US20040211378A1 - Pressure-supply device for an electrohydraulic valve control of gas-exchange valves in internal combustion engines - Google Patents
Pressure-supply device for an electrohydraulic valve control of gas-exchange valves in internal combustion engines Download PDFInfo
- Publication number
- US20040211378A1 US20040211378A1 US10/480,513 US48051304A US2004211378A1 US 20040211378 A1 US20040211378 A1 US 20040211378A1 US 48051304 A US48051304 A US 48051304A US 2004211378 A1 US2004211378 A1 US 2004211378A1
- Authority
- US
- United States
- Prior art keywords
- pressure
- valve
- supply device
- fluid
- 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.)
- Abandoned
Links
- 238000002485 combustion reaction Methods 0.000 title claims abstract description 9
- 239000012530 fluid Substances 0.000 claims abstract description 84
- 238000006073 displacement reaction Methods 0.000 claims abstract description 31
- 230000000903 blocking effect Effects 0.000 claims abstract description 5
- 238000010586 diagram Methods 0.000 description 3
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000010349 pulsation Effects 0.000 description 2
- 238000011144 upstream manufacturing Methods 0.000 description 2
- 230000008901 benefit Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 238000013016 damping Methods 0.000 description 1
- 230000009849 deactivation Effects 0.000 description 1
- 239000010720 hydraulic oil Substances 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 239000003921 oil Substances 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
- F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L2800/00—Methods of operation using a variable valve timing mechanism
Definitions
- the present invention relates to a pressure-supply device for an electrohydraulic valve control of gas-exchange valves in internal combustion engines.
- a high-pressure pump takes the form of a variable-displacement pump, regulated on the delivery side or suction side, which supplies a variable pressure and a variable volumetric flow.
- the variable-displacement pump is connected with its pump inlet directly to the fluid reservoir, and with its pump outlet, is connected via a non-return valve, with a blocking direction pointing toward the pump outlet, to the pressure-supply-device fluid output, to which is connected a high-pressure accumulator used for storing energy and damping pressure pulsation.
- the electrohydraulic valve control is supplied with fluid under high pressure via the fluid output, the distributor line or rail connected to the fluid output being designated as a high-pressure circuit of the electrohydraulic valve control.
- the electrohydraulic valve control has a hydraulic actuator or valve adjuster which has a positioning piston for the valve actuation, as well as two fluid-filled working chambers acting on the positioning piston.
- All the valve adjusters are linked to the distributor line or rail, which is under high pressure, in a manner that, in each case, the lower working chamber, acting in the valve-closing direction on a smaller effective area of the positioning piston, is connected directly to the rail, and the upper working chamber, acting in the valve-opening direction on a larger effective area of the positioning piston, is connected to the rail via a first electromagnetic control valve.
- the upper working chamber of each valve adjuster is linked via a second electronic control valve to a second rail forming a feedback line which leads to the fluid reservoir.
- a pressure-supply device, according to an example embodiment of the present invention, for the electrohydraulic valve control of gas-exchange valves may have the advantage that, by the combination of a constant-displacement pump and a switchover valve between the high-pressure circuit and unpressurized circulation, the very good efficiency of the cost-effective constant-displacement pump may be utilized, and a consumption-oriented coupling between the useful fluid flow and the circulation fluid flow is possible, so that the pressure characteristics in the high-pressure rail, linked to the fluid output of the pressure-supply device, for the electrohydraulic valve adjusters may be directly influenced.
- pulsations in the pressure may be smoothed by purposeful overlapping of delivery of fluid into a high-pressure accumulator connected to the fluid output and removal of fluid from the high-pressure accumulator by the valve adjusters.
- the switchover valve is designed as an electrically controlled solenoid valve, the switchover between delivery quantity zero and maximum delivery is carried out extremely quickly in the millesecond range, so that very high system dynamics are achieved.
- the switchover valve may be switched synchronously with consumption, time and/or crank angle. The switchover of the constant-displacement pump to unpressurized circulation during delivery pause also ensures a constant cooling and lubrication of the constant-displacement pump by the fluid.
- the constant-displacement pump is self-priming and is connected with its pump inlet to the fluid reservoir.
- a presupply pump taking in fluid from the fluid reservoir may be arranged upstream from the pump inlet of the constant-displacement pump.
- the oil pump of the internal combustion engine may advantageously be utilized as a presupply pump.
- the switchover valve is made up of a 2/2-way solenoid valve and a non-return valve.
- the non-return valve is positioned in a bypass which connects the outlet of the constant-displacement pump to the fluid reservoir.
- the non-return valve with the blocking direction pointing toward the pump outlet, is connected on the incoming side to the pump outlet, at which the bypass also branches off, and is connected on the output side to the fluid output, and during unpressurized circulation of the fluid, blocks the high-pressure circuit with respect to the bypass and the high-pressure pump.
- the switchover valve is a 3/2-way solenoid valve, of whose three valve connections, one valve output is connected to the pressure-supply-device fluid output making the high pressure available for the valve control, one valve output is connected to the fluid reservoir, and one valve input, switchable alternately to the valve outputs, is connected to the outlet of the constant-displacement pump, so that depending upon the switching position of the solenoid valve, the high-pressure circuit is blocked with respect to the high-pressure pump or is connected to it.
- FIG. 1 shows a circuit diagram of a pressure-supply device for the valve control of gas-exchange valves of an internal combustion engine.
- FIG. 2 shows an identical representation as in FIG. 1 according to a further example embodiment.
- the pressure-supply device shown in the block diagram in FIG. 1 is used for the fluid supply of an electrohydraulic valve control of gas-exchange valves of an internal combustion engine.
- a valve control is described, for example, in German Patent Application No. DE 198 26 047.
- the valve control is connected to a fluid output 11 of the pressure-supply device via a so-called rail which conducts fluid, preferably hydraulic oil, to all valve adjusters of the valve control.
- the pressure-supply device has a fluid reservoir 12 , a presupply pump 13 , a constant-displacement pump 14 and a high-pressure accumulator 15 that is connected directly to fluid output 11 .
- Fluid output 11 is connected via a pressure-limiting valve 16 , that is set to the maximum permitted high pressure in high-pressure accumulator 15 , to a return line 17 running to fluid reservoir 12 .
- a restrictor 18 is also arranged in return line 17 .
- presupply pump 13 is connected to fluid reservoir 12 , and with its pump outlet, is connected on one hand to the inlet of constant-displacement pump 14 , and on the other hand, is connected to return line 17 upstream of restrictor 18 .
- constant-displacement pump 14 With its pump outlet, constant-displacement pump 14 is connected via a switchover valve 19 to high-pressure accumulator 15 and fluid output 11 , respectively.
- the switchover valve is designed as a 3/2-way solenoid valve 20 having spring resetting, the valve being controlled by an electronic control unit 21 as a function of the fluid pressure prevailing at fluid output 11 and in high-pressure accumulator 15 , respectively.
- the fluid pressure is detected by a sensor taking the form of pressure gauge 22 .
- 3/2-way solenoid valve 20 has a valve input 201 connected to the outlet of constant-displacement pump 14 , and two valve outputs 202 , 203 , to which valve input 201 may be switched alternately depending on the switching position.
- Valve output 202 is connected to fluid output 11 and high-pressure accumulator 15
- valve output 203 is connected to return line 17 on the input side of restrictor 18 .
- 3/2-way solenoid valve 20 If 3/2-way solenoid valve 20 is in the switching position shown in FIG. 1, then high-pressure accumulator 15 is being charged, that is to say, constant-displacement pump 14 is delivering fluid into high-pressure accumulator 15 until the maximum pressure set by pressure-limiting valve 16 is reached in high-pressure accumulator 15 and at fluid output 11 . If 3/2-way solenoid valve 20 is transferred by control unit 21 into its other switching position, then fluid output 11 and high-pressure accumulator 15 are blocked vis-à-vis constant-displacement pump 14 , and the outlet of constant-displacement pump 14 is connected to return line 17 . This results in a nearly pressureless circulation of the fluid, and only as much energy is needed as is necessary for overcoming friction.
- switchover valve 19 has a 2/2-way solenoid valve 23 with spring resetting, as well as a non-return valve 24 .
- 2/2-way solenoid valve 23 has a valve input 231 and a valve output 232 which are connected to each other or blocked from each other depending upon the switching position of 2/2-way solenoid valve 23 .
- Valve input 231 is connected to the outlet of constant-displacement pump 14
- valve output 232 is connected to return line 17 , so that 2/2-way solenoid valve 23 is situated in a bypass 25 circumventing fluid output 11 and high-pressure accumulator 15 , and alternately opens or blocks it.
- Non-return valve 24 is positioned between the outlet of constant-displacement pump 14 , and fluid output 11 and high-pressure accumulator 15 , respectively, with a flow-through direction pointing toward fluid output 11 or high-pressure accumulator 15 .
- a pressure-limiting valve 26 or a non-return valve 27 having a defined opening pressure is used, as symbolized in FIGS. 1 and 2 by components 26 , 27 depicted next to restrictor 18 .
- One is thereby able to ensure a constant intake pressure for presupply pump 13 , and to avoid cavitations during the deactivation of the outlet of constant-displacement pump 14 by opening switchover valve 19 .
- constant-displacement pump 14 is self-priming, and is connected with its inlet directly to fluid reservoir 12 , so that it is possible to dispense with the presupply pump.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE10219786A DE10219786A1 (de) | 2002-05-03 | 2002-05-03 | Druckversorgungseinrichtung für eine elektrohydraulische Ventilsteuerung von Gaswechselventilen in Brennkraftmaschinen |
| DE10219786.5 | 2002-05-03 | ||
| PCT/DE2002/004545 WO2003093655A1 (de) | 2002-05-03 | 2002-12-12 | Druckversorgungseinrichtung für eine elektrohydraulische ventilsteuerung von gaswechselventilen in brennkraftmaschinen |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| US20040211378A1 true US20040211378A1 (en) | 2004-10-28 |
Family
ID=29225013
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| US10/480,513 Abandoned US20040211378A1 (en) | 2002-05-03 | 2002-12-12 | Pressure-supply device for an electrohydraulic valve control of gas-exchange valves in internal combustion engines |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US20040211378A1 (de) |
| EP (1) | EP1504173A1 (de) |
| DE (1) | DE10219786A1 (de) |
| WO (1) | WO2003093655A1 (de) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20060150935A1 (en) * | 2005-01-12 | 2006-07-13 | Donaldson Joshua M | Camless engine hydraulic valve actuated system |
| CN105090134A (zh) * | 2014-05-23 | 2015-11-25 | 大众汽车有限公司 | 液压供给装置 |
| US20160312752A1 (en) * | 2015-04-24 | 2016-10-27 | Randy Wayne McReynolds | Multi-Fuel Compression Ignition Engine |
| US11156134B2 (en) * | 2017-05-22 | 2021-10-26 | EMPA Eidgenössische Materialprüfungs-und Forschungsanstalt | Hydraulic drive for accelerating and braking dynamically moving components |
| US11319844B2 (en) * | 2019-12-26 | 2022-05-03 | Harbin Engineering University | Fully variable valve train with rotary plunger for internal combustion engine |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102007045276A1 (de) | 2007-09-21 | 2009-04-02 | Schaeffler Kg | Vorrichtung zur Ansteuerung von mindestens einem Motorventil |
| FR3071869B1 (fr) * | 2017-10-02 | 2019-10-11 | Vianney Rabhi | Actionneur hydraulique de soupape a regeneration |
| DE102020127070A1 (de) | 2020-10-14 | 2022-04-14 | Fte Automotive Gmbh | Pumpenaggregat zur Kuppplungsbetätigung |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5562070A (en) * | 1995-07-05 | 1996-10-08 | Ford Motor Company | Electrohydraulic camless valvetrain with rotary hydraulic actuator |
| US6308690B1 (en) * | 1994-04-05 | 2001-10-30 | Sturman Industries, Inc. | Hydraulically controllable camless valve system adapted for an internal combustion engine |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1992007174A1 (en) * | 1990-10-16 | 1992-04-30 | Lotus Cars Ltd. | Valve control apparatus |
| DE19816817A1 (de) * | 1997-11-25 | 1999-10-21 | Bayerische Motoren Werke Ag | Hydraulische Betätigungsvorrichtung für ein Gaswechselventil einer Brennkraftmaschine |
| DE19854891C2 (de) * | 1997-11-28 | 2003-02-06 | Aisin Seiki | Ventilzeitsteuervorrichtung |
-
2002
- 2002-05-03 DE DE10219786A patent/DE10219786A1/de not_active Withdrawn
- 2002-12-12 US US10/480,513 patent/US20040211378A1/en not_active Abandoned
- 2002-12-12 WO PCT/DE2002/004545 patent/WO2003093655A1/de not_active Ceased
- 2002-12-12 EP EP02805689A patent/EP1504173A1/de not_active Withdrawn
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6308690B1 (en) * | 1994-04-05 | 2001-10-30 | Sturman Industries, Inc. | Hydraulically controllable camless valve system adapted for an internal combustion engine |
| US5562070A (en) * | 1995-07-05 | 1996-10-08 | Ford Motor Company | Electrohydraulic camless valvetrain with rotary hydraulic actuator |
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20060150935A1 (en) * | 2005-01-12 | 2006-07-13 | Donaldson Joshua M | Camless engine hydraulic valve actuated system |
| WO2006076306A1 (en) * | 2005-01-12 | 2006-07-20 | Motorola, Inc. | Camless engine hydraulic valve actuation system |
| US7204212B2 (en) * | 2005-01-12 | 2007-04-17 | Temic Automotive Of North America, Inc. | Camless engine hydraulic valve actuated system |
| CN105090134A (zh) * | 2014-05-23 | 2015-11-25 | 大众汽车有限公司 | 液压供给装置 |
| US10018235B2 (en) | 2014-05-23 | 2018-07-10 | Volkswagen Aktiengesellschaft | Hydraulic supply apparatus |
| US20160312752A1 (en) * | 2015-04-24 | 2016-10-27 | Randy Wayne McReynolds | Multi-Fuel Compression Ignition Engine |
| US10113453B2 (en) * | 2015-04-24 | 2018-10-30 | Randy Wayne McReynolds | Multi-fuel compression ignition engine |
| US11156134B2 (en) * | 2017-05-22 | 2021-10-26 | EMPA Eidgenössische Materialprüfungs-und Forschungsanstalt | Hydraulic drive for accelerating and braking dynamically moving components |
| US11319844B2 (en) * | 2019-12-26 | 2022-05-03 | Harbin Engineering University | Fully variable valve train with rotary plunger for internal combustion engine |
Also Published As
| Publication number | Publication date |
|---|---|
| EP1504173A1 (de) | 2005-02-09 |
| DE10219786A1 (de) | 2003-11-13 |
| WO2003093655A1 (de) | 2003-11-13 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| AS | Assignment |
Owner name: ROBERT BOSCH GMBH, GERMANY Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:DIEHL, UDO;MISCHKER, KARSTEN;ROSENAU, BERND;AND OTHERS;REEL/FRAME:015466/0697;SIGNING DATES FROM 20040114 TO 20040120 |
|
| STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |