CN102235203A - Lubricant circuit - Google Patents

Lubricant circuit Download PDF

Info

Publication number
CN102235203A
CN102235203A CN2011101130174A CN201110113017A CN102235203A CN 102235203 A CN102235203 A CN 102235203A CN 2011101130174 A CN2011101130174 A CN 2011101130174A CN 201110113017 A CN201110113017 A CN 201110113017A CN 102235203 A CN102235203 A CN 102235203A
Authority
CN
China
Prior art keywords
control unit
distributor
lubricant circuit
lubricant
temperature
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.)
Pending
Application number
CN2011101130174A
Other languages
Chinese (zh)
Inventor
乔格.兹维克勒
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.)
GM Global Technology Operations LLC
Original Assignee
GM Global Technology Operations LLC
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
Priority to DE102010019007.1 priority Critical
Priority to DE201010019007 priority patent/DE102010019007A1/en
Application filed by GM Global Technology Operations LLC filed Critical GM Global Technology Operations LLC
Publication of CN102235203A publication Critical patent/CN102235203A/en
Pending legal-status Critical Current

Links

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01MLUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00Pressure lubrication
    • F01M1/16Controlling lubricant pressure or quantity
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01MLUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00Pressure lubrication
    • F01M1/02Pressure lubrication using lubricating pumps
    • F01M2001/0207Pressure lubrication using lubricating pumps characterised by the type of pump
    • F01M2001/0238Rotary pumps
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01MLUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00Pressure lubrication
    • F01M1/02Pressure lubrication using lubricating pumps
    • F01M2001/0207Pressure lubrication using lubricating pumps characterised by the type of pump
    • F01M2001/0246Adjustable pumps
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01MLUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M2250/00Measuring
    • F01M2250/60Operating parameters

Abstract

The invention relates to a lubricant circuit for an internal combustion engine. The lubricant circuit includes a lubricant pump (1), which is connected on the suction side to a reservoir (3) and on the pressure side to a distributor (4, 7), at least one lubricating point (9), which is connected to the distributor (4, 7) and a return leading to the reservoir (3), and an electronic control unit (21), which is set up to regulate the output pressure of the lubricant pump (1) by reference to the temperature of the lubricant.

Description

Lubricant circuit
Technical field
The present invention relates to a kind of be particularly useful for lubricated internal-combustion engine, for example lubricant circuit of petrol engine in the automobile or diesel engine.
Background technique
Because the oiling agent demand of this internal-combustion engine increases along with its rotating speed, lubricant circuit generally comprise for this reason one that be coupled with the internal-combustion engine driven shaft regularly and by this oil-engine driven lubricating pump.Because this is coupled, the flow of lubricating pump is along with the rotating speed of internal-combustion engine increases.Because the flow of lubricant of motor be not accurately with the linear ratio of rotating speed, but relevant, so lubricating pump must be designed for the amounts of lubrication that provides sufficient under all operating conditionss with the temperature of other factors, especially internal-combustion engine.As if the flow of the amounts of lubrication of being carried by pump greater than internal-combustion engine, the pressure in lubricating pump and oil duct outlet port that be attached thereto, that be directed to each lubricant housings raises so, and the power of IC engine share that must consume for the driving lubricating pump increases.
For preventing, directly be provided with one usually and make can surpass a limiting value at the pressure at pump discharge place the time lubricant flow be back to excess pressure valve in the cistern in the outlet port of lubricating pump owing to pump discharge place overpressure causes lubricant circuit impaired.When the situation of this value of overstepping the extreme limit appears at the cold start-up of internal-combustion engine mostly, because this moment, pressure was obviously than increasing quickly in service continuously, and the propagation of pressure at pump discharge place to arranged downstream in oil duct controlling device and before this controlling device can oppositely control, the pressure at pump discharge place can the value of overstepping the extreme limit.For this reason, this excess pressure valve is also referred to as the cold start-up valve.Although this cold start-up valve provides the effective protection that prevents from lubricant circuit to occur critical high pressure, when oiling agent during by the cold start-up valve, energy has not just been lost with being utilized at every turn.
Summary of the invention
Therefore, in order to drive internal-combustion engine by energy efficient, technical problem to be solved by this invention is, expectation has a lubricant circuit, this lubricant circuit can be given the well-off oiling agent of internal-combustion engine on the one hand at any time, and on the other hand can be that the cold start-up valve must respond with making, needn't be restricted to minimum or can avoid so high lubricant pressure appearance fully by so high lubricant pressure.If can avoid this critical high pressure to appear in the lubricant circuit fully, then can also save this cold start-up valve, from and obtain cost advantage.
This technical problem solves by a kind of lubricant circuit in particular for internal-combustion engine by the present invention, this lubricant circuit comprises lubricating pump that an oil-feed side is connected with cistern, on the pressure side is connected with distributor, lubricant housings and an electronic control unit that is used for the control pump operation that at least one is connected with a reversion circuit that is directed to cistern with distributor, by the present invention, this control unit is designed for the outlet pressure of regulating lubricating pump according to lubricant temperature.Because the temperature of oiling agent just can be measured before internal combustion engine start, so can just suitably predesignate the specified outlet pressure of a lubricating pump in the moment of internal combustion engine start, make and just can avoid necessary traditionally by cold start-up valve pressure peak that stop, pump discharge from beginning.
According to first kind of design proposal, control unit can be designed for the temperature of estimating oiling agent according to model.This model for example can be according to the engine loading curve in past with in case of necessity according to other parameter estimation lubricant temperature.
Certainly, also can be connected as the alternative control unit with temperature transducer.Traditional motor car engine does not set the sensor that is used to detect the oil temperature, but can use the measured value of the cooling-water temperature sensor of common existence to come estimated oil temperature without a doubt.For temporary transient at least estimated oil temperature after can shutting down in the internal-combustion engine long period, also can consider to use the intake air temperature sensor that in a lot of Hyundai Motors, is used to mix control and itself just exists.
Because at internal-combustion engine (and oiling agent) when temperature is higher, the flow of lubricant of general internal-combustion engine is higher and stickiness oiling agent is lower, thus suitable be that the temperature that records is high more, just selects big more outlet pressure.It is just enough to have confirmed to carry out simple threshold value control in practice, and wherein, whether control unit is below or above limiting temperature according to the temperature that records and regulates low outlet pressure or the high outlet pressure that forms lubricating pump.
Because the flow of lubricant of internal-combustion engine also can be subjected to other factors, with Temperature Influence or may become coarse linear relationship with rotating speed, suitable is as rotating speed, with the transformable pump of transfer rate as lubricating pump.Especially preferably a vane pump that has housing and rotor can be controlled transfer rate by the effect change housing and the mutual throw of eccentric of rotor that account for leading pressure in distributor.In practice, the preferred support structure location of pump relatively of the rotor shaft of this vane pump is fixed, and radially regulates pump case by the phase countershaft and change throw of eccentric.
In order to drive the adjusting of throw of eccentric, first control unit that links to each other with distributor can be set aptly.
This control unit especially can act on the housing on the one hand, acts on the other hand on the rotor or supporting structure of lubricating pump.
For the outlet pressure that makes vane pump relevant with temperature, this electronic control unit is preferably controlled a valve that second control unit optionally is connected with distributor or is connected with the distributor disconnection, and this second control unit is designed for the throw of eccentric of regulating lubricating pump equally.
If both having had first control unit in lubricant circuit also has second control unit, they are arranged to regulate in the same way the throw of eccentric of lubricating pump aptly so.When two control units were supported mutually by this way, then the pressure ratio on the pump discharge just was enough to realize that given throw of eccentric changes and realizes that therefore given pump transfer rate changes in that the situation of having only a control unit to do the time spent is littler.
For when this second control unit is connected by valve and distributor disconnection, second control unit does not hinder the relative movement of housing and rotor, this valve is preferably designed to selector valve, and this selector valve disconnects in the position that is connected second control unit and distributor at it second control unit is connected with cistern.
First control unit is connected with the downstream section of distributor usually, so that guarantee also can realize required pressure at this place, and valve preferably is connected with the upstream zone of distributor, to realize the rapid reaction of second control unit to the pressure surge of pump discharge place.
This suits especially at this moment, promptly between distributor upstream and downstream section, arrange a throttle element, especially lubricant cooler and/or oiling agent filter cleaner, it causes upstream zone to descend and/or the high pressure that delays the pump discharge place is passed to downstream section to the pressure of downstream section.
For under all operating conditionss of internal-combustion engine, when having the higher-security that prevents the overvoltage of not allowing, guarantee sufficient oiling agent supply, suitable is is arranged to also outlet pressure according to the rotational speed regulation lubricating pump of internal-combustion engine with control unit.For this purpose, this control unit can be connected with the speed probe on the internal-combustion engine main shaft.
So, above-mentioned limiting temperature is a function of rotating speed aptly, or the result the same be all to have a limit speed for each temperature, control unit is regulated and is formed low outlet pressure when being lower than this limit speed, and control unit is regulated and formed high outlet pressure when being higher than this limit speed.
The rotating speed that records is high more, and limiting temperature is just low more aptly, or temperature is high more, and limit speed is just low more, and control unit just is transformed into high outlet pressure when surpassing this limit speed.
Description of drawings
From the explanation of following each form of implementation and with reference to accompanying drawing, obtain other characteristics of the present invention and advantage.In the accompanying drawings:
Fig. 1 is the block diagram by lubricant circuit of the present invention; And
Fig. 2 is the switching characteristic of control unit when different start-up temperature.
Embodiment
Fig. 1 is the schematic representation of oil circuit in the motor car engine.Vane pump 1 is connected with oil sump 3 by oil inlet pipe 2.Comprise an intake line 4 and an oil duct 7 with the distributor that on the pressure side is connected of vane pump 1, on this intake line 4, be in series with a lubricating oil purifier 5 and lube oil cooler 6, from this oil duct 7, branch out the different lubricant housings 9 that some are connected to motor, for example the branched line 8 of the bearing of bent axle 10.This lubricant oil does not flow back to the oil sump 3 from these lubricant housings 9 with being guided.
Vane pump 1 has a housing 11 that has cylindrical cavity in a manner known way, be provided with a rotor 12 that has a plurality of blades 13 in this cavity, the internal surface of these blades 13 by positioning ring and housing 11 keeps in touch and cavity is divided into a plurality of capacitors.This rotor 12 has fixing rotating shaft, and housing 11 can should move transverse to it under the effect of spring 14 and two hydraulic control components 15,16 in fixing rotating shaft relatively.This motion is around a flip-flop movement with axis shaft parallel, that extend in housing 11 outsides of rotor mostly in practice.These two control units are in reverse to the moving of driving direction drive shell 11 of spring 14 along identical direction, need this spring 14 is envisioned for pressure spring in the diagram of Fig. 1.Schematically illustrated control unit 15,16 has a cylinder and the piston that can move respectively in this cylinder in Fig. 1, wherein, piston action on housing 11 and cylinder be connected with the bearing of 12 of rotors rigidly.In practice, control unit is embodied as the pressure chamber mostly, this pressure chamber is limited by integral type frame unshowned among a Fig. 1, that also comprise the bearing of axle on the one hand, and the outer surface by housing 11 limits on the other hand, and the oil pressure in the pressure chamber directly affacts on this outer surface.
Spring 14 and control unit 15,16 are arranged to respectively, make a power that applies by spring 14 cause that the eccentricity of rotor 12 relative housings 11 increases and therefore make the transfer rate increase of pump 1, and the pressure in contrast of control unit 15,16 ground cause reducing of eccentricity and transfer rate.
The control chamber of control unit 15 is connected with the end in oil duct 7 downstreams by measuring pipeline 17, makes to account in the control chamber that leading pressure also is present in control unit 15 in oil duct 7 and apply a power that reacts on spring 14 on housing 11.The so mutual coupling of the intensity of the cross section of the control chamber of control unit 15 and spring 14 makes that when second control unit 16 does not have pressure the oil pressure in the oil duct 7 reaches about 4bar in steady operational status.
When engine start, oil duct 7 does not have pressure and spring 14 that housing 11 is remained in the position of maximum eccentricity.So transfer rate maximum when engine start of pump 1, thereby itself also suit in the short as far as possible time, to supply oil to effectively on all lubricant housings 9.Yet because engine temperature is lower, pump 1 higher transfer rate can cause pressure too high at short notice when lubricating oil viscosity denseness height and volume flow demand are little, and this can damage some parts, therefore must avoid its generation.In order to realize this point, control unit 16 is measured pipeline 18 by second and directly is connected with the pressure export of vane pump 1.For this purpose, measure pipeline 18 and keep short as much as possible, and preferably extend in the inside of the element of construction that vane pump 1 and two control units 15,16 are combined into one fully.In practice the high pressure in vane pump 1 outlet port via whole distributor be passed to control unit 15 can experience several seconds, and in fact this pressure can not affact on the control unit 16 with delaying time.The cross section of the control chamber of control unit 16 is the same big with the cross section of the control chamber of control unit 15, therefore, when exerting pressure for two control units 15,16, forms the pressure of 2bar in steady state on oil duct 7.
Even when engine start, also do not transfer to control unit 15 by the pressure of the oil of pump 1 supply, control unit 16 also can avoid can damaging on the delivery line 4 critical pressure of lubricating oil purifier 5 effectively.
Lubricated fully when the higher rotation speed for guaranteeing bearing 9, oil duct 7 should reach the pressure of 4bar.For this purpose, in measuring pipeline 18 selector valve 19 is set, it can interrupt measuring pipeline 18 and make the control chamber of control unit 16 not have pressure by a connecting pipeline 20 that is directed to oil sump 3.When control unit 16 did not have pressure, control unit 15 is the transfer rate of control pump 1 or the pressure on the oil duct 7 individually.
Selector valve 19 is by controlling with the electronic control unit 21 that temperature transducer 22 is connected with speed probe 23.Control unit 21 is preferably implemented with the form of the additional software module of known programme controlled control unit of engine (ECU) itself.Because this control unit of engine is connected with speed probe with the temperature transducer that is used for the detection of engine cooling water temperature traditionally mostly, control unit 21 can be with the realization that expends of minimum.
To control unit 21 programmings, measure pipeline 18 and apply the pressure in pump 1 outlet port for thus control unit 16 so that when engine start, connect at first in short time respectively.The moment that is transformed into control unit 16 pressure-less states is not only depended on the rotating speed of bent axle 10 but also depend on the temperature that records, as among Fig. 2 by shown in many curve C 1 to C8.C1 represents the characteristic of control unit 21 when temperature is-30 degrees centigrade, that is, when reaching the high rotating speed of 5000 and 6000 commentaries on classics/per minutes, control unit 21 just switches to no pressure with control unit 16, so that the oil pressure in the oil duct 7 rises to 4bar from 2bar.When being-20 degrees centigrade (C2), temperature is suitable for identical switching threshold.Switching threshold reduces to a value between 4000 and 5000 commentaries on classics/per minutes when-10 degrees centigrade (C3).Identical value also is suitable for when temperature is 0 degree centigrade (C4).In the scope of 10 to 20 degrees centigrade (C5, C6), switching threshold reduces to 3000 to 4000 commentaries on classics/per minutes, and the temperature that occurs when continuous service equals and when surpassing 60 degrees centigrade (C7, C8), switching threshold is in 2000 to 3000 commentaries on classics/per minutes.Therefore, by in the engine steady state temperature, also making the outlet pressure work of pump 1 to reduce, can be used to flow to the energy requirement of stand oil amount because rotating speed is lower than a hour minimizing in the oily demand of motor, thereby when lubricant circuit is worked, can additionally save energy.
List of numerals
1. vane pump
2. oil inlet pipe
3. oil sump
4. delivery line
5. lubricating oil purifier
6. oil cooler
7. oil duct
8. branched line
9. lubricant housings
10. bent axle
11. housing
12. rotor
13. blade
14. spring
15. control unit
16. control unit
17. measurement pipeline
18. measurement pipeline
19. selector valve
20. connecting pipeline
21. control unit
22. temperature transducer
23. speed probe

Claims (15)

1. the lubricant circuit in particular for internal-combustion engine comprises lubricating pump (1), and it is connected with cistern (3) in the oil-feed side, and on the pressure side is being connected with distributor (4,7); At least one lubricant housings (9), it is connected with the reversion circuit that is directed to described cistern (3) with described distributor (4,7); And an electronic control unit (21) that is used to control described pump (1) operation, it is characterized in that described control unit (21) is provided for the outlet pressure according to the described lubricating pump of the temperature regulation of described oiling agent (1).
2. by the described lubricant circuit of claim 1, it is characterized in that described control unit is designed for the temperature of estimating described oiling agent according to model.
3. by the described lubricant circuit of claim 1, it is characterized in that described control unit (21) is connected with temperature transducer (22).
4. by the described lubricant circuit of claim 3, it is characterized in that the cooling water of described temperature transducer (22) and internal-combustion engine or the hot connecting of suction air.
5. by the described lubricant circuit of one of claim 1 to 4, it is characterized in that described control unit (21) is designed for and whether is below or above limiting temperature according to the temperature that records and regulates and form low outlet pressure or high outlet pressure.
6. by one of claim 1 to 5 described lubricant circuit, it is characterized in that described lubricating pump (1) is the vane pump that accounts for adjustable eccentric distance under the leading pressure effect in described distributor (4,7).
7. by the described lubricant circuit of claim 6, it is characterized in that, be provided with first control unit (15) that is connected with described distributor (4,7), so that regulate the throw of eccentric of described lubricating pump (1).
8. by claim 6 or 7 described lubricant circuit, it is characterized in that, described electronic control unit (21) is controlled described lubricating pump (1) by valve (19), and second control unit (16) that this valve (19) will be provided for regulating described lubricating pump (1) throw of eccentric optionally is connected with described distributor (4,7) or disconnects with described distributor (4,7) and to be connected.
9. by claim 7 and 8 described lubricant circuit, it is characterized in that described first and second control units (15,16) are provided for regulating in the same way the throw of eccentric of described lubricating pump (1).
10. by claim 8 or 9 described lubricant circuit, it is characterized in that, described valve (19) is a selector valve, and it makes described second control unit (16) be connected with described cistern (3) in that described second control unit (16) and described distributor (4,7) are disconnected in the position that is connected.
11. press claim 4 and claim 8,9 or 10 described lubricant circuit, it is characterized in that, described valve (19) is connected with the upstream zone (4) of described distributor (4,7), and described first control unit (15) is connected with the downstream section (7) of described distributor (4,7).
12. by the described lubricant circuit of claim 11, it is characterized in that, between the upstream zone of described distributor and downstream section, arrange at least one throttle element, especially lubricant cooler (6) and/or oiling agent filter cleaner (5).
13., it is characterized in that described control unit (21) is provided for also the outlet pressure according to the described lubricating pump of the rotational speed regulation of described internal-combustion engine (1) by the described lubricant circuit of one of claim 1 to 12.
14., it is characterized in that described limiting temperature is the function of described rotating speed by claim 5 and 13 described lubricant circuit.
15. by the described lubricant circuit of claim 13, it is characterized in that measured rotating speed is high more, described limiting temperature is just low more.
CN2011101130174A 2010-05-03 2011-05-03 Lubricant circuit Pending CN102235203A (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE102010019007.1 2010-05-03
DE201010019007 DE102010019007A1 (en) 2010-05-03 2010-05-03 Lubricating circuit

Publications (1)

Publication Number Publication Date
CN102235203A true CN102235203A (en) 2011-11-09

Family

ID=44786433

Family Applications (1)

Application Number Title Priority Date Filing Date
CN2011101130174A Pending CN102235203A (en) 2010-05-03 2011-05-03 Lubricant circuit

Country Status (4)

Country Link
US (1) US20110266090A1 (en)
CN (1) CN102235203A (en)
DE (1) DE102010019007A1 (en)
RU (1) RU2011116958A (en)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102705034A (en) * 2012-06-08 2012-10-03 湖南机油泵股份有限公司 Oil pump electricity-liquid proportion overflow variable control method and device
CN103775165A (en) * 2012-08-31 2014-05-07 株式会社山田制作所 Engine lubrication control system
CN108533355A (en) * 2017-02-28 2018-09-14 曼卡车和巴士股份公司 It can be by the method for the lubrication for the mechanism that lubricant circuit lubricates for evaluating
CN110268142A (en) * 2016-10-31 2019-09-20 康明斯公司 The parasitic lubricating oil system simplified

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012209120A1 (en) * 2012-05-30 2013-12-05 Skf Lubrication Systems Germany Ag Apparatus and method for operating a conveyor system for conveying a lubricant
US9103433B2 (en) * 2013-02-26 2015-08-11 Arvinmeritor Technology, Llc Axle assembly and method of lubrication control
DE102014107659A1 (en) * 2014-05-30 2015-12-03 Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg Transmission for a motor vehicle

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4302610C2 (en) * 1993-01-30 1996-08-08 Daimler Benz Ag Process for regulating the pump output of lubricant pumps and lubricant pump therefor
DE10161131B4 (en) * 2000-12-12 2013-11-07 Slw Automotive Inc. Vane pump variable displacement
DE10124564A1 (en) * 2001-05-14 2002-11-28 Joma Hydromechanic Gmbh Control of variable-displacement lubricant pump for use in internal combustion engine, involves measurement of engine parameters and matching pump delivery to engine requirements
DE10223466B4 (en) * 2001-05-31 2015-07-02 Magna Powertrain Hückeswagen GmbH pump
DE10138187B4 (en) * 2001-07-27 2013-03-14 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Variable volume vane pump
US7726948B2 (en) * 2002-04-03 2010-06-01 Slw Automotive Inc. Hydraulic pump with variable flow and variable pressure and electric control
GB2388634A (en) * 2002-05-15 2003-11-19 Dana Automotive Ltd Engine lubrication system having dual/auxiliary pump operation
DE10239364A1 (en) * 2002-08-28 2004-03-18 Dr.Ing.H.C. F. Porsche Ag Device for controlling the pump output of a lubricant pump for an internal combustion engine
ITBO20040008A1 (en) * 2004-01-09 2004-04-09 Pierburg Spa PUMPING PLANT
US7322800B2 (en) * 2004-04-16 2008-01-29 Borgwarner Inc. System and method of providing hydraulic pressure for mechanical work from an engine lubricating system
US7506724B2 (en) * 2004-07-23 2009-03-24 Honeywell International Inc. Active gas turbine lubrication system flow control
US7198020B1 (en) * 2006-03-13 2007-04-03 Steven G Beddick Lubrication systems and methods for an internal combustion engine
DE102006037461A1 (en) * 2006-08-10 2008-02-14 Bayerische Motoren Werke Ag Operation of variable-delivery oil-lubrication pump of diesel engine, employs pressure-regulated bypass with temperature-controlled pumping modes
TW200839096A (en) * 2007-03-20 2008-10-01 Fu Sheng Ind Co Ltd A hydraulic fluid circuit
JP2008291897A (en) * 2007-05-23 2008-12-04 Nsk Warner Kk Lubrication controlling method and device for starting clutch
US20120241258A1 (en) * 2011-03-23 2012-09-27 Pradip Radhakrishnan Subramaniam Lubricant supply system and method for controlling gearbox lubrication

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102705034A (en) * 2012-06-08 2012-10-03 湖南机油泵股份有限公司 Oil pump electricity-liquid proportion overflow variable control method and device
CN102705034B (en) * 2012-06-08 2014-09-03 湖南机油泵股份有限公司 Oil pump electricity-liquid proportion overflow variable control method and device
CN103775165A (en) * 2012-08-31 2014-05-07 株式会社山田制作所 Engine lubrication control system
CN110268142A (en) * 2016-10-31 2019-09-20 康明斯公司 The parasitic lubricating oil system simplified
CN110268142B (en) * 2016-10-31 2021-05-25 康明斯公司 Simplified parasitic lubricating oil system
CN108533355A (en) * 2017-02-28 2018-09-14 曼卡车和巴士股份公司 It can be by the method for the lubrication for the mechanism that lubricant circuit lubricates for evaluating

Also Published As

Publication number Publication date
RU2011116958A (en) 2012-11-10
US20110266090A1 (en) 2011-11-03
DE102010019007A1 (en) 2011-11-03

Similar Documents

Publication Publication Date Title
CN102235203A (en) Lubricant circuit
US8196385B2 (en) Turbomachine control system
US20090000592A1 (en) Engine pre-lubrication system
EP1945920B1 (en) Lubrication system and internal combustion engine comprising such a system
US20190055886A1 (en) Lubrication system for gas turbine engines
EP0933506A1 (en) Electric motor driven primary oil pump for an internal combustion engine
US10677095B2 (en) Lubrication device for a turbine engine
CN204344190U (en) Motor and there is the vehicle of this motor
CN212337444U (en) Series connection type turbocharger forced lubrication protection device
CN102985657A (en) Engine with electronically controlled piston cooling jets and method for controlling the same
RU93462U1 (en) LUBRICATION SYSTEM OF THE TURBOCHARGER OF THE INTERNAL COMBUSTION ENGINE
CN204492918U (en) Combined changable displacement oil pump
US20110129359A1 (en) Variable output pump
FR2972488A1 (en) THERMAL ENGINE LUBRICATING SYSTEM COMPRISING A VARIABLE CYLINDER OIL PUMP
RU69159U1 (en) LUBRICATION SYSTEM OF THE TURBOCHARGER OF THE INTERNAL COMBUSTION ENGINE
CN104864080A (en) Megawatt-level fan transmission lubricating system
CN202039942U (en) Independent lubricating and driving system of turbo charger
CN202065030U (en) Lubricating device for engine
GB2595874A (en) A method for operating a lubricating and piston cooling system for an engine of a vehicle and a lubricating and piston cooling system
CN104594968A (en) Combined type variable displacement oil pump
KR101924343B1 (en) Medium-speed diesel engines for disaster countermeasures and independent power plants
CN214092002U (en) Engine oil primary supply device of agricultural diesel engine
RU134593U1 (en) LUBRICATION SYSTEM OF THE TURBOCHARGER OF THE INTERNAL COMBUSTION ENGINE
CN101532408B (en) Internal combustion engine high pressure engine oil supply system
CN203130249U (en) Turbocharger oil supplying device of combustion engine

Legal Events

Date Code Title Description
PB01 Publication
C06 Publication
WD01 Invention patent application deemed withdrawn after publication

Application publication date: 20111109

C02 Deemed withdrawal of patent application after publication (patent law 2001)