WO2018092931A1 - Système de commande de pompe à huile variable et soupape de commande de pompe à huile variable utilisée à cet effet - Google Patents

Système de commande de pompe à huile variable et soupape de commande de pompe à huile variable utilisée à cet effet Download PDF

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Publication number
WO2018092931A1
WO2018092931A1 PCT/KR2016/013230 KR2016013230W WO2018092931A1 WO 2018092931 A1 WO2018092931 A1 WO 2018092931A1 KR 2016013230 W KR2016013230 W KR 2016013230W WO 2018092931 A1 WO2018092931 A1 WO 2018092931A1
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WO
WIPO (PCT)
Prior art keywords
oil pump
control valve
land
variable oil
variable
Prior art date
Application number
PCT/KR2016/013230
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English (en)
Korean (ko)
Inventor
이창훈
문국찬
박지훈
박준효
Original Assignee
주식회사 유니크
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 주식회사 유니크 filed Critical 주식회사 유니크
Priority to PCT/KR2016/013230 priority Critical patent/WO2018092931A1/fr
Publication of WO2018092931A1 publication Critical patent/WO2018092931A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/02—Pressure lubrication using lubricating pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/16—Controlling lubricant pressure or quantity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M11/00—Component parts, details or accessories, not provided for in, or of interest apart from, groups F01M1/00 - F01M9/00
    • F01M11/10—Indicating devices; Other safety devices
    • 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

Definitions

  • the present invention relates to a variable oil pump control system and a variable oil pump control valve used therein, and more particularly, to a variable oil pump control system having a fail-safe function and a variable oil pump control valve used therein.
  • the oil pump sucks oil stored in an oil pan and drives the oil pump to each part of the engine when the engine is driven.
  • the oil pressurized by the oil pump is applied to the friction causing part to reduce the frictional resistance and prevent the wear of the part.
  • the oil pump control system for controlling the oil pump comprises a relief valve.
  • the relief valve prevents the pressure of the oil discharged from the oil pump (hereinafter referred to as 'oil pump discharge pressure') to rise above the set value. That is, the relief valve recirculates a part of the discharged oil to the suction part of the oil pump when the oil pump discharge pressure applied to the plunger upper surface is greater than the supporting force of the spring supporting the plunger.
  • the relief valve performs the opening and closing operation by a mechanical operation, there is a limit in actively controlling the oil pump discharge pressure in response to the engine operating condition, the temperature of the oil, the temperature of the cooling water, and the like.
  • the oil pump control system calculates the set value of the oil pump discharge pressure in response to information related to the hydraulic pressure and the operating state of the engine, and performs feedback control so that the measured value input from the sensor follows the set value. It is possible to manage the load of the oil pump by preventing the oil pump discharge pressure rises more than necessary when driving the load, thereby improving the fuel efficiency reduction effect.
  • the conventional oil pump control system does not include a fail safe function to ensure the minimum safety in the event of an abnormality in the hydraulic control valve for controlling the discharge pressure of the oil pump may cause a safety problem.
  • the discharge pressure of the oil pump may be higher than the maximum setting value or lower than the minimum setting value, thereby causing a problem in the vehicle oil pump control system.
  • the present invention is to solve the above problems of the prior art variable oil pump control system that can provide a fail-safe function without adding a separate configuration to a variable oil pump control system for a vehicle and a variable oil pump control valve used therein
  • the purpose is to provide.
  • Variable oil pump control system for achieving the above object, a variable oil pump for pumping oil stored in the oil pan to the engine, a control valve for adjusting the pressure of the oil discharged to the variable oil pump, the engine It includes a sensor for sensing the state of the oil being pumped to, and the controller for controlling the operation of the control valve according to the vehicle information input from the outside and the state of the oil sensed by the sensor. At this time, the control valve is operated by the electrical signal transmitted from the controller and the oil discharged from the variable oil pump.
  • the control valve may have a structure that is opened by the pressure of the oil discharged from the variable oil pump when a defect occurs or closed by the pressure of the oil discharged from the variable oil pump.
  • variable oil pump control valve used in the variable oil pump control system includes a valve for intercepting oil in and out and a solenoid for operating the valve.
  • the valve has a pipe-shaped holder having a discharge port formed at an upper end, a control port formed at an interruption thereof, and a supply port formed at a lower end thereof, and a first land and a second land contacting the inner circumferential surface of the holder at an upper end and a lower end, respectively. And a spool formed with a working groove formed between the first land and the second land.
  • the first land and the second land may be formed to have different diameters.
  • the first land may be formed with a larger diameter than the second land, or the second land may be formed with a larger diameter than the first land.
  • the present invention has a structure in which the control valve for adjusting the variable oil pump discharge pressure is operated by the electrical signal of the controller and the oil discharged from the variable oil pump, so that even if a defect occurs in the control valve, the variable oil pump discharge pressure is the highest. It can be prevented from rising above the set value or below the minimum set value. This provides a fail-safe feature that ensures minimal safety without adding a separate configuration to the variable oil pump control system.
  • variable oil pump control valve of the present invention is operated by the electrical signal of the controller and the oil discharged from the variable oil pump, it is possible to extend the control section compared to the conventional valve that operates only by the electrical signal of the controller. That is, since the variable oil pump discharge pressure gradually increases in proportion to the electrical signal (the strength of the current), the control section can be extended.
  • FIG. 1 is a schematic diagram of a variable oil pump control system according to an embodiment of the present invention.
  • Figure 2 is a cross-sectional view of the control valve of the variable oil pump control system according to an embodiment of the present invention.
  • FIG. 3 is an enlarged view of one of the control valves shown in FIG. 2;
  • FIG. 4 is a view showing a modification of the valves of the control valve shown in FIG.
  • variable oil pump control system for pumping the oil stored in the oil pan (P) to the engine (E), and the oil discharged to the variable oil pump (2)
  • a control valve also referred to as a variable oil pump control valve for regulating pressure, that is, a variable oil pump discharge pressure, a sensor (3) for detecting a state of oil being fed to the engine (E), and input from the outside
  • a controller 4 for controlling the operation of the control valve 1 according to the vehicle information and the state of the oil sensed by the sensor 3.
  • the variable oil pump 2 may be an oil pump capable of reducing the load of the pump in the high speed operation section and improving fuel efficiency by adjusting the pressure and flow rate of the oil.
  • the variable oil pump 2 rotates and pumps the first chamber 22 and the slider (not shown) connected to the main gallery M to transmit the discharge pressure of the variable oil pump 2 to the engine E.
  • a second chamber 24 connected to the control valve 1 to adjust the volume.
  • variable oil pump 2 is illustrated as having two chambers 22 and 24, but the present invention is not limited thereto, and the variable oil pump 2 may be a variable oil pump having a structure in which a slider is rotated into one chamber. to be.
  • the control valve 1 is a valve for adjusting the variable oil pump discharge pressure, and more specifically, the variable oil pump discharge pressure is controlled by controlling the oil supplied to the second chamber 24 to rotate the slider (not shown). To adjust the valve.
  • the control valve 1 of this embodiment is a three-port two-way solenoid valve operated by an electrical signal (intensity of current) received from the controller 4 and oil discharged from the variable oil pump 2.
  • the control valve 1 is moved by the current supplied through the connector 260 of the solenoid 200 and the oil supplied through the supply port 112 of the valve 100 and the spool 120 is moved. Enforce access (see FIG. 2).
  • the sensor 3 detects the pressure of the oil ( variable oil pump discharge pressure), the temperature of the oil, etc., which is supplied to the engine E through the main gallery M, and transmits it to the controller 4, and whether its own function is normal. Check it and pass it to the controller (4). That is, the sensor 3 has a function of detecting the pressure of the oil, a function of detecting the temperature of the oil, and a function of diagnosing whether it is normal.
  • the controller 4 controls the overall operation of the variable oil pump control system.
  • the controller 4 monitors the state of the oil (pressure, temperature, etc.) detected by the vehicle information and the sensor 3 input from the outside, and controls the control valve 1 to adjust the variable oil pump discharge pressure.
  • variable oil pump control system having the above-described configuration calculates the set value of the variable oil pump discharge pressure according to the vehicle information input from the outside and the state of the oil sensed by the sensor 3, and sets the variable oil pump discharge pressure.
  • the control valve 1 is controlled to follow the value. At this time, the control valve 1 is operated by oil discharged from the variable oil pump 2 in addition to the electrical signal (intensity of current) received from the controller 4.
  • oil discharged from the variable oil pump 2 and delivered to the engine E is branched from the main gallery M and supplied to the control valve 1.
  • the oil supplied to the control valve 1 flows into the supply port (112 in FIG. 2) of the valve (100 in FIG. 2) and affects the movement of the spool (120 in FIG. 2).
  • the oil introduced into the supply port 112 serves to raise the spool 120.
  • the oil introduced into the supply port 112 serves to lower the spool 120.
  • control valve 1 which is operated by the electrical signal (intensity of current) of the controller 4 and the oil discharged from the variable oil pump 2 provides a fail safe function of the variable oil pump control system.
  • the control valve 1 which is operated by the electrical signal (intensity of current) of the controller 4 and the oil discharged from the variable oil pump 2 can extend the control section of the variable oil pump discharge pressure.
  • the control valve 1 when the control valve 1 is operated, the variable oil pump discharge pressure discharged from the variable oil pump 2 is lowered.
  • the variable oil pump discharge pressure When the variable oil pump discharge pressure is lowered, the variable oil pump discharge pressure is branched from the main gallery M to control the valve 1.
  • the oil supplied to the reactor is reduced. That is, in order to operate the control valve 1, the strength of the current applied from the controller 4 must be increased. Therefore, although the discharge pressure of the variable oil pump increases in proportion to the intensity of the applied current, since the slope is gentle, the current control of the control valve 1 can be extended.
  • control valve 1 of the variable oil pump control system according to an embodiment of the present invention will be described.
  • variable oil pump control valve 1 includes a valve 100 for controlling oil in and out, and a solenoid 200 for operating the valve 100.
  • the solenoid 200 first, the case 210 surrounding the magnetic portion 110b of the holder 110, the bobbin 220 installed inside the case 210, and the coil wound around the outer peripheral surface of the bobbin 220 ( 230, a plunger 240 installed inside the magnetic part 110b, a cover 250 coupled to the other end of the case 210, and a connector 260 protruding to the side of the case 210. .
  • the case 210 has a cup shape in which a lower surface is opened and the upper surface is closed.
  • An accommodation space 212 is formed inside the case 210, and a bobbin 220 is installed in the storage space 212.
  • the lower end of the case 210 is curled to surround the cover 250.
  • Bobbin 220 is a hollow spool shape.
  • the coil 230 is wound around the outer circumferential surface of the bobbin 220.
  • the magnetic field generated from the coil 230 when the power is applied is induced by the magnetic part 110b and the case 210 to raise the plunger 240.
  • the strength of the magnetic field is proportional to the strength of the current flowing along the coil 230 and the number of coils 230 wound on the bobbin 220. Therefore, since a strong magnetic field is generated as a strong current is applied to the coil 230 or the coil 230 is wound much, the movement of the plunger 240 can be reliably controlled.
  • the plunger 240 is a movable iron core reciprocating by the magnetic field generated by the coil 230, is installed to be movable in the magnetic part 110b, and is in contact with the lower end of the spool 120.
  • the plunger 240 is formed with a passage 242 penetrating the plunger 240 up and down.
  • the passage 242 has oil filled in the upper portion of the plunger 240 to the lower portion of the plunger 240 and oil filled in the lower portion of the plunger 240 is the plunger 240. Is transported to the top of the.
  • the passage 242 is eccentric a predetermined distance from the center of the plunger 240, to prevent the passage 242 is closed by the contact with the spool 120.
  • the lower end of the plunger 240 is formed into a curved surface to make local surface contact with the bottom of the cover 250.
  • the plunger 240 and the cover 250 is in contact with the local surface, the plunger 240 can be smoothly raised by blocking the flow of the magnetic field which was directly led to the plunger 240 through the cover 250.
  • the frictional resistance due to the inclination of the plunger 240 may be eliminated without affecting the inclination of the plunger 240.
  • the surface of the plunger 240 is electroless nickel plated.
  • the inner circumferential surface of the holder 110 in particular, the inner circumferential surface of the magnetic portion 110b in contact with the plunger 240 is softened. As described above, when the plunger 240 is plated and the magnetic portion 110b is soft nitrided, friction generated when the plunger 240 is moved may be reduced.
  • the connector 260 is a means for applying power to the coil 230.
  • a plurality of terminals 262 are installed inside the connector 260.
  • the connector 260 protrudes outward through the side of the case 210.
  • the valve 100 includes a holder 110, an spool 120 movably installed inside the holder 110, and an adjustment coupled to an upper portion of the spool 120. Screw 130, and the spring 140 is interposed between the spool 120 and the adjusting screw 130.
  • the holder 110 has a pipe shape extending from the valve 100 to the solenoid 200.
  • the upper part of the holder 110 (the upper part based on the flange 110c) is a part which controls and discharges the pressure of the oil supplied to the valve 100, and the lower part of the holder 110 is a magnetic field for operating the valve 100. This is the part that induces.
  • the upper portion of the holder 110 will be referred to as the hydraulic portion 110a and the lower portion of the holder 110 will be referred to as the magnetic portion 110b.
  • the hydraulic part 110a has a pipe shape having an outer diameter larger than that of the magnetic part 110b.
  • a supply port 112 for supplying oil is formed at a lower end of the hydraulic part 110a, and a control port 114 for discharging oil controlled at a predetermined pressure is formed at the hydraulic part 110a.
  • an O-ring 116 is installed on the lower outer circumferential surface of the hydraulic unit 110a to prevent leakage of oil.
  • the adjusting screw 130 is provided at the upper end of the hydraulic part 110a, and the discharge port 132 is formed at the adjusting screw 130.
  • the discharge port 132 discharges a portion of the oil introduced from the supply port 112 and the oil introduced from the control port 114 to the outside, that is, the oil pan (not shown).
  • a spring 140 is installed below the adjustment screw 130.
  • the adjusting screw 130 controls the moving distance and the moving speed of the spool 120 by adjusting the elasticity of the spring 140 supporting the spool 120.
  • the adjusting screw 130 is screwed to the top of the hydraulic portion (110a) to finely adjust the elasticity of the spring (140).
  • the magnetic part 110b has a pipe shape having an outer diameter smaller than that of the hydraulic part 110a.
  • a magnetic induction groove 118 is formed on the outer peripheral surface of the magnetic part 110b, and an O-ring 116 is installed on the lower outer peripheral surface to prevent leakage of oil.
  • Magnetic induction groove 118 is a means for securing a sufficient magnetic force to effectively control the high pressure and high flow oil. As shown in FIG. 1, the stopping wall surface of the magnetic part 110b in which the magnetic induction grooves 118 are formed is formed to be thinner than the upper and lower portions thereof. The magnetic field generated from the coil 230 when the power is applied is induced along the magnetic part 110b but is concentrated in the magnetic induction groove 118 having a relatively thin thickness.
  • the magnetic induction groove 118 described above uses the principle that the magnetic flux density increases as the area of the object on which the magnetic field is formed decreases.
  • the magnetic induction groove 118 of the present embodiment has a tapered shape, the thickness of which becomes thinner toward the center, and thus can concentrate the magnetic field more effectively. Therefore, it is possible to precisely control the plunger 240 moving by the magnetic field, through which it is possible to control the high pressure and high flow oil.
  • the spool 120 is a means for selectively connecting the supply port 112, the control port 114, the discharge port 132 during its movement.
  • the spool 120 has a rod shape having a plurality of stages having different outer diameters, and is installed to be movable in the hydraulic part 110a.
  • the spool 120 has a rod shape extending in the longitudinal direction of the holder 110.
  • the first land 122 and the second land 124 are formed at the upper end and the lower end of the spool 120, and the operation groove 126, which is a small diameter part, is formed at the middle of the spool 120.
  • a flow path 128 connecting the discharge port 132 and the magnetic part (110b of FIG. 2) is formed in the spool 120.
  • the first land 122 and the second land 124 contact the inner circumferential surface of the holder 110 to guide the movement of the spool 120.
  • the first land 122 contacts the upper or lower portion of the control port 114 when the spool 120 moves to block the connection of the ports 112, 114, and 132.
  • the spool 120 rises, the supply port 112 and the control port 114 are connected, and the connection between the control port 114 and the discharge port 132 is blocked (see FIG. 6).
  • the connection of the supply port 112 and the control port 114 is blocked, and the control port 114 and the discharge port 132 are connected.
  • the first land 122 and the second land 124 of the holder 110 is formed with a different diameter.
  • the first land 122 is formed to have a larger diameter than the second land 124 (D 1 > D 2 ), and the large diameter part which contacts the first land 122 in the holder 110. 152 and the small diameter portion 154 in contact with the second land 124.
  • the diameter D 1 of the first land 122 is larger than the diameter D 2 of the second land 124.
  • a greater pressure is applied to the lower surface of the first land 122 than the upper surface of the second land 124. Therefore, the oil supplied through the supply port 112 in the state in which power is not supplied to the solenoid 200 (200) will raise the spool 120.
  • variable oil pump control valve 1 As a result, in the variable oil pump control valve 1 according to the present embodiment, even when it is impossible to operate due to an electrical defect, the spool 120 is raised by the oil supplied through the supply port 112 so that the control port 114 ) Prevents the variable oil pump discharge pressure from rising above the maximum set value. That is, it has a fail-safe function for the highest set value of the variable oil pump discharge pressure.
  • variable oil pump control valve 1 since the diameter D 1 of the first land 122 is smaller than the diameter D 2 of the second land 124, the supply port ( When oil is supplied through 112, a greater pressure is applied to the upper surface of the second land 124 than the lower surface of the first land 122. Therefore, the oil supplied through the supply port 112 in a state in which power is not supplied to the solenoid (200 of FIG. 2) will lower the spool 120.
  • variable oil pump control valve 1 of this structure when the spool 120 is maintained in a raised state due to a failure (ie, a mechanical defect) of the spring 140 or the like, the supply port 112 is opened. By the oil supplied through the spool 120 is lowered to close the control port 114 to prevent the variable oil pump discharge pressure is lowered below the minimum set value. That is, it has a fail safe function with respect to the lowest set value of the variable oil pump discharge pressure.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Magnetically Actuated Valves (AREA)

Abstract

La présente invention concerne un système de commande de pompe à huile variable ayant une fonction à sécurité intégrée, et une soupape de commande de pompe à huile variable utilisée à cet effet. La présente invention comprend : une pompe à huile variable pour alimenter en pression une huile stockée dans un carter d'huile à un moteur; une soupape de commande pour commander la pression de l'huile qui est évacuée vers la pompe à huile variable; un capteur pour détecter l'état de l'huile qui est alimenté en pression au moteur; et un dispositif de commande pour commander le fonctionnement de la soupape de commande en fonction de l'état de l'huile détectée au moyen du capteur et des informations de véhicule entrées depuis l'extérieur. La soupape de commande fonctionne au moyen d'un signal électrique transmis à partir du dispositif de commande et de l'huile évacuée par la pompe à huile variable, et peut ainsi empêcher la pression de refoulement de la pompe à huile variable de devenir égale ou supérieure à une valeur de consigne maximale ou égale ou inférieure à une valeur de consigne minimale, même si un défaut se produit dans la soupape de commande.
PCT/KR2016/013230 2016-11-16 2016-11-16 Système de commande de pompe à huile variable et soupape de commande de pompe à huile variable utilisée à cet effet WO2018092931A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/KR2016/013230 WO2018092931A1 (fr) 2016-11-16 2016-11-16 Système de commande de pompe à huile variable et soupape de commande de pompe à huile variable utilisée à cet effet

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/KR2016/013230 WO2018092931A1 (fr) 2016-11-16 2016-11-16 Système de commande de pompe à huile variable et soupape de commande de pompe à huile variable utilisée à cet effet

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WO2018092931A1 true WO2018092931A1 (fr) 2018-05-24

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH08225011A (ja) * 1994-12-20 1996-09-03 Mitsubishi Motors Corp 可変流量制御装置
KR101160470B1 (ko) * 2012-05-14 2012-06-27 주식회사 유니크 솔레노이드 밸브
KR101167503B1 (ko) * 2011-11-01 2012-07-20 주식회사 유니크 오일펌프 컨트롤 밸브
KR20130066837A (ko) * 2011-12-13 2013-06-21 현대자동차주식회사 차량용 오일펌프 제어시스템
KR101559423B1 (ko) * 2014-10-08 2015-10-13 주식회사 유니크 오일펌프 컨트롤 밸브

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH08225011A (ja) * 1994-12-20 1996-09-03 Mitsubishi Motors Corp 可変流量制御装置
KR101167503B1 (ko) * 2011-11-01 2012-07-20 주식회사 유니크 오일펌프 컨트롤 밸브
KR20130066837A (ko) * 2011-12-13 2013-06-21 현대자동차주식회사 차량용 오일펌프 제어시스템
KR101160470B1 (ko) * 2012-05-14 2012-06-27 주식회사 유니크 솔레노이드 밸브
KR101559423B1 (ko) * 2014-10-08 2015-10-13 주식회사 유니크 오일펌프 컨트롤 밸브

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