CN1160120A - Hydraulic valve drive - Google Patents
Hydraulic valve drive Download PDFInfo
- Publication number
- CN1160120A CN1160120A CN96122831A CN96122831A CN1160120A CN 1160120 A CN1160120 A CN 1160120A CN 96122831 A CN96122831 A CN 96122831A CN 96122831 A CN96122831 A CN 96122831A CN 1160120 A CN1160120 A CN 1160120A
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- CN
- China
- Prior art keywords
- hydraulic
- valve
- piston
- fluid
- cylinder
- 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.)
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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
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/26—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder
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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
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
- F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
- F01L2013/0089—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque with means for delaying valve closing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B3/00—Engines characterised by air compression and subsequent fuel addition
- F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F7/00—Casings, e.g. crankcases or frames
- F02F2007/0097—Casings, e.g. crankcases or frames for large diesel engines
Abstract
The invention relates to a hydraulic driving device 1 which is suitable for being used in the case that the engine cylinder is provided with valves and in particular to suitable for being used in the case that large diesel engine has gas inlet valves (11,11`) or discharge valves. Hydraulic synchronous pistons (121,122) have corresponding driving cavities (1210,1220) for each to-be-driven valves, the synchronous pistons drive the pistons (13,13`) of the to-be-driven corresponding valves (11,11`), so that the valve pistons (13,13`) performs synchronous movement and have same strokes. A buffer device 124 can buffer the return movement from the synchronous piston 12 to the original position. The hydraulic device 1 can compensate the difference of extension lengths (H,H`) of shaft rods (112,112`) of the valves (11,11`).
Description
The present invention relates to a kind of independent claims 1 preceding described hydraulic valve drive of thread.
Such valve actuator can be used for replacing has lever system, for example has the air inlet of motor and/or the mechanical type driving apparatus of the push rod on the outlet valve (pushrods).Mechanical actuation device be easy to cause this device mechanical part wearing and tearing and must carry out quite frequent readjusting.And hydraulic pressure installation can change the control time with quite simple method.This adjustment is strict especially and accurate for the motor with a more than air inlet and/or drain tap.
For example, for having two suction valves/or the cylinder of outlet valve, importantly, two valves can synchronous switches.In hydraulic valve drive, so-called valve piston (ValVe piston) generally all clashes into valve axostylus axostyle (shaft of the valve) mutually, because the valve axostylus axostyle is beared down on one to valve piston by spring force.
Particularly for big diesel engine (diesel engine), when cylinder head (cylindercover) goes up manufacturing valve base (valve seat), especially in the grinding process of valve and valve base, may occur some differences slightly, this species diversity can cause the difference on the valve axostylus axostyle extrusion.These differences may be in positive and negative several millimeters scope.Usually these differences are almost always between-1/+3mm.These deviations have the order of magnitude of the stone submersion (immersiondepth) of buffer (damper), and this may cause valve big departing from and difference to occur when closing.Improve machining accuracy and reduce the processing tolerance and may make moderate progress, but can not be considered to worthwhile owing to relate to manufacture cost to this.Even so, in the valve closing process, must reckon with and some irritating difference to occur.
The objective of the invention is to create a kind of hydraulic valve drive that can both synchronously open and close reliably can guaranteed at given condition lower inlet valve or outlet valve.
According to of the present invention, such hydraulic valve drive has following characteristics: it has synchronous piston, an actuator chamber is all arranged and be driven the hydraulically powered valve piston in chamber for each valve to be driven, can make that like this valve piston is synchronized with the movement, and for the motion that makes synchronous piston and valve return initial position obtain the buffering, also be provided with a damping device, in addition, also have a hydraulic pressure installation to compensate the difference of extrusion of the axostylus axostyle of two or more valves, above-mentioned valve is driven by fluid pressure drive device.All subordinates require item all to relate to further some favourable development of the present invention.Valve actuator can be driven by a kind of hydraulic piston pump with hydraulic plumbing system easily.
Can promote two or more valves synchronously according to fluid pressure drive device of the present invention.Difference at the sassafras resistance that rubs of each valve does not say that to influencing on this meaning synchronously the driving of each valve is irrelevant each other.The difference of each valve axostylus axostyle extrusion can be mended reward, and the change of each valve axostylus axostyle extrusion also can constantly be corrected in operating process.Damping device (dampingdevice) is guaranteed the synchronous piston of fluid pressure drive device, thereby valve too, contacts with valve base with damping mode.The impact stress of non-cushioned big pulsation can be avoided.This has just increased the working life of valve and valve base.In addition, so-called depression (pitting), the hollow that on the sealing surfaces of valve, forms just, also available damping device prevents.But fluid pressure drive device can also make the seal process of valve temporarily be delayed in certain limit.
Should be noted that except the hydraulic piston pump of being addressed other hydraulic pressure source also is applicable to hydraulic valve drive.For example, the hydraulic pressure high-pressure system that is named as " common rail system (common rail system) " is also very suitable, high-pressure liquid wherein is to be fed to fluid pressure drive device by solenoid electric valve by high-pressure liquid system, from fluid pressure drive device the hydraulic fluid foldback is returned the reservoir of high-pressure liquid system again.Use " common rail system " also to be convenient to damping device is installed in front end, i.e. an end of the vary in diameter of synchronous piston is so that slow down impact to cylinder head.In the different structure form of " common rail system ", can on the perforate direction of valve, a damping device be installed to valve piston.
To make a more detailed description to the present invention according to schematic representation below, these schematic representation exemplary embodiments more of the present invention that drawn.Now that their brief introductions is as follows.
Fig. 1 is the cross-section schematic representation of the fluid pressure drive device of two valves of driving of the present invention.
Fig. 2 is the function curve of the relation of expression valve location of four stroke engine and crankshaft angles.
Fig. 3 is of the present invention for operating the hydraulic piston pump with hydraulic plumbing system that fluid pressure drive device is used.
Fig. 4 illustrates the piston position (following curve) of valve location (top curve) and reciprocating pump with the respective function relation of crankshaft angles and eccentric wheel angle and for the driven pump operation, the possibility of valve closing process lag.
Fig. 1 has drawn one by of the present invention, for example two of diesel engine air intake valves 11,11 ' fluid pressure drive device.Valve base 111 and 111 ' be that processing is on cylinder head 10 (part of only having drawn).Two axostylus axostyles 112 and 112 ' all respectively have a corresponding flange (collar) 113 and 113 ', a corresponding spring 115 and 115 ' head on is all arranged on each flange.Valve spring 115 and 115 ' the other end be supported on the cylinder head 10.
Valve 11 and 11 ' fluid pressure drive device also have a synchronous piston 12, this piston is made into a stepped shape piston (stepped piston) herein.The piston section 121 and 122 of different-diameter is motion in corresponding chamber thorax 1210 and 1220 respectively.It is when making piston motion that synchronous piston is made the stepped shape form, and the Volume Changes that produces in each chamber thorax 1210 and 1220 always equates.As long as the flow of pressurized physical efficiency flow back into hydraulic piston pump 31 from cylinder space 120 through pipelines 1200, then synchronous piston 121 will be pushed initial position to by valve spring 115,115 by valve piston 13,13 ' and their hydraulic pressure connecting line.Can not arrive initial position again owing to fluid loss (gap) probably, still, 1211 on the spring that is installed in the chamber thorax 1210 still can back into synchronous piston 12 on its initial position fully.
Too fierce in order to prevent 123 impacts of 12 pairs of cylinder bottom of synchronous piston, the end of the cylinder bottom of synchronous piston 12 and synchronous piston 12 is made into such shape, makes them can form a buffer 124 jointly.This buffer 124 hinders hydraulic oil backflow inlet pipe line 1200, thereby has reduced the capacity of reflux of unit time.
The buffering that synchronous piston 12 impacts for cylinder bottom 123 also causes valve 11 and 11 ' to the buffering of valve base 111 and 111 ' impact.
If two valve pistons 13,13 ' have equal size and synchronous piston 12 corresponding active areas 125,125 ' size also equate, when then synchronous piston moves a given stroke (when movingover a given path), two valve pistons 13,13 ' mobile distance also equates.Valve axostylus axostyle 112 and 112 ' also can same like this moved further.With regard to the meaning of this paper, " synchronously " is to be used for expression " side by side and with the same manner moving same distance ".
Certainly, the active area 125,125 of synchronous piston ' other synchronous piston that differs in size and the configuration of valve piston also are possible.Only importantly, chamber thorax 1210 of synchronous piston 12 or 1220 mobile volume should with respective valves piston 13,13 ' in respective cylinder 130,130 ' mobile volume matched, so that corresponding valve piston 13,13 ', thereby corresponding valve 11,11 ' also have identical stroke (stroke).
In order to compensate possible the loss cause owing to leaking, can be by two supply lines 114 and 114 ' to hydraulic pipe line supply hydraulic fluid.One-way valve 1141 and 1141 ' be used for the preventing backflow of hydraulic oil.In any case, the hydraulic oil feeding system is also had following consequence: valve piston all the time all with valve axostylus axostyle 112,112 ' end contact and with valve axostylus axostyle 112,112 ' extrusion (distance) H from the valve shaft boom end to cylinder head, any difference that H ' may exist is irrelevant.
Other possibilities of the loss of the oil that compensation is caused by leakage are, for example introduce the oil of a breakage by an aperture in the synchronous piston 12, and this aperture is connected pressure chamber 120 and chamber thorax 1210,1220.In order to make the influence between the thorax of chamber enough little, some throttle orifices (choke aperture) are set in the passage between them.In a different device, these are used for supplying the hole that hydraulic oil that compensation leaks uses can lead to each chamber thorax through shell.
The drawn relation curve of valve opening and closing and crank angle in the four-cycle diesel engine of Fig. 2.When crank angle was greatly between 180 ° and 250 °, valve was opened.After valve closing, valve 11,11 ' still remain static, or closed condition R are opened once more up to it.Its phase of closing is to be between 470 ° and 540 ° at crank angle like this.If valve 11,11 ' would be that hydraulic oil just replenishes into system via supply pipeline when remaining static R.
Hydraulic piston pump with pipe-line system 3 schematically is drawn in Fig. 3. in.It can be used for driving the synchronous piston of fluid pressure drive device for example shown in Figure 1.This device comes down to be made up of the reciprocating pump 31 of a delivery hydraulic pressure oil.Main line 32 with one-way valve 321 leads to drive unit from this reciprocating pump, as shown in Figure 1.
By-pass line 33 is connected across the both sides of one-way valve 321, hydraulic oil is entered the cylinder space 310 of reciprocating pump 31.By-pass line 34 also is connected across the both sides of one-way valve 321, hydraulic oil is entered main line 32 from two ends.One selector valve (switchable valve) is housed in bypass 34, and available, for example compressed air line 342 is with its commutation.
Selector valve 341 is the selector valve of hydraulic type, electromagnetic type or other form also.If the one-way valve in the main line 321 may get clogged, can enable by-pass line 34 when open mode.
Supply pipeline 35 is used to provide the hydraulic fluid that loses owing to leakage loss in the hydraulic system.This pipeline comprises an one-way valve 351.Unnecessary hydraulic oil can be sent this supply line back to by bypass 352.The piston of reciprocating pump 31 can by, for example the eccentric wheel (not shown) drives.
Effect and function mode with reciprocating pump of pipe-line system 3 are illustrated in down.
Suppose that the pilot pressure in the pilot line 342 is opened.Following situation will take place in the exhaust stroke (delivery stroke) of pump piston 311: 3512 by piston 311 sealing after, hydraulic fluid then will be sent to fluid pressure drive device to drive valve via path 33,32,34.Afterwards, the connection mouth 332 of bypass 33 is closed, and hydraulic fluid continues to flow through 32,34.
In the downward stroke of pump piston 311 following situation will take place: main line 32 is by closed check valve.The piston 311 that bypass 33 still is blocked hole 332 seals.But bypass 34 but is that the closing movement of that opening and driven synchronous piston is to follow after the closing movement of piston 311.This motion is illustrated in the top of Fig. 4 with solid line 41.
Suppose that the pilot pressure in the pilot line 342 is shut, this means that bypass 34 is closed.Following situation will appear in the exhaust stroke at pump piston 311: after piston 311 was with 3512 sealings, then hydraulic fluid was sent to fluid pressure drive device to drive valve via path 33,32.Afterwards, the connection mouth 332 of bypass 33 is closed, and hydraulic oil then can flow through the path in 32 continuation.
Following situation will occur in the downward stroke of pump piston 311: main road 32 is by closed check valve.Bypass 33 also is plugged the piston 311 in hole 332 and closes.Bypass 34 is also closed.As long as the connection mouth 332 of bypass 33 is closed by piston 311, driven Hydraulic Synchronizing piston 121 is not just followed piston 311 motions.Like this, when piston 311 moved downward, initial, valve (Fig. 1) was not opened by the motion of synchronous piston 12.The curve with dashed lines 42 that closes closed procedure is shown in the top of Fig. 4.
The increase of system bulk is compensated (equalised) by the hydraulic fluid that is provided by supply pipeline 35.Usually, very little in supply line, for example the low pressure of 3-10 crust (bar) is just enough.In case piston 311 begins to open hole 332, then reverse flow (revese f1ow) has just begun via 33.The valve closing motion also begins now thereupon, and is controlled by moving downward of piston 311.Near the following turning point of piston 311, hole 3512 just is opened.Closing movement (closure motion) will continue and " not having control " now.For fear of fierce impact to valve, the buffer 124 on the synchronous piston at this moment just work (Fig. 1).
The closing movement of valve is represented with dotted line 42 in Fig. 4.Among the figure, curve 40 has been expressed by the stroke procedure of the piston 311 of device shown in Figure 3 (the course of thestroke) below Fig. 4.Point 44 on the curve 40 below is equivalent to such position of piston 311, and on this position, piston 311 has just been decontroled hole 332 when reversing motion, makes hydraulic oil to reflux.This curve 40 the drawn movement process of piston 311 and the function relation of crank angle.If valve 11,11 ' the pass closed procedure be before this position 44 of piston arrives the beginning, then the backflow of hydraulic oil realizes with regard to the available method of opening valve 341.
Fluid pressure drive device 1 is suitable for having two or more valves 11,11 on the cylinder ' situation, especially be suitable for the air intake valve 11,11 of big diesel engine ' or the situation of drain tap.Hydraulic Synchronizing piston 12,122 all has an actuator chamber 1210,1220 for each valve to be driven, they drive respectively a corresponding valve 11,11 to be driven ' piston 13,13 ', make valve piston 13,13 ' synchronously move and have same stroke.The drawback movement that damping device 124 makes synchronous piston 12 return initial position obtains buffering.Adopt hydraulic pressure installation 1 can make valve 11,11 ' axostylus axostyle 112,112 ' extrusion H, the difference of H ' is compensated.
Claims (10)
1. be used for plural cylinder valve, the fluid pressure drive device of the air intake valve of especially big diesel engine (1), it is characterized in that: it has synchronous piston (12,122), for each valve to be driven 11,11 ' all have an actuator chamber (1210,1220) and are driven the hydraulically powered valve piston in chamber (13,13 '), can make valve piston (13 like this, 13 ') be synchronized with the movement, and for the motion that makes synchronous piston (12) and valve (11,11 ') return initial position obtain the buffering, also be provided with a damping device (124), in addition, also have a hydraulic pressure installation (1) to compensate the axostylus axostyle (112 of two or more valves (11,11 '), 112 ') extrusion (H, H) difference, above-mentioned valve (11,11 ') is driven by fluid pressure drive device (1).
2. according to the described fluid pressure drive device of claim 1 (1), it is characterized in that: the damping mechanism that is used to cushion the return movement of synchronous piston (12) has the device (124) of the liquid stream cross section of a hydraulic driving fluid that reduces to return.
3. according to the described fluid pressure drive device of claim 2 (1), it is characterized in that: the device (124) that reduces liquid stream cross section is to be made of the driving side (drive side) of synchronous piston (121) and the shape of piston-cylinder wall.
4. according to each described fluid pressure drive device (1) among the claim 1-3, it is characterized in that: compensation extrusion (H, the hydraulic pressure installation of difference H ') (hydraulic device) has the feeding means (114,114 ') (feeding device) of a hydraulic fluid.
5. according to each described fluid pressure drive device (1) of claim 1-4, it is characterized in that: it has one makes the reciprocating driven plunger of synchronous piston, also has a hydraulic switch device (3), it can be used to postpone the motion that synchronous piston (12) returns initial position, this delay is the motion of returning its initial position with driven plunger (311), thereby is back to hydraulic fluid just that the motion of the cylinder space (310) of driven plunger (311) compares.
6. according to the described hydraulic piston pump (31) that is used for the primer fluid hydraulic driver of one of claim 1-5, it is characterized in that: it has
A pipe-line system of being made up of hydraulic pipe line (32,33,34,35,352), these pipelines are used between reciprocating pump (31) and drive unit delivering hydraulic fluid back and forth,
Main line (32), this one-way valve with one-way valve (321) can prevent fluid flow back to the cylinder of pump (310) and
Bypass (34) with change-over valve (341) of one-way valve (321) both sides that are connected across main line (32) in addition, also has
Supply and return pipeline (33) for one second, it also is connected across one-way valve (321) both sides of main line (32), and by the connection mouth on the cylinder wall of hydraulic piston pump (31) (332) hydraulic oil is entered cylinder space (310).
7. according to the hydraulic piston pump (31) of the described promotion fluid pressure drive device of one of claim 1-5, it is characterized in that: it has:
One is used between reciprocating pump (31) and drive unit the hydraulic plumbing system of delivering hydraulic fluid (32,33,35,352) back and forth,
Main line (32) with an one-way valve (321), one-way valve can remain on open mode selectively, simultaneously it can prevent fluid reflux to the pump cylinder (310) that is in open state (in unblocked state) and
Second supply and a return pipeline (33) that is connected across one-way valve (321) both sides on the main line (32), it enters fluid by the connection mouth on the cylinder wall of hydraulic piston pump (31) (332) cylinder space (310) of reciprocating pump (31).
8. according to claim 6 or 7 described hydraulic piston pumps (31), it is characterized in that: it has:
A feeding means (35,352), it is used for a hydraulic fluid with taking-up in the liquid receiver with to wherein entering.
A feed line (feeding line) (35), be equipped with on it one prevent hydraulic fluid be back to the one-way valve of liquid receiver (reservoir) (351) and
Supply and return pipeline (352), it is in parallel with the one-way valve (351) on the feed line (35), and near rollback point down, it drains into fluid by interface (3512) cylinder (310,3512) of reciprocating pump (311).
9. according to the described hydraulic piston pump of claim 8 (311), it is characterized in that: feed line (35) is discharged hydraulic fluid inlet casing space (310) near last rollback point, supply and return pipeline (352,3512) they are near the rollback point fluid to be entered cylinder space (310) down, and
Second of fluid pressure drive device is supplied with and return pipeline (33) is last, on the height between the following rollback point hydraulic fluid is entered cylinder space (310).
10. according to the described big diesel engine of one of claim 1-9, it is characterized in that: the drive unit (1) that all has a cylinder intake valve (11,11 ') or drain tap.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| EP95810620A EP0767295B1 (en) | 1995-10-03 | 1995-10-03 | Hydraulic valve |
| EP95810620.5 | 1995-10-03 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1160120A true CN1160120A (en) | 1997-09-24 |
| CN1088145C CN1088145C (en) | 2002-07-24 |
Family
ID=8221802
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN96122831A Expired - Fee Related CN1088145C (en) | 1995-10-03 | 1996-09-28 | Hydraulic valve drive |
Country Status (8)
| Country | Link |
|---|---|
| EP (1) | EP0767295B1 (en) |
| JP (1) | JP3986585B2 (en) |
| KR (1) | KR100403693B1 (en) |
| CN (1) | CN1088145C (en) |
| DE (1) | DE59507966D1 (en) |
| DK (1) | DK0767295T3 (en) |
| FI (1) | FI107751B (en) |
| NO (1) | NO311188B1 (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2005038201A1 (en) * | 2003-10-13 | 2005-04-28 | Ji Fang | A hydraulic actuating mechanism for inlet and exhaust |
| CN101994536A (en) * | 2009-08-13 | 2011-03-30 | 万国引擎知识产权有限责任公司 | Intake valve closing hydraulic adjuster |
| CN101660435B (en) * | 2009-09-14 | 2012-10-24 | 奇瑞汽车股份有限公司 | Hydraulic camshaft and hydraulic control system thereof |
| CN105814320A (en) * | 2013-10-16 | 2016-07-27 | 弗瑞瓦勒夫股份公司 | Combustion engine and gas handling system for pneumatic operation of a valve actuator |
Families Citing this family (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2758857A1 (en) * | 1997-01-27 | 1998-07-31 | Aisin Seiki | IC engine valve actuating mechanism |
| EP1114918B1 (en) * | 2000-01-06 | 2004-08-11 | Wärtsilä Schweiz AG | Valve arrangement for an internal combustion engine and driving method |
| DK176119B1 (en) * | 2000-02-16 | 2006-09-04 | Man B & W Diesel As | Hydraulic actuation system for an exhaust valve in an internal combustion engine |
| DE10124869C2 (en) * | 2001-05-22 | 2003-06-26 | Caterpillar Motoren Gmbh & Co | Hydraulic control device for equivalent engine valves of a diesel engine |
| DE10140528A1 (en) * | 2001-08-17 | 2003-02-27 | Bosch Gmbh Robert | Device for controlling gas exchange valves |
| JP2004084670A (en) * | 2002-08-28 | 2004-03-18 | Man B & W Diesel As | Valve operated with hydraulic pressure |
| DE10239747A1 (en) * | 2002-08-29 | 2004-03-11 | Robert Bosch Gmbh | Hydraulic valve actuator for actuating a gas exchange valve |
| US8365690B2 (en) | 2006-07-04 | 2013-02-05 | Renault Trucks | Hydraulically operated valve control system and internal combustion engine comprising such a system |
| CN101936199B (en) * | 2010-09-20 | 2012-10-03 | 武央 | Hydraulic transmission air distribution system of motorcar engine |
| GB2552499B (en) * | 2016-07-26 | 2019-11-27 | Jaguar Land Rover Ltd | Apparatus for controlling valves using a hydraulic control system |
| GB2553120B (en) * | 2016-08-24 | 2019-12-25 | Jaguar Land Rover Ltd | Variable valve lift system with a diffusing system |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3807699A1 (en) * | 1988-03-09 | 1989-09-21 | Audi Ag | Adjustable hydraulic valve timing gear |
| US4887562A (en) * | 1988-09-28 | 1989-12-19 | Siemens-Bendix Automotive Electronics L.P. | Modular, self-contained hydraulic valve timing systems for internal combustion engines |
| DE69218971T2 (en) * | 1991-06-24 | 1997-07-24 | Ford Werke Ag | Hydraulic valve control device for an internal combustion engine |
| JP3121011B2 (en) * | 1991-07-12 | 2000-12-25 | キャタピラー インコーポレイテッド | Recovery type engine valve system and method of operating the same |
-
1995
- 1995-10-03 EP EP95810620A patent/EP0767295B1/en not_active Expired - Lifetime
- 1995-10-03 DK DK95810620T patent/DK0767295T3/en active
- 1995-10-03 DE DE59507966T patent/DE59507966D1/en not_active Expired - Lifetime
-
1996
- 1996-07-29 JP JP19920596A patent/JP3986585B2/en not_active Expired - Fee Related
- 1996-09-06 KR KR1019960038663A patent/KR100403693B1/en not_active IP Right Cessation
- 1996-09-28 CN CN96122831A patent/CN1088145C/en not_active Expired - Fee Related
- 1996-10-02 NO NO19964175A patent/NO311188B1/en not_active IP Right Cessation
- 1996-10-02 FI FI963945A patent/FI107751B/en not_active IP Right Cessation
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2005038201A1 (en) * | 2003-10-13 | 2005-04-28 | Ji Fang | A hydraulic actuating mechanism for inlet and exhaust |
| CN101994536A (en) * | 2009-08-13 | 2011-03-30 | 万国引擎知识产权有限责任公司 | Intake valve closing hydraulic adjuster |
| CN101994536B (en) * | 2009-08-13 | 2012-12-12 | 万国引擎知识产权有限责任公司 | Intake valve closing hydraulic adjuster |
| CN101660435B (en) * | 2009-09-14 | 2012-10-24 | 奇瑞汽车股份有限公司 | Hydraulic camshaft and hydraulic control system thereof |
| CN105814320A (en) * | 2013-10-16 | 2016-07-27 | 弗瑞瓦勒夫股份公司 | Combustion engine and gas handling system for pneumatic operation of a valve actuator |
| CN105814320B (en) * | 2013-10-16 | 2017-09-26 | 弗瑞瓦勒夫股份公司 | Internal combustion engine and the pneumatically-operated gas handling system for valve actuator |
Also Published As
| Publication number | Publication date |
|---|---|
| DE59507966D1 (en) | 2000-04-13 |
| DK0767295T3 (en) | 2000-06-05 |
| FI963945A (en) | 1997-04-04 |
| FI963945A0 (en) | 1996-10-02 |
| KR100403693B1 (en) | 2004-01-28 |
| NO311188B1 (en) | 2001-10-22 |
| EP0767295A1 (en) | 1997-04-09 |
| KR970021645A (en) | 1997-05-28 |
| NO964175D0 (en) | 1996-10-02 |
| EP0767295B1 (en) | 2000-03-08 |
| FI107751B (en) | 2001-09-28 |
| JPH09100706A (en) | 1997-04-15 |
| NO964175L (en) | 1997-04-04 |
| CN1088145C (en) | 2002-07-24 |
| JP3986585B2 (en) | 2007-10-03 |
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