CN105422203A - Valve mechanism system with hydraulic lash adjuster and exhaust brake - Google Patents
Valve mechanism system with hydraulic lash adjuster and exhaust brake Download PDFInfo
- Publication number
- CN105422203A CN105422203A CN201510513920.8A CN201510513920A CN105422203A CN 105422203 A CN105422203 A CN 105422203A CN 201510513920 A CN201510513920 A CN 201510513920A CN 105422203 A CN105422203 A CN 105422203A
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- CN
- China
- Prior art keywords
- rocker arm
- valve
- exhaust valve
- lash adjuster
- assembly
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- 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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Abstract
The invention relates to a valve mechanism system with a hydraulic lash adjuster and an exhaust brake. In the brake mode of an engine, an operable exhaust valve rocker arm assembly comprises a rocker arm shaft, a rocker arm, a valve cross arm, a discharge valve, a hydraulic lash adjuster and an elastic tank box. The rocker arm shaft defines a pressurized oil supply pipeline. The rocker arm receives the rocker arm shaft and is configured to rotate about the rocker arm shaft. The rocker arm is provided with an oil supply passage defined therein. The valve cross arm is engaged with a first exhaust valve and a second exhaust valve. The discharge valve is provided with a piston capable of moving between a retractable position and an extendable position. The hydraulic lash adjuster assembly is arranged on the rocker arm and comprises a first plunger that moves between a first position and a second position. At the first position, the first plunger extends rigidly to be cooperatively engaged with the valve cross arm.
Description
The cross reference of related application
This application claims on June 26th, 2014 submit to U.S. Patent application No.62/017,321 and on July 15th, 2014 submit to U.S. Patent application No.62/024, the preference of 633.The content of above-mentioned patent application is incorporated to herein by reference.
Technical field
Present invention relates in general to a kind ofly be used in the rocker arm assembly in valve mechanism (valvetrain) assembly with exhaust brake and the rocker arm assembly relating more specifically to that one has the rocking arm being integrated with hydraulic pressure capsule (hydraulic bag, hydrauliccapsule) and hydraulic lash adjuster.
Background technique
Engine braking can be used for hindering in-engine power to slow down finally to make vehicle.In the typical valve train assembly used together with engine brake, exhaust valve is activated by the rocking arm being engaged described exhaust valve by valve cross arm (valvebridge).Rocking arm in response to rotate camshaft on cam and swing and under be pressed on valve cross arm, be pressed under this valve cross arm self on exhaust valve to open it.
A kind of form of engine braking comprises exhaust brake.Exhaust brake can provided the auxiliary brake relatively large-scale vehicle (such as truck) of power is used as except wheel brake by heavy or medium duty diesel machine.Exhaust brake generally includes the piston optionally extending to total travel.In total travel, piston can maintain exhaust valve and open fixed amount in whole cycle of engine.Therefore, mechanical clearance can be produced in valve mechanism.In many cases, this gap may not be compatible with general hydraulic lash adjuster (HLA).Hydraulic lash adjuster can also be arranged in valve train assembly to remove any gap or gap that are formed between each parts in valve train assembly.Once exhaust brake stop using, mechanical clearance can allow HLA adversely pump liter, stop exhaust valve closing. when exhaust valve do not take one's seat/in place time, valve will transmit the firing pressure of valve mechanism under the adverse effect of valve mechanism parts.In extreme circumstances, the air in cylinder arrives be prevented from the suitable compression pressure needed for burning.
Background technique provided herein describes normally in order to illustrate content of the present invention.Both impliedly do not admitted the work done the present inventor described by background technique part ambiguously yet and may can't be for prior art of the present invention as each side of the specification of prior art when submit applications.
Summary of the invention
A kind of exhaust valve rocker arm assembly that can operate in engine braking (EB) pattern comprises pitman arm shaft, rocking arm, valve cross arm, bleeder valve/gas bleeder valve, hydraulic lash adjuster and elasticity capsule.Pitman arm shaft defines compressed oil supply line.Rocking arm is received pitman arm shaft and is configured to rotate around pitman arm shaft.Rocking arm has the oil supply gallery be limited to wherein.Valve cross arm engages first row valve and second row valve.Bleeder valve has can the piston of movement between retracted position and extended position.Hydraulic lash adjuster arrangement of components is on rocking arm and comprise can the first plunger body of movement between the first position and the second position. and in primary importance, the first plunger body extends rigidly and engages collaboratively for valve cross arm.Elasticity capsule to be arranged in rocking arm and hydraulic lash adjuster is biased toward valve cross arm.
According to further feature, hydraulic lash adjuster assembly is received by the hole be limited on rocking arm at least in part.Elasticity capsule is received by the hole be limited on rocking arm at least in part.Hydraulic lash adjuster assembly also comprises the second plunger body received by the first plunger body at least in part.Second plunger body defines valve seat.
In further feature, hydraulic lash adjuster comprises the check ball assembly between the first and second plunger bodies.Check ball assembly comprises the first biasing member, the second biasing member, retainer (cage) and check ball.The piston structure of bleeder valve becomes to extend to the total travel keeping first row valve to open predetermined spacing.In one example, predetermined spacing is 2 millimeters.Elasticity capsule comprises the idle running spring providing the first power.Hydraulic lash adjuster assembly provides the second power.First power is greater than the second power. and the first plunger body has the first closed end defining the first connector be received in the first socket, and described first socket acts on valve cross arm. and elasticity capsule provides the stroke of the half of the correspondence course equaling piston.
Accompanying drawing explanation
By describe in detail and accompanying drawing by comprehend the present invention, wherein:
Fig. 1 is integrated with the partial side view of the exhaust valve rocker arm assembly of hydraulic pressure capsule and hydraulic lash adjuster according to an example constructions of the present invention for exhaust brake;
Fig. 2 is the legend listing the variable used in whole drawing and description;
Fig. 3 shows the form of driving mode, engine braking modes and transient mode, and each pattern provides idle running and dry gap width;
Fig. 4 A-4C shows the valve lift diagram of driving mode, engine braking modes and transient mode for confirming in Fig. 3;
Fig. 5 shows for the driving mode of Fig. 3, engine braking modes and the engine braking valve of transient mode and the plotted curve of servo valve;
Fig. 6 shows the exhaust brake keeping exhaust valve to open in whole four stroke engine cycle period;
Fig. 7 is integrated with the partial side view of the exhaust valve rocker arm assembly of hydraulic pressure capsule and hydraulic lash adjuster according to another example constructions of the present invention for exhaust brake;
Fig. 8 shows the functional principal of the exhaust brake according to each example of the present invention; And
Fig. 9 shows the key point of exhaust brake.
Embodiment
First reference Fig. 1, is illustrated according to the part valve train assembly of an example constructions of the present invention and overall by reference number 10 represents.Part valve train assembly 10 uses engine braking.Part valve train assembly 10 can comprise the rocker arm assembly 20 with a series of inlet valve rocker assembly (not specifically illustrating) and a series of exhaust valve rocker arm assembly 30.Pitman arm shaft 34 is received by shearer ranging arm (not specifically illustrating).As understood from following discussion, pitman arm shaft 34 is with rocker arm assembly 20 and more specifically cooperate, during engine braking, oil is sent to exhaust valve rocker arm assembly 30 with exhaust valve rocker arm assembly 30.
Present cardinal principle is with reference to Fig. 1-5, and exhaust valve rocker arm assembly 30 can generally include Rocker arm 40, valve cross arm 42, elasticity capsule 44 and hydraulic lash adjuster (HLA) assembly 46.Valve cross arm 42 engages the first and second exhaust valves 50 and 52. push rod (not specifically illustrating) of being associated with the cylinder (not shown) of motor and moves up and down based on the lifting curve of camshaft (not shown).The arm that the moving upward of push rod can promote to be fixed to Rocker arm 40 and make Rocker arm 40 rotate clockwise around pitman arm shaft 34 subsequently. pitman arm shaft 34 can limit compressed oil supply line 54. Rocker arm 40 can limit the rocking arm pipeline 56. being configured to oil is passed to HLA assembly 46 from the compressed oil supply line 54 of pitman arm shaft 34
HLA assembly 46 can comprise the plunger assembly 60 comprising the first plunger body 62 and the second plunger body 64.Second plunger body 64 can partly be received by the first plunger body 62.Plunger assembly 60 is received by the first hole 66 be limited in Rocker arm 40. and the first plunger body 62 can have the first closed end defining the first connector 70 be received in the first socket 72, and described first socket acts on valve cross arm 42.Second plunger body 64 has the opening defining valve seat 76.Check ball assembly 80 can be arranged between the first and second plunger bodies 62 and 64.Check ball assembly 80 can comprise the first biasing member, retainer, the second biasing member and check ball.
Exhaust brake 100 can comprise hydraulic piston 102. hydraulic piston 102 and be configured to move between extended position and retracted position.When needs braking function, hydraulic piston 102 extends to stroke X
b.At stroke X
b, valve 50 moves opens identical spacing. under these circumstances, be configured to do not have the exhaust valve rocker arm assembly 30 of elasticity capsule 44 to cause the pump liter of HLA46, close after engine braking is stopped using to stop valve 50.
The Rocker arm 40 of exhaust valve rocker arm assembly 30 is integrated with elasticity capsule 44, and it provides the stroke L of the restriction of the half of the stroke equaling piston 102
m.As shown in Figure 2, L
m=1/2X
b.Opening slope and closing slope of valve lift curve extends identical amount L
m.In normal working conditions, system always runs idle running stroke L
m.Maximum valve lift is by acting on laterostigmatal maximum cam lift and reduction L
mobtain.
When enabling exhaust brake 100, hydraulic piston 102 stretches out, and makes to keep exhaust valve 50 to open spacing X
b.1/2X is created in valve cross arm 42 with the contacting part of Rocker arm 40
bmechanical clearance.HLA46 will extend 1/2X
b, mechanical clearance is decreased to 0 the most at last.
When no longer needing exhaust brake 100, hydraulic piston 102 will be pushed back and valve 50 will be closed.The power of power Fs ratio (acting on the valve 50) valve spring of the spring 120 in elasticity capsule 44 is much smaller, and elasticity capsule 44 will be forced to and shrink to make L completely
mmove to zero, that is, HLA46 extends 1/2X now
badditional travel. in a state in which, the first valve lift under the driving mode after engine braking is stopped using will be applied to laterostigmatal whole cam lift, i.e. present L
m=0.The idle running spring 120 of elasticity capsule 44 is designed to always produce the power Fs higher than the producible power of HLA46.For this reason, when elasticity capsule 44 shrinks completely, when cam is on basic circle, HLA46 applies can promote the power Fs that HLA46 makes it contraction.This state will occur, until elasticity capsule 44 extends to its 1/2X completely in particular cycle number of times after engine braking is stopped using
brange and HLA46 by contraction phase with amount to arrive its normally dry interstitial site.
In some cases, the lift that the exhaust lift after engine braking is just stopped using may be compared to cycle-index the best of specific engines wants high and length.Therefore engine performance will be affected.But this state can be accepted by user, therefore system disclosed herein can be avoided transmitting and anyly uncontrolledly be loaded to relevant to the incomplete valve-closing after engine braking is stopped using and relevant with the extension of HLA46 valve mechanism.
Referring now to Fig. 6, be illustrated according to the exhaust brake configuration of an example and totally represent with reference character 200.Exhaust brake configuration 200 comprises and extends to total travel to make to keep exhaust valve 204 in the circulation of whole four stroke engine, one in 206 hydraulic piston 202 opening very little constant spacing (such as 2mm).Because exhaust brake configuration 200 only keeps exhaust valve 204,206 to open fixing spacing, it can be designed so that it does not place any load on camshaft and most of overhead parts.This configuration is particularly useful for more small-sized diesel engine.
Referring now to Fig. 7, the portion discharge door rocker arm assembly for the exhaust brake of another example according to the present invention is illustrated and entirety by reference number 230 represents.Unless other description, exhaust valve rocker arm assembly 230 can be configured to exhaust valve rocker arm assembly 30 as above similar.Exhaust valve rocker arm assembly 230 can comprise rocking arm 240, valve cross arm (not illustrating particularly) generally, idle running capsule 244 and hydraulic lash adjuster (HLA) assembly 246.Rocking arm 240 can limit the rocking arm pipeline 256 being configured to oil is passed to HLA assembly 246 from compressed oil supply line (reference character 54 see Fig. 1).
HLA assembly 246 can comprise plunger assembly 260. second plunger body 264 comprising the first plunger body 262 and the second plunger body 264 and can partly be received by the first plunger body 262. and plunger assembly 260 is received by the first hole 266 be limited in rocking arm 240. and the first plunger body 262 can have the first closed end defining the first connector 270 be received in the first socket 272, and described first socket 272 acts on valve cross arm.Second plunger body 264 has the opening defining valve seat 276.Check ball assembly 280 can be arranged between the first and second plunger bodies 262 and 264.Check ball assembly 280 can comprise the first biasing member 282, retainer 284, second biasing member 286 and check ball 290.
In one example, idle running capsule 244 can have the total kilometres (such as seeing 102 of 202, Fig. 1 of Fig. 6) of the stroke of the exhaust brake piston of 1/2nd.Idle running capsule 244 can comprise biasing member 258. biasing member 258 can have the spring force larger than the maximum axial force of HLA assembly 246.As explained further, the maximum axial force of HLA assembly 246 can be the summation that the power of the second biasing member 286 adds the maximum engine oil pressure be applied on the first plunger body 262. in a kind of configuration, cam profile can compensate the idle running stroke of 1mm by the valve inclined-plane extended.
Fig. 8 shows the working principle of exhaust brake.In traveling mode 3 00A (position 1), at basic circle place, HLA assembly 246 is in nominal position.Idle running capsule 244 stretches out completely.In traveling mode 3 00B (position 2), during valve event, HLA assembly 246 is in nominal position and idle running capsule 244 is fully compressed. and in engine braking modes 300C (position 3), HLA assembly 246 extends 1/2nd of brake piston.Idle running capsule 244 is compressed and is extended on basic circle under valve event.In from engine braking modes to the transient mode 300D of driving mode (4 to position, position 5), produce multiple action.After engine brake just cuts off, HLA assembly 246 extends 1/2nd of brake piston.Idle running capsule 244 is fully compressed.Because do not have idle running at this point, maximum lift will be higher.Between transient period, this idle running by one circulation then one cyclically promote HLA downwards.Therefore idle running capsule 244 will extend upwardly to its maximum elongation.Therefore maximum lift will reduce and idle running stroke will increase.After transient state, original state will be repeated.Idle running capsule 244 will remain on its maximum extended spot.HLA assembly 246 will remain on its nominal position.
Fig. 9 shows the key point of exhaust brake.Idle running capsule 244 can absorb the pump liter of HLA assembly 246 during engine braking modes. and when engine braking is cut off, HLA assembly 246 can push back to its nominal position by idle running spring 258.Idle running capsule 244 will guarantee the correct closedown of exhaust valve during driving mode.The additional load be applied on valve mechanism because firing pressure causes can be avoided.Back pressure peak value additional arbitrarily can be adopted under control to avoid uncontrolled HLA pump liter.
The explanation to previous embodiment is provided for the object illustrated and describe.This is not want exhaustive or restriction the present invention.The independent element of specific embodiment or feature are not limited to this specific embodiment usually, but can exchange and can be used for (if words applicatory) in the embodiment selected, even without being illustrated particularly or describing.Described element or feature also can change in a number of different manners.These changes are not considered as departing from the present invention, and these all changes are all contained within the scope of the invention.
Claims (11)
1. the exhaust valve rocker arm assembly that can operate in engine braking modes, described exhaust valve rocker arm assembly comprises:
Limit the pitman arm shaft of compressed oil supply line;
Receive pitman arm shaft and be configured to the rocking arm around pitman arm shaft rotation, described rocking arm has the oil supply gallery be limited to wherein;
Engage the valve cross arm of first row valve and second row valve;
Have can between retracted position and extended position the bleeder valve of the piston of movement;
Be arranged in the hydraulic lash adjuster assembly on rocking arm, described hydraulic lash adjuster assembly has can the first plunger body of movement between the first position and the second position, wherein, in the mat woven of fine bamboo strips one position, the first plunger body extends rigidly and engages collaboratively for valve cross arm; And
Be arranged in elasticity capsule in rocking arm, that hydraulic lash adjuster is biased toward valve cross arm.
2. exhaust valve rocker arm assembly according to claim 1, wherein, hydraulic lash adjuster assembly is received by the hole be limited on rocking arm at least in part.
3. exhaust valve rocker arm assembly according to claim 1, wherein, elasticity capsule is received by the hole be limited on rocking arm at least in part.
4. exhaust valve rocker arm assembly according to claim 1, wherein, hydraulic lash adjuster assembly also comprises the second plunger body received by the first plunger body at least in part, and the second plunger body defines valve seat.
5. exhaust valve rocker arm assembly according to claim 4, wherein, hydraulic lash adjuster comprises the check ball assembly between the first and second plunger bodies.
6. exhaust valve rocker arm assembly according to claim 5, wherein, check ball assembly comprises the first biasing member, the second biasing member, retainer and check ball.
7. exhaust valve rocker arm assembly according to claim 1, wherein, the piston structure of bleeder valve becomes to extend to the total travel keeping first row valve to open predetermined spacing.
8. exhaust valve rocker arm assembly according to claim 7, wherein, described predetermined spacing is 2 millimeters.
9. exhaust valve rocker arm assembly according to claim 1, wherein, elasticity capsule comprises the idle running spring providing the first power, and hydraulic lash adjuster assembly provides the second power, and wherein the first power is greater than the second power.
10. exhaust valve rocker arm assembly according to claim 1, wherein, the mat woven of fine bamboo strips one plunger body has the first closed end defining the first connector be received in the first socket, and described first socket acts on valve cross arm.
11. exhaust valve rocker arm assemblies according to claim 1, wherein, elasticity capsule provides the stroke of the half of the correspondence course equaling piston.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US201462017321P | 2014-06-26 | 2014-06-26 | |
| US62/017321 | 2014-06-26 | ||
| US201462024633P | 2014-07-15 | 2014-07-15 | |
| US62/024633 | 2014-07-15 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105422203A true CN105422203A (en) | 2016-03-23 |
| CN105422203B CN105422203B (en) | 2019-05-14 |
Family
ID=55500691
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510513920.8A Active CN105422203B (en) | 2014-06-26 | 2015-06-26 | Valvetrain system with hydraulic lash adjuster and exhaust brake |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN105422203B (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108952872A (en) * | 2017-05-19 | 2018-12-07 | 卡特彼勒公司 | Public rocker arm for hydraulic lash adjuster and non-hydraulic clearance adjuster |
| CN109154216A (en) * | 2016-04-07 | 2019-01-04 | 伊顿智能动力有限公司 | Rocking arm set component |
| CN105422203B (en) * | 2014-06-26 | 2019-05-14 | 伊顿(意大利)有限公司 | Valvetrain system with hydraulic lash adjuster and exhaust brake |
| CN111033003A (en) * | 2017-08-24 | 2020-04-17 | 伊顿智能动力有限公司 | Spherical engine brake mechanism |
| CN112065524A (en) * | 2020-09-11 | 2020-12-11 | 潍柴动力股份有限公司 | Rocker arm assembly and engine |
| CN113047921A (en) * | 2016-05-10 | 2021-06-29 | 伊顿智能动力有限公司 | Modular rocker arm |
| US11549404B2 (en) | 2017-08-24 | 2023-01-10 | Eaton Intelligent Power Limited | Ball engine decompression mechanism |
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| EP1568850A1 (en) * | 2004-02-25 | 2005-08-31 | OTICS Corporation | Hydraulic lash adjuster |
| US20050229886A1 (en) * | 2004-04-16 | 2005-10-20 | Peter Sailer | Valve train with hydraulic lash adjustment |
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| EP2067943A1 (en) * | 2007-12-07 | 2009-06-10 | Otics Corporation | Valve gear and rocker arm unit |
| CN102037219A (en) * | 2008-05-21 | 2011-04-27 | 卡特彼勒公司 | A valve bridge having a centrally positioned hydraulic lash adjuster |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105422203B (en) * | 2014-06-26 | 2019-05-14 | 伊顿(意大利)有限公司 | Valvetrain system with hydraulic lash adjuster and exhaust brake |
-
2015
- 2015-06-26 CN CN201510513920.8A patent/CN105422203B/en active Active
Patent Citations (5)
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| EP1568850A1 (en) * | 2004-02-25 | 2005-08-31 | OTICS Corporation | Hydraulic lash adjuster |
| US20050229886A1 (en) * | 2004-04-16 | 2005-10-20 | Peter Sailer | Valve train with hydraulic lash adjustment |
| JP2008025394A (en) * | 2006-07-19 | 2008-02-07 | Toyota Motor Corp | Lash adjuster of internal combustion engine |
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Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105422203B (en) * | 2014-06-26 | 2019-05-14 | 伊顿(意大利)有限公司 | Valvetrain system with hydraulic lash adjuster and exhaust brake |
| CN109154216A (en) * | 2016-04-07 | 2019-01-04 | 伊顿智能动力有限公司 | Rocking arm set component |
| CN114622963A (en) * | 2016-04-07 | 2022-06-14 | 伊顿智能动力有限公司 | Box subassembly, rocking arm subassembly and valve assembly |
| CN114622963B (en) * | 2016-04-07 | 2024-04-05 | 伊顿智能动力有限公司 | Box assembly, rocker arm assembly and valve assembly |
| CN113047921A (en) * | 2016-05-10 | 2021-06-29 | 伊顿智能动力有限公司 | Modular rocker arm |
| CN108952872A (en) * | 2017-05-19 | 2018-12-07 | 卡特彼勒公司 | Public rocker arm for hydraulic lash adjuster and non-hydraulic clearance adjuster |
| CN108952872B (en) * | 2017-05-19 | 2021-12-31 | 卡特彼勒公司 | Common rocker arm for hydraulic and non-hydraulic lash adjusters |
| CN111033003A (en) * | 2017-08-24 | 2020-04-17 | 伊顿智能动力有限公司 | Spherical engine brake mechanism |
| CN111033003B (en) * | 2017-08-24 | 2022-04-05 | 伊顿智能动力有限公司 | Spherical engine brake mechanism |
| US11549404B2 (en) | 2017-08-24 | 2023-01-10 | Eaton Intelligent Power Limited | Ball engine decompression mechanism |
| CN112065524A (en) * | 2020-09-11 | 2020-12-11 | 潍柴动力股份有限公司 | Rocker arm assembly and engine |
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| CN105422203B (en) | 2019-05-14 |
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