CN100379951C - Engine valve actuation system and method using reduced pressure common rail and dedicated engine valve - Google Patents
Engine valve actuation system and method using reduced pressure common rail and dedicated engine valve Download PDFInfo
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- CN100379951C CN100379951C CNB038075997A CN03807599A CN100379951C CN 100379951 C CN100379951 C CN 100379951C CN B038075997 A CNB038075997 A CN B038075997A CN 03807599 A CN03807599 A CN 03807599A CN 100379951 C CN100379951 C CN 100379951C
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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
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
- F01L13/06—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for braking
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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
- F01L9/20—Valve-gear or valve arrangements actuated non-mechanically by electric means
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- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
- Exhaust-Gas Circulating Devices (AREA)
Abstract
A system and method for actuating an engine valve to provide engine braking and/or exhaust gas recirculation using a common source of hydraulic fluid is disclosed. The system receives high-pressure hydraulic fluid from a common rail system, such as those used to provide fuel injection. The fluid pressure is reduced before being used to actuate an engine valve for engine braking or EGR. Preferably an engine valve that is dedicated to the engine braking or EGR function is provided in the engine. The dedicated engine braking/EGR valve may be driven by an electromagnetic actuator in an alternative embodiment.
Description
Technical field
The present invention relates to a kind ofly be used for driving engine valve in the internal-combustion engine to realize the method and apparatus of compression-release braking event, bleeder type engine braking event and/or internal exhaust gas recirculation (EGR) process.
Background technique
During engine braking, outlet valve can open the air compressor that at least temporarily the internal-combustion engine that produces power is converted to absorbed power selectively.When piston moved upward during compression stroke, the gas that is collected in the cylinder was compressed.The gas that compressed stops piston to move upward.At the engine braking duration of work, when piston during near top dead center (TDC), at least one engine valve that is connected with gas exhaust manifold is opened and discharges pressurized gas, thereby the energy that prevents to be stored in the pressurized gas when expanding downward stroke subsequently turns back in the motor.In doing so, motor has produced retarding power to help that vehicle is slowed down.
The work of the compression-release engine brake as leading portion is described is known.A description the earliest that is used for the system of compression-release braking is disclosed in the U.S. Patent No. 3220392 of Cummins.This system in Cummins 392 patents of being described in obtains motion opening a pair of outlet valve, thereby makes existing air inlet, exhaust or sparger push rod or rocking arm carry out compression-release events.Compression-release motion is delivered to the bridge by selectively expandable hydraulic linkage from push rod or rocking arm, and this bridge engages two outlet valves.This hydraulic connecting rod expands with the transmission compression-release motion at the engine braking duration of work, and shrinks to absorb this motion at the positive duration of work.Hydraulic connecting rod makes has lost compression-release motion that during positive correspondingly, these systems are commonly referred to " empty moving " valve drive system shrinking during the positive.
As the Cummins system, engine valve is typically driven by fixing builder cam (profile cam), more particularly, is driven by one or more fixed lobe on each cam in these empty moving systems.Use feasible timing and/or the size that is difficult to adjust engine valve lift of fixing builder cam, and this timing and/or size are as making the engine performance optimization needed in various engine conditions under the different engine speeds during the engine braking.
In recent years, these system and methods that are described in Cummins 392 patents various improvement have been carried out.Such improvement is to use shared high-pressure fluid source, and for example this fluid source is used for fuel injection system, carries out engine braking to drive one or more valve.These systems usually are called " coorbital " system.In common rail valve actuation systems, source of high pressure hydraulic fluid can be applied on the power piston selectively, carries out compression-release events to drive one or more valve.Select to drive with these valves of realizing engine braking the most frequently used be outlet valve.The example of these systems is disclosed in the U.S. Patent No.s 5787859,5809964 and 6082328 such as Sickler U.S. Patent No. 4572114, Pitzi U.S. Patent No. 5012778 and Meistrick, and each in these patents is here introduced with for referencial use.In some common rail systems, dedicated auxiliary valve is provided to carry out engine braking.Some examples of these systems are disclosed in U.S. Patent No.s 5609134 such as U.S. Patent No. 5564386, Schmidt such as Korte and the Bergmann U.S. Patent No. 5794590, and each in these patents is here introduced with for referencial use.
Common rail system in fact can provide unlimited adjustment is carried out in the valve timing, because source of high pressure hydraulic fluid often can realize the driving of valve.Because common rail system can almost ad infinitum change the valve timing in theory, therefore they can be used for realizing almost engine valve events such as air inlet, exhaust, compression-release braking, bleeder brake or the exhaust gas recirculation (EGR) of any kind, as long as driven valve is connected with suitable manifold (being intake manifold or gas exhaust manifold).Correspondingly, produce complexity and high speed control when applying hydraulic pressure, common rail system should provide valve to drive according to the requirement of various valve events, and is promoting and providing some controls on the endurance.
But so far, the joint-track type engine valve actuation systems that is used for braking with EGR is not used widely.Needed complexity is controlled, especially needed complicated control is not effectively realized when engine valve is taken a seat.Especially hinder and use two problems that are total to the rail drive system to be: realize that needed these parts of desired control degree are more expensive, and this system is easy to produce fault under the situation of hydraulic pressure loss.Solved up to all problems, empty moving system becomes the system of the main type that is used for realizing engine braking probably continuously.
These front problems of common rail system partly result from the very high pressure source of use and open engine valve, and partly result from the system that realizes promptly main intake process of critical valve events and main exhaust process that relies on.Proposed to use very high pressure system at the joint-track type engine braking by following method: promptly carry engine braking system at the place cover that leaves common rail fuel injection system, wherein this common rail fuel injection system is installed on the vehicle.This " cover carries " is considered to the expense of obviously having saved, because two systems are that engine braking and fuel injection can only need a high-voltage power supply (with the part group).Need very high pressure promptly to need about 3000psi because fuel sprays, therefore attempt to provide a kind of engine braking common rail system, this common rail system uses fluid with similar pressure.But the usage requirement actuating valve of this high pressure makes the very large Returnning spring of exerting oneself, and this actuating valve needs complicated valve seat device again.In addition, for high-pressure system, leakage is bigger problem, and Element Design itself key and expense are more expensive more.Correspondingly, need a kind of such common rail system: this common rail system can be used for engine braking and EGR, and this engine braking and EGR do not have to use the shortcoming of the high-pressure liquid institute association of rail driving altogether.
By use engine valve actuation common rail system produced second obviously challenge be thrashing potentially.Hydraulic system produces the shortcoming of inefficacy owing to escape of liquid.Prevent that the scope of leaking is big more, this system is just expensive more so.Common rail system can not carry out engine braking and/or EGR just can not produce disaster, because vehicle is not having certainly to carry out work under the situation of these features, but this is less preferred.But what can not bear is master air suction valve or main exhaust valve akinesia, because it can cause motor thoroughly to lose efficacy.Correspondingly, need a kind of such common rail system: it only causes engine braking and/or EGR valve events, but does not need main air inlet or main exhaust engine valve events.
The claimant has solved various top problems so that common rail system is used for engine braking and EGR effectively by following method: the actuator and the special engine braking/EGR engine valve that reduce pressure common rail system or Electromagnetic Drive are coupled together.Use the pressure that reduces just can reduce the possibility and the effect of leaking, and can reduce the load of distribution device.In addition, that this system can provide is almost unlimited, the timing variation of engine braking and internal EGR, and can not endanger main intake ﹠ exhaust valves work.
Other purpose and the advantage of some embodiments of the present invention (but needing not to be all embodiments) are partly proposed in the explanation below, and by description and/or by putting into practice the present invention, the part in them says it is conspicuous for those of ordinary skill in the art.
Summary of the invention
According to top challenge, the claimant provides a kind of new work engine valve drive system that is used for engine braking and/or exhaust gas recirculation, and this system comprises: source of high pressure hydraulic fluid; Hydrodynamic pressure reduces device, and it is connected in the source of high pressure hydraulic fluid; Hydraulic fluid control valve, it is connected to hydrodynamic pressure and reduces in the device; And engine valve actuator, it is connected in the hydraulic fluid control valve.
In one embodiment, the invention provides a kind of engine valve actuation systems, this system comprises: the high pressure hydraulic fluid passage; Source of high pressure hydraulic fluid; Hydrodynamic pressure reduces device, and it is connected in the hydraulic fluid source by the high pressure hydraulic fluid passage; The low pressure hydraulic fluid passage; Hydraulic fluid control valve, it is connected to hydrodynamic pressure by the low pressure hydraulic fluid passage and reduces in the device; Activate hydraulic fluid channel; And engine valve actuator, it is used for producing engine valve events, and this engine valve actuator is connected with hydraulic fluid control valve by activating hydraulic fluid channel.
In another embodiment, the invention provides and a kind ofly be used for driving engine valve in the internal-combustion engine to produce the method for engine valve events.This method comprises these steps: hydraulic fluid is provided to hydrodynamic pressure reduces in the device; Make the pressure of hydraulic fluid reduce to second pressure from first pressure; Selectively the hydraulic fluid of second pressure is applied in the engine valve actuator; And drive engine valve to produce engine valve events.
Should be understood that top general description and following detailed are examples, and be example, rather than restriction the present invention for required protection.Here introduce with accompanying drawing for referencial use and that constituted the part of declaratives and show some embodiments of the present invention, and be used for explaining principle of the present invention with describing in detail.
Description of drawings
In order to help to understand the present invention, referring now to accompanying drawing, in these accompanying drawings, same numeral is represented similar elements.These accompanying drawings are example, and can not be used for limiting the present invention.
Fig. 1 is the Block Diagram of the engine valve actuation systems of first embodiment of the invention.
Fig. 2 is the Block Diagram of the engine valve actuation systems of second embodiment of the invention.
Fig. 3 is the schematic representation of the engine valve actuation systems of third embodiment of the invention.
Fig. 4 is the Block Diagram of the engine valve actuation systems of fourth embodiment of the invention.
Fig. 5 is the schematic representation of the engine valve actuation systems of fifth embodiment of the invention.
Embodiment
Now, at length with reference to embodiments of the invention, an example among these embodiments illustrates in the accompanying drawings.With reference to Fig. 1, it shows the valve actuation system 10 of internal-combustion engine.In one embodiment, valve actuation system 10 comprises: source of high pressure hydraulic fluid 100; Hydrodynamic pressure reduces device 300, and it is connected in the source of high pressure hydraulic fluid 100; Hydraulic fluid control valve 400, it is connected to hydrodynamic pressure and reduces on the device 300; And engine valve actuator 600, it is connected on the hydraulic fluid control valve 400, to drive engine valve 700.Engine valve 700 comprises special-purpose brake valve.But it is contemplated that engine valve 700 can comprise exhaust valve and/or intake valve.
In other embodiments of the invention, as shown in Figure 2, valve actuation system 10 can also comprise: accumulator 500, and it is connected on the hydraulic fluid control valve 400; And low pressure hydraulic fluid case 200, it is connected on the high-pressure fluid source 100.
With reference to Fig. 3, in one embodiment of the invention, valve actuation system 10 comprises high-pressure fluid source 100, for example can be used for supplying with common rail fuel injection system.Hydraulic electronic unit injection (HEUI) system that is sold by Navistar International is an example of this common rail fuel injection system.
High-pressure fluid source 100 can comprise high-pressure service pump 110, pressure regulator 120 and high pressure forced ventilation system 130.High pressure fluid pump 110 can be from low-pressure cabinet 200 inhalant liquid hydraulic fluid such as diesel oil.By pump 110 formed hydrodynamic pressures (for example 3000) psi that is approximately several thousand.In the prior art of high-pressure fluid source 100 in fuel injection system is known.The pressure that high-pressure fluid source 100 is provided is represented with pressure P 1.
In the embodiment of the invention shown in Figure 3, the high-pressure liquid that is provided by source 100 not only can be used to provide the fuel injection, and can also be used to providing the promotion source for the braking work of motor.Use high-pressure fluid source such as source 100 with an advantage of carrying out engine braking to be, it is Already in the motor.In order to utilize high-voltage power supply 100 to carry out engine braking, be provided to pressure from the pressure fluid of high-pressure fluid source 100 by high-tension line 140 and reduce in the device 300.Pressure reduces device 300 preferably makes hydrodynamic pressure approximately reduce by a size, and more preferably, reduces to the value of about 300psi.The fluid that pressure reduces can be provided in the control valve 400 by circuit 310.Represent with pressure P 2 by the pressure that pressure minimizing device 300 is provided.
In one embodiment, pressure minimizing device 300 can comprise pressure reducing valve.Pressure reduces device 300 can comprise direct operated pressure reducing valve, two-way pilot-operated pressure reducing valve and/or any other known pressure reducing valve.The road is the same as known to persons of ordinary skill in the art, is suitable for reducing other pressure from the pressure of the fluid in the high-pressure fluid source 100 and reduces device and also think to fall in the scope and spirit essence of the present invention.
Continuation is with reference to Fig. 3, and control valve 400 can comprise valve body 410 and controller 420.Valve body 410 is preferably the control valve of 3/2 direction, and can comprise some inner passages, and these passages make first opening 412 be communicated with second opening 414, and the 3rd opening 416 is communicated with the 4th opening 418.By control valve spring 430 valve body 410 is biased on the default location.
On this default location, the inner passage in the valve body 410 can make brake actuation (brakeactuator) circuit 440 be communicated with accumulator 500.In another embodiment, as shown in Figure 4, accumulator 500 can replace with ventilation or fluid return line, and this ventilation or fluid return line are connected to control valve 400 in the low-pressure cabinet 200.
What also know is, controller 420 is preferably controlled by electrical signal, and this electrical signal is sent by the engine control module (ECM) (not shown).The road is the same as known to persons of ordinary skill in the art, ECM can comprise microprocessor, and can be connected in some sensors, and these sensors for example are connected on other engine part on cylinder, outlet pipe, suction tude or any other engine part, with control controller 420.
Returnning spring 630 is shown to and is positioned at fluid chamber 610, but should be understood that Returnning spring can be set in place on any position between engine valve actuator 600 and the cylinder (not shown).Returnning spring 630 even can be arranged to the Returnning spring of special-purpose brake valve 700 also makes power piston 620 turn back on its uppermost position because special-purpose brake valve 700 turns back on its uppermost position.
Under the influence of controller 420, control valve 400 is on two main positions.The primary importance of control valve 400 is corresponding with following situation: in this case, wishing does not have engine braking and/or exhaust gas recirculation, and promptly dedicated engine valve 700 has been closed.When dedicated engine valve 700 was closed, controller 420 remained on valve body 410 on the position shown in Figure 3.On this position, first opening 412 of valve body 410 is connected with brake actuator line 440, and second opening 414 is connected with accumulator 500.Consequently, valve body 410 provides connection between fluid chamber 610 and accumulator 500.Hydrodynamic pressure in the accumulator 500 is less, correspondingly, dedicated engine valve Returnning spring (it can the be a spring 630) power piston 620 that can move up, thus force fluid effluent fluid chamber 610 and enter into accumulator 500.Do not have new fluid can flow in the fluid chamber 610 to move down power piston 620, because control valve 400 is not on such position: on this position, it provides circulation reducing between pressure line 310 and the brake actuator line 440.
As the result who is applied to from the minimizing pressure fluid in the control valve 400 on the power piston, when being desirable to provide engine braking and/or exhaust gas recirculation, power piston 620 can move down to drive dedicated engine valve 700.When power piston 620 was moved down in the dedicated engine valve 700, dedicated engine valve was opened, and gas carries out free-flow between cylinder that links to each other with dedicated engine valve and gas exhaust manifold.
As initial thing, this system can forward " opening " to, with by a minimizing hydrodynamic pressure that reduces device 300 from pressure is applied to reduce in the pressure line 310 brake, EGR or other valve activate task.Reduce in the pressure line 310 in case hydrodynamic pressure is present in, controller 420 says the word to move down valve body 410 so.Move down the 3rd opening 416 that causes valve body and reduce pressure line 310 and aims at and the 4th opening 418 and brake actuator line 440 are aligned.On this position, valve body 410 provides the fluid connection between minimizing pressure line 310 and brake actuator line 440.This connection causes that brake actuator piston 620 moves down and open engine valve 700, to carry out engine braking or exhaust gas recirculation event.
Realize that the above-mentioned circulation that opens and closes engine valve 700 makes fluid chamber's 610 emptyings and is full of the same fast again with controller 420.Be clear that the speed dependent of this system is in the size of the speed of control valve 400 and size, brake actuator line 440 and length, and the viscosity of working fluid.Correspondingly, control valve 400 being arranged to be positioned as close to fluid chamber 610 is favourable with the response time of improving this system.For some embodiments of the present invention, what wish is, this system can carry out the engine valve events that surpasses once in each engine cycles, and this system provides the almost unlimited timing selection that changes that is used for opening, closing and continue braking and EGR process.Although wish that this system can high-speed driving, this system needn't be always to carry out work to produce favourable result at a high speed.For example, at the time durations of worrying brake noise (in cities and towns or city), system 10 can be used to provide some or all of cycle bleeder braking (bleederbraking), and less worry noise At All Other Times the time compression-release braking is provided.
Use minimizing hydrodynamic pressure (be about 300psi, this pressure is relative with 3000psi) to drive special engine brake valve 700 many advantages can be provided.Some advantages that realized during braking and/or EGR comprise: the high-speed trigger valve as control valve 400 is more prone to make, and more reliable, because it only needs to handle to reduce pressure fluid.Use the minimizing pressure fluid also can reduce the seating velocity of impact load and braking component, and make these loads and speed can control more.In addition, use the minimizing pressure fluid can reduce the escape of liquid and the vibration of braking system, and make whole system compact more.The advantage that is realized during positive comprises makes the valve timing near unlimited variation, with provide be suitable for engine speed and/the inside GER of load.This system 10 also improves the internal EGR that cooling is provided, because the outlet passage of special valve can be different from the outlet passage of main exhaust valve, cooler can be arranged in the designated lane.
An alternative embodiment of the present invention is illustrated among Fig. 5, and in the figure, identical label is represented components identical.In system shown in Figure 5, engine valve actuator 600 provides by electromagnetic actuators 690.In this embodiment, do not need common rail system, as the system of Fig. 3.In all others, the system of ground the same control diagram 5 with system shown in Figure 3.
In one embodiment, electromagnetic actuators 690 comprises high-speed electromagnetic valve, and this solenoid valve drives engine valve 700 with each engine cycles speed at least once.In another embodiment, electromagnetic actuators 690 comprises low-speed solenoid valve.Other embodiment who comprises the engine valve actuator 600 of piezo actuator (but being not limited to this) also should think and falls in the scope and spirit essence of the present invention.
The dedicated engine valve 700 of engine braking and EGR can be less than main exhaust valve, and only needs less power to open it.In case this valve has been opened fully, control by the annular space between hole and valve rod by the flow region of valve so, and even only need littler power to come maintaining valve to open.
Those of ordinary skills should be understood that under the situation that does not break away from the scope of the invention or essence the present invention can carry out various distortion and improvement.For example, high-pressure system and the relative pressure that reduces pressure system can be different from discussed above these, and can not break away from the scope of protection of present invention.The size of part and design can change separately, and can save some parts such as accumulator, pressure transducer etc., and can not break away from the scope of protection of present invention.In addition, the design of control valve 400 can change and can not break away from the scope of protection of present invention.In addition, employed hydraulic fluid can change and can not break away from the scope of protection of present invention.In addition, some embodiments of these method and apparatus of the present invention are suitable for two-cycle engine braking and four stroke engine braking, and in this two-cycle engine braking, normal engine exhaust and suction valve action have been modified.Therefore, as long as they fall in the scope of accessory claim and their equivalents, the present invention includes all these distortion of the present invention and improvement so.
Claims (23)
1. engine valve actuation systems, this system comprises:
High pressure hydraulic fluid passage (140);
Source of high pressure hydraulic fluid (100);
Hydrodynamic pressure reduces device (300), it has first end and second end that low pressure hydraulic fluid is provided that is connected to source of high pressure hydraulic fluid (100) by high pressure hydraulic fluid passage (140), wherein when the second portion with high pressure hydraulic fluid remained on identical pressure, hydrodynamic pressure minimizing device (300) was reduced to the pressure that is less than about this high pressure one order of magnitude greatly with the pressure of the first portion of high pressure hydraulic fluid;
Low pressure hydraulic fluid passage (310) is connected to second end that hydrodynamic pressure reduces device (300);
Hydraulic fluid control valve (400), it is connected to second end that hydrodynamic pressure reduces device by low pressure hydraulic fluid passage (310);
Activate hydraulic fluid channel (440); And
Engine valve actuator (600), it drives engine valve (700) to produce engine valve events, and this engine valve actuator is connected with hydraulic fluid control valve by activating hydraulic fluid channel.
2. the system as claimed in claim 1 is characterized in that, described engine valve events chooses from set, and this group action comprises compression-release braking maneuver, bleeder brake action and exhaust gas recirculation action.
3. the system as claimed in claim 1 is characterized in that, hydraulic fluid source comprises fuel injection system.
4. the system as claimed in claim 1 is characterized in that, hydrodynamic pressure reduces device makes the pressure of hydraulic fluid reduce to second pressure from first pressure, and wherein the size of second pressure is approximately less than first pressure.
5. system as claimed in claim 4 is characterized in that second pressure is approximately 300psi.
6. the system as claimed in claim 1 is characterized in that, control valve comprises:
Valve body, it has some fluid passages that are formed at wherein, and valve body is fit to move between first working position and second working position selectively;
Controller, it is used for mobile valve; And
Spring, it is biased into valve body on first working position.
7. system as claimed in claim 6 is characterized in that, controller is with each engine cycles speed mobile valve at least once.
8. system as claimed in claim 6 also comprises accumulator, it is characterized in that, when valve body was on first working position, control valve made the actuating hydraulic fluid channel be communicated with accumulator.
9. system as claimed in claim 6 is characterized in that, when valve body was on first working position, control valve made the actuating hydraulic fluid channel be communicated with the low pressure hydraulic fluid case.
10. system as claimed in claim 6 is characterized in that, when valve body was on second working position, control valve made and activates hydraulic fluid channel and low pressure hydraulic fluid channel connection.
11. the system as claimed in claim 1 is characterized in that, engine valve actuator comprises:
Fluid chamber, it holds from the hydraulic fluid that activates in the hydraulic fluid channel;
Power piston, it is slidably disposed in the fluid chamber; And
Returnning spring, it contacts with power piston.
12. the system as claimed in claim 1 also comprises:
The low pressure hydraulic fluid case, wherein hydraulic fluid source also comprises:
High-pressure service pump, it is connected with the low-pressure fluid case;
Pressure regulator; And
The high pressure forced ventilation system, it is connected in the high pressure hydraulic fluid passage.
13. the system as claimed in claim 1 is characterized in that, engine valve is special-purpose engine exhaust valve.
14. the system as claimed in claim 1 is characterized in that, compares with main exhaust valve, described engine valve only needs littler power to drive it.
15. system as claimed in claim 13 is characterized in that, also comprises the special-purpose exhaust passage that is connected with the special engine outlet valve.
16. system as claimed in claim 15 is characterized in that, also comprises the cooling unit that is connected to special-purpose exhaust passage.
17. system as claimed in claim 16 is characterized in that, described engine valve events is waste gas cooled recirculation action.
18. an engine valve actuation systems, this system comprises:
Source of high pressure hydraulic fluid, it provides the hydraulic fluid of first pressure;
Hydrodynamic pressure reduces device, and it is connected in the described hydraulic fluid source, and described hydrodynamic pressure minimizing device is reduced to the second lower pressure with first pressure of the first portion of high pressure hydraulic fluid, and the second portion of high pressure hydraulic fluid remains on first pressure simultaneously;
Hydraulic fluid control valve, it is connected in the hydrodynamic pressure minimizing device and has first working position and second working position; And
Engine valve actuator, when hydraulic fluid control valve was on second working position, it drove engine valve to produce engine valve events, and this engine valve events is fit to hold the hydraulic fluid of second pressure.
19. system as claimed in claim 18 is characterized in that, second pressure is approximately 300psi.
20. one kind drives engine valve in the internal-combustion engine to produce the method for engine valve events, this method comprises these steps:
High pressure hydraulic fluid is provided to hydrodynamic pressure to be reduced in the device;
Make the pressure of the first portion of high pressure hydraulic fluid reduce to the second lower pressure from the first higher pressure, wherein said second pressure is less than about higher first pressure, one order of magnitude greatly, and wherein after the pressure of the first portion that has reduced high pressure hydraulic fluid, the second portion of high pressure hydraulic fluid remains on high pressure;
Selectively the hydraulic fluid of the second lower pressure is applied in the engine valve actuator; And
Drive engine valve to produce described engine valve events.
21. method as claimed in claim 20 is characterized in that, the step that drives engine valve also comprises such step: produce the compression-release braking maneuver.
22. method as claimed in claim 20 is characterized in that, the step that drives engine valve also comprises such step: produce the bleeder brake action.
23. method as claimed in claim 20 is characterized in that, the step that drives engine valve also comprises such step: the action that produces exhaust gas recirculation.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US35227502P | 2002-01-30 | 2002-01-30 | |
| US60/352,275 | 2002-01-30 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1646795A CN1646795A (en) | 2005-07-27 |
| CN100379951C true CN100379951C (en) | 2008-04-09 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB038075997A Expired - Fee Related CN100379951C (en) | 2002-01-30 | 2003-01-30 | Engine valve actuation system and method using reduced pressure common rail and dedicated engine valve |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US20030140876A1 (en) |
| EP (1) | EP1483484A2 (en) |
| JP (1) | JP2005516144A (en) |
| KR (1) | KR20040094419A (en) |
| CN (1) | CN100379951C (en) |
| WO (1) | WO2003064820A2 (en) |
Families Citing this family (35)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6932063B1 (en) | 2004-08-12 | 2005-08-23 | Eaton Corporation | Internal EGR cooler |
| US7555998B2 (en) * | 2005-12-01 | 2009-07-07 | Jacobs Vehicle Systems, Inc. | System and method for hydraulic valve actuation |
| US7594485B2 (en) | 2006-12-26 | 2009-09-29 | Caterpillar Inc. | Valve actuation system for internal combustion engine |
| JP2008248838A (en) * | 2007-03-30 | 2008-10-16 | Man Diesel As | Cam driven exhaust valve operation system for large size two cycle diesel engine |
| US8047166B2 (en) | 2008-04-02 | 2011-11-01 | General Electric Company | Electric valve actuation system |
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| US9038586B2 (en) | 2010-03-19 | 2015-05-26 | Eaton Corporation | Rocker assembly having improved durability |
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| US20190309663A9 (en) | 2008-07-22 | 2019-10-10 | Eaton Corporation | Development of a switching roller finger follower for cylinder deactivation in internal combustion engines |
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| US9581058B2 (en) | 2010-08-13 | 2017-02-28 | Eaton Corporation | Development of a switching roller finger follower for cylinder deactivation in internal combustion engines |
| US10415439B2 (en) | 2008-07-22 | 2019-09-17 | Eaton Intelligent Power Limited | Development of a switching roller finger follower for cylinder deactivation in internal combustion engines |
| US8985074B2 (en) | 2010-03-19 | 2015-03-24 | Eaton Corporation | Sensing and control of a variable valve actuation system |
| JP5015975B2 (en) * | 2009-02-04 | 2012-09-05 | エムエーエヌ・ディーゼル・アンド・ターボ・フィリアル・アフ・エムエーエヌ・ディーゼル・アンド・ターボ・エスイー・ティスクランド | Cam-driven exhaust valve actuation system for large two-cycle diesel engines |
| US11181013B2 (en) | 2009-07-22 | 2021-11-23 | Eaton Intelligent Power Limited | Cylinder head arrangement for variable valve actuation rocker arm assemblies |
| US9194261B2 (en) | 2011-03-18 | 2015-11-24 | Eaton Corporation | Custom VVA rocker arms for left hand and right hand orientations |
| US10087790B2 (en) | 2009-07-22 | 2018-10-02 | Eaton Corporation | Cylinder head arrangement for variable valve actuation rocker arm assemblies |
| IT1395581B1 (en) * | 2009-09-12 | 2012-10-16 | Gen Electric | DRIVING SYSTEM FOR ELECTRIC VALVE |
| US8146572B2 (en) * | 2009-12-21 | 2012-04-03 | Chrysler Group Llc | Cooled exhaust gas recirculation system with cylinder-level control |
| US9885258B2 (en) | 2010-03-19 | 2018-02-06 | Eaton Corporation | Latch interface for a valve actuating device |
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| CN107859565B (en) * | 2010-07-27 | 2021-01-05 | 雅各布斯车辆系统公司 | Combined engine braking and positive power engine lost motion valve actuation system |
| US9045120B2 (en) * | 2011-11-04 | 2015-06-02 | Robert Bosch Gmbh | Pedal oscillation suppression |
| USD750670S1 (en) | 2013-02-22 | 2016-03-01 | Eaton Corporation | Rocker arm |
| CN105121090A (en) | 2014-03-03 | 2015-12-02 | 伊顿公司 | Valve actuating device and method of making same |
| US9506382B2 (en) * | 2015-03-30 | 2016-11-29 | Caterpillar Inc. | Variable valve actuator |
| DE102016002051A1 (en) * | 2016-02-22 | 2017-08-24 | GM Global Technology Operations LLC (n. d. Gesetzen des Staates Delaware) | Motor vehicle drive train control |
| KR102375326B1 (en) * | 2017-08-03 | 2022-03-15 | 자콥스 비히클 시스템즈, 인코포레이티드. | Systems and Methods for Backflow Management and Sequencing of Valve Motion in Enhanced Engine Braking |
| DK179683B1 (en) * | 2017-09-04 | 2019-03-20 | MAN Energy Solutions | A large two-stroke compression-ignited internal combustion engine with dual fuel systems |
| CN111156064B (en) * | 2019-12-25 | 2022-05-10 | 浙江吉利新能源商用车集团有限公司 | Electric control valve structure and engine |
| ES2954608A1 (en) * | 2022-04-14 | 2023-11-23 | De Castro De La Fuente Jose Luis Bermudez | DUAL VALVE DRIVING METHOD AND VALVE DRIVING SYSTEM WHERE IT IS APPLIED (Machine-translation by Google Translate, not legally binding) |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4592319A (en) * | 1985-08-09 | 1986-06-03 | The Jacobs Manufacturing Company | Engine retarding method and apparatus |
| US5209453A (en) * | 1989-11-20 | 1993-05-11 | Nippondenso Co., Ltd. | Laminated type piezoelectric apparatus |
| US5339777A (en) * | 1993-08-16 | 1994-08-23 | Caterpillar Inc. | Electrohydraulic device for actuating a control element |
| US5509383A (en) * | 1991-02-20 | 1996-04-23 | Itt Automotive Europe Gmbh | Hydraulic unit |
| US5619965A (en) * | 1995-03-24 | 1997-04-15 | Diesel Engine Retarders, Inc. | Camless engines with compression release braking |
| US5967115A (en) * | 1994-10-07 | 1999-10-19 | Diesel Engine Retarders, Inc. | Electronic controls for compression release engine brakes |
| CN1323947A (en) * | 2000-05-17 | 2001-11-28 | 罗伯特·博施有限公司 | Light fuel oil directional jetting device for piston type internal combustion engine |
Family Cites Families (31)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US24500A (en) * | 1859-06-21 | Improvement in cultivators | ||
| US37765A (en) * | 1863-02-24 | Improvement in end-thrust bearings | ||
| US157623A (en) * | 1874-12-08 | Improvement in magazines for fire-arms | ||
| US10315A (en) * | 1853-12-13 | Sectional bedstead | ||
| US69853A (en) * | 1867-10-15 | smith | ||
| US106313A (en) * | 1870-08-16 | Improvement in compound for fertilizer | ||
| US3220392A (en) * | 1962-06-04 | 1965-11-30 | Clessie L Cummins | Vehicle engine braking and fuel control system |
| US4691520A (en) * | 1983-07-21 | 1987-09-08 | Osborne Lyle E | Hydraulic brake system |
| US4572114A (en) * | 1984-06-01 | 1986-02-25 | The Jacobs Manufacturing Company | Process and apparatus for compression release engine retarding producing two compression release events per cylinder per engine cycle |
| US4898078A (en) * | 1987-09-11 | 1990-02-06 | Deere & Company | Hydraulic system for a work vehicle |
| US4996957A (en) * | 1990-06-04 | 1991-03-05 | Jacobs Brake Technology Corporation | Control valve for a compression release engine retarder |
| US5012778A (en) * | 1990-09-21 | 1991-05-07 | Jacobs Brake Technology Corporation | Externally driven compression release retarder |
| AU2418992A (en) * | 1991-08-07 | 1993-03-02 | Microhydraulics, Inc | Active suspension system |
| US5501186A (en) * | 1993-07-27 | 1996-03-26 | Unisia Jecs Corporation | Engine valve control mechanism |
| DE4423657C2 (en) * | 1994-07-06 | 1997-10-02 | Daimler Benz Ag | Actuating device for an engine brake valve of an internal combustion engine |
| DE4424802C1 (en) * | 1994-07-14 | 1995-07-13 | Daimler Benz Ag | EGR system for four=stroke engine |
| DE4433258C1 (en) * | 1994-09-19 | 1996-03-07 | Daimler Benz Ag | Engine brake for a diesel engine |
| US5539777A (en) * | 1995-01-26 | 1996-07-23 | Motorola, Inc. | Method and apparatus for a DMT receiver having a data de-formatter coupled directly to a constellation decoder |
| US5758499A (en) * | 1995-03-03 | 1998-06-02 | Hitachi Construction Machinery Co., Ltd. | Hydraulic control system |
| DE19615739C2 (en) * | 1996-04-20 | 1998-04-09 | Daimler Benz Ag | Engine brake for a multi-cylinder diesel engine |
| US5787859A (en) * | 1997-02-03 | 1998-08-04 | Diesel Engine Retarders, Inc. | Method and apparatus to accomplish exhaust air recirculation during engine braking and/or exhaust gas recirculation during positive power operation of an internal combustion engine |
| US5809964A (en) * | 1997-02-03 | 1998-09-22 | Diesel Engine Retarders, Inc. | Method and apparatus to accomplish exhaust air recirculation during engine braking and/or exhaust gas recirculation during positive power operation of an internal combustion engine |
| DE19849914C1 (en) * | 1998-10-29 | 1999-11-04 | Daimler Chrysler Ag | Internal combustion engine with auxiliary inlet valve |
| US6584954B2 (en) * | 2000-03-31 | 2003-07-01 | Robb Janak | Use of external exhaust gas recirculation (“EGR”) to improve compression release braking and method for EGR valve and system cleaning |
| US6868824B2 (en) * | 2000-03-31 | 2005-03-22 | Diesel Engine Retarders, Inc. | System and method of gas recirculation in an internal combustion engine |
| AU2002225937A1 (en) * | 2000-12-04 | 2002-06-18 | Sturman Industries, Inc. | Hydraulic valve actuation systems and methods |
| US6446598B1 (en) * | 2000-12-11 | 2002-09-10 | Caterpillar Inc. | Compression brake actuation system and method |
| US20030010315A1 (en) * | 2001-07-10 | 2003-01-16 | Cornell Sean O. | Engine compression release brake and engine using same |
| US6568367B2 (en) * | 2001-07-31 | 2003-05-27 | Caterpillar Inc | Engine compression release brake system and method of operation |
| US20030037765A1 (en) * | 2001-08-24 | 2003-02-27 | Shafer Scott F. | Linear control valve for controlling a fuel injector and engine compression release brake actuator and engine using same |
| US6662705B2 (en) * | 2001-12-10 | 2003-12-16 | Caterpillar Inc | Electro-hydraulic valve control system and method |
-
2003
- 2003-01-30 WO PCT/US2003/002634 patent/WO2003064820A2/en active Application Filing
- 2003-01-30 EP EP03735064A patent/EP1483484A2/en not_active Withdrawn
- 2003-01-30 JP JP2003564398A patent/JP2005516144A/en active Pending
- 2003-01-30 KR KR10-2004-7011884A patent/KR20040094419A/en not_active Application Discontinuation
- 2003-01-30 CN CNB038075997A patent/CN100379951C/en not_active Expired - Fee Related
- 2003-01-30 US US10/353,717 patent/US20030140876A1/en not_active Abandoned
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4592319A (en) * | 1985-08-09 | 1986-06-03 | The Jacobs Manufacturing Company | Engine retarding method and apparatus |
| US5209453A (en) * | 1989-11-20 | 1993-05-11 | Nippondenso Co., Ltd. | Laminated type piezoelectric apparatus |
| US5509383A (en) * | 1991-02-20 | 1996-04-23 | Itt Automotive Europe Gmbh | Hydraulic unit |
| US5339777A (en) * | 1993-08-16 | 1994-08-23 | Caterpillar Inc. | Electrohydraulic device for actuating a control element |
| US5967115A (en) * | 1994-10-07 | 1999-10-19 | Diesel Engine Retarders, Inc. | Electronic controls for compression release engine brakes |
| US5619965A (en) * | 1995-03-24 | 1997-04-15 | Diesel Engine Retarders, Inc. | Camless engines with compression release braking |
| CN1323947A (en) * | 2000-05-17 | 2001-11-28 | 罗伯特·博施有限公司 | Light fuel oil directional jetting device for piston type internal combustion engine |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2003064820A2 (en) | 2003-08-07 |
| EP1483484A2 (en) | 2004-12-08 |
| CN1646795A (en) | 2005-07-27 |
| WO2003064820A3 (en) | 2003-10-16 |
| JP2005516144A (en) | 2005-06-02 |
| US20030140876A1 (en) | 2003-07-31 |
| KR20040094419A (en) | 2004-11-09 |
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