상기 상단과 접촉하거나 분리되는 핀틀(50)을 포함하여 구성될 수 있다.The oil control valve 10 includes a body 30 and a body including a communication hole 32 whose one end and the other end are respectively in communication with the first hydraulic chamber 21a and the second hydraulic chamber 22a. 30) is formed or fixedly mounted at the lower end of the upper portion, the height of the upper end is located in the inner space of the communication hole 32 so that the communication hole 32 communicates with the upper part and the oil gallery 34 and the lower part supplying oil It is arranged between the lower frame 40 of the communication, the actuator 15 and the lower frame 40 for vertical movement, and penetrates the communication hole 32 up and down, and the lower frame 40 of the It may be configured to include a pintle 50 that is in contact with or separated from the top.

상기 오일 제어 밸브(10)는, 상기 핀틀(50)과 상기 하부틀(40)이 서로 접촉할 시, 상기 연통홀(32)의 일단과 타단은 서로 연통되지 않도록 구성된다. 즉, 상기 일단과 타단은 상기 하부틀(40)과 상기 핀틀(50)에 의해 서로 막히게 된다.The oil control valve 10 is configured such that when the pintle 50 and the lower frame 40 contact each other, one end and the other end of the communication hole 32 do not communicate with each other. That is, the one end and the other end are blocked by each other by the lower frame 40 and the pintle 50.

이를 위해, 상기 하부틀(40), 상기 연통홀(32), 그리고 상기 핀틀(50)은 각기 실린더 모양을 가지고, 상기 하부틀(40) 및 상기 핀틀(50)의 직경은 상기 연통홀(32)의 직경보다 크도록 형성될 수 있다. 그러나, 실시 예는 여기에 한정되지 않으며, 상기 하부틀(40)과 상기 핀틀(50)의 접촉 시 상기 하부틀(40)과 상기 핀틀(50)이 상기 연통홀(32)의 내부를 막아서 상기 연통홀(32)의 일단과 타단이 서로 연통되지 않는 한, 어떠한 구조도 허용된다.To this end, the lower frame 40, the communication hole 32, and the pintle 50 each have a cylinder shape, the diameter of the lower frame 40 and the pintle 50 is the communication hole 32 ) Can be formed to be larger than the diameter. However, the embodiment is not limited to this, and when the lower frame 40 and the pintle 50 are in contact, the lower frame 40 and the pintle 50 block the inside of the communication hole 32 so that the Any structure is allowed as long as one end and the other end of the communication hole 32 do not communicate with each other.

상기 제1유압 챔버(21a)와 상기 연통홀(32)의 일단은 좌 파이프(5)에 의해 연통될 수 있고, 상기 제2유압 챔버(22a)와 상기 연통홀(32)의 타단은 우 파이프(6)에 의해 연통될 수 있다. 이 경우, 상기 좌우 파이프(5, 6)들은 실린더 헤드(7)에 형성될 수 있다. 상기 오일 제어 밸브(10)는 일반적으로 상기 실린더 헤드(7)에 장착된다.One end of the first hydraulic chamber 21a and the communication hole 32 may be communicated by a left pipe 5, and the other end of the second hydraulic chamber 22a and the communication hole 32 may be a right pipe. (6). In this case, the left and right pipes 5 and 6 may be formed in the cylinder head 7. The oil control valve 10 is generally mounted on the cylinder head 7.

상기 제1,2유압 챔버(21a, 22a)들이 각기 상기 제1,2EHV 장치(21, 22)들 내에 형성되는 메커니즘은 당해 기술 분야의 통상의 기술자에게 잘 알려져 있으므로 자세한 설명은 생략된다.Mechanisms in which the first and second hydraulic chambers 21a and 22a are formed in the first and second EHV devices 21 and 22, respectively, are well known to those skilled in the art, and thus detailed description is omitted.

상기 핀틀(50)이 상기 하부틀(40)의 상단으로부터 분리될 시, 상기 제1,2EHV 장치(21, 22)들은 상기 제1,2유압 챔버(21a, 22a), 상기 좌우 파이프(5, 6), 그리고 상기 연통홀(32)을 통해 서로 연통될 수 있다.When the pintle (50) is separated from the upper end of the lower frame (40), the first and second EHV devices (21, 22) are the first and second hydraulic chambers (21a, 22a), the left and right pipes (5, 6) and may communicate with each other through the communication hole 32.

또한, 도2를 참조하면, 본 발명의 실시 예에 따른 오일 제어 밸브(10)가 장착된 밸브 트레인 구조는, 실린더 헤드(7) 내에 형성되는 어큐뮬레이터(25)를 더 포함할 수 있다. 이 경우, 상기 오일 제어 밸브(10)가 개방될 때 즉, 상기 핀틀(50)이 상기 하부틀(40)과 분리될 때, 상기 제1,2EHV 장치(21, 22)들 내의 오일이 상기 어큐뮬레이터(25)에 축적되도록 상기 밸브 트레인 구조가 형성될 수 있다. 상기 어큐뮬레이터(25)로의 오일 유출에 의해, 상기 제1,2밸브(3, 4)는 제1,2캠(1, 2)의 작동에도 불구하고 닫히게 된다.In addition, referring to FIG. 2, the valve train structure equipped with the oil control valve 10 according to the embodiment of the present invention may further include an accumulator 25 formed in the cylinder head 7. In this case, when the oil control valve 10 is opened, that is, when the pintle 50 is separated from the lower frame 40, oil in the first and second EHV devices 21 and 22 is the accumulator. The valve train structure may be formed to accumulate in (25). Due to the outflow of oil to the accumulator 25, the first and second valves 3 and 4 are closed despite the operation of the first and second cams 1 and 2.

도1을 참조하면, 본 발명의 실시 예에 따른 오일 제어 밸브(10)에 있어서, 상기 핀틀(50)은 중공일 수 있다. 또한 상기 오일 제어 밸브(10)는, 상단은 상기 핀틀(50)의 상부에 연결되고, 하단은 상기 하부틀(40)의 내부 공간에 형성된 지지부(35)에 연결됨으로써, 상기 핀틀(50)에 복원력을 작용시키는 스프링(60)을 더 포함할 수 있다.1, in the oil control valve 10 according to an embodiment of the present invention, the pintle 50 may be hollow. In addition, the oil control valve 10, the upper end is connected to the upper portion of the pintle 50, the lower end is connected to the support portion 35 formed in the inner space of the lower frame 40, thereby to the pintle 50 It may further include a spring 60 for acting on the restoring force.

상기 오일 제어 밸브(10) 내에 배치되는 작동기(15)는 솔레노이드에 의해 상하로 작동할 수 있다. 이 경우, 상기 오일 제어 밸브(10)에 전류가 인가되면 상기 작동기(15)는 아래로 또는 위로 작동하게 된다.The actuator 15 disposed in the oil control valve 10 may be operated up and down by a solenoid. In this case, when a current is applied to the oil control valve 10, the actuator 15 operates down or up.

따라서, 상기 작동기(15)가 아래로 작동하여 상기 핀틀(50)이 상기 하부틀(40)에 접촉할 시, 상기 스프링(60)은 압축될 수 있고, 상기 작동기(15)가 위로 작동하여 상기 핀틀(50)이 상기 하부틀(40)과 분리될 시, 상기 스프링(60)은 인장될 수도 있다. 상기 오일 제어 밸브(10)에 인가된 전류가 끊어질 경우에는, 압축 또는 인장된 상기 스프링(60)의 복원력에 의해 상기 핀틀(50)은 초기 위치로 돌아갈 수 있다.Therefore, when the actuator 15 is operated downward and the pintle 50 is in contact with the lower frame 40, the spring 60 can be compressed, and the actuator 15 is operated upward so that the When the pintle 50 is separated from the lower frame 40, the spring 60 may be tensioned. When the current applied to the oil control valve 10 is cut off, the pintle 50 may return to its initial position by the restoring force of the compressed or tensioned spring 60.

상기 핀틀(50)은 상기 작동기(15)의 하단부와 일체로 형성될 수 있지만, 반드시 그래야만 하는 것은 아니다. 상기 핀틀(50)은 상기 작동기(15)와 분리된 별개 부품일 수도 있다. 상기 핀틀(50)은 상기 작동기(15)와 상기 스프링(60)에 의해 상기 하부틀(40)에 선택적으로 접촉 또는 분리될 수 있기만 하면 된다.The pintle 50 may be formed integrally with the lower end of the actuator 15, but this is not necessary. The pintle 50 may be a separate part separate from the actuator 15. The pintle 50 only needs to be selectively contacted or separated from the lower frame 40 by the actuator 15 and the spring 60.

도3은 본 발명의 실시 예에 따른 오일 제어 밸브의 A-A 단면도이다.3 is an A-A cross-sectional view of an oil control valve according to an embodiment of the present invention.

도4는 본 발명의 실시 예에 따른 오일 제어 밸브의 B-B 단면도이다.4 is a B-B cross-sectional view of an oil control valve according to an embodiment of the present invention.

도3 및 도4를 참조하면, 본 발명의 실시 예에 따른 오일 제어 밸브(10)에 있어서, 상기 핀틀(50)에는 상기 핀틀(50) 하단의 외주 면을 따라 챔퍼(52)가 형성되고, 상기 하부틀(40)의 상단에는, 상기 챔퍼(52)와 만남으로써 고정 및 기밀 상태가 유지되도록, 챔퍼면(42)이 형성될 수 있다. 상기 챔퍼(52)와 상기 챔퍼면(42)의 결합에 의해 상기 핀틀(50)과 상기 하부틀(40)의 고정 상태 및 상기 연통홀(32)의 일단 및 타단 간 기밀 상태의 완전성이 확보될 수 있다.3 and 4, in the oil control valve 10 according to an embodiment of the present invention, the pintle 50 is formed with a chamfer 52 along the outer circumferential surface of the lower end of the pintle 50, A chamfer surface 42 may be formed at an upper end of the lower frame 40 so as to maintain a fixed and airtight state by contacting the chamfer 52. The combination of the chamfer 52 and the chamfer surface 42 ensures the integrity of the pintle 50 and the lower frame 40 and the integrity of the airtight state between one end and the other end of the communication hole 32. Can be.

도3 및 도4는 모두 상기 하부틀(40)과 상기 핀틀(50)이 서로 분리된 상태를 도시한다. 이 분리된 틈과 상기 연통홀(32)을 통해 상기 제1,2EHV 장치(21, 22)로 오일이 공급되거나, 상기 제1,2EHV 장치(21, 22)로부터 어큐뮬레이터(25)로 오일이 유출될 수 있다.3 and 4 both show the lower frame 40 and the pintle 50 separated from each other. Oil is supplied to the first and second EHV devices 21 and 22 through the separated gap and the communication hole 32, or oil is leaked from the first and second EHV devices 21 and 22 to the accumulator 25. Can be.

도1, 도3 및 도4를 참조하면, 본 발명의 실시 예에 따른 오일 제어 밸브(10)는, 상기 핀틀(50)이 상기 하부틀(40)과 분리될 때, 상기 제1EHV 장치(21) 및 상기 제2EHV 장치(22)로부터 오일이 유출됨으로써 상기 제1캠(1) 및 제2캠(2)의 작동에도 불구하고 상기 제1밸브(3) 및 상기 제2밸브(4)가 작동하지 않도록 구성된다.1, 3 and 4, the oil control valve 10 according to an embodiment of the present invention, when the pintle 50 is separated from the lower frame 40, the first EHV device 21 ) And the first valve 3 and the second valve 4 are operated despite the operation of the first cam 1 and the second cam 2 by the oil flowing out from the second EHV device 22. It is configured not to.

상기 오일 제어 밸브(10)는, 상기 핀틀(50)이 상기 하부틀(40)과 접촉할 때에는, 상기 제1캠(1) 및 제2캠(2)의 작동에 의해 상기 제1밸브(3) 및 상기 제2밸브(4)가 작동하도록 구성된다.The oil control valve 10, when the pintle 50 is in contact with the lower frame 40, the first valve (3) by the operation of the first cam (1) and the second cam (2) ) And the second valve 4 are configured to operate.

도6은 본 발명의 실시 예에 따른 오일 제어 밸브가 적용된 경우 캠각도에 따른 밸브 리프트를 도시한 그래프이다.6 is a graph showing the valve lift according to the cam angle when the oil control valve according to an embodiment of the present invention is applied.

도6을 참조하면, 본 발명의 실시 예에 따른 오일 제어 밸브(10)를 이용하면 제1,2밸브(3, 4)의 리프트가 거의 일치하게 됨을 알 수 있다. 이는 상기 연통홀(32)이 상기 하부틀(40)과 상기 핀틀(50)에 의해 막히지 않는 경우에는 상기 제1,2EHV 장치(21, 22)가 서로 연통됨으로써 압력이 동일해지고, 막히는 경우에는 상기 제1,2EHV 장치(21, 22)가 유체적으로 서로 분리되어 동일 압력 상태에서 독립적으로 작동하기 때문이다.Referring to FIG. 6, it can be seen that the lifts of the first and second valves 3 and 4 are almost identical when the oil control valve 10 according to the embodiment of the present invention is used. This means that when the communication hole 32 is not blocked by the lower frame 40 and the pintle 50, the first and second EHV devices 21 and 22 communicate with each other so that the pressure becomes the same, and when blocked, the This is because the first and second EHV devices 21 and 22 are fluidly separated from each other and operate independently under the same pressure.

이상으로 본 발명에 관한 바람직한 실시 예를 설명하였으나, 본 발명은 상기 실시 예에 한정되지 아니하며, 본 발명의 실시 예로부터 당해 발명이 속하는 기술분야에서 통상의 지식을 가진 자에 의한 용이하게 변경되어 균등하다고 인정되는 범위의 모든 변경을 포함한다.The preferred embodiments of the present invention have been described above, but the present invention is not limited to the above embodiments, and is easily changed and equalized by those skilled in the art from the embodiments of the present invention. Includes all changes to the extent deemed acceptable.

10: 오일 제어 밸브 15: 작동기
21: 제1EHV 장치 22: 제2EHV 장치
30: 바디 32: 연통홀
34: 오일 갤러리 35: 지지부
40: 하부틀 42: 챔퍼면
50: 핀틀 52: 챔퍼
60: 스프링10: oil control valve 15: actuator
21: first EHV device 22: second EHV device
30: body 32: communication hole
34: oil gallery 35: support
40: lower frame 42: chamfer surface
50: pintle 52: chamfer
60: spring

Claims (8)

제1캠 및 제2캠에 의해 각기 구동되며, 하부들에는 각기 제1밸브 및 제2밸브가 연결된, 제1전기유압밸브(Electro Hydraulic Valve; EHV) 장치 및 제2EHV 장치의 내부들에 각기 형성된 제1유압 챔버 및 제2유압 챔버의 오일 압력을 제어하도록 된 오일 제어 밸브에 있어서,
일단과 타단이 상기 제1유압 챔버와 상기 제2유압 챔버에 각기 연통되는 연통홀을, 포함하는 바디;
상기 바디의 하단부에 형성되거나 고정 장착되며, 상단의 높이가 상기 연통홀의 내부 공간에 위치함으로써 상기 연통홀과 상부가 연통되고, 오일을 공급하는 오일 갤러리와 하부가 연통되는, 중공의 하부틀; 그리고
상하 운동을 하는 작동기와 상기 하부틀 사이에 배치됨으로써 상기 연통홀을 상하로 관통하며, 상기 하부틀의 상기 상단과 접촉하거나 분리되는 핀틀;
을 포함하되,
상기 핀틀과 상기 하부틀이 서로 접촉할 시, 상기 연통홀의 상기 일단과 상기 타단이 연통되지 않는 것을 특징으로 하는 오일 제어 밸브.It is driven by the first cam and the second cam, and the first valve and the second valve are respectively connected to the lower parts, respectively formed in the interiors of the first electro-hydraulic valve (EHV) device and the second eHV device. An oil control valve adapted to control oil pressure in the first hydraulic chamber and the second hydraulic chamber,
A body including a communication hole through which one end and the other end communicate with the first hydraulic chamber and the second hydraulic chamber, respectively;
A hollow lower frame formed at a lower end of the body or fixedly mounted, the height of the upper end being located in the inner space of the communication hole, thereby communicating with the communication hole and the upper portion, and communicating with an oil gallery supplying oil and a lower portion; And
A pintle disposed between the actuator for vertical movement and the lower frame, penetrating the communication hole up and down, and contacting or separating the upper end of the lower frame;
Including,
When the pintle and the lower frame are in contact with each other, the oil control valve, characterized in that the one end and the other end of the communication hole is not in communication. 제1항에 있어서,
상기 핀틀은 중공이며,
상기 오일 제어 밸브는,
상단은 상기 핀틀의 상부에 연결되고, 하단은 상기 하부틀의 내부 공간에 형성된 지지부에 연결됨으로써, 상기 핀틀에 복원력을 작용시키는 스프링;
을 더 포함하는 것을 특징으로 하는 오일 제어 밸브.According to claim 1,
The pintle is hollow,
The oil control valve,
The upper end is connected to the upper portion of the pintle, and the lower end is connected to a support formed in the inner space of the lower frame, thereby applying a restoring force to the pintle;
Oil control valve further comprising a. 제1항에 있어서,
상기 작동기는 솔레노이드에 의해 상하로 작동하는 것을 특징으로 하는 오일 제어 밸브.According to claim 1,
The actuator is an oil control valve, characterized in that it operates up and down by a solenoid. 제1항에 있어서,
상기 핀틀은 상기 작동기의 하단부와 일체로 형성되는 것을 특징으로 하는 오일 제어 밸브.According to claim 1,
The pintle is an oil control valve, characterized in that formed integrally with the lower end of the actuator. 제1항에 있어서,
상기 하부틀, 상기 연통홀, 그리고 상기 핀틀은 각기 실린더 모양을 가지고, 상기 하부틀 및 상기 핀틀의 직경은 상기 연통홀의 직경보다 큰 것을 특징으로 하는 오일 제어 밸브.According to claim 1,
Each of the lower frame, the communication hole, and the pintle has a cylinder shape, and the diameter of the lower frame and the pintle is larger than the diameter of the communication hole. 제1항에 있어서,
상기 핀틀에는 상기 핀틀 하단의 외주 면을 따라 챔퍼가 형성되고,
상기 하부틀의 상단에는, 상기 챔퍼와 만남으로써 고정 및 기밀 상태가 유지되도록, 챔퍼면이 형성되는 것을 특징으로 하는 오일 제어 밸브.According to claim 1,
A chamfer is formed in the pintle along an outer circumferential surface of the bottom of the pintle,
The upper end of the lower frame, the oil control valve, characterized in that the chamfer surface is formed to maintain a fixed and airtight state by meeting the chamfer. 제1항에 있어서,
상기 핀틀이 상기 하부틀과 분리될 때, 상기 제1EHV 장치 및 상기 제2EHV 장치로부터 오일이 유출됨으로써 상기 제1캠 및 제2캠의 작동에도 불구하고 상기 제1밸브 및 상기 제2밸브가 작동하지 않도록 된 것을 특징으로 하는 오일 제어 밸브.According to claim 1,
When the pintle is separated from the lower frame, the first valve and the second valve do not operate despite the operation of the first cam and the second cam due to oil flowing out from the first EHV device and the second EHV device. Oil control valve characterized in that it is not. 제1항에 있어서,
상기 핀틀이 상기 하부틀과 접촉할 때, 상기 제1캠 및 제2캠의 작동에 의해 상기 제1밸브 및 상기 제2밸브가 작동하도록 된 것을 특징으로 하는 오일 제어 밸브.According to claim 1,
When the pintle is in contact with the lower frame, the oil control valve, characterized in that the first valve and the second valve is operated by the operation of the first cam and the second cam.
KR1020180159341A 2018-12-11 2018-12-11 Oil control valve KR20200071518A (en)

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