CN105378236B - Method for the response time for optimizing the hydraulic pressure latch pin in cylinder deactivation rocking arm - Google Patents
Method for the response time for optimizing the hydraulic pressure latch pin in cylinder deactivation rocking arm Download PDFInfo
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- CN105378236B CN105378236B CN201480037996.1A CN201480037996A CN105378236B CN 105378236 B CN105378236 B CN 105378236B CN 201480037996 A CN201480037996 A CN 201480037996A CN 105378236 B CN105378236 B CN 105378236B
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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
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
- F01L13/0005—Deactivating valves
-
- 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
- F01L1/12—Transmitting gear between valve drive and valve
- F01L1/18—Rocking arms or levers
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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
- F01L2303/00—Manufacturing of components used in valve arrangements
-
- 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
- F01L2305/00—Valve arrangements comprising rollers
Abstract
Provide a kind of method for optimizing the response time of the lock bolt in cylinder deactivation rocker arm assembly.It is moved between the position and retracted position of the inner arm engagement of the bolt structure Cheng Yu rocker arm assemblies.Determine the main outer diameter L1 of the lock bolt.Determine the installation length L2 of the spring of lock bolt described in bias.Determine the gap L 3 between the main internal diameter of the outer arm of L1 and rocker arm assembly.It determines in the radial clearance L4 shrouded between the main internal diameter of lock bolt for being attached to outer arm.Determine the path L5 of lock bolt.Relationship between the response time and L1, L2, L3, L4 and L5 of establishing the lock bolt.The component of cylinder deactivation rocker arm assembly is selected based on the relationship.
Description
The intersection of related application is quoted
The U.S. Provisional Patent Application No.61/872,621 that is submitted for 30th this application claims August in 2013, in August, 2013
The U.S. Provisional Patent Application No.61/872,624 and the U.S. Provisional Patent Application submitted on November 1st, 2013 submitted for 30
The equity of No.61/898,475.The disclosure of above-mentioned application is incorporated herein by reference.
Technical field
The present invention relates generally to conversion roller type finger-type driven members, more particularly relate to the lock bolt of optimization cylinder deactivation rocking arm
The method of the response time of pin.
Background technology
A kind of conversion roller type finger-type allowing to control valve actuation between two or more states by converting from
Moving part or conversion rocking arm, are usually directed to multiple arms, such as inner arm and outer arm.Converting rocking arm can be in variable valve actuation (VVA) system
Middle use is to improve the fuel economy of engine.
The description of background technology presented herein is for the overall background that the present invention is presented.With regard to the background parts institute
This meaning of the various aspects of the description as prior art qualification is otherwise not yet obtained when description and submission
For upper, the prior art also not recognized impliedly for relative to the present invention is neither expressed in the work of the inventor currently signed.
Invention content
Provide a kind of method for optimizing the response time of the lock bolt in cylinder deactivation rocker arm assembly.The bolt structure at
It is moved between the position that the inner arm with rocker arm assembly engages and retracted position.Determine main outer diameter/major diameter (L1) of the lock bolt.
Determine the installation length (L2) of the spring of lock bolt described in bias.Between determining between the main internal diameter of the outer arm of L1 and rocker arm assembly
Gap (L3).It determines in the radial clearance (L4) shrouded between the main internal diameter of lock bolt for being attached to outer arm.Determine the path of lock bolt
(L5).Relationship between the response time and L1, L2, L3, L4 and L5 of establishing the lock bolt.In L1, L2, L3, L4 and L5 extremely
Influence of few one to the response time is more than other each in L1, L2, L3, L4 and L5.It is shaken based on relationship selection cylinder deactivation
The component of arm component.
Response time can be lock bolt from inner arm movement and make it possible to be transformed into the ON response times needed for deactivation mode.
In an example, influence biggers of L4 ratio L1, L2 and the L3 to the response time.In another example, L5 ratios L1, L2 and L3 are to sound
Influence bigger between seasonable.In one example, the relationship is established by following equation：
The ON response times (ms)=22.1431+1.2675*L1-1.28*L2-0.2625*L3-8.8762*L4+8.1951*
L5+0.55*L1*L2–2.825*L1*L4–2.77*L1*L5+0.655*L2*L4–0.6050*L2*L5–0.4875*L3*L4–
4.035*L4*L5。
In another example, the response time is that lock bolt is moved to OFF response times needed for bonding station from retracted position.
L1 can be than the influence bigger of L2, L3, L4 and L5 to the response time.L4 can be than L2, L3 and L5 to the response time influence more
Greatly.L5 can be than influence biggers of the L2 and L3 to the response time.In an example, the relationship is established by following equation：
The OFF response times (ms)=19.731+15.8987*L1+1.17163*L2-1.53*L3-7.6401*L4-
4.405*L5+1.3375*L1*L2–10.265*L1*L4–1.837*L1*L5–1.005*L2*L5+1.7875*L4*L5。
Provide ON and the OFF response for optimizing the lock bolt in cylinder deactivation rocker arm assembly of another example according to the present invention
The method of time.Lock bolt moves between the position that the inner arm with rocker arm assembly engages and retracted position.This method includes determining
The main outer diameter (L1) of lock bolt.Determine the installation length (L2) of the spring of bias lock bolt.Determine the outer of the rocking arm of L1 and rocker arm assembly
Gap (L3) between the main internal diameter of arm.Determine the radial clearance shrouded between the main internal diameter of lock bolt for being attached to outer arm
(L4).Determine the path (L5) of lock bolt.Establish the relationship between the response time of lock bolt and L1, L2, L3, L4 and L5.L1, L2 and
Each of L5 has reversed/reverse relationship about ON response times and OFF response times.Based on the relationship established
Select the component of cylinder deactivation rocker arm assembly.
According to other feature, lock bolt is mobile from inner arm and makes it possible to be transformed into deactivation mode and needs the ON response times.L4
It can be than the influence bigger of L1, L2 and L3 to the response time.L5 can be than the influence bigger of L1, L2 and L3 to the response time.L5
It can be than the influence bigger of L1, L2 and L3 to the response time.In an example, the ON response times are established by following equation：
The ON response times (ms)=22.1431+1.2675*L1-1.28*L2-0.2625*L3-8.8762*L4+8.1951*
L5+0.55*L1*L2–2.825*L1*L4–2.77*L1*L5+0.655*L2*L4–0.6050*L2*L5–0.4875*L3*L4–
4.035*L4*L5。
According to additional example, lock bolt is moved to bonding station from retracted position and needs the OFF response times.L1 can compare
The influence bigger of L2, L3, L4 and L5 to the response time.L4 can be than the influence bigger of L2, L3 and L5 to the response time.L5 can be with
Influence bigger than L2 and L3 to the response time.In an example, the OFF response times are established by following equation：
The OFF response times (ms)=19.731+15.8987*L1+1.17163*L2-1.53*L3-7.6401*L4-
4.405*L5+1.3375*L1*L2–10.265*L1*L4–1.837*L1*L5–1.005*L2*L5+1.7875*L4*L5。
Description of the drawings
The present invention can be more fully understood from detailed description and drawings, in the accompanying drawings：
Fig. 1 is the front perspective view of the exemplary transformation rocking arm of an instance constructs according to the present invention；
Fig. 2 is the partial sectional view of the switching mechanism of the conversion rocking arm of Fig. 1, and shows that valve is in Lifting scheme,
Lock bolt is engaged；
Fig. 3 is the partial sectional view of the conversion rocking arm of Fig. 2, and shows that valve is in deactivation mode, and lock bolt is detached from；
Fig. 4 is the partial sectional view of the conversion rocking arm of Fig. 1, and shows that lock bolt is engaged with inner arm；
Fig. 5 is the partial sectional view of the conversion rocking arm of Fig. 1, and shows that lock bolt is in retracted position and is connect with shrouding
It touches；
Fig. 6 A are the partial sectional views for converting rocking arm, show that lock bolt is moved from bonding station to retracted position；
Fig. 6 B are the end-views of the conversion rocking arm of Fig. 6 A shrouded with lock bolt；
Fig. 7 is lock bolt to the force diagram shrouded in moving process；
Fig. 8 is lock bolt far from the force diagram shrouded in moving process；
Fig. 9 A are the partial sectional views according to the conversion rocking arm of Fig. 1 of exemplary baseline design；
Fig. 9 B are the sectional views that Fig. 9 A are intercepted along line A-A；
Figure 10 A are the partial sectional views of the conversion rocking arm of Fig. 9 A designed according to exemplary optimized；
Figure 10 B are the sectional views that Figure 10 A are intercepted along line A-A；
Figure 11 is the curve graph for the effect for indicating the diametric clearance (L3) between lock bolt and outer arm；
Figure 12 is the curve graph of the effect of the radial clearance (L4) between indicating lock bolt and shrouding；With
Figure 13 is the curve graph for the effect for indicating the contact length (L6) between lock bolt and outer arm.
Specific implementation mode
Introduction is for the method for the lock bolt response time in transformation rocking arm below.Specifically, discussion below
It provides the optimization lock bolt response time or lock bolt moves so that conversion rocking arm can be transformed into deactivated mode from Lifting scheme
The method of time (vice versa).
With reference first to Fig. 1, show that the exemplary transformation roller type finger-type of an instance constructs according to the present invention is driven
Part (SRFF) component, and it is generically designated as reference label 10.SRFF components 10 can be compact actuated by cams single salient angle/it is convex
Portion's cylinder deactivation (CDA) converts rocking arm 12, is mounted on the internal combustion engine of piston driving, and pass through double-fed type hydraulic lash adjuster
(DFHLA) 14 and the combination of oil control valve (OCV) 16 activate.SRFF components 10 can be engaged by single salient angle cam 20.Conversion
Rocking arm 12 may include inner arm 22, outer arm 24.Default configuration is in normal hoisting (locking) position, wherein 24 quilt of inner arm 22 and outer arm
It locks together, engine valve 26 is caused to open and cylinder is allowed to be run in a manner of standard valve mechanism.DFHLA 14 has two
A hydraulic fluid port.Lower hydraulic fluid port or backlash compensation pressure port 28 provide backlash compensation and are supplied to the machine oil similar to standard HLA.Upper hydraulic fluid port
30 --- being known as switching to pressure mouth ---, provided the pipeline (Fig. 2) between the controlled oil pressure from OCV 16 and lock bolt 32.When
When lock bolt 32 is engaged, inner arm 22 is co-operated as standard rocking arm to open engine valve 26 with outer arm 24.It is carried non-
When rising (unlock) position, inner arm 22 and outer arm 24 can be moved independently so that cylinder is closed down.
With continued reference to Fig. 1 and additional reference Fig. 2, the additional feature of SRFF components 10 is illustrated.A pair of of lost motion torsion bullet
Spring 40 is combined with the position of bias inner arm 22, it is made to remain and 20 continuous contact of camshaft lobe.Torque spring 40 is logical
It crosses on the bearing that spring retainer 44 is fixed on outer arm 24.Lost motion torque spring 40 is needed than using setting for more salient angles
Higher preloading is counted to contribute to camshaft lobe 20 and 50 continuous contact of inner arm roller bearing.Engine valve 26 may include
Valve seating 54 and valve guide part 56.Valve spring 58 can be biased into valve seating 54 far from outer arm 24.
OCV 16 can be electronic control ON/OFF (ON/OFF) valve, and telecommunications is received from control unit of engine (ECU) 70
Number.Machine oil is supplied to OCV 16.As described above, OCV 16 is hydraulically connected to DFHLA 14.The quilt at pivot 76 of inner arm 22
It is pivotally coupled to outer arm 24.Connection at pivot 76 allows inner arm 22 to be swung relative to outer arm 24.Lock bolt 32 is mounted on outer
The end of arm 24 pivots side, and the top of DFHLA 14, the purpose is to provide the secondary connection between inner arm 22 and outer arm 24.Lock bolt
Expanding location bias lock bolt 32 of the compressed spring 80 in engagement inner arm 22.One end of lock bolt compressed spring 80 is captured simultaneously by lock bolt 32
And the other end shrouds 82 captures by permanent link outer arm 24.Lost motion spring 40 makes camshaft lobe 20 that permanent contact be kept to be located at
Roller bearing 50 in inner arm 22.Balance between oil pressure in switching to pressure mouth and the power of lock bolt compressed spring 80 pushes lock bolt
32 so that inner arm 22 is engaged or disengaged with outer arm 24.
The exemplary mode of operation of cylinder deactivation will be described.Lifting scheme can be up to 7200rpm and all works in engine speed
Occur at a temperature of work.When no electric signal reaches OCV 16, converting the oil pressure of mouth can be adjusted to 0.2 bar (bar) to 0.4
Bar.Lock bolt 32 is in extended position and is engaged with inner arm 22.Cylinder deactivation or non-Lifting scheme can be up to 3500rpm in engine speed
It can be used in the case of being 20 degrees Celsius or more with oil temperature.Non- Lifting scheme is triggered by from ECU 70 to OCV 16 electric signal,
This makes the oil pressure of switching to pressure mouth increase in 2.0 Palestine and Israels.The increase of pressure makes lock bolt 32 retract to be detached from inner arm 22.At one
In example, the oil pressure under 20 degrees Celsius is in 4.0 Palestine and Israels.In addition, 2.0 bars of oil pressure are can at 100 degrees Celsius or more of temperature
Capable.As a result, the oil pressure under low temperature can be 3 bars.
Referring now particularly to Fig. 2, it will illustrate section of the SRFF components 10 during Lifting scheme.It is arrived in no electric signal
When up to OCV 16, the oil pressure of switching to pressure mouth is 0.2 bar to 0.4 bar.Lock bolt 32 is stretched out and is engaged with inner arm 22.SRFF components 10
Inner arm 22 and outer arm 24 are working as similar to the single main body of standard rocking arm of linking together.Camshaft rotary motion
It is transmitted to valve 26 by inner arm 22 and outer arm 24.Promotion profile of the valve 26 based on camshaft lifts salient angle 20 is opened and is closed
It closes.
Referring now particularly to Fig. 3, it will illustrate section of the SRFF components 10 during non-Lifting scheme.From ECU's 70
Electric signal encourages OCV 16 to pressurize to conversion mouth by engine oil pressure.In one configuration, at least 2.0 bars are needed to overcome
The preload force of lock pin spring 80, the compression lock pin spring 80 and mobile lock bolt 32 in retracted position, make inner arm 22 with it is outer
Arm 24 is detached from.SRFF components 10 may include gap between lock bolt 32 and inner arm 22, be known as lock bolt gap.The gap allows lock bolt
32 are moved into and out outer arm 24 based on the oil pressure converted in mouth and when camshaft is on basic circle.Between lock bolt 32 and inner arm 22
Lack the inner arm 22 that connection causes camshaft rotary motion to be simply transferred to the rotation of around the pivot 76.Camshaft motion is not transferred to
The valve 26 of remains stationary on valve seating 54.
CDA conversion rocking arms 12 make it possible to be transformed into deactivated mode from Lifting scheme, and vice versa.Crest places the cam starts
There are one OCV 16 for equipment, and input is provided to four SRFF components 10 (two are used for exhaust valve for inlet valve and two).
It activates and the sequence for the valve of closing down is important the normal work of engine.(mould of closing down is transformed into from Lifting scheme
Formula) preferred sequence be the connection of SRFF and exhaust valve of closing down first, so that exhaust gas is trapped in cylinder, then, close down SRFF with
The connection of inlet valve.When being converted from closing down Lifting scheme, exhaust valve is activated first to be come from releasing in periodic process of closing down
The pressure of the retention gas of middle holding in the cylinder.Then, the connection of SRFF to inlet valve is activated, and allows inlet valve close
It is opened under the pressure of atmospheric pressure.The exhaust gas being trapped in cylinder in periodic process of closing down is beneficial, because it reduces pumping
It loses and cylinder deactivation is kept not cool down, maintain the thermal efficiency of engine.Conversion between pattern needs in cam axle one encloses
Occur and the sequence of conversion intake and exhaust is important and must keep the normal work for engine.SRFF it
One, which is more than conversion time, may cause to convert SRFF with the sequence of mistake.
The window that can be used for converting, which is defined as hydraulic pressure, with change pattern and can complete lock bolt mechanical movement to produce
The time of the raw variation (vice versa) from closing down activation.Pattern conversion is happened at the state that SRFF is on camshaft basic circle
Under, when lock bolt 32 is under the load from inner arm 22 and can be moved freely.
The lock bolt response time is defined for lock bolt 32 and moves so that SRFF can be transferred to from Lifting scheme closing down
The time of pattern (vice versa).Lock bolt 32 is moved from inner arm 22 and the time that SRFF can be made to be transformed into needed for deactivated mode is known as
" ON responses ".The movement of lock bolt 32 is realized by encouraging OCV 16.This makes the pressure of switching to pressure mouth increase to start
Oil pressure.The increase of the pressure overcomes the power of lock bolt snap 80, and lock bolt 32 is made to be moved to retracted position from bonding station.
Turning now to Fig. 4, lock bolt 32 is illustrated in bonding station.When the front surface of lock bolt 32 and inner arm 22 contact, lock
Door bolt 32 is in bonding station.The oil pressure increase of switching to pressure mouth makes lock bolt 32 move distance from bonding station to retracted position
D1.Distance D1 can be 1.86mm in the example shown.
Referring now to Fig. 5, lock bolt 32 is illustrated in retracted position.In retracted position, lock bolt 32 is contacted with shrouding 82.Lock bolt 32
Connection completely inside outer arm 24 and between inner arm 22 and lock bolt 32 is aborted.Inner arm 22 is kept freely in the period of closing down
It pivots.When not having signal to be sent to OCV 16, OCV 16 is de-energized.Oil pressure in switching to pressure mouth is adjusted to 0.2 bar and arrives
0.4 bar.The insufficient pressure makes lock bolt 32 be moved to extended position to overcome compressed spring force.Lock bolt 32 is from retracted position
Traveling time to partially engaged position is referred to herein as " OFF responses ".
Referring now to Fig. 6 A and 6B, show that lock bolt 32 is run from bonding station to retracted position.Fig. 6 A are shown along lock
Fasten the section for the axis advanced with a bolt or latch.Fig. 6 B show the section of the plane by the direction of motion perpendicular to lock bolt.When lock bolt 32 moves
If when moving disengaging configuration oil cannot quickly leave SRFF by the hole in shrouding, the lock bolt in bag and shroud 82 it
Between be resident oil generate back pressure.Draining path 100 is formed in lock bolt 32 and between shrouding 82.Draining path 100 helps to reduce
The ON response times.As described herein, lock bolt 32 and the design for the interface for shrouding 82 are changed for reducing the ON response times.
Fig. 7 shows the force diagram that lock bolt 32 is shrouded in direction in 82 motion processes.The power of driving latch movement is due to lock
Fasten the hydraulic coupling that the pressure from OCV 16 at closed end towards main outer diameter generates, F with a bolt or latchpa1.The power opposite with latch movement be due to
The viscous friction power that fluid between lock bolt 32 and outer arm 24 generates, Fviscous1And Fviscous2, lock pin spring compressing force Fspring,
Towards the hydraulic coupling F of path at lock bolt closed endpa2, and act on from open end the hydraulic coupling F on lock bolt 32pa3.Latch displacement x by
Newton interpolation algorithm exports in following equation, and wherein m is latch mass：
When OCV 16 is de-energized, the oil pressure for converting mouth drops to 0.4 bar of maximum.Insufficient pressure is compressed to overcome
The power of spring allows lock bolt to be moved away from from lock bolt 32 with the retracted position for shrouding 82 contacts and shrouds 82.Fig. 8 shows that lock bolt 32 exists
Force diagram in the motion process, wherein it is lock pin spring preload force F to drive the power of latch movementspring, court at lock bolt closed end
To the hydraulic coupling F of small ODpa2With the hydraulic coupling F acted on from open end on lock bolt 32pa3.The power opposite with latch movement is lock bolt
Fluid viscous frictional force F on full diameter and pathviscous1And Fviscous2, and due to the hydraulic pressure of the oil pressure generation in conversion mouth
Power Fpa1.Lock bolt indicates that wherein x represents displacement far from the movement for shrouding 82 with following equation derived from Newton's second law
The quality of lock bolt 32 is represented with m：
Determining according to the method for the present invention influences the various parameters of response time.Fig. 9 A and 10A are shown to be transported in lock bolt
The section by SRFF 12 on dynamic direction, is used for baseline design (Fig. 9 A) and optimization design (Figure 10 A).Fig. 9 B and 10B are shown
Perpendicular to the respective section of latch movement axis, wherein lock bolt 32 is between bonding station and retracted position.Following parameter
It is determined.The main outer diameter of lock bolt (OD) L1, the installation length L2 of spring 80.The main outer diameter OD of lock bolt and the main internal diameter in 24 hole of outer arm (ID) it
Between gap L 3.Lock bolt 32 is to the radial clearance L4 for shrouding 82.The small OD L5 of lock bolt 32.The contact of lock bolt 32 to outer arm 24 is grown
Spend L6.Lock bolt 32 and shroud the volume L7 between 82.Fluid is escaped from lock bolt open end to the outlet for shrouding 82, by between radial direction
Gap L4 is exposed to cylinder head.
It will now describe the influence of lock bolt main OD, L1 according to this teaching.The ON response times with lock bolt main OD, L1 increasing
It reduces greatly, because leading to hydraulic coupling Fpa1The available area of pressure increase.The OFF response times increase as diameter increases,
Because higher action of hydraulic force is on lock bolt main OD, L1.During lock bolt is moved from disengaging configuration to bonding station, turn
It is 0.4 bar maximum to change available back pressure in pressure port.In addition, the rate that the pressure in conversion mouth declines also works to OFF responses.
Initial tension of spring effectively promotes latch movement after being only minimized pressure under stress.Therefore it is minimized under stress
Before pressure, the dynamic that OCV interacts with lock bolt and fluid path is important the OFF Accurate Predictions responded.Due to
The dynamic of lock bolt front/positive interaction, OCV is influenced by lock bolt full diameter.
It will now describe the influence of spring installation length L2 according to this teaching.The load variation of spring changes with L2.Peace
Filling length L2 influences spring preload power.The installation length of spring is bigger, and spring force is smaller.ON responds the increase with installation length
And decline, because the resistance provided by spring during being moved from bonding station to disengaging configuration is relatively low.OFF response with
The reduction of spring installation length and decline because the preload in spring is larger, the preload from disengaging configuration to engagement position
It sets and is used as driving force in moving process.
Referring to Fig.1 1, by the influence of the diametric clearance L3 of explanation according to this teaching.Between lock bolt main OD, L1 and the main ID of outer arm
Gap L 3 influence the viscous friction F between the lock bolt main OD and main ID of outer armviscous1.Lock bolt main OD, L1 and the main ID of outer arm it
Between gap increase to ON and OFF response have an impact.OFF responses reduce as diametric clearance L3 increases, because of lock bolt
Increased flow increases pressure F at open endpa3.ON responses reduce until gap reaches preset distance, such as 0.12mm.It rings
Then increase between seasonable.In this respect, increasing to the up to gap of 0.12mm reduces viscous friction power simultaneously thus under ON responses
Drop.When beyond 0.12mm, leakage is very high, therefore the hydraulic coupling acted on lock bolt main OD, L1 is very low, so as to cause increased
ON is responded.
Referring to Fig.1 2, it will now describe the influence of radial clearance L4 according to this teaching.From bonding station to retracted position
Latch movement make oil dispersed in volume chamber L7.Leakage stream is since diametric clearance L3, by chamber volume L7 and across diameter
SRFF is left after to gap L 4.When Figure 12 shows that the radial clearance shrouded between 82 and the main ID of lock bolt responds ON and OFF
Between influence.The ON response times reduce as radial clearance increases, because due to caused by the pressure that cavity volume L7 is generated
Opposite power Fpa3It is smaller.As gap increases, the pressure in cavity volume L7 declines, because fluid is by shrouding the opening in 82
It is exposed to atmospheric pressure rapidly.OFF responses follow similar physical in the latch movement of backstroke process.OFF is responded
Response with ON respond compared with slope it is steeper.
It will now describe the influence of lock bolt path L5 according to this teaching.ON responses increase as lock bolt path L5 increases
Add, because of hydraulic coupling Fpa2The F of resistance is provided with the retraction movement for lock bolt 32pa1Increase compared to relatively opposite.OFF is responded with small
Diameter increases and reduces, because acting on the spring force F of the same directionspringWith hydraulic coupling Fpa2Combined effect.
Referring additionally to Figure 13, the influence of contact length L6 according to this teaching will now describe.Lock bolt 32 and outer arm 24 it
Between contact length L6 increase ON the and OFF response times are had no significant effect.When Figure 13 shows contact length L6 to response
Between correlation.The increase of contact length makes frictional force increase.Compared to other parameters, contact length L6 and chamber volume L7 ginsengs
Several variations do not influence the response time.
According to the method for the present invention, the quantitative transmission of the relationship between the governing factor for having an impact output response is provided
Function.Five governing factors have an impact the response time：The main OD of lock bolt (L1), spring installation length (L2), diametric clearance (L3),
Radial clearance (L4) and the small ID of lock bolt (L5).Transmission function is obtained from the output result of analysis ON and OFF response times
's.The influence of the factor is directly proportional to the amplitude of related coefficient.The amplitude of coefficient is higher, and the variation of response is stronger.Below
In equation the coefficient of radial clearance (L4) and the small OD of lock bolt (L5) respectively illustrate (- 40%) and (+37%) powerful influence and
Contribution.This demonstrate the level 1 that radial clearance (L4) is moved to dimensionless number and make other factors be maintained at level 0 to lead to ON
Response time reduces by 40.0% or about 9ms.Higher levels of interaction has insignificant influence.It obtains and is used for dimensionless
Value " 0 " and the transmission function of "+1 " simultaneously show ON and OFF responses in following equation：
ON responds (ms)=22.1431+1.2675*L1-1.28*L2-0.2625*L3-8.8762*L4+8.1951*L5+
0.55*L1*L2–2.825*L1*L4–2.77*L1*L5+0.655*L2*L4–0.6050*L2*L5–0.4875*L3*L4–
4.035*L4*L5
The main OD's of lock bolt (L1), radial clearance (L4) and the small OD of lock bolt (L5) in OFF response times equation (following) is
Number shows respectively+81.0%, -39.0% and -22.0% higher contribution.This shows to keep the main OD of lock bolt (L1) mobile
Level 2 to dimensionless number makes OFF responses increase about 16ms.Transmission function is to outgoing direction so that radial clearance (L4) and lock bolt
Small OD (L5) is moved to the level 1 of dimensionless number, to reduce the OFF response times.The interaction coefficient of L1 and L4 is shown
52.0% bigger contribution, and indicate and reduce OFF responses, the main OD of lock bolt (L1) can be together with factor lock bolt radial clearance L4
It is moved to the level 1 of dimensionless number.Remaining higher levels of interaction has insignificant influence.
OFF responds (ms)=19.731+15.8987*L1+1.17163*L2-1.53*L3-7.6401*L4-4.405*L5+
1.3375*L1*L2–10.265*L1*L4–1.837*L1*L5–1.005*L2*L5+1.7875*L4*L5
The main OD of lock bolt (L1), spring installation length (L2), the small OD of lock bolt (L5) are relative to ON the and OFF response times at reversed
Relationship.Response optimization device function is developed for understanding that different tests set the influence to ON the and OFF response times, purpose
It is to explore the sensitivity of ON and OFF responses when input variable changes.The function determines that input variable, the generation of L1 to L5 are most short
The best possible combination of ON and OFF response times.Optimization aim is farthest to reduce two response times and select
The arbitrary target of 12.0ms is to provide steady design variant.It was found that two transmission functions, design variables previously having obtained are most
Good combination is responded with the farthest synchronous ON and OFF that reduces.For the best ON and OFF response times make optimization after provide it is following
Ideal dimensions.Lock bolt full diameter L1=7.947mm, spring installation length L2=7.126mm, between the main OD of lock bolt and outer arm aperture
Gap L 3=0.103mm, lock bolt to the small OD L5=5.741 of radial clearance L4=0.400mm and lock bolt shrouded.Here institute
The design method of elaboration makes L2, L3 and L4 be moved to the movement of level 1 and L1 and L5 to level 0.
Figure 10 A and 10B show the design of optimization, wherein the similar reference label with suffix " A " is for indicating similar
Component.Optimization design includes changing lock bolt 32A, shrouding 82A and spring installation length L2 to reduce the response time and balance ON
It is responded with OFF.Find the optimal value of factor L1 to L5.The considerations of packaging, limits the main OD of lock bolt (L1) and lock bolt path (L5)
Variation.Following change in design is carried out：L2 reduces 3.87% to balance ON/OFF responses.L3 increases 44% to reduce lock
It fastens the viscous friction in motion process with a bolt or latch and reduces by two response times.L4 increases 53%.Optimization design have modified shroud it is small
OD simultaneously increases lock bolt ID.In addition, as it would be appreciated, the ON and OFF response times etc. that method through the invention is provided
Formula can be used when selecting the component of SRFF components 10.
Multiple and different embodiments shown in the drawings of the present invention of the application.It is shown in different embodiments of the invention
Similar feature.Similar feature is distinguished by common reference number into line label and by letter suffix.In addition, in order to carry
High consistency, the structure in any certain figures share identical letter suffix, even if special characteristic is not in all embodiments
It shows.Similar feature can be similarly constructed, similarly operate and/or function having the same, unless by attached drawing or this theory
Bright book separately adds explanation.In addition, the special characteristic of one embodiment can replace corresponding feature in another embodiment, can also mend
Other embodiments are filled, unless separately adding explanation by attached drawing or this specification.
In order to show and describe and provide the preceding description of embodiment.It is not intended to the exhaustive or limitation present invention.It is specific
The individual element or feature of embodiment is generally not limited to the specific embodiment, but can be interchanged in where applicable, and can be with
It is used in selected embodiment, even if being not shown or described in detail.It can also equally change in many aspects.It is such
Variation is not to be regarded as a departure from the invention, and all this modifications are intended to be included within the scope of this invention.
Claims (20)
1. a kind of method for optimizing the response time of lock bolt in cylinder deactivation rocker arm assembly, the lock bolt with rocker arm assembly
It is moved between the position and retracted position of inner arm engagement, this method includes：
Determining influences the governing factor of response time, and the governing factor includes：The main outer diameter L1 of the lock bolt；It is locked described in bias
The installation length L2 of the spring of door bolt；Gap L 3 between the main internal diameter of the outer arm of L1 and rocker arm assembly；It is being attached to outer arm
Shroud the radial clearance L4 between the main internal diameter of lock bolt；With the path L5 of lock bolt；
There is provided the quantitative transmission function of the relationship between the governing factor for the response time for having an impact the lock bolt, wherein institute
Stating quantitative transmission function requires the influence of at least one of L1, L2, L3, L4 and L5 to the response time to be more than L1, L2, L3, L4
With remaining each in L5；With
Component based on the relational design cylinder deactivation rocker arm assembly.
2. according to the method described in claim 1, wherein, the response time is lock bolt from inner arm movement and makes it possible to convert
To the ON response times needed for deactivation mode.
3. according to the method described in claim 2, wherein, influence biggers of L4 ratio L1, L2 and the L3 to the response time.
4. according to the method described in claim 3, wherein, influence biggers of L5 ratio L1, L2 and the L3 to the response time.
5. according to the method described in claim 4, wherein, the relationship includes：
The ON response times (ms)=22.1431+1.2675*L1-1.28*L2-0.2625*L3-8.8762*L4+8.1951*L5+
0.55*L1*L2–2.825*L1*L4–2.77*L1*L5+0.655*L2*L4–0.6050*L2*L5–0.4875*L3*L4–
4.035*L4*L5。
6. according to the method described in claim 1, wherein, the response time is that lock bolt is moved to bonding station from retracted position
The required OFF response times.
7. according to the method described in claim 6, wherein, influence biggers of L1 ratio L2, L3, L4 and the L5 to the response time.
8. according to the method described in claim 7, wherein, influence biggers of L4 ratio L2, L3 and the L5 to the response time.
9. according to the method described in claim 8, wherein, influence biggers of the L5 ratio L2 and L3 to the response time.
10. according to the method described in claim 9, wherein, the relationship includes：
The OFF response times (ms)=19.731+15.8987*L1+1.17163*L2-1.53*L3-7.6401*L4-4.405*L5+
1.3375*L1*L2–10.265*L1*L4–1.837*L1*L5–1.005*L2*L5+1.7875*L4*L5。
11. a kind of method for optimizing the response time of lock bolt in cylinder deactivation rocker arm assembly, the lock bolt with rocker arm assembly
Inner arm engagement position and retracted position between move, this method includes：
Determining influences the governing factor of response time, and the governing factor includes：The main outer diameter L1 of lock bolt；The spring of bias lock bolt
Installation length L2；Gap L 3 between the main internal diameter of the outer arm of L1 and rocker arm assembly；It is attached to shrouding and lock bolt for outer arm
Radial clearance L4 between main internal diameter；With the path L5 of lock bolt；
First quantitative transmission function of the relationship between the governing factor for the ON response times for having an impact the lock bolt is provided；
Second quantitative transmission function of the relationship between the governing factor for the OFF response times for having an impact the lock bolt is provided,
Wherein, both first and second quantitative transmission functions are for determining in the governing factor for generating the most short ON and OFF response times
The optimized dimensions of each；
For the first and second quantitative transmission function selection target ON and OFF response times；With
The optimum organization of the size of each governing factor is determined based on target ON and the OFF response time.
12. according to the method for claim 11, wherein the lock bolt is mobile from inner arm and makes it possible to be transformed into cylinder deactivation mould
Formula needs the ON response times.
13. according to the method for claim 12, wherein influence biggers of L4 ratio L1, L2 and the L3 to the response time.
14. according to the method for claim 13, wherein influence biggers of L5 ratio L1, L2 and the L3 to the response time.
15. according to the method for claim 14, wherein described first, which quantifies transmission function, includes：
The ON response times (ms)=22.1431+1.2675*L1-1.28*L2-0.2625*L3-8.8762*L4+8.1951*L5+
0.55*L1*L2–2.825*L1*L4–2.77*L1*L5+0.655*L2*L4–0.6050*L2*L5–0.4875*L3*L4–
4.035*L4*L5。
16. according to the method for claim 11, wherein the lock bolt is moved to from retracted position described in bonding station needs
The OFF response times.
17. according to the method for claim 16, wherein influence biggers of L1 ratio L2, L3, L4 and the L5 to the response time.
18. according to the method for claim 17, wherein influence biggers of L4 ratio L2, L3 and the L5 to the response time.
19. according to the method for claim 18, wherein influence biggers of the L5 ratio L2 and L3 to the response time.
20. according to the method for claim 19, wherein described second, which quantifies transmission function, includes：The OFF response times (ms)
=19.731+15.8987*L1+1.17163*L2-1.53*L3-7.6401*L4-4.405*L5+1.3375*L1*L2-
10.265*L1*L4–1.837*L1*L5–1.005*L2*L5+1.7875*L4*L5。
Applications Claiming Priority (7)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US201361872621P | 2013-08-30 | 2013-08-30 | |
| US201361872624P | 2013-08-30 | 2013-08-30 | |
| US61/872,624 | 2013-08-30 | ||
| US61/872,621 | 2013-08-30 | ||
| US201361898475P | 2013-11-01 | 2013-11-01 | |
| US61/898,475 | 2013-11-01 | ||
| PCT/US2014/053689 WO2015031887A1 (en) | 2013-08-30 | 2014-09-02 | Method for optimizing response time of hydraulic latch-pin in cylinder deactivation rocker arm |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105378236A CN105378236A (en) | 2016-03-02 |
| CN105378236B true CN105378236B (en) | 2018-10-12 |
Family
ID=52587411
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201480037996.1A Expired - Fee Related CN105378236B (en) | 2013-08-30 | 2014-09-02 | Method for the response time for optimizing the hydraulic pressure latch pin in cylinder deactivation rocking arm |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US20160169064A1 (en) |
| EP (1) | EP3039256B1 (en) |
| CN (1) | CN105378236B (en) |
| WO (1) | WO2015031887A1 (en) |
Families Citing this family (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US10563549B2 (en) | 2015-09-25 | 2020-02-18 | Eaton Intelligent Power Limited | Cylinder deactivation control and methods |
| DE112016005846T5 (en) | 2016-01-19 | 2018-08-30 | Eaton Intelligent Power Limited | Cylinder deactivation and engine braking for thermal management |
| WO2017182631A1 (en) * | 2016-04-21 | 2017-10-26 | Eaton Srl | Valve train assembly |
| EP3455469B1 (en) * | 2016-05-12 | 2021-01-06 | Eaton Intelligent Power Limited | Rocker arm |
| US11578672B2 (en) | 2016-08-17 | 2023-02-14 | Eaton Intelligent Power Limited | Friction mitigation in cylinder deactivation |
| US11187162B2 (en) | 2016-08-17 | 2021-11-30 | Eaton Intelligent Power Limited | Extended coast and controlled deceleration using cylinder deactivation |
| US11905860B2 (en) | 2019-11-20 | 2024-02-20 | Eaton Intelligent Power Limited | Latch assembly, latching device, and rocker arm |
| KR20230173470A (en) | 2022-06-17 | 2023-12-27 | 현대자동차주식회사 | CDA Rocker Arm System with Oil Double Supply Line and Method thereof |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5431133A (en) * | 1994-05-31 | 1995-07-11 | General Motors Corporation | Low mass two-step valve lifter |
| US6966291B1 (en) * | 2004-10-28 | 2005-11-22 | Delphi Technologies, Inc. | Latch timing mechanism for a two-step roller finger cam follower |
| US7121241B1 (en) * | 2006-01-10 | 2006-10-17 | Eaton Corporation | Valve control system including deactivating rocker arm |
| US7798112B2 (en) * | 2005-11-21 | 2010-09-21 | Eaton Corporation | Dual lift rocker arm latch mechanism and actuation arrangement therefor |
| CN103114884A (en) * | 2011-11-06 | 2013-05-22 | 伊顿公司 | Latch pin assembly, rocker arm employing the latch pin assembly and method |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6588394B2 (en) * | 2000-09-22 | 2003-07-08 | Delphi Technologies, Inc. | Model-based control of a solenoid-operated hydraulic actuator for engine cylinder deactivation |
| US20050188930A1 (en) * | 2004-02-18 | 2005-09-01 | Best Richard R. | Valve deactivation device |
| CN102892977B (en) * | 2010-03-19 | 2015-04-01 | 伊顿公司 | Switching rocker arm and method for orientedly switching latch of rocker arm |
-
2014
- 2014-09-02 CN CN201480037996.1A patent/CN105378236B/en not_active Expired - Fee Related
- 2014-09-02 EP EP14840581.4A patent/EP3039256B1/en not_active Not-in-force
- 2014-09-02 WO PCT/US2014/053689 patent/WO2015031887A1/en active Application Filing
-
2016
- 2016-02-25 US US15/053,231 patent/US20160169064A1/en not_active Abandoned
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5431133A (en) * | 1994-05-31 | 1995-07-11 | General Motors Corporation | Low mass two-step valve lifter |
| US6966291B1 (en) * | 2004-10-28 | 2005-11-22 | Delphi Technologies, Inc. | Latch timing mechanism for a two-step roller finger cam follower |
| US7798112B2 (en) * | 2005-11-21 | 2010-09-21 | Eaton Corporation | Dual lift rocker arm latch mechanism and actuation arrangement therefor |
| US7121241B1 (en) * | 2006-01-10 | 2006-10-17 | Eaton Corporation | Valve control system including deactivating rocker arm |
| CN103114884A (en) * | 2011-11-06 | 2013-05-22 | 伊顿公司 | Latch pin assembly, rocker arm employing the latch pin assembly and method |
Also Published As
| Publication number | Publication date |
|---|---|
| US20160169064A1 (en) | 2016-06-16 |
| EP3039256A4 (en) | 2017-04-19 |
| WO2015031887A1 (en) | 2015-03-05 |
| CN105378236A (en) | 2016-03-02 |
| EP3039256B1 (en) | 2018-03-21 |
| EP3039256A1 (en) | 2016-07-06 |
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