US20040144345A1 - Device for controlling charge exchange valves - Google Patents
Device for controlling charge exchange valves Download PDFInfo
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- US20040144345A1 US20040144345A1 US10/473,528 US47352804A US2004144345A1 US 20040144345 A1 US20040144345 A1 US 20040144345A1 US 47352804 A US47352804 A US 47352804A US 2004144345 A1 US2004144345 A1 US 2004144345A1
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- 239000012530 fluid Substances 0.000 claims abstract description 29
- 238000002485 combustion reaction Methods 0.000 claims abstract description 14
- 238000006073 displacement reaction Methods 0.000 claims description 16
- 238000011144 upstream manufacturing Methods 0.000 claims description 2
- 230000003213 activating effect Effects 0.000 description 3
- 238000010586 diagram Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 1
- 235000019577 caloric intake Nutrition 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000001960 triggered effect Effects 0.000 description 1
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Classifications
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- 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
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- 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 is based on a device for controlling gas exchange valves according to the definition of the species in claim 1 .
- each electrohydraulic valve actuator has an operating piston that acts on a gas-exchange valve, and two hydraulic working chambers that are delimited by the operating piston.
- the first working chamber which acts on the gas-exchange valve in the closing direction, is constantly filled with a fluid under high pressure
- the second working chamber which acts on the gas-exchange valve in the opening direction, is alternately able to be filled with, or relieved of, a working medium or fluid under high pressure via a first and a second electrical control valve.
- a pressure-supply device delivers a fluid under high pressure, which is conveyed via the first electrical control valve to first working chamber, on the one hand, and to the second working chamber, on the other hand.
- the second working chamber is connected to a return line leading back to the fluid reservoir by way of the second electrical control valve.
- the pressure-supply device includes a working-pressure accumulator and a controlled variable displacement pump, which conveys fluid from a fluid reservoir to the working-pressure accumulator via a check valve.
- the second working chamber In the closed state of the gas exchange valve, the second working chamber is separated from the pressure supply device by the closed first control valve, and connected to the return line through the open second control valve, so that the operating piston is displaced into its closed position by the fluid pressure prevailing in the first working chamber.
- the control valves are switched over, so that the second working chamber is cut off from the return line and connected to the pressure supply device.
- the operating piston While opening the gas exchange valve, the operating piston is displaced toward the first working chamber since the piston area of the operating piston is larger in the second working chamber than the effective area of the operating piston in the first working chamber, the length of the opening stroke depending on the formation of the electric control signal applied to the first control valve and the opening velocity depending on the fluid pressure controlled by the pressure supply device.
- control valves switch over again, thereby connecting the second working chamber, which is blocked off from the pressure supply device, to the return line, and the fluid pressure prevailing in the first working chamber guiding the operating piston back into its valve-closed position, so that the gas exchange valve is closed by the operating piston.
- the device according to the present invention for controlling gas exchange valves having the features of claim 1 , has the advantage that by dividing the pressure accumulator unit into two high-pressure accumulators for separately supplying of fluid to the valve actuators for the at least one intake valve, on the one hand, and for the at least one discharge valve, on the other hand, the fluid pressure in the two high-pressure circuits can be adapted for the intake and the discharge valve depending on the requirement for the degree of freedom allowed in the valve control by the electrohydraulic valve control, such as instant of valve actuation, lift, lift velocity and valve opening duration; and different pressure levels can be implemented.
- Dividing the pressure-supply device into two separate high-pressure circuits for the intake valves and for the discharge valves as proposed by the present invention also allows the use of a constant displacement pump, which has a simple design, instead of the variable delivery pump, which has generally been used heretofore and has a technically more complicated design, thereby achieving a considerable savings effect in the production cost of the control device.
- the known constant displacement pump is distinguished in that it generates a delivery or volumetric rate that is a function of only its driving speed, regardless of the delivery pressure.
- the constant displacement pump may either be operated by an upstream delivery pump, for instance by the oil pump of the internal combustion engine, or it may be configured as a self-priming pump.
- the switching member is provided for the alternate connecting of the two high-pressure accumulators to the constant displacement pump and is configured as a 4/3 directional solenoid control valve having spring resetting.
- One of the three valve outlets of the solenoid valve is connected to one of the high-pressure accumulators and one is connected to the other high-pressure accumulator, and the third to the return line, while the valve inlet of the solenoid valve is connected to the pump outlet of the constant displacement pump.
- FIG. 1 a circuit diagram of a device for controlling gas exchange valves for an internal combustion engine
- FIG. 2 a detailed circuit diagram of an electrohydraulic valve actuator for actuating a gas-exchange valve in the control device according to FIG. 1.
- the device for controlling gas-exchange valves shown as a circuit diagram in FIG. 1, controls a total of four intake valves 11 and a total of four discharge valves 12 of an internal combustion engine via an electronic control device 13 .
- the number of intake valves 11 and discharge valves 12 may vary, however.
- Each intake valve 11 and discharge valve 12 is arranged in a cylinder head 14 , shown in a cutaway view in FIG. 2, of a combustion cylinder and seals a combustion chamber formed in the combustion cylinder in a gastight manner.
- each gas exchange valve has a valve seat 16 , which encloses an opening cross section 15 in cylinder head 14 , and a valve element 17 , which has a valve closure element 172 sitting on a valve shaft 171 that is guided so as to be axially displacable and cooperates with valve seat 16 to close and release opening cross section 15 .
- valve closure element 172 lifts off from valve seat 16 or sets down on valve seat 16 .
- each gas-exchange valve that is each intake valve 11 and each discharge valve 12 , is assigned an electrohydraulic valve actuator 18 for its actuation.
- Electrohydraulic valve actuator 18 which is known per se, is illustrated in detail in FIG. 2. It includes a double-acting hydraulic working cylinder 19 and two electrical control valves 20 , 21 , which are preferably configured as 2/2 directional solenoid control valves having spring resetting. Electrical control valves 20 , 21 are controlled by electronic control device 13 .
- hydraulic working cylinder 19 has a cylinder housing 22 and an operating piston 23 , which is connected to valve shaft 171 of a gas-exchange valve and guided in cylinder housing 22 so as to be axially displacable, the operating piston dividing the interior of cylinder housing 25 into a first working chamber 24 and a second working chamber 25 .
- First working chamber 24 is connected directly, and second working chamber 25 via first electrical control valve 20 , to an hydraulic inlet 181 of valve actuator 18 .
- Second working chamber 25 is connected to an hydraulic outlet 182 of valve actuator 18 via second electrical control valve 21 .
- the mode of action of valve actuators 18 for opening and closing the associated gas-exchange valve is known and described in the introduction in the section “Background Information”.
- the control device has a pressure-supply device 26 .
- Pressure-supply device 26 includes a constant displacement pump 27 for generating high pressure, which is supplied from a fluid reservoir 29 by a presupply pump 28 ; a switching member 30 connected to the pump outlet of constant displacement pump 27 ; and two high-pressure accumulators 31 , 32 which, depending on the switching position of switching member 30 , are alternately able to be connected to the pump outlet of constant displacement pump 27 via a check valve 33 and 34 , respectively.
- First high-pressure accumulator 31 is connected to a first outlet 261 of the pressure-supply device, and the second high-pressure accumulator to a second outlet 262 of pressure-supply device 26 .
- each high-pressure accumulator 31 , 32 is connected to a pressure-relief valve 35 and 36 , respectively, whose valve outlet is connected to a return line 37 discharging into fluid reservoir 29 .
- switching member 30 is configured as a 4/3 directional solenoid control valve 41 having spring resetting, which is triggered by electronic control device 13 .
- a first valve outlet 412 having a check valve 33 interposed, is connected to first high-pressure accumulator 31
- a second valve outlet 413 having check valve 34 interposed, to second high-pressure accumulator 32
- a third valve outlet 414 is connected to return line 37 or directly to fluid reservoir 29 via a connecting line 42
- valve inlet 411 is connected to the pump outlet of constant displacement pump 27 .
- All electrohydraulic valve actuators 18 activating an intake valve 11 are connected to first output 261 of pressure-supply device 26 by way of their hydraulic input 181 and thus are connected to first high-pressure accumulator 31 .
- All hydraulic outlets 182 of these valve actuators 18 are connected to return line 37 via a shared connecting line 38 .
- All electrohydraulic valve actuators 18 for activating discharge valves 12 are connected to second input 262 of pressure-supply device 26 by way of their hydraulic inlets 181 and thus are connected to second high-pressure accumulator 32 .
- Hydraulic outlets 182 of these valve actuators 18 are in turn connected to return line 37 via a shared connecting line 39 .
- a check valve 43 and 44 may also be arranged in both connecting lines 38 and 39 , respectively, the check valves opening toward return line 37 .
- Electrohydraulic valve actuators 18 for all gas-exchange valves i.e., for all intake valves 11 and all discharge valves 12
- the actuating force that must be generated by valve actuators 18 for discharge valves 12 which is predefined by the combustion-chamber pressure, is considerably higher than the actuating force that valve actuators 18 must generate to actuate intake valves 11 .
- These different forces are realized by different pressure levels in high-pressure accumulators 31 , 32 .
- the different pressure levels are realized by an appropriate adjustment of pressure-relief valves 35 , 36 .
- high-pressure accumulators 31 or high-pressure accumulator 32 are then tensioned by constant displacement pump 37 to the pressure level specified by respective pressure-relief valve 35 and 36 . Since high-pressure accumulator 31 is set to a lower pressure level, the energy required for pressure generation is reduced. If no fluid is drawn off from the two high-pressure circuits via valve actuators 18 , 4/3 directional solenoid control valve 41 is controlled to its intermediate position shown in FIG. 1, in which the fluid circulates without pressure via fluid reservoir 29 .
- Constant displacement pump 27 may alternatively be configured as a self-priming pump. In this case, presupply pump 28 is omitted, and constant displacement pump 27 draws in fluid directly from fluid reservoir 29 .
- the present invention is not limited to the described exemplary embodiment.
- the number of intake valves 11 and discharge valves 12 operated by the control device may vary.
- a so-called 3-valve operation is possible as well, in which each combustion chamber formed in a combustion cylinder of the internal combustion engine is assigned two intake valves 11 and one discharge valve 12 .
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
Abstract
A device is proposed for controlling gas-exchange valves, at least one of which is assigned as intake valve (11) and at least one of which as discharge valve (12) to a combustion chamber of an internal combustion engine. The internal combustion engine includes electrohydraulic valve actuators (18) assigned in each case to a gas-exchange valve for its actuation, and a pressure-supply reservoir (26) having a high-pressure pump and a pressure-storage unit, which supplies the valve-actuators (18) with a fluid at high pressure. To reduce the energy consumed by the control device, the pressure-storage unit has two separate high-pressure reservoirs (31, 32), one of which is connected to the valve actuator (18) for the at least one intake valve (11) and the other to the valve actuator (18) for the at least one discharge valve (12). With the aid of a switching member (30), the high-pressure pump (27) is alternatively able to be connected to one or the other high-pressure reservoir (31, 32) and to a return line (37) leading to a fluid reservoir (29).
Description
- The present invention is based on a device for controlling gas exchange valves according to the definition of the species in claim1.
- In a known device of this type (DE 198 26 047 A1), each electrohydraulic valve actuator has an operating piston that acts on a gas-exchange valve, and two hydraulic working chambers that are delimited by the operating piston. The first working chamber, which acts on the gas-exchange valve in the closing direction, is constantly filled with a fluid under high pressure, and the second working chamber, which acts on the gas-exchange valve in the opening direction, is alternately able to be filled with, or relieved of, a working medium or fluid under high pressure via a first and a second electrical control valve. For this purpose, a pressure-supply device delivers a fluid under high pressure, which is conveyed via the first electrical control valve to first working chamber, on the one hand, and to the second working chamber, on the other hand. The second working chamber is connected to a return line leading back to the fluid reservoir by way of the second electrical control valve. The pressure-supply device includes a working-pressure accumulator and a controlled variable displacement pump, which conveys fluid from a fluid reservoir to the working-pressure accumulator via a check valve. In the closed state of the gas exchange valve, the second working chamber is separated from the pressure supply device by the closed first control valve, and connected to the return line through the open second control valve, so that the operating piston is displaced into its closed position by the fluid pressure prevailing in the first working chamber. To open the gas exchange valve, the control valves are switched over, so that the second working chamber is cut off from the return line and connected to the pressure supply device. While opening the gas exchange valve, the operating piston is displaced toward the first working chamber since the piston area of the operating piston is larger in the second working chamber than the effective area of the operating piston in the first working chamber, the length of the opening stroke depending on the formation of the electric control signal applied to the first control valve and the opening velocity depending on the fluid pressure controlled by the pressure supply device. To close the gas exchange valve, the control valves switch over again, thereby connecting the second working chamber, which is blocked off from the pressure supply device, to the return line, and the fluid pressure prevailing in the first working chamber guiding the operating piston back into its valve-closed position, so that the gas exchange valve is closed by the operating piston.
- The device according to the present invention for controlling gas exchange valves, having the features of claim1, has the advantage that by dividing the pressure accumulator unit into two high-pressure accumulators for separately supplying of fluid to the valve actuators for the at least one intake valve, on the one hand, and for the at least one discharge valve, on the other hand, the fluid pressure in the two high-pressure circuits can be adapted for the intake and the discharge valve depending on the requirement for the degree of freedom allowed in the valve control by the electrohydraulic valve control, such as instant of valve actuation, lift, lift velocity and valve opening duration; and different pressure levels can be implemented. This makes it possible, for instance, to set a lower fluid pressure in the high-pressure circuit for the intake valves than the fluid pressure in the high-pressure accumulator for the discharge valves, which is predefined by the force required at the discharge valve, as specified by the combustion-chamber pressure. Because of this pressure drop in the one high-pressure circuit, it is possible to reduce the required energy. As a result, the hydraulic valve actuators for the intake and discharge valves may be standardized, since the higher forces required for activating the discharge valves against the combustion-chamber pressure are realized via the higher fluid pressure in the associated high-pressure circuit. Furthermore, appropriate control of the switching element for the alternate supply of the two high-pressure accumulators allows a torque compensation in the energy intake. In this way, a more homogeneous torque pick-up with a reduced effect on the driving comfort is attained.
- The measures specified in the further claims permit advantageous further developments and improvements of the device for controlling gas-exchange valves indicated in claim1.
- Dividing the pressure-supply device into two separate high-pressure circuits for the intake valves and for the discharge valves as proposed by the present invention also allows the use of a constant displacement pump, which has a simple design, instead of the variable delivery pump, which has generally been used heretofore and has a technically more complicated design, thereby achieving a considerable savings effect in the production cost of the control device. The known constant displacement pump is distinguished in that it generates a delivery or volumetric rate that is a function of only its driving speed, regardless of the delivery pressure. The constant displacement pump may either be operated by an upstream delivery pump, for instance by the oil pump of the internal combustion engine, or it may be configured as a self-priming pump.
- According to an advantageous specific embodiment of the present invention, the switching member is provided for the alternate connecting of the two high-pressure accumulators to the constant displacement pump and is configured as a 4/3 directional solenoid control valve having spring resetting. One of the three valve outlets of the solenoid valve is connected to one of the high-pressure accumulators and one is connected to the other high-pressure accumulator, and the third to the return line, while the valve inlet of the solenoid valve is connected to the pump outlet of the constant displacement pump.
- The present invention is elucidated in the following on the basis of an exemplary embodiment depicted in the drawing.
- The figures show:
- FIG. 1 a circuit diagram of a device for controlling gas exchange valves for an internal combustion engine;
- FIG. 2 a detailed circuit diagram of an electrohydraulic valve actuator for actuating a gas-exchange valve in the control device according to FIG. 1.
- In the chosen exemplary embodiment, the device for controlling gas-exchange valves, shown as a circuit diagram in FIG. 1, controls a total of four
intake valves 11 and a total of fourdischarge valves 12 of an internal combustion engine via anelectronic control device 13. The number ofintake valves 11 anddischarge valves 12 may vary, however. Eachintake valve 11 anddischarge valve 12 is arranged in acylinder head 14, shown in a cutaway view in FIG. 2, of a combustion cylinder and seals a combustion chamber formed in the combustion cylinder in a gastight manner. In a known manner, each gas exchange valve has avalve seat 16, which encloses anopening cross section 15 incylinder head 14, and avalve element 17, which has avalve closure element 172 sitting on avalve shaft 171 that is guided so as to be axially displacable and cooperates withvalve seat 16 to close and releaseopening cross section 15. By displacingvalve shaft 171 in one axial direction or the other,valve closure element 172 lifts off fromvalve seat 16 or sets down onvalve seat 16. - In the control device for the gas-exchange valves, each gas-exchange valve, that is each
intake valve 11 and eachdischarge valve 12, is assigned anelectrohydraulic valve actuator 18 for its actuation.Electrohydraulic valve actuator 18, which is known per se, is illustrated in detail in FIG. 2. It includes a double-acting hydraulic workingcylinder 19 and twoelectrical control valves Electrical control valves electronic control device 13. In a manner known per se, hydraulic workingcylinder 19 has acylinder housing 22 and anoperating piston 23, which is connected tovalve shaft 171 of a gas-exchange valve and guided incylinder housing 22 so as to be axially displacable, the operating piston dividing the interior ofcylinder housing 25 into afirst working chamber 24 and asecond working chamber 25.First working chamber 24 is connected directly, andsecond working chamber 25 via firstelectrical control valve 20, to anhydraulic inlet 181 ofvalve actuator 18.Second working chamber 25 is connected to anhydraulic outlet 182 ofvalve actuator 18 via secondelectrical control valve 21. The mode of action ofvalve actuators 18 for opening and closing the associated gas-exchange valve is known and described in the introduction in the section “Background Information”. - To provide
electrohydraulic valve actuator 18 with a working medium or a fluid under high pressure, the control device has a pressure-supply device 26. Pressure-supply device 26 includes aconstant displacement pump 27 for generating high pressure, which is supplied from afluid reservoir 29 by apresupply pump 28; aswitching member 30 connected to the pump outlet ofconstant displacement pump 27; and two high-pressure accumulators switching member 30, are alternately able to be connected to the pump outlet ofconstant displacement pump 27 via acheck valve pressure accumulator 31 is connected to afirst outlet 261 of the pressure-supply device, and the second high-pressure accumulator to asecond outlet 262 of pressure-supply device 26. Viaoutlet supply device 26, each high-pressure accumulator relief valve return line 37 discharging intofluid reservoir 29. In the exemplary embodiment shown, switchingmember 30 is configured as a 4/3 directionalsolenoid control valve 41 having spring resetting, which is triggered byelectronic control device 13. Of the altogether three valve outlets ofsolenoid valve 41, afirst valve outlet 412, having acheck valve 33 interposed, is connected to first high-pressure accumulator 31, asecond valve outlet 413, havingcheck valve 34 interposed, to second high-pressure accumulator 32, and athird valve outlet 414 is connected toreturn line 37 or directly tofluid reservoir 29 via aconnecting line 42;valve inlet 411 is connected to the pump outlet ofconstant displacement pump 27. - All
electrohydraulic valve actuators 18 activating anintake valve 11 are connected tofirst output 261 of pressure-supply device 26 by way of theirhydraulic input 181 and thus are connected to first high-pressure accumulator 31. Allhydraulic outlets 182 of thesevalve actuators 18 are connected toreturn line 37 via a shared connectingline 38. Allelectrohydraulic valve actuators 18 for activatingdischarge valves 12 are connected tosecond input 262 of pressure-supply device 26 by way of theirhydraulic inlets 181 and thus are connected to second high-pressure accumulator 32.Hydraulic outlets 182 of thesevalve actuators 18 are in turn connected toreturn line 37 via a sharedconnecting line 39. Acheck valve lines return line 37. -
Electrohydraulic valve actuators 18 for all gas-exchange valves, i.e., for allintake valves 11 and alldischarge valves 12, have a uniform design. However, the actuating force that must be generated byvalve actuators 18 fordischarge valves 12, which is predefined by the combustion-chamber pressure, is considerably higher than the actuating force thatvalve actuators 18 must generate to actuateintake valves 11. These different forces are realized by different pressure levels in high-pressure accumulators relief valves solenoid control valve 41, high-pressure accumulators 31 or high-pressure accumulator 32 are then tensioned byconstant displacement pump 37 to the pressure level specified by respective pressure-relief valve pressure accumulator 31 is set to a lower pressure level, the energy required for pressure generation is reduced. If no fluid is drawn off from the two high-pressure circuits viavalve actuators 18, 4/3 directionalsolenoid control valve 41 is controlled to its intermediate position shown in FIG. 1, in which the fluid circulates without pressure viafluid reservoir 29. -
Constant displacement pump 27 may alternatively be configured as a self-priming pump. In this case,presupply pump 28 is omitted, andconstant displacement pump 27 draws in fluid directly fromfluid reservoir 29. - The present invention is not limited to the described exemplary embodiment. For instance, the number of
intake valves 11 anddischarge valves 12 operated by the control device may vary. A so-called 3-valve operation is possible as well, in which each combustion chamber formed in a combustion cylinder of the internal combustion engine is assigned twointake valves 11 and onedischarge valve 12.
Claims (10)
1. A device for controlling gas-exchange valves, at least one of which is assigned as an inlet valve (11) and at least one as a discharge valve (12) to a combustion chamber of the internal combustion engine, each having an electrohydraulic valve actuator (18) assigned to a gas-exchange valve (11, 12) for its actuation, and having a pressure-supply device (26) supplying the valve actuators (18) with a fluid at high pressure, the pressure-supply device (26) having a high-pressure pump and a pressure-storage unit, wherein the pressure accumulator unit has two separate high-pressure accumulators (31, 32), one of which is connected to the valve actuator (18) for the at least one intake valve (11) and the other to the valve actuator (18) for the at least one discharge valve (12), and the high-pressure pump is optionally connectable by way of a switching member (30) to the one or to the other high-pressure accumulator (31, 32) and to a return line (37) leading to a fluid reservoir (29).
2. The device as recited in claim 1 , wherein the high-pressure pump is configured as constant displacement pump (27) whose pump outlet is connected to the inlet of the switching member (30).
3. The device as recited in claim 1 or 2, wherein the switching member (30) is configured as a 4/3 directional solenoid control valve (41) having one valve inlet (411) and three valve outlets (412, 413, 414) having spring setting, whose valve inlet (411) is connected to the pump outlet and one of whose three valve outlets (412, 413, 414) is connected to the one and the other to the other high-pressure accumulator (31, 32) and the third is connected to the return line (37).
4. The device as recited in claim 3 , wherein the 4/3 directional solenoid control valve (41) is controlled by an electronic control device (13).
5. The device as recited in one of claims 1 through 4, wherein the two high-pressure reservoirs (31, 32) are set to different pressure levels.
6. The device as recited in claim 5 , wherein the high-pressure reservoirs (31, 32) are in each case connected via a pressure relief valve (35, 36) to the return line (37).
7. The device as recited in one of claims 1 through 6, wherein in a plurality of gas-exchange valves (11, 12) the valve actuators (18) of all intake valves (11) are connected to one, and the valve actuators (18) of all outlet valves (12) are connected to the other high-pressure reservoir (31, 32).
8. The device as recited in one of claims 2 through 7, wherein a presupply pump (28) delivering from the fluid reservoir (29) is arranged upstream from the constant displacement pump (27).
9. The device as recited in one of claims 2 through 7, wherein the constant displacement pump (27) is implemented as self-priming pump whose pump intake is directly connected to the fluid reservoir (29).
10. The device as recited in one of claims 1 through 9, wherein each electrohydraulic valve actuator (18) has a double-acting hydraulic working cylinder (19) for valve actuation and electric control valves (20, 21) controlling the operating pressure in the working cylinder (19).
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10203275A DE10203275A1 (en) | 2002-01-29 | 2002-01-29 | Device for controlling gas exchange valves |
DE10203275.0 | 2002-01-29 | ||
PCT/DE2002/004365 WO2003064823A1 (en) | 2002-01-29 | 2002-11-28 | Device for controlling charge exchange valves |
Publications (1)
Publication Number | Publication Date |
---|---|
US20040144345A1 true US20040144345A1 (en) | 2004-07-29 |
Family
ID=7713253
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/473,528 Abandoned US20040144345A1 (en) | 2002-01-29 | 2002-11-28 | Device for controlling charge exchange valves |
Country Status (6)
Country | Link |
---|---|
US (1) | US20040144345A1 (en) |
EP (1) | EP1481148B1 (en) |
JP (1) | JP2005516146A (en) |
KR (1) | KR20040077808A (en) |
DE (2) | DE10203275A1 (en) |
WO (1) | WO2003064823A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
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US11156134B2 (en) * | 2017-05-22 | 2021-10-26 | EMPA Eidgenössische Materialprüfungs-und Forschungsanstalt | Hydraulic drive for accelerating and braking dynamically moving components |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN1287069C (en) * | 2003-11-27 | 2006-11-29 | 宁波华液机器制造有限公司 | Pressure differential style air valve variation control system |
KR20040013033A (en) * | 2004-01-09 | 2004-02-11 | (주)하이드로 메틱스 | Oil compressure device for driving gas valve with several oil pressure accumulators and cylinders |
US8602002B2 (en) | 2010-08-05 | 2013-12-10 | GM Global Technology Operations LLC | System and method for controlling engine knock using electro-hydraulic valve actuation |
DE102016213976B4 (en) * | 2016-07-29 | 2018-07-05 | Schaeffler Technologies AG & Co. KG | Electrohydraulic valve train of an internal combustion engine |
DE102016224772A1 (en) * | 2016-12-13 | 2018-06-14 | Bayerische Motoren Werke Aktiengesellschaft | reciprocating internal combustion engine |
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US4353286A (en) * | 1979-07-17 | 1982-10-12 | Mds Mannesmann Demag Sack Gmbh | Hydraulic control system with a pipeline antiburst safety device for a double acting drive cylinder |
US4833971A (en) * | 1988-03-09 | 1989-05-30 | Kubik Philip A | Self-regulated hydraulic control system |
US5478045A (en) * | 1991-10-11 | 1995-12-26 | Caterpillar Inc. | Damped actuator and valve assembly |
US5645030A (en) * | 1995-08-04 | 1997-07-08 | Daimler-Bauz Ag | Motorbrake for a diesel engine |
US6067946A (en) * | 1996-12-16 | 2000-05-30 | Cummins Engine Company, Inc. | Dual-pressure hydraulic valve-actuation system |
US6321703B1 (en) * | 1998-06-12 | 2001-11-27 | Robert Bosch Gmbh | Device for controlling a gas exchange valve for internal combustion engines |
US6408807B1 (en) * | 2000-08-03 | 2002-06-25 | Aisin Seiki Kabushiki Kaisha | Variable valve timing system |
Family Cites Families (3)
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DE69218971T2 (en) * | 1991-06-24 | 1997-07-24 | Ford Werke Ag | Hydraulic valve control device for an internal combustion engine |
US6148778A (en) * | 1995-05-17 | 2000-11-21 | Sturman Industries, Inc. | Air-fuel module adapted for an internal combustion engine |
DE19816817A1 (en) * | 1997-11-25 | 1999-10-21 | Bayerische Motoren Werke Ag | Hydraulic operating device for gas exchange valve of internal combustion engine |
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2002
- 2002-01-29 DE DE10203275A patent/DE10203275A1/en not_active Withdrawn
- 2002-11-28 JP JP2003564401A patent/JP2005516146A/en active Pending
- 2002-11-28 WO PCT/DE2002/004365 patent/WO2003064823A1/en active IP Right Grant
- 2002-11-28 DE DE50204351T patent/DE50204351D1/en not_active Expired - Lifetime
- 2002-11-28 EP EP02805683A patent/EP1481148B1/en not_active Expired - Lifetime
- 2002-11-28 US US10/473,528 patent/US20040144345A1/en not_active Abandoned
- 2002-11-28 KR KR10-2004-7011583A patent/KR20040077808A/en not_active Application Discontinuation
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4353286A (en) * | 1979-07-17 | 1982-10-12 | Mds Mannesmann Demag Sack Gmbh | Hydraulic control system with a pipeline antiburst safety device for a double acting drive cylinder |
US4833971A (en) * | 1988-03-09 | 1989-05-30 | Kubik Philip A | Self-regulated hydraulic control system |
US5478045A (en) * | 1991-10-11 | 1995-12-26 | Caterpillar Inc. | Damped actuator and valve assembly |
US5645030A (en) * | 1995-08-04 | 1997-07-08 | Daimler-Bauz Ag | Motorbrake for a diesel engine |
US6067946A (en) * | 1996-12-16 | 2000-05-30 | Cummins Engine Company, Inc. | Dual-pressure hydraulic valve-actuation system |
US6321703B1 (en) * | 1998-06-12 | 2001-11-27 | Robert Bosch Gmbh | Device for controlling a gas exchange valve for internal combustion engines |
US6408807B1 (en) * | 2000-08-03 | 2002-06-25 | Aisin Seiki Kabushiki Kaisha | Variable valve timing system |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11156134B2 (en) * | 2017-05-22 | 2021-10-26 | EMPA Eidgenössische Materialprüfungs-und Forschungsanstalt | Hydraulic drive for accelerating and braking dynamically moving components |
Also Published As
Publication number | Publication date |
---|---|
WO2003064823A1 (en) | 2003-08-07 |
DE10203275A1 (en) | 2003-08-07 |
KR20040077808A (en) | 2004-09-06 |
DE50204351D1 (en) | 2005-10-27 |
JP2005516146A (en) | 2005-06-02 |
EP1481148B1 (en) | 2005-09-21 |
EP1481148A1 (en) | 2004-12-01 |
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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;ROSENAU, BERND;KIESER, SIMON;REEL/FRAME:015123/0028;SIGNING DATES FROM 20031031 TO 20031105 |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |