EP2674583A1 - Appareil d'alimentation en huile pour moteur et pourvue de soupape de surpression à deux étages - Google Patents

Appareil d'alimentation en huile pour moteur et pourvue de soupape de surpression à deux étages Download PDF

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Publication number
EP2674583A1
EP2674583A1 EP12172117.9A EP12172117A EP2674583A1 EP 2674583 A1 EP2674583 A1 EP 2674583A1 EP 12172117 A EP12172117 A EP 12172117A EP 2674583 A1 EP2674583 A1 EP 2674583A1
Authority
EP
European Patent Office
Prior art keywords
outlet side
working fluid
engine
speed
relief valve
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
EP12172117.9A
Other languages
German (de)
English (en)
Other versions
EP2674583B1 (fr
Inventor
Hyuk In Kwon
Jin Yong Kim
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.)
Myunghwa Ind Co Ltd
Original Assignee
Myunghwa Ind Co Ltd
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 Myunghwa Ind Co Ltd filed Critical Myunghwa Ind Co Ltd
Priority to EP12172117.9A priority Critical patent/EP2674583B1/fr
Publication of EP2674583A1 publication Critical patent/EP2674583A1/fr
Application granted granted Critical
Publication of EP2674583B1 publication Critical patent/EP2674583B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F01M1/16—Controlling lubricant pressure or quantity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/08—Regulating by delivery pressure
    • 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
    • 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
    • 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
    • F04C13/00—Adaptations of machines or pumps for special use, e.g. for extremely high pressures

Definitions

  • the present invention relates to an oil supply apparatus for an engine provided with a two-stage relief valve, and more particularly, to an oil supply apparatus for an engine provided with a two-stage relief valve capable of reducing a rotational load of an engine and improving fuel efficiency by relieving a supply oil pressure at two stages of a medium speed range and a high speed range of the engine using the oil supply apparatus to prevent excessive supply of an oil pressure to the engine requiring lubrication.
  • an engine requires a lubrication apparatus that can lubricate operating components such as a piston and a crankshaft.
  • the lubrication apparatus requires an oil supply apparatus such as an oil pump that can supply a working fluid such as oil to places where a lubrication operation is needed.
  • a rotor-type oil supply apparatus is connected to a crankshaft to be used to adjust an ejected amount of a working fluid in proportion to an engine speed. Accordingly, a flow rate of an ejected working fluid of a conventional oil supply apparatus is increased in proportion to the engine speed.
  • the present invention provides an oil supply apparatus for an engine provided with a two-stage relief valve, in which a sufficient amount of working fluid is supplied in proportion to an engine speed in a low speed range where sufficient lubrication is not performed and a flow rate of the working fluid is reduced in a medium and high speed range where smooth lubrication is performed to reduce a rotational load applied to a crankshaft, capable of reducing an engine load to decrease fuel consumption to improve fuel efficiency as well as improving a lubrication operation through supply of an appropriate flow rate.
  • the present invention is directed to an oil supply apparatus for an engine provided with a two-stage relief valve including: an oil pump housing having an inlet side and an outlet side configured to enable entry and exit of a working fluid; a rotor mounted in the oil pump housing and driven in proportion to an engine speed; a relief valve operated by a pressure of the working fluid between the inlet side and the outlet side; and first and second flow paths formed between the inlet side and the relief valve, wherein the relief valve is elastically supported and opened in a sequence from a low speed, a medium speed, a medium/high speed, and a high speed in proportion to the engine speed, and a working fluid amount of the outlet side is returned to the inlet side through the first or second flow path in proportion to the engine speed at the medium speed and the high speed.
  • the relief valve may block the first and second flow paths regardless of the working fluid pressure of the outlet side when the rotor is rotated at the low speed, may be opened by a hydraulic pressure of the outlet side to return a portion of the working fluid of the outlet side to the inlet side through the second flow path when the rotor is rotated at the medium speed, may be further opened by the hydraulic pressure of the outlet side to block the first and second flow paths when the rotor is rotated at the medium/high speed, and may be opened by the hydraulic pressure of the outlet side to return a portion of the working fluid of the outlet side to the inlet side through the first flow path when the rotor is rotated at the high speed.
  • the relief valve may include: a valve housing having both ends connected to branch pipes branched from the inlet side and the outlet side, respectively; a valve body having a fluid path hole to communicate the outlet side with the second flow path at the medium speed, and installed in the valve housing to communicate the outlet side with the first flow path at the high speed; and an elastic spring mounted in the valve housing to provide a recovering force to the valve body operated by the working fluid pressure introduced from the outlet side.
  • FIG. 1 is a partial cross-sectional view showing a configuration of an oil supply apparatus in accordance with an exemplary embodiment of the present invention
  • FIG. 2A is a schematic view for explaining operation states of the oil supply apparatus in accordance with an exemplary embodiment of the present invention.
  • arrows shown in dotted lines represent conveyance directions of the working fluid.
  • An oil supply apparatus 1000 in accordance with an exemplary embodiment of the present invention includes an oil pump housing 100 and a rotor 200 configured to supply a working fluid in proportion to an engine speed, a relief valve 300 configured to return a portion of the working fluid of an output side to an input side, a first flow path 400 configured to form a flow path such that a portion of the working fluid output from the oil pump housing 100 is returned when the engine speed is at a medium speed, and a second flow path 500 configured to form a flow path such that a portion of the working fluid output from the oil pump housing 100 is returned when the engine speed is at a high speed.
  • the oil pump housing 100 has inner teeth 130 formed therein, and an inlet side 110 and an outlet side 120 formed at both sides thereof and configured to receive the working fluid and discharge the working fluid at a predetermined pressure.
  • a branch pipe 111 is provided at the inlet side 110 to receive the working fluid returned from the relief valve 300, and another branch pipe 121 is provided at the outlet side 120 to divide the working fluid to the relief valve 300.
  • the branch pipes 111 and 121 are connected to both ends of the relief valve 300, respectively.
  • the rotor 200 is a rotary body, which is conventionally connected to a crankshaft of an engine and driven in proportion to a speed of the engine.
  • the rotor 200 has outer teeth 210 formed at an outer circumference thereof.
  • the outer teeth 210 compress a space between the inner teeth 130 and the outer teeth 210 to pressurize the working fluid filled therein as the rotor 200 is rotated.
  • Driving of the rotor 200 is conventionally performed by a well known configuration of a rotor-type oil pump, and thus, detailed description thereof will be omitted.
  • the relief valve 300 includes a valve housing 310 having both ends connected to the branch pipes 111 and 121, respectively, a valve body 320 installed in the valve housing 310 and operating in a longitudinal direction thereof, and an elastic spring 330 configured to provide a constant elastic force to the valve body 320.
  • the valve housing 310 has a hollow cylindrical shape, and is provided with both ends connected to the branch pipes 111 and 121 to receive a working fluid pressure from the inlet side 110 and the outlet side 120.
  • the valve body 320 has a compartment 321a formed at one side thereof and configured to receive the working fluid through the branch pipe 121, and a seat surface 322 formed at the other side and on which the elastic spring 330 is mounted.
  • the compartment 321a has a fluid path hole 321 through which the working fluid of the outlet side 120 is returned to the inlet side 110.
  • the fluid path hole 321 is formed at a position that can be in communication with the second flow path 500 (described later) when the engine speed is at a medium speed.
  • the compartment 321a is manufactured to have a length such that the first and second flow paths 400 and 500 are blocked when the engine speed is at a medium/high speed or less and the branch pipe 121 is in communication with the first flow path 400 when the engine speed is at a high speed.
  • the elastic spring 330 functions to provide an elastic force to a rear portion of the valve body 320 to allow the valve body 320 to block the outlet side 120 in the valve housing 310.
  • the elastic spring 330 is installed to be supported in the valve housing 310 at one end and seated on the seat surface 322 at the other end.
  • the first flow path 400 and the second flow path 500 are flow paths formed to communicate between the inlet side 110 and the valve housing 310.
  • the first flow path 400 and the second flow path 500 are formed to sandwich the fluid path hole 321 therebetween.
  • a position of the fluid path hole 321 is shown when the valve body 320 is closed by the elastic force of the elastic spring 330 and the working fluid pressure of the inlet side 110.
  • the first flow path 400 configured as described above is kept closed by the valve body 320, and is connected to be in communication with the inlet side 110 only when the valve body 320 is opened by a pressure of the outlet side 120 while the engine is rotated at a high speed.
  • the second flow path 500 is kept closed by the valve body 320, and is connected to be in communication with the fluid path hole 321 to communicate the outlet side 120 with the inlet side 110 as the valve body 320 is opened by the pressure of the outlet side 120 while the engine is rotated at a medium speed.
  • FIGS. 2A to 2D are schematic views for explaining operation states of the oil supply apparatus in accordance with an exemplary embodiment of the present invention
  • FIG. 3 is a graph showing a relation between a pressure of a working fluid of the oil supply apparatus in accordance with an exemplary embodiment of the present invention and an engine speed.
  • arrows shown in dotted lines represent a conveyance direction of the working fluid
  • arrows shown in solid lines represent a returned direction of the working fluid
  • a dotted line represents a pressure variation line increased in proportion to the engine speed.
  • the oil supply apparatus 1000 in accordance with an exemplary embodiment of the present invention is divided into a low speed range A, a medium speed range B, a medium/high speed range C and a high speed range D, which have different pressures of the working fluid.
  • the pressure of the outlet side 120 is higher than that of the inlet side 110 due to an increase in engine speed.
  • the valve body 320 moves leftward in a longitudinal direction of the valve housing 310 to be opened, the fluid path hole 321 is in communication with the second flow path 500.
  • the pressure of the outlet side 120 is partially returned to the inlet side 110 through the second flow path 500 to be decreased below the dotted line, which represents a graph in proportion to the engine speed, as shown in FIG. 3 .
  • the valve body 320 is further pushed leftward. Accordingly, the fluid path hole 321 in communication with the second flow path 500 is blocked to prevent the pressure of the outlet side 120 from returning to the inlet side 110.
  • the pressure of the outlet side 120 is increased, and at this time, since the pressure in the medium/high speed range C is reduced under the pressure already decreased from the medium speed range B as shown in FIG. 3 , the pressure is increased from the low pressure to a pressure in proportion to the engine speed.
  • the flow rate of the working fluid can be supplied according to an amount required by the lubrication operation, and thus, the load applied to the engine can be reduced to decrease the fuel consumption and improve the engine output.
  • the oil supply apparatus for an engine provided with a two-stage relief valve in accordance with the present invention has the following effects.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
EP12172117.9A 2012-06-15 2012-06-15 Appareil d'alimentation en huile pour moteur et pourvue de soupape de surpression à deux étages Not-in-force EP2674583B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP12172117.9A EP2674583B1 (fr) 2012-06-15 2012-06-15 Appareil d'alimentation en huile pour moteur et pourvue de soupape de surpression à deux étages

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP12172117.9A EP2674583B1 (fr) 2012-06-15 2012-06-15 Appareil d'alimentation en huile pour moteur et pourvue de soupape de surpression à deux étages

Publications (2)

Publication Number Publication Date
EP2674583A1 true EP2674583A1 (fr) 2013-12-18
EP2674583B1 EP2674583B1 (fr) 2016-07-20

Family

ID=46384167

Family Applications (1)

Application Number Title Priority Date Filing Date
EP12172117.9A Not-in-force EP2674583B1 (fr) 2012-06-15 2012-06-15 Appareil d'alimentation en huile pour moteur et pourvue de soupape de surpression à deux étages

Country Status (1)

Country Link
EP (1) EP2674583B1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106762014A (zh) * 2015-11-23 2017-05-31 湖南机油泵股份有限公司 一种新型高效率机油泵

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19631296A1 (de) * 1996-08-02 1998-02-05 Ford Werke Ag Vorrichtung zur Begrenzung des Öldrucks in dem Schmierölkreislauf einer Verbrennungskraftmaschine
DE19952287A1 (de) * 1999-08-04 2001-03-22 Unisia Jecs Corp Druckentlastungsventil
DE102004004055A1 (de) * 2003-01-28 2004-08-12 Aisin Seiki K.K., Kariya Entlastungsventilmechanismus für eine Ölpumpe

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19631296A1 (de) * 1996-08-02 1998-02-05 Ford Werke Ag Vorrichtung zur Begrenzung des Öldrucks in dem Schmierölkreislauf einer Verbrennungskraftmaschine
DE19952287A1 (de) * 1999-08-04 2001-03-22 Unisia Jecs Corp Druckentlastungsventil
DE102004004055A1 (de) * 2003-01-28 2004-08-12 Aisin Seiki K.K., Kariya Entlastungsventilmechanismus für eine Ölpumpe

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106762014A (zh) * 2015-11-23 2017-05-31 湖南机油泵股份有限公司 一种新型高效率机油泵

Also Published As

Publication number Publication date
EP2674583B1 (fr) 2016-07-20

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