US20160169082A1 - A hydraulic circuit associated with an internal combustion engine - Google Patents

A hydraulic circuit associated with an internal combustion engine Download PDF

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Publication number
US20160169082A1
US20160169082A1 US14/908,270 US201414908270A US2016169082A1 US 20160169082 A1 US20160169082 A1 US 20160169082A1 US 201414908270 A US201414908270 A US 201414908270A US 2016169082 A1 US2016169082 A1 US 2016169082A1
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US
United States
Prior art keywords
engine
fluid
pump
circuit
flow rate
Prior art date
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Abandoned
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US14/908,270
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English (en)
Inventor
Giulio Contaldi
Alessandro Ventura
Cinzia Cipollone
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.)
SEI - SERVIZI PER L'ECONOMIA E PER L'INGEGNERIA Srl
Ing Enea Mattei SpA
Meccanotecnica Umbra SpA
Original Assignee
SEI - SERVIZI PER L'ECONOMIA E PER L'INGEGNERIA Srl
Ing Enea Mattei SpA
Meccanotecnica Umbra SpA
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Application filed by SEI - SERVIZI PER L'ECONOMIA E PER L'INGEGNERIA Srl, Ing Enea Mattei SpA, Meccanotecnica Umbra SpA filed Critical SEI - SERVIZI PER L'ECONOMIA E PER L'INGEGNERIA Srl
Assigned to ING ENEA MATTEI S.P.A. reassignment ING ENEA MATTEI S.P.A. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: CIPOLLONE, Cinzia, VENTURA, ALESSANDRO, CONTALDI, GIULIO
Assigned to SEI - SERVIZI PER L'ECONOMIA E PER L'INGEGNERIA SRL reassignment SEI - SERVIZI PER L'ECONOMIA E PER L'INGEGNERIA SRL ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: CIPOLLONE, Cinzia, VENTURA, ALESSANDRO, CONTALDI, GIULIO
Assigned to MECCANOTECNICA UMBRA S.P.A. reassignment MECCANOTECNICA UMBRA S.P.A. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: CIPOLLONE, Cinzia, VENTURA, ALESSANDRO, CONTALDI, GIULIO
Publication of US20160169082A1 publication Critical patent/US20160169082A1/en
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P7/00—Controlling of coolant flow
    • F01P7/14—Controlling of coolant flow the coolant being liquid
    • F01P7/16—Controlling of coolant flow the coolant being liquid by thermostatic control
    • F01P7/165—Controlling of coolant flow the coolant being liquid by thermostatic control characterised by systems with two or more loops
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P5/00—Pumping cooling-air or liquid coolants
    • F01P5/10—Pumping liquid coolant; Arrangements of coolant pumps
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
    • F04C15/008—Prime movers
    • 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
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C2/3441—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/04—Heating; Cooling; Heat insulation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P2060/00—Cooling circuits using auxiliaries
    • F01P2060/02—Intercooler
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P2060/00—Cooling circuits using auxiliaries
    • F01P2060/04—Lubricant cooler
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P2060/00—Cooling circuits using auxiliaries
    • F01P2060/08—Cabin heater
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P2060/00—Cooling circuits using auxiliaries
    • F01P2060/16—Outlet manifold
    • 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
    • F04C14/06—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for stopping, starting, idling or no-load operation
    • 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
    • F04C2210/00—Fluid
    • F04C2210/24—Fluid mixed, e.g. two-phase fluid
    • F04C2210/247—Water

Definitions

  • the present invention relates to a hydraulic circuit associated with an internal combustion engine.
  • Engine cooling is the subject of major attention by manufacturers because it can significantly contribute to reducing primary pollutant levels.
  • Emission limits are defined on European level by the sequence of Euro 1-2-3-4-5-6 standards for passenger cars and Euro I-II-III-IV-V for heavy vehicles.
  • the evaluation of the aforesaid limits for light vehicles includes performing a mission with a predetermined speed profile as a function of time, starting from cold engine condition (NEDC cycle).
  • the engine warms up in an interval of time which is equal to about 2 ⁇ 3 of the total time test (1200 s). Therefore, most of the test is carried out before the engine has warmed up, and thus under disadvantageous conditions for emission levels.
  • a quick warm-up of the engine after cranking allows a considerable reduction of emissions; such a reduction is particularly significant, as mentioned, because it favorably conditions emission determination according to the standards in force.
  • a faster engine warm-up also promotes consumption reduction for various reasons, including the reduction of the power lost by friction due to a faster reaching of the optimal viscosity conditions of the lubricant oil.
  • a further reduction of fuel consumption may be obtained by improving the organic efficiency of the engine, which implies reducing the power drawn by the auxiliary members of the engine itself.
  • the cooling fluid pump also named “water pump” plays a significant role.
  • a centrifuge pump which is dimensioned to obtain maximum efficiency under maximum engine power conditions, which corresponds to the maximum thermal power to be removed, is normally utilized to circulate the cooling fluid.
  • the pump is driven at slower speeds, such as those typical of the type-approval cycle, but also of most of the real operating conditions of the vehicle, especially in cities, efficiency is lower and the power drawn by the pump becomes significant for consumptions.
  • FIG. 1 is a diagram of a first embodiment of a hydraulic circuit according to the present invention
  • FIG. 2 is a side elevation view of a pump of the circuit in FIG. 1 ;
  • FIG. 3 is a section taken along line III-III in FIG. 2 ;
  • FIG. 4 is an exploded perspective view of a rotor of the pump in FIG. 2 ;
  • FIG. 5 is a chart showing the characteristic curves of the circuit in FIG. 1 ;
  • FIG. 6 is a chart showing the efficiency trend of the pump in FIG. 2 , as a function of the working pressure, in two operating conditions of the circuit in FIG. 1 ;
  • FIG. 7 is a chart showing the trend of the flow rate of the pump in FIG. 2 according to rotation speed variations
  • FIG. 8 is a chart showing the trend of the flow rate of a conventional centrifuge pump according to rotation speed variations
  • FIG. 9 is a chart showing the extra flow rate made available by the pump in FIG. 2 as compared to a conventional pump according to engine speed variations.
  • FIG. 10 is a diagram of a further embodiment of the circuit of the invention.
  • reference numeral 1 indicates as a whole a hydraulic circuit associated with an internal combustion engine M, in particular for a motor vehicle.
  • Circuit 1 essentially comprises a main cooling circuit 2 (partially shown) and an auxiliary circuit 3 connected to and branched from the main cooling circuit 2 (also partially shown).
  • the main circuit 2 essentially comprises a circulation pump 4 of the cooling fluid (hereinafter referred to as “fluid” for conciseness) and a radiator 5 .
  • the main circuit 2 further comprises a thermostatic valve or thermostat (of conventional type and not shown), which is configured so as to assume two positions as a function of the fluid temperature: a closed position under a threshold temperature (i.e. with the “engine cold”), with which the fluid is recirculated between pump 4 and engine M without sending it to the radiator 5 to promote rapidly reaching a warmed up condition, and an open position, when the temperature of the fluid exceeds the aforesaid threshold value, which allows the circulation of the fluid through the radiator.
  • a threshold temperature i.e. with the “engine cold”
  • the main circuit may be of any type and comprise, in addition to radiator 5 , other heat exchangers, such as for example a heater for the air entered into the passenger compartment, a heat exchanger for cooling the EGR gases, etc.
  • pump 4 is a rotary volumetric pump and preferably, but not necessarily, a vane pump.
  • the vane pump 4 is made as shown in figures from 2 to 4 , and comprises, in particular, a casing 6 defining a cylindrical cavity 7 of axis A, and a cylindrical rotor 8 mounted eccentrically within cavity 7 and integrally rotational with a shaft 14 about an axis B thereof.
  • Rotor 8 has four radial vanes 9 arranged at 90°, adapted to substantially cooperate in a fluid-tight manner with the walls of cavity 7 to delimit four compartments 10 therewith having a volume varying with the rotation of rotor 8 .
  • Casing 7 is further provided with an intake port 11 and with a delivery port 12 , diametrically opposite to each other, with which the compartments 10 cyclically communicate.
  • the opposite vanes 9 are opposite in pairs and integrally defined by a single element 15 slidingly housed in a respective diametral slot 16 of rotor 8 .
  • the auxiliary circuit 3 branches off from the main circuit 2 by means of a three-way, two-position solenoid valve 20 , arranged in the illustrated example immediately downstream of pump 4 ( FIG. 3 ).
  • the auxiliary circuit 3 comprises a first heat exchanger 21 , in which the fluid exchanges heat with (and absorbs heat from) a first fluid 23 at higher temperature, already available when the engine is cold, and a second heat exchanger 22 , in which the fluid exchanges heat with (gives heat to) a second fluid 24 at lower temperature which it is intended to warm up as rapidly as possible.
  • the first fluid 23 consists of the exhaust gases of engine M
  • the second fluid 24 consists of the engine oil; alternatively, instead of the engine oil, the second fluid 24 may consist of air entered into the passenger compartment.
  • FIG. 5 shows:
  • the rotation speed of the rotary volumetric pump is determined in relation to the mass flow rate needed to cool the engine; such a flow rate value must be considered as necessary to ensure the cooling of the engine, and is the same which should be supplied by a centrifuge circulation pump of the conventional type.
  • V geom V int ⁇ ⁇ ⁇ n 60 ( 1 )
  • ⁇ indicating the rotation speed of the pump in RPM and n the number of compartments characteristic of the machine (equal to the number of vanes of a rotary vane machine).
  • the fluid pressure is fixed by the volumetric features of the downstream circuit which, being characterized by a characteristic curve which defines the load losses as a function of the flow rate, will pressurize the fluid delivered by the pump: for such a reason, the delivery head will always be ensured by the engine circuit, the flow rate being equal.
  • a control law of the rotation speed of the rotary volumetric pump can be defined by taking volumetric efficiency data into account.
  • a law which corresponds to the real situation being discussed is shown in FIG. 7 , in which the upper curve relates to the open thermostat condition and the lower curve to the closed thermostat condition.
  • the “intermediate” line represents an average value which may be considered as a good approximation of the two curves.
  • the flow rate delivered by the rotary volumetric pump is only one (regardless of the position of the thermostat, and thus of the load losses in the circuit) and thus linearly variable (as inferred from Equation 1) with the rotation speed of the pump itself.
  • the flow rate depends on the position of the thermostat because the working point is defined by the balance between the characteristic curve of the circuit (which is modified) and those of the pump.
  • FIG. 8 shows the flow rates which correspond to a hydraulic circuit with the thermostat open and closed as a function of the rotation speed of the pump mechanically connected to the thermal engine: the higher hydraulic permeability of the circuit with the thermostat open makes the circulating flow rates higher, the rotation speed being equal.
  • FIG. 7 shows that with the thermostat closed (i.e. during the step of warming up the engine), the speed controlled vane pump (as shown in FIG. 7 : a single rotation speed of the pump is identified for a defined cooling fluid flow rate) produces, with the thermostat closed, an “extra flow rate” with respect to the cooling needs of the engine.
  • This extra flow rate is represented, in the discussed case, but with general validity, by the values shown in FIG. 9 .
  • the same figure shows the possibility of binding the rotation speed of the rotary volumetric pump to that of the engine by means of a fixed rotation ratio (5:1).
  • FIG. 10 shows a variant of the auxiliary circuit 3 in which the extra flow rate, before reaching the heat exchanger 21 , is circulated through a third heat exchanger 25 , in which it exchanges heat with the supercharging compressed air 26 of engine M.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Valve Device For Special Equipments (AREA)
US14/908,270 2013-07-29 2014-07-29 A hydraulic circuit associated with an internal combustion engine Abandoned US20160169082A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
IT000637A ITTO20130637A1 (it) 2013-07-29 2013-07-29 Circuito idraulico associato ad un motore a combustione interna
ITTO2013A000637 2013-07-29
PCT/IB2014/063527 WO2015015426A1 (en) 2013-07-29 2014-07-29 A hydraulic circuit associated with an internal combustion engine

Publications (1)

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US20160169082A1 true US20160169082A1 (en) 2016-06-16

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US14/908,270 Abandoned US20160169082A1 (en) 2013-07-29 2014-07-29 A hydraulic circuit associated with an internal combustion engine

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US (1) US20160169082A1 (it)
EP (1) EP3027861A1 (it)
CN (1) CN105637191B (it)
IT (1) ITTO20130637A1 (it)
WO (1) WO2015015426A1 (it)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20180341280A1 (en) * 2017-05-24 2018-11-29 Mann+Hummel Gmbh Control Valve for Adjusting a Fluid Flow
US11118731B2 (en) 2019-04-05 2021-09-14 Bendix Commercial Vehicle Systems Llc Apparatus and method for cooling a high heat-generating component of a vehicle

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107620628B (zh) * 2017-08-28 2020-11-17 吉林大学 可精调流量的汽车发动机水泵

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US4180032A (en) * 1976-02-10 1979-12-25 Societe Anonyme Des Usines Chausson Device for the regulation of the temperature of a supercharged diesel engine
US4236492A (en) * 1976-12-04 1980-12-02 Klockner-Humboldt-Deutz Aktiengesellschaft Internal combustion engine having a supercharger and means for cooling charged air
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US5894834A (en) * 1996-09-06 1999-04-20 Hyundai Motor Company Cooling system for water cooling type engine
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US6260766B1 (en) * 1998-04-07 2001-07-17 Denso Corporation Heating apparatus for vehicle
US6273033B1 (en) * 1998-11-12 2001-08-14 Ab Volvo Internal combustion engine installation in a motor vehicle
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US4096697A (en) * 1974-06-28 1978-06-27 Societe D'etudes De Machines Thermiques S.E.M.T. Method and means for conditioning the intake air of a supercharged, low-compression ratio diesel engine
US4180032A (en) * 1976-02-10 1979-12-25 Societe Anonyme Des Usines Chausson Device for the regulation of the temperature of a supercharged diesel engine
US4236492A (en) * 1976-12-04 1980-12-02 Klockner-Humboldt-Deutz Aktiengesellschaft Internal combustion engine having a supercharger and means for cooling charged air
CN86101132A (zh) * 1986-02-22 1987-10-21 蒋铭华 低速高效节能泵
US5730089A (en) * 1995-03-08 1998-03-24 Nippondenso Co., Ltd. Cooling water circulating system for internal combustion engine of vehicle
US5797265A (en) * 1995-06-12 1998-08-25 Waertsilae Nsd Oy Ab Utilization of low-value heat in a supercharged thermal engine
US5894834A (en) * 1996-09-06 1999-04-20 Hyundai Motor Company Cooling system for water cooling type engine
US6260766B1 (en) * 1998-04-07 2001-07-17 Denso Corporation Heating apparatus for vehicle
US6273033B1 (en) * 1998-11-12 2001-08-14 Ab Volvo Internal combustion engine installation in a motor vehicle
US6243642B1 (en) * 1999-03-31 2001-06-05 Detroit Diesel Corporation System and method for detecting cold engine operation
US7040303B2 (en) * 2004-08-20 2006-05-09 Electro-Motive Diesel, Inc. Combined aftercooler system with shared fans

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20180341280A1 (en) * 2017-05-24 2018-11-29 Mann+Hummel Gmbh Control Valve for Adjusting a Fluid Flow
US10691146B2 (en) * 2017-05-24 2020-06-23 Mann+Hummel Gmbh Control valve for adjusting a fluid flow
US11118731B2 (en) 2019-04-05 2021-09-14 Bendix Commercial Vehicle Systems Llc Apparatus and method for cooling a high heat-generating component of a vehicle

Also Published As

Publication number Publication date
EP3027861A1 (en) 2016-06-08
WO2015015426A1 (en) 2015-02-05
CN105637191A (zh) 2016-06-01
ITTO20130637A1 (it) 2015-01-30
CN105637191B (zh) 2018-12-11

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