EP3674550A1 - Zweistufiges variables entlastungsventil für ölpumpe - Google Patents

Zweistufiges variables entlastungsventil für ölpumpe Download PDF

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Publication number
EP3674550A1
EP3674550A1 EP19206842.7A EP19206842A EP3674550A1 EP 3674550 A1 EP3674550 A1 EP 3674550A1 EP 19206842 A EP19206842 A EP 19206842A EP 3674550 A1 EP3674550 A1 EP 3674550A1
Authority
EP
European Patent Office
Prior art keywords
passage
bypass
primary
inlet passage
oil pump
Prior art date
Legal status (The legal status 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 status listed.)
Granted
Application number
EP19206842.7A
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English (en)
French (fr)
Other versions
EP3674550B1 (de
Inventor
Dong-Hun Kang
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hyundai Motor Co
Kia Corp
Original Assignee
Hyundai Motor Co
Kia Motors Corp
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Publication date
Application filed by Hyundai Motor Co, Kia Motors Corp filed Critical Hyundai Motor Co
Publication of EP3674550A1 publication Critical patent/EP3674550A1/de
Application granted granted Critical
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Active legal-status Critical Current
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/102—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes
    • 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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C14/26—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels

Definitions

  • the present disclosure relates to a relief valve for controlling a flow rate of an oil pump for supplying oil to a vehicle engine side.
  • an oil pump for pumping oil is used to feed oil for lubrication and cooling of an engine, and as illustrated in FIG. 1 , the oil pump discharges an oil pressure to an outlet while a rotor R connected to the engine side is driven.
  • a relief valve for preventing the discharge pressure discharged from the oil pump from rising by a certain pressure or more is used in the oil pump.
  • the relief valve is received to be elevated in the figure by elastically supporting a plunger 120 by a spring 130 inside a valve housing 110, bypass passages 111, 112, 113, 114 are formed in the valve housing 110, and the plunger is formed with a bypass hole.
  • the relief valve adjusts the discharge degree of the oil by repeatedly opening and closing the bypass passages 111, 112, 113, 114 according to the degree of the plunger 120 pressing the spring 130 by the discharge pressure of the oil.
  • the bypass passage of a two-stage variable relief valve is formed of the primary bypass inlet passage 111, the primary bypass outlet passage 112, the secondary bypass inlet passage 113, and the secondary bypass outlet passage 114 to be operated to bypass to a suction side through the primary bypass outlet passage 112 through the primary bypass inlet passage 111 at the time of the primary bypass according to the displacement of the plunger 120, and to bypass to the suction side through the secondary bypass outlet passage 114 through the secondary bypass inlet passage 113 at the time of the secondary bypass.
  • the oil pressure hysteresis means a phenomenon that a timing difference occurs in the section between the closing and the opening of the valve due to the inherent phenomena of the spring and the valve.
  • Patent Document 1 Korean Patent Laid-Open Publication No. 10-2005-0048151
  • the present disclosure is intended to solve the above problem, and an object of the present disclosure is to provide a two-stage variable relief valve for an oil pump, which can reduce an oil pump hysteresis phenomenon, thereby improving oil lubrication performance.
  • a two-stage variable relief valve for an oil pump includes, as the relief valve for adjusting discharge of oil to an engine side by the oil pump, a plunger operated in a valve housing, and a spring for elastically supporting the plunger, and the valve housing is formed with a bypass inlet passage and a bypass outlet passage, and the bypass inlet passage and the bypass outlet passage are opened or closed according to the displacement of the plunger, and the area of the bypass inlet passage is smaller than the area of the bypass outlet passage.
  • the overall area of the bypass inlet passage is smaller than 1/2 or less of the overall area of the bypass outlet passage.
  • each of the bypass inlet passage and the bypass outlet passage is disposed so that a plurality of passage holes are spaced apart from each other in parallel, and the area of each passage hole of the bypass inlet passage is smaller than the area of each passage hole of the bypass outlet passage.
  • each of the bypass inlet passage and the bypass outlet passage is disposed so that a plurality of passage holes are spaced apart from each other in parallel, and the number of passage holes of the bypass inlet passage is smaller than the number of passage holes of the bypass outlet passage.
  • bypass inlet passage includes a primary bypass inlet passage and a secondary bypass inlet passage
  • bypass outlet passage includes a primary bypass outlet passage and a secondary bypass outlet passage
  • the primary bypass inlet passage and the primary bypass outlet passage are opened and closed at the same time
  • the secondary bypass inlet passage and the secondary bypass outlet passage are opened and closed at the same time.
  • the primary bypass inlet passage and the primary bypass outlet passage are opened when the displacement of the plunger is relatively small compared to the secondary bypass inlet passage and the secondary bypass outlet passage, and the area of the primary bypass inlet passage is smaller than the area of the primary bypass outlet passage.
  • each of the primary bypass inlet passage and the primary bypass outlet passage is disposed so that a plurality of passage holes are spaced apart from each other in parallel, and the area of each passage hole of the primary bypass inlet passage is smaller than the area of each passage hole of the primary bypass outlet passage.
  • each of the primary bypass inlet passage and the primary bypass outlet passage is disposed so that a plurality of passage holes are spaced apart from each other in parallel, and the number of passage holes of the primary bypass inlet passage is smaller than the number of passage holes of the primary bypass outlet passage.
  • the opening/closing timings of the bypass in the oil pump are closely related to the fuel efficiency and function of the engine.
  • the bypass In the main fuel efficiency section, the bypass is opened to suppress the occurrence of a high oil pressure to maintain a constant and low pressure level, and in the high speed section requiring the high oil pressure, the bypass is temporarily closed to transmit the oil of a high pressure to various hydraulic mechanisms side.
  • valve timing for opening and closing the bypass is an important design factor that is determined by considering both the performance/function of the engine.
  • the present disclosure can reduce the area of the primary bypass inlet passage of the two-stage variable relief valve by 50% or more or reduce the places thereof compared to the primary bypass outlet passage, thereby minimizing or completely avoiding the hysteresis phenomenon.
  • FIG. 1 is a diagram illustrating a general relief valve for an oil pump
  • FIG. 2 is a diagram illustrating a performance map between the pressure and the flow rate of the oil pump
  • FIG. 3 is a diagram illustrating an oil pressure hysteresis phenomenon.
  • the present disclosure is for solving the oil pressure hysteresis of an oil pump by a two-stage variable relief valve.
  • the oil pump operates by opening the secondary bypass passages 113, 114 after the primary bypass passages 111, 112 are closed.
  • the slope of the bypass section (a ratio of a change in a flow rate according to a change in pressure) is related to the area of each corresponding passage of the oil pump.
  • the number and the area of the primary bypass inlet passage 111 and the primary bypass outlet passage 112 are designed to be the same.
  • the oil pressure hysteresis phenomenon of about 1,300 rpm occurs as a difference of the bypass closing timing occurs according to the speed-up/speed-down conditions.
  • the present disclosure solves the oil pressure hysteresis by optimizing the area of the oil pump bypass passage considering the relevance between the area of the oil pump bypass passage and the oil pressure hysteresis phenomenon.
  • FIGS. 4A to 5B are diagrams illustrating the results of reducing the area of the bypass passage compared to the conventional one.
  • FIG. 4A is a diagram illustrating the result of reducing the area of the primary bypass inlet passage 111 by 60%
  • FIG. 4B is a diagram illustrating the result of reducing the area of the primary bypass outlet passage 112 by 60%
  • FIG. 5A is a diagram illustrating the result of reducing the area of the secondary bypass outlet passage 114 by 60%
  • FIG. 5B is a diagram illustrating the result of reducing the area of the secondary bypass inlet passage 113 by 60%.
  • the present disclosure reduces the area of the primary bypass inlet passage of the two-stage variable relief valve, thereby reducing the hysteresis phenomenon.
  • FIG. 6 is a diagram illustrating the hysteresis result according to a reduction ratio of a primary bypass inlet passage
  • FIG. 7 is a diagram illustrating a performance map between the pressure and the flow rate of the oil pump according to the reduction ratio of the primary bypass inlet passage.
  • FIG. 7 is a graph illustrating the flow rate measured by increasing the pressure applied to the rear end of the oil pump at the same rpm, and it can be seen that when the primary bypass inlet passage 111 is reduced compared to the primary bypass outlet passage 112, a change in the bypass flow rate according to the same pressure change becomes small. That is, it can be seen that the slope becomes gentle in the bypass opening section and closing section.
  • the present disclosure reduces the area of a primary bypass inlet passage 11 of the two-stage variable relief valve having a pair of the bypass inlet passages and a pair of the bypass outlet passages compared to the area of a primary bypass outlet passage 12, thereby reducing the oil pressure hysteresis.
  • FIG. 9 is a diagram illustrating the hypothesis result according to the two-stage variable relief valve for the oil pump according to the present disclosure of FIG. 8 .
  • the time point at which the primary bypass passage is closed becomes early from 3,200 rpm to 2,300 rpm, thereby reducing the hysteresis.
  • the bypass passage can be configured in the form of dividing a plurality of passage holes. That is, the primary bypass inlet passage, the primary bypass outlet passage, the secondary bypass inlet passage, and the secondary bypass outlet passage can be arranged, respectively, so that a plurality of the passage holes are spaced apart from each other in parallel.
  • the present disclosure can reduce the area of each of the plurality of passage holes of the primary bypass inlet passage to 1/2 or less of the primary bypass outlet passage.
  • FIG. 10 is a diagram illustrating the hypothesis result in case of reducing the primary bypass inlet passage from two places to one place. Through this, it can be seen that the oil pressure hysteresis can also be reduced to the level of about 600 rpm, and as illustrated in FIG. 11 , it can be seen that the slope becomes gentle in the bypass section.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
EP19206842.7A 2018-12-27 2019-11-04 Zweistufiges variables entlastungsventil für ölpumpe Active EP3674550B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
KR1020180170482A KR102726692B1 (ko) 2018-12-27 2018-12-27 오일펌프용 2단 가변 릴리프 밸브

Publications (2)

Publication Number Publication Date
EP3674550A1 true EP3674550A1 (de) 2020-07-01
EP3674550B1 EP3674550B1 (de) 2024-02-28

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ID=68426261

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Application Number Title Priority Date Filing Date
EP19206842.7A Active EP3674550B1 (de) 2018-12-27 2019-11-04 Zweistufiges variables entlastungsventil für ölpumpe

Country Status (2)

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EP (1) EP3674550B1 (de)
KR (1) KR102726692B1 (de)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5921274A (en) * 1996-06-10 1999-07-13 Corken, Inc. Internal relief and bypass valve for pumps and piping systems
KR20050048151A (ko) 2003-11-19 2005-05-24 현대자동차주식회사 가변 릴리프 밸브의 구조
US20080041472A1 (en) * 2006-08-15 2008-02-21 Tbk Co., Ltd. Tandem pump valve structure
EP2600004A2 (de) * 2011-12-02 2013-06-05 Myunghwa Ind. Co., Ltd. Variable Ölpumpe

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR102715969B1 (ko) * 2016-12-30 2024-10-14 명화공업주식회사 오일펌프용 릴리프 밸브의 편마모 방지 구조

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5921274A (en) * 1996-06-10 1999-07-13 Corken, Inc. Internal relief and bypass valve for pumps and piping systems
KR20050048151A (ko) 2003-11-19 2005-05-24 현대자동차주식회사 가변 릴리프 밸브의 구조
US20080041472A1 (en) * 2006-08-15 2008-02-21 Tbk Co., Ltd. Tandem pump valve structure
EP2600004A2 (de) * 2011-12-02 2013-06-05 Myunghwa Ind. Co., Ltd. Variable Ölpumpe

Also Published As

Publication number Publication date
KR102726692B1 (ko) 2024-11-06
KR20200080724A (ko) 2020-07-07
EP3674550B1 (de) 2024-02-28

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