CN204804892U - Switch switching rocking arm subassembly of rocking arm subassembly, latch assembly that is used for switching rocking arm subassembly, manufacture equipment and economy - Google Patents

Abstract

The utility model discloses a switch the new face breech lock seat of rocking arm subassembly, should switch in variable valve actuator disk (VVA) the system that the rocking arm subassembly was used in explosive motor. This breech lock seat utilizes new face fixing device and pressure spare interact ground to form in the switching rocking arm of having assembled. This pressure spare interact ground forms the crooked concave part that has suitable camber, position and the degree of depth, simultaneous measurement several gap size. Because the breech lock seat forms on the rocking arm subassembly of having assembled, the degree of depth design of this breech lock seat has become to consider the error in the parts in the formation clearance of rocking arm subassembly. Consequently, because the size of breech lock seat has compensated the error of all parts, so may not make all parts so accurately. This rocking arm subassembly part can make to such an extent that do not accord with the strict standard so now, but still has formed the accuracy that those rocking arm subassemblies are the same that has and make according to previous method.

Description

Switch rocker arm assembly, for switching the switching rocker arm assembly of the latch assembly of rocker arm assembly, manufacturing equipment and economy

The cross reference of related application

This application claims the rights and interests of following U.S. Provisional Application: the name submitted on March 1st, 2013 is called 61/771 of " ProcesstoFormaLatchInterfaceforaValveActuatingDevice ", 721 (EATN-0106-P01) and name are called 61/771,716 (EATN-0105-P01) of " LatchingMechanismInterfaceforaValveActuatiingDevice "; The name submitted on March 1st, 2013 is called 61/771,769 (EATN-0202-P01) of " DiscreteVariableValveLiftDeviceandMethods "; The U.S. Patent application 14/188,339 (EATN-0212-U01) that on February 24th, 2014 submits to; The U.S. Patent application 13/868,068 (EATN-0210-U01) that on April 22nd, 2013 submits to; The U.S. Patent application 13/868,067 (EATN-0209-U01) that on April 22nd, 2013 submits to; The U.S. Patent application 13/873,797 (EATN-0208-U01) that on April 30th, 2013 submits to; The U.S. Patent application 13/873,774 (EATN-0207-U01) that on April 30th, 2013 submits to; The U.S. Patent application 13/868,061 (EATN-0206-U01) that on April 22nd, 2013 submits to; The U.S. Patent application 13/868,054 (EATN-0202-U01-C01) that on April 22nd, 2013 submits to; The U.S. Patent application 13/868,045 (EATN-0202-U01) that on April 22nd, 2013 submits to; The U.S. Patent application 13/868,035 (EATN-0201-U01-C01) that on April 22nd, 2013 submits to; The U.S. Patent application 13/868,025 (EATN-0201-U01) that on April 22nd, 2013 submits to; International Patent Application PCT/US2013/068503 (EATN-0211-WO) that on November 5th, 2013 submits to; International Patent Application PCT/US2013/038896 (EATN-0210-WO) that on April 30th, 2013 submits to; International Patent Application PCT/US2013/037665 (EATN-0206-WO) that on April 22nd, 2013 submits to and International Patent Application PCT/US2013/037667 (EATN-0204-WO) that on April 22nd, 2013 submits to.

U.S. Patent application 14/188, 339 (EATN-0212-U01) require the U.S. Provisional Patent Application 61/768 that on February 22nd, 2013 submits to, the rights and interests of 214 (EATN-0100-P01), and be 61/722 of requirement submission on November 5th, 2012, the part continuation application of the International Patent Application PCT/US2013/068503 (EATN-0211-WO) of the rights and interests of 765 (EATN-0211-P01), or the part continuation application of following U.S. Patent application and international patent application: the U.S. Patent application 13/868 that on April 22nd, 2013 submits to, 068 (EATN-0210-U01), the U.S. Patent application 13/868 that on April 22nd, 2013 submits to, 067 (EATN-0209-U01), the U.S. Patent application 13/873 that on April 30th, 2013 submits to, 797 (EATN-0208-U01), the U.S. Patent application 13/873 that on April 30th, 2013 submits to, 774 (EATN-0207-U01), the U.S. Patent application 13/868 that on April 22nd, 2013 submits to, 061 (EATN-0206-U01), the U.S. Patent application 13/868 that on April 22nd, 2013 submits to, 054 (EATN-0202-U01-C01), the U.S. Patent application 13/868 that on April 22nd, 2013 submits to, 045 (EATN-0202-U01), the U.S. Patent application 13/868 that on April 22nd, 2013 submits to, 035 (EATN-0201-U01-C01), the U.S. Patent application 13/868 that on April 22nd, 2013 submits to, 025 (EATN-0201-U01), International Patent Application PCT/US2013/068503 (EATN-0211-WO) that on November 5th, 2013 submits to, International Patent Application PCT/US2013/038896 (EATN-0210-WO) that on April 30th, 2013 submits to, International Patent Application PCT/US2013/037665 (EATN-0206-WO) that on April 22nd, 2013 submits to and International Patent Application PCT/US2013/037667 (EATN-0204-WO) that on April 22nd, 2013 submits to.

Submit on April 22nd, 2013 13/868, 068 (EATN-0210-U01), submit on April 22nd, 2013 13/868, 067 (EATN-0209-U01), submit on April 30th, 2013 13/873, 797 (EATN-0208-U01), submit on April 30th, 2013 13/873, 774 (EATN-0207-U01), submit on April 22nd, 2013 13/868, 061 (EATN-0206-U01), submit on April 22nd, 2013 13/868, 054 (EATN-0202-U01-C01), submit on April 22nd, 2013 13/868, 045 (EATN-0202-U01), submit on April 22nd, 2013 13/868, 035 (EATN-0201-U01-C01), submit on April 22nd, 2013 13/868, the PCT/US2013/038896 (EATN-0210-WO) that 025 (EATN-0201-U01) these U.S. Patent applications and on April 30th, 2013 submit to, the PCT/US2013/037665 (EATN-0206-WO) that on April 22nd, 2013 submits to and PCT/US2013/037667 (EATN-0204-WO) these international patent applications that on April 22nd, 2013 submits to require the rights and interests of following U.S. Provisional Patent Application and U.S. Non-provisional Patent application: the U.S. Provisional Patent Application 61/640 that on April 30th, 2012 submits to, 713 (EATN-0210-P01), the U.S. Provisional Patent Application 61/640 that on April 30th, 2012 submits to, 709 (EATN-0209-P01), the U.S. Provisional Patent Application 61/637 that on April 24th, 2012 submits to, 786 (EATN-0206-P01), the U.S. Provisional Patent Application 61/636 that on April 20th, 2012 submits to, 277 (EATN-0205-P01), the U.S. Provisional Patent Application 61/771 that on March 1st, 2012 submits to, 769 (EATN-0202-P01), all in the U.S. Non-provisional Patent application 13/051 that on March 18th, 2011 submits to, 839 and 13/051, 848.Application 13/051,839 and 13/051,848 all requires the rights and interests of the U.S. Provisional Application 61/315,464 that on March 19th, 2010 submits to.

Application 13/873,774 (EATN-0207-U01), 13/873,797 (EATN-0208-U01) requires the rights and interests of 61/640,705 (EATN-0207-P01) and 61/640,707 (EATN-0208-P01) all submitted on April 30th, 2012.These applications are all included in herein with way of reference.

Technical field

The application relate to for explosive motor, more specifically for more effective novelty variable valve actuation switch rocker arm system rocking arm design.

Background technique

Energy cost about the grobal environment of gasoline consumption growth and greenhouse gas emission and economic focus, global range rises and makes law-making stipulation and consumption demand produce compared with the demand of low operating cost and changes.Along with these regulations and demand become more and more urgent, the engine technology of advanced person must be developed and the advantage needed for realization.

Figure 1B 1 to 1B4 describes some the valve mechanism devices used now.In model I (21) and model II (22) two kinds of devices, the camshaft with one or more valve actuation lobe 30 is positioned at (overhead cam) on engine valve 29.In model I (21) valve mechanism, overhead cam salient angle 30 is by hydraulic lash adjuster (HLA) 812 Direct driver valve.In model II (22) valve mechanism, overhead cam salient angle 30 drives rocking arm 25, and rocking arm first end pivotable on HLA812, simultaneously the second end actuate valves 29.

In model III (23), the first end of rocking arm 28 rides over and is positioned on cam lobe 30, simultaneously the second end actuate valves 29 of rocking arm 28.When cam lobe 30 is rotated, rocking arm is around stationary axle 31 pivotable.HLA812 can be placed between valve 29 top and rocking arm 28.

In model V (24), cam lobe 30 utilizes the first end of push rod 27 Direct driver rocking arm 26.The HLA812 illustrated is placed between cam lobe 30 and push rod 27.Second end actuate valves 29 of rocking arm 26.When cam lobe 30 rotates, rocking arm is around stationary axle 31 pivotable.

Also as shown in Figure 1A 1-1A2, the percentage-indicate the most general structure manufactured by 2019 of manufacturing forecast-the be shown as whole market of model II (22) valve mechanism in motor car engine.

Technology emphasis is at model II (22) valve mechanism, and it rubs by reducing, pumping improves petrolic whole efficiency, and thermal loss is introduced into and uses in-engine fuel oil with the best.Some in these variable valve actuation (VVA) technology have been introduced into and have had documentary evidence.

VVA device can be lift range variable (VVL) system, cylinder deactivation (CDA) system, the middle description of U.S. Patent application NO.13/532777 " SingleLobeDeactivatingRockerArm " as submitted on July 25th, 2012-overall the including at this of the document is quoted, and can also be other valve actuation systems.As indication, improve these mechanisms to improve performance, fuel economy and/or to reduce motor discharge.The VVA rocker arm assembly of some models is included in the inner rocker arm within outer rocker arm, and they are biased together by torque spring.Breech lock is when making interior both outer rocker arms with a cell moving when latched position.When non-latched position, rocking arm can move independently of each other.

Switch rocking arm and can control valve actuation by switching between kayser and non-kayser state, as mentioned above, generally include inner arm and outer arm.In some cases, the cam lobe that these arm contact are different, such as low lift lobe, high lift lobe and without lift lobe.Mechanism needs to switch rocking arm pattern in the mode of applicable internal combustion engine operation.

Rocking arm passes through camshaft actuated, to activate the cylinder air-breathing or exhaust valve that are usually arranged in cylinder head.

Be provided with stretch out from cylinder head mechanism, such as cam tower, to guarantee that camshaft designs for overhead cam.Spark plug tube is also had to protrude upward from the top of each cylinder through lid to hold spark plug.

As mentioned above, the VVA switching rocker arm assembly of some mode of executions is included in the rocking arm in rocking arm, and they are biased together by the spring of any side.Because the design of inside/outside arm uses roller to contact cam lobe usually at center, advantageously keep the width that roller is same with cam lobe.Therefore, the structure of any one end of roller adds width to rocker arm assembly and causes it wider compared with first non-VVA rocking arm, and too wide and can not be applicable to specific Cylinder head design.

Such as, some model II engine cylinder covers use the spark plug tube of the cam tower with the hydraulic lash adjuster (HLA) of close lid center line and the one end hindering wide VVA switching rocker arm assembly.

The manufactured person of many engine components is designed to and specific cylinder head cooperating, makes cylinder head be difficult to change, because change may affect some inter-related components, may increase cost or cause fit up gap problem.

To run and the example improving the VVA technology of fuel economy is discrete variable valve lift (DVVL) for changing in model II fuel engine, sometimes switching rocking arm also referred to as DVVL.DVVL is limited by the engine valve that use discrete variable valve lift state and standard " partial throttling " contrast and starts the work of cylinder intake stream.Second example is cylinder deactivation (CDA).Under part load condition by using CDA that fuel economy can be improved, close other cylinders with the combustion cylinders running selection under high loads simultaneously.

Environmental Protection Agency (EPA) display fuel economy when DVVL is applied to various motorcar engine improves 4%.The report more early initiated by american energy mechanism is pointed out, the benefit of DVVL be improve 4.5% fuel economy.Due to normaling cruise the most life consumption of automobile in operation at " partial throttling ", can take as when these restriction losses minimize and greatly improving fuel economy.For CDA, research display fuel economy increases, after considering and causing local resistance due to shifter cylinder, on average between 2 and 14%.Current, need the VVA rocking arm of applicable specific Cylinder head design for increasing performance, Economy and/or reduction discharge.

Switch rocking arm for changing running and the performance of motor.Such as, can use provide variable valve actuation (VVA)-such as lift range variable (VVL) and cylinder deactivation (CDA)-specific rocking arm.U.S. Provisional Patent Application 61/636,277 (EATN-0205-P01, pending trials) are described VVL in detail and are switched the 26S Proteasome Structure and Function of rocking arm, and reader for whole description with reference to this file.Research and develop improving the performance of motor, fuel economy and/or reducing discharge.The VVA rocker arm assembly of some types comprises the inner rocker arm being positioned at outer rocker arm, and they are biased in together by torque spring.Cause inner rocker arm and outer rocker arm to move as integrated unit when breech lock is in locked position.During unblock, rocking arm is allowed to move independently of each other.The breech lock of inner rocker arm abuts against on the breech lock seat of outer rocker arm (or, breech lock can on outer rocker arm).

Thinking in the past, in order to utilize round rocking arm breech lock, needing the fitting surface of the outer rocker arm in assembly to have bending fitting surface through grinding.This fitting surface can be called breech lock seat.

Described breech lock seat needs to have the radius very strictly mated with breech lock radius.The release that slightly too small breech lock seat causes clamping and postpones.Also cause the bight of breech lock slam latch seat in breech lock engaging process.Larger breech lock seat or less breech lock seat can cause less desirable wearing and tearing.

Due to tolerance, needs are processed by grinding.This can require more accurately and the manufacturing process of costliness.In addition, should not limit breech lock suitably extend and shrink.

Another latch design comprises the multiple breech lock of formation, measures each breech lock, and is classified to them by breech lock width.From breech lock miscellaneous, select breech lock that be applicable to, that have specific frame height, wherein transformable frame height forms applicable gap.This is consuming time, and needs a large amount of parts.

Current, need to have suitable breech lock, operate switch rocking arm breech lock efficiently with breech lock seat good alignment, and needs are for the manufacture of the method for switching rocking arm breech lock seat.

Model utility content

VVA system for the advanced person of piston internal combustion engines combines CDA or DVVL of valve lift control gear-such as and switches rocking arm, the hydraulic actuating of valve lift actuating method-such as use pressurized engine fluid (lubricant oil), software and hardware control system and enabling tool.Enabling tool can comprise sensing detection and arrange instrument, OCV design, DFHLA design, torque spring, special coating, algorithm, physical layout etc.

In one embodiment, disclose a kind of rocker arm assembly, this rocker arm assembly comprise multiple rocking arm and link together additional structure-they have the manufacturing tolerances causing mechanical clearance, also comprise the breech lock with latch pin and breech lock seat, this breech lock seat is suitable for receiving and fixing latch pin.This breech lock seat comprises the recess had with the shape of the shape complementarity of latch pin, the degree of depth that described recess is such, and this degree of depth is chosen to compensate mechanical clearance at least partially, to form predetermined gap.

In many embodiment:, disclose a kind of switching rocker arm assembly of economy, even if this assembly is configured with when its tolerance is greater than the parts of existing design also can provide predetermined gap.With the first rocking arm of the tolerance produced rocker arm assembly larger than prior art design, there is first end and the second end.Also have with tolerance produced second rocking arm larger than prior art design, this first rocking arm has the first end be pivotally connected to the first end of the first rocking arm, and the roller bearing be positioned on the first rocking arm to be suitable for riding on cam and to activate the first rocking arm.This rocker arm assembly has breech lock, this breech lock has the latch pin on the second end of that is arranged in the first and second rocking arms, be positioned at the breech lock seat on the second end of another rocking arm, breech lock runs to cause rocking arm relative to each other to fix when locking, and allows pivotable independently of each other when unlocking.Breech lock seat has recess, and the shape of this recess is for receiving latch pin, and the increase gap that the dimension compensation of this recess is formed because of the manufacturing tolerances increased at least partially, and forms predetermined gap.

In one embodiment, disclose a kind of rocker arm assembly of improvement, it has obstruction side (side be obstructed) and without hindrance side (side be not obstructed), and comprise the external structure with first end, the inner rocker arm structure be assemblied in this external structure, this inner structure also has first end.The rocker arm assembly of this improvement has axle, and this axle pivotable connects the first end of inner structure to external structure, can rotate to make inner structure in external structure around this axle.At least one torque spring on the side of this axle, and rotates this inner structure of bias voltage relative to external structure.External structure is when producing the first Offset portion, to provide additional gap in obstruction side when hindering and side extending from the second end to first end towards the skew of without hindrance side.This design makes the rocking arm of improvement can be fitted in this engine cylinder cover in the obstruction side of the engine cylinder cover with obstruction.

In one embodiment, disclose a kind of rocker arm assembly of improvement, it has obstruction side and without hindrance side, and comprises the external structure with first end, the inner rocker arm structure be assemblied in this external structure, and this inner structure also has first end.One axle makes the first end of inner structure be pivotally connected to external structure, and such inner structure can rotate around this axle in external structure.At least one torque spring is arranged on the without hindrance side of this axle, and this torque spring rotates this inner structure of bias voltage relative to external structure.When hindering the external structure on side to extend from the second end towards first end, this external structure produces the first Offset portion towards the skew of without hindrance side.This first Offset portion provides additional gap on obstruction side.

In one embodiment, disclose a kind of rocker arm assembly of improvement, it has obstruction side and without hindrance side.The rocker arm assembly of this improvement comprises the external structure of the first end with band Offset portion, is assemblied in the inner rocker arm structure in external structure.This inner structure also has first end.Axle makes the first end pivotable of inner structure be connected to external structure, can rotate to make inner structure in external structure around this axle.The rocker arm assembly of this improvement has at least one torque spring on the side of this axle, to be rotatably biased toward inner structure relative to external structure.When on obstruction side, external structure extends from the second end towards first end, this external structure bends smoothly towards without hindrance side.This produces the first Offset portion, and this first Offset portion provides additional gap on obstruction side.This makes this mode of execution can be assembled to and have in the engine cylinder cover of obstruction in obstruction side.

In one embodiment, a kind of discrete variable valve lift (DVVL) system of improvement is disclosed.Discrete variable valve lift (DVVL) system of this improvement for providing two discrete valve lift states in single rocking arm.Describe above the mode of execution of the method proposed relates to and model II valve mechanism shown in Figure 1B 2.Can be applied in motorcar engine (having four cylinders in an embodiment) at the mode of execution of this system proposed, this motor has electric hydraulic fluid control valve, two supply hydraulic lash adjuster (DFHLA) and DVVL and switches rocking arm.DVVL described here switches rocking arm embodiment and focuses on the design and improvement that switch roller finger wheel follower (SRFF) rocker arm system, and it makes carry out double mode discrete variable valve lift on end pivot roller finger wheel follower valve mechanism.This switching rocking arm configuration comprises the low friction roller bearing interface for low lift events, and keeps the adjustment of normal hydraulic lash to non-maintaining valve mechanism operation.

Pattern switches (otherwise that is, from low to high lift or) and rotates in (rotating a circle) at a cam and complete, and makes driver clearer and more definite.SRFF installs the larger change of required top board in preventing available engine from designing.The load-bearing surface of cam interface can comprise the roller bearing for low lift operation and the diamond like carbon coating slide block (skidding) for high lift operation.The instruction of the application can reduce quality and moment of inertia, increases rigidity to complete power performance required in low and high lift pattern simultaneously.

Diamond like carbon coating (DLC coating) allows the higher slide block interfacial stress in close package.Test result shows, and this technology is sane and meets all life-span needs, extends to the demand in working life of six times in some respects.Screened substituting material and surface treatment method, result display DLC coating is the most feasible.The technological progress that the application proposes is to use diamond-like-carbon (DLC) coating on the slide block that DVVL switches rocking arm.

System Verification Test result shows, and this system meets power and durability demand.Present patent application is also devoted to the durability of SRFF design, for meeting car durability demand.A large amount of durability tests has been carried out to high speed, low speed, switching and cold start operation.High engine speed test result is presented at more than motor 7000rpm has stable valve mechanism dynamic.System wear resistance need satisfaction is for switching, sliding, roll and the end-of-life standard at torque spring interface.An important measurement Law for assessment of wearing and tearing monitors the change in valve clearance.The life-span display gap change that wear resistance needs is can accept in window.Mechanical aspects shows sane performance in all tests comprising the slide block interface containing diamond-like-carbon (DLC) coating.

Due to flexible and compact packaging, this DVVL system can be embodied in multiple cylinder engine.DVVL arranges the combination of any air inlet or the exhaust valve that can be applied on piston driven internal combustion machine.Enabling tool comprises OCV, DFHLA, DLC coating.

In this second embodiment, a kind of single salient angle cylinder deactivation (cylinderdeactivation) (CDA-1L) system of improvement is described.Single salient angle cylinder deactivation (CDA-1L) system of this improvement is for stopping one or more cylinder.The embodiment proposed at this relates to model II valve above-mentioned and shown in Figure 22.Motorcar engine can be applied at the mode of execution of this system proposed and (there are doubly several cylinders of 2 in embodiments, such as 2,4,6,8) in, this motor has electric hydraulic fluid control valve, two supply hydraulic lash adjuster (DFHLA) and CDA-1L and switches rocking arm.CDA-1L described here switches rocking arm embodiment and focuses on the design and improvement that switch roller finger wheel follower (SRFF) rocker arm system, and this system makes carry out lift/without lift operation for end roller finger wheel follower valve.This switching rocking arm configuration comprises the low friction roller bearing interface for cylinder deactivation event, and keeps the adjustment of normal fluid pressure gap to non-maintaining valve mechanism operation.

Pattern for CDA-1L system switches in a cam rotation and completes, so that more transparent to driver.SRFF installs the larger change of required top board in preventing available engine from designing.The instruction of the application can reduce quality and moment of inertia, simultaneously increase rigidity in case lift or without lift mode in realize required power performance.

CDA-1L System Verification Test result shows, and this system meets power and durability demand.Present patent application is also devoted to the durability demand of the SRFF design met needed for car durability demand.A large amount of durability test is carried out to high speed, low speed, switching and cold start operation.High engine speed test result is presented at more than motor 7000rpm stable valve mechanism power.System wear resistance need satisfaction is for switching, rolling and the end-of-life standard at torque spring interface.An important measurement Law for assessment of wearing and tearing is the change monitoring valve clearance.The life-span display that wear resistance needs, gap change is can accept in window.Mechanical aspects shows sane performance in whole test.

By flexible and compact packaging, this CDA-1L system can be embodied in multiple cylinder engine.Enabling tool comprises OCV, DFHLA and the design of special torque spring.

Rocking arm is described for joint pin has lift lobe cam to each valve.This rocking arm comprises outer arm, inner arm, pivotal axis, the lift lobe of contact bearing, bearing shaft and at least one bearing shaft spring.Outer arm has the first and second outer webs and is configured to install the outer pivot axis hole of pivotal axis.Inner arm is between the first and second outer webs, and the first inner webs and the second inner webs.First and second inner webs have in order to hold and to keep pivot axis hole and the inner bearing shaft through-hole for installing bearing shaft in pivotal axis.

Pivotal axis is assemblied in interior pivot axis hole and outer pivot axis hole.

Bearing shaft is arranged in the bearing axis hole of inner arm.

Bearing shaft spring be fixed to outer arm and with bearing shaft biased contact.Lift lobe contact is installed to the bearing in the bearing shaft between the first and second inner webs.

Another mode of execution can be described as the rocking arm for contacting each engine valve with the cam of single lift lobe.This rocking arm comprises outer arm, inner arm, is configured to move to from the single lift lobe transmission of cam cam contact assembly and at least one biasing spring of rocking arm.

Rocking arm also comprises the first outer webs and the second outer webs.

Inner arm is placed between the first and second outer webs, and has the first inner webs and the second inner webs.

Inner arm is fixed to outer arm by the pivotal axis being configured to allow inner arm to be rotated around pivotal axis relative to outer arm.

Cam contact assembly is placed between the first and second inner webs.

At least one biasing spring is fixed to outer arm and biased contact cam contact assembly.

Another mode of execution can be described as the stopping rocking arm for contacting the cam with single lift lobe.This stopping rocking arm comprising first end and the second end, outer arm, inner arm, pivotal axis, be configured to can from the lift lobe transmission of cam move to rocking arm lift lobe contact assembly, be configured to selectivity to stop breech lock and at least one biasing spring of rocking arm.

Outer arm comprise the first outer webs and the second outer webs, for install pivotal axis outer pivot axis hole, for receiving the axial trough of lift lobe contact assembly, to allow the free-runing operation of lift lobe contact member.

Inner arm is placed between first the second outer webs, and has the first inner webs and the second inner webs.First inner webs and the second inner webs have for installing in pivotal axis pivot axis hole and for installing lift lobe contact element piece bores in lift lobe contact member.

The first end of the contiguous rocking arm of pivotal axis is installed and is placed in interior pivot axis hole and outer pivot axis hole.

Breech lock is arranged to the second end of contiguous rocking arm.

Lift lobe contact member is arranged in the lift lobe contact element piece bores of inner arm and the axial trough of outer arm, and is between pivotal axis and breech lock.

Biasing spring is fixed to outer arm and biased contact lift lobe contact member.

Accompanying drawing explanation

Be appreciated that the scope of element shown in figure only represents an example in scope.It will be understood by those skilled in the art that discrete component can be designed as multiple element or multiple element can be designed as discrete component.The element being expressed as internal feature can be implemented as surface, and vice versa.

In addition, in the accompanying drawings and the description below, whole drawing and description use the parts that identical reference character represents similar respectively.Correspondingly, accompanying drawing may not drawn and the ratio of some parts is exaggerated for convenience of description to scale.

Figure 1A 1-1A2 illustrates 2012 and the relative percentage of engine model in 2019.

Figure 1B 1-1B4 illustrates model I, model II, the general device of model III and model V valve mechanism and commercially available size.

Fig. 2 A and 2B illustrates that air inlet and exhaust valve system arrange respectively.

Fig. 3 A-3B illustrates the critical piece comprising DVVL system, comprises hydraulic actuator.

Fig. 4 illustrates to be in operation and can arrange the perspective view of the exemplary switching rocking arm with three salient angle cams.

Fig. 5 represents the valve lift state diagram for for the air inlet of example DVVL embodiment and the camshaft crankcase temperature of exhaust valve.

Fig. 6 is the Systematical control chart for hydraulic actuating DVVL rocker arm assembly.

Fig. 7 illustrates that rocking arm oil duct and control valve are arranged.

Fig. 8 illustrates and switches rocker arm system in the hydraulic actuation system of low lift (non-kayser) operation period and condition for example DVVL.

Fig. 9 illustrates and switches rocker arm system in the hydraulic actuation system of high lift (kayser) operation period and condition for example DVVL.

Figure 10 illustrates that the example with Double-hydraulic clearance adjuster (DFHLA) switches the side cross-sectional view of rocker arm assembly.

Figure 11 is the sectional view of DFHLA.

Figure 12 illustrates diamond like carbon coating.

Figure 13 illustrates the instrument for the position or relative movement responding to DFHLA ball plunger.

Figure 14 illustrates and is combined to measure the instrument of valve relative to known state movement with valve stem.

Figure 14 A and 14B illustrates that use three coils are to measure the sectional drawing of the first linear variable differential transducer of valve stem motion.

Figure 14 C and 14D illustrates that use two coils are to measure the sectional drawing of the second linear variable differential transducer of valve stem motion.

Figure 15 illustrates that example switches another perspective view of rocking arm.

Figure 16 illustrates the instrument being designed to sensed position and/or motion.

Figure 17 is described in the transition period between high lift and low lift condition, OCV actuating current, activates the plotted curve of the relation between oil pressure and valve lift condition.

Figure 17 A is described in the breech lock transition period, OCV actuating current, activates the plotted curve of the relation between oil pressure and latch mode.

Figure 17 B is described in another breech lock transition period, OCV actuating current, activates the plotted curve of the relation between oil pressure and latch mode.

Figure 17 C describes valve lift curve and the plotted curve for the relation between high lift and the actuating oil pressure of low lift condition.

Figure 18 is the control logic figure of DVVL system.

Figure 19 illustrates that example switches the decomposition view of rocking arm.

Figure 20 is the chart described for the low lift of DVVL rocker arm assembly and the oil pressure conditions of high lift operation and fluid control valve (OCV) state.

Figure 21-22 illustrates and represents oil temperature and the plotted curve of relation between the breech lock response time.

Figure 23 is the time diagram of the existing variable switch window switching rocking arm for example DVVL, in 4 cylinder engines, by each control two cylinder activation oil pressure cntrol of two OCV.

Figure 24 is the side cross-sectional view that the DVVL being described in the breech lock preload before switching from high lift to low lift switches rocking arm.

Figure 25 is the side cross-sectional view of the DVVL switching rocking arm of the breech lock preload be described in from low lift to high lift before switching.

Figure 25 A is the side cross-sectional view of the DVVL switching rocking arm describing the critical gear when switching between low lift and high lift.

Figure 26 switches the variable switch window of rocking arm for example DVVL and forms the expansion time diagram of mechanism's switching time, in 4 cylinder engines, is controlled the actuating oil pressure cntrol of two cylinders by two OCV separately.

Figure 27 illustrates that example switches the perspective view of rocking arm.

Figure 28 illustrates that example switches the top view of rocking arm.

Figure 29 illustrates the sectional view intercepted from the line 29-29 Figure 28.

Figure 30 A-30B illustrates the sectional view of example torque spring.

Figure 31 illustrates the bottom view of outer arm.

Figure 32 illustrate bolt lock mechanism kayser state along the line 32 of Figure 28,33-32,33 sectional view.

Figure 33 illustrates the sectional view of bolt lock mechanism in non-kayser state.

Figure 34 illustrates that substituting latch pin designs.

Figure 35 A-35F illustrates the several retention devices for locating stud.

Figure 36 illustrates that example latch pin designs.

Figure 37 illustrates substituting bolt lock mechanism.

Figure 38-40 illustrates that assembling switches the exemplary method of rocking arm.

Figure 41 illustrates the alternate embodiments of pin.

Figure 42 illustrates the alternate embodiments of pin.

Figure 43 illustrates the various gap measurement switching rocking arm.

Figure 44 illustrates the perspective view of the example inner arm switching rocking arm.

Figure 45 illustrates the perspective view that the inner arm switching rocking arm is looked from below.

Figure 46 illustrates the perspective view of the example outer arm switching rocking arm.

Figure 47 illustrates that example switches the sectional view of the latch assembly of rocking arm.

Figure 48 is the plotted curve of the gap-camshaft angle switching rocking arm.

Figure 49 illustrates that example switches the side cross-sectional view of rocker arm assembly.

Figure 50 illustrates to have the perspective view that maximum deflection determines the outer arm in region under that loading condition.

Figure 51 illustrates that example switches the top view of rocking arm and three salient angle cams.

Figure 52 illustrates that example switches the sectional view of rocking arm along the line 52-52 of Figure 51.

Figure 53 illustrates that example switches the decomposition view of rocking arm, and display example switches the critical piece affecting inertia of rocker arm assembly.

Figure 54 illustrates and optimizes the design cycle that example switches relation between the inertia of rocker arm assembly and rigidity.

Figure 55 illustrates and switches the inertia of rocker arm assembly design iteration and the indicatrix of rigidity for example.

Figure 56 illustrates and represents that example switches the pressure of rocker arm assembly, deviation, load and the rigidity indicatrix relative to position.

Figure 57 illustrates and represents that some examples switch the indicatrix of rigidity relative to inertia of rocker arm assembly.

Figure 58 A-58C illustrates that many DVVL switch the rigidity of constituent elements of rocker arm assembly and the tolerance interval of the centrifugal pump of inertia.

Figure 59 is the side cross-sectional view of the example switching rocker arm assembly comprising DFHLA and valve.

Figure 60 illustrates and represents that example switches the indicatrix of some rigidity values relative to position of the constituent elements of rocker arm assembly.

Figure 61 illustrates that example switches the indicatrix of some mass distribution relative to position of the constituent elements of rocker arm assembly.

Figure 62 illustrates the test bench for measuring breech lock displacement.

Figure 63 is the view for testing the non-ignition test bench switching rocker arm assembly.

Figure 64 is the curve of valve displacement relative to camshaft angle.

Figure 65 illustrates the level of the key test for testing the durability switching roller finger wheel follower (SRFF) rocker arm assembly.

Figure 66 represents the test protocol through accelerated ageing system test cycle in assessment SRFF.

Figure 67 is the cake chart of the dependence test time representing SRFF durability test.

Figure 68 represents and to connect at test period and to monitor the resistance strain gauge of SRFF.

Figure 69 is the curve of the valve-closing speed of low lift mode.

Figure 70 is the distribution of valve height of drop.

Figure 71 shows the distribution of critical gear relative to camshaft angle.

Figure 72 represents one end of the new outer arm before use.

Figure 73 illustrates the typical wear of the outer arm after use.

Figure 74 illustrates average torque spring load loss in end-of-life test.

Figure 75 illustrates total mechanical clearance change of accelerated ageing system testing.

Figure 76 illustrates the end-of-life of the slide block with DLC coating, has minimal wear.

Figure 77 adopts crown camshaft surface embodiment.

Figure 78 illustrates a pair slide block on the support rocking arm that is connected on sample.

Figure 79 A illustrates the early stage loss of DLC coating in sample testing.

Figure 79 B represents the typical case of the sample tested under the design maximum with 0.2 degree of groove angle.

Figure 80 is the curve relative to engine life of the test pressure level with DLC coating test sample.

Figure 81 represents that the slide block before covering DLC coating with polishing or non-polished surface is increasing the curve in engine life.

Figure 82 describes and the flow chart tested the product grinding simultaneously carried out and glossing and be in progress.

Figure 83 represents that slider angles controls the result relative to three kinds of different grinding tools.

Figure 84 illustrates the Surface finish measurement for three kinds of different grinding tools.

Figure 85 illustrates the result at slide block grinding action period six different fixture maintenance outer arm.

Figure 86 is the curve of high lift pattern valve-closing speed.

Figure 87 illustrates the durability test stage.

Figure 88 illustrates the perspective view that example CDA-1L designs.

Figure 89 A illustrates the partial cross section side front view of the example SRFF-1L system with bolt lock mechanism and roller bearing.

Figure 89 B illustrates the front elevation of the example SRFF-1L system of Figure 89 A.

Figure 90 A and 90B represents that example SRFF-1L rocker arm assembly is in exhaust or the engine design of intake valve.

Figure 91 illustrates hydraulic fluid control system.

Figure 92 A-92B illustrates operating example SRFF-1L system, shows normal lift engine valve operation.

Figure 93 A, 93B and 93C illustrate operating example SRFF-1L system, show without lift engine valve operation.

Figure 94 illustrates example switch window.

Figure 95 illustrates the effect of camshaft phase modulation at switch window.

Figure 96 illustrates the breech lock response time for SRFF-1 system embodiment.

Figure 97 is the curve of the switch window time more than 40 degrees Celsius illustrated for example SRFF-1 system.

Figure 98 represents the curve considering the switch window time of camshaft phase modulation and oil temperature for example SRFF-1 system.

Figure 99 illustrates example SRFF-1L rocker arm assembly.

Figure 100 illustrates the decomposition view of the example SRFF rocker arm assembly of Figure 99.

Figure 101 illustrates the side view of the example SRFF-1L rocker arm assembly comprising DFHLA, valve stem and cam lobe.

Figure 102 illustrates the end elevation of the example SRFF-1L rocker arm assembly comprising DFHLA, valve stem and cam lobe.

The breech lock that Figure 103 represents in pressure loss situation is rejoined feature.

Figure 104 A-104B represents the camshaft alignment situation of example SRFF-1L system.

Figure 105 represents the power be applied on the RFF using hydraulic lash adjuster.

Figure 106 A-106B represents the equilibrium of forces of example SRFF-1L system in without lift mode.

Figure 107 is the chart of the oil pressure demand representing example SRFF-1 system.

Figure 108 A-108B represents the mechanical clearance of example SRFF-1 system.

Figure 109 represents for three salient angle CDA systems and the camshaft lift profile for example SRFF-1L system.

Figure 110 represents rigidity that many rocking arms the design plotted curve relative to moment of inertia.

Figure 111 illustrates the bottom closing velocity of the generation of the intake valve of example SRFF-1L system.

Figure 112 is the chart representing that torque spring test is summed up.

Figure 113 is the curve representing the displacement of pumping test period and pressure.

Figure 114 represents that example SRFF-1L system is through the durability in fc-specific test FC stage and gap change.

Figure 115 is in order to the clear perspective view removing the prior art cylinder head of parts.

Figure 116 is the elevational sectional view of the cylinder head of Figure 115.

Figure 117 is the perspective view of lift range variable (VVL) rocker arm assembly of prior art.

Figure 118 be according to an aspect of the utility model instruction, the perspective view of a left side (improvement) rocker arm assembly that lift range variable is provided.

Figure 119 is the top plan view of the improvement rocker arm assembly of Figure 118.

Figure 120 is the side view of the rocker arm assembly 400 of the improvement of Figure 118-119.

Figure 121 is the end elevation that the rocker arm assembly of the improvement of Figure 118-120 is observed from its hinge (first) end.

Figure 122 is the end elevation that the rocker arm assembly of the improvement of Figure 118-121 is observed from its breech lock (second) end.

Figure 123 is from the planimetric map of looking above the external structure of the first and second offset areas is shown.

Figure 124 is the planimetric map of looking from below of the external structure of Figure 123.

Figure 125 is the side view of external structure of an aspect according to the utility model instruction.

Figure 126 is the view on top of the inner structure of one side according to the utility model instruction.

Figure 127 is the view of the bottom of the inner structure of Figure 126.

Figure 128 is the view that the inner structure of Figure 126-127 is looked from top.

Figure 129 is the view that the inner structure of Figure 126-128 is looked from bottom.

Figure 130 is the end elevation that the inner structure of Figure 126-129 is observed from hinge (first) end.

Figure 131 is the end elevation that the inner structure of Figure 126-130 is observed from breech lock (second) end.

Figure 132 is that the rocker arm assembly of the improvement of Figure 118-122 is installed in the perspective view presented in cylinder head.

Figure 133 is from the perspective view of the improvement rocker arm assembly 400 of another viewpoint, Figure 118-122, and its display is installed in cylinder head.

Figure 134 illustrates the switching rocking arm of sections fit and the bottom of outer arm fitting surface.

Figure 135 illustrates the rocker arm assembly in Fig. 1, is just pressed at pin the carbide pin be in before in fitting surface in latch recesses shown in it.

Figure 136 illustrates the fixing device for forming recess in fitting surface.

Figure 137 illustrates the pressing step for being pressed into by pin in fitting surface.

Figure 138 illustrates a part for only outer arm, illustrates the recess in breech lock seat.

Embodiment

Word has their conventional and common implications as used herein, unless redefined in this manual, so will replace common implication in new definition.

Be appreciated that wording and term object illustrate and should not regard as restriction as used herein.Relating to single plural form is not to limit system of the present disclosure or method, their composition, behavior or element.The things listed after " comprising " used herein, " comprising ", " having ", " containing " and their distortion are meant to comprise or equivalent and other things.Relate to "or" to can be understood as and included, thus the phrase that any use "or" describes can be understood as single, more than one and all description phrases.Any relate to front and rear, left and right, upper and lower, high and low be for convenience of description, instead of restriction native system method or they consist of any one position or specific direction.Term " punching press ", " impression ", " impression " are synonyms.In addition, " carbide pin " and " carbide bar " is also synonym.

As described in different figures, in order to some sizes of the object structure that describes or part are amplified relative to other structures or part, thus, provide a description the general structure of the utility model theme.In addition, the All aspects of of the utility model theme describe with reference to structure shaping in other structures, part or part, or both simultaneously.As can be understood by persons skilled in the art, relate to structure to be formed in another structure or part " on " or " on " and to be interpreted as and can to relate to other component or part.Described here relate to structure or part be formed in another structure or part " on " and do not have intermediate structure or part be described as " directly " on component or part.Similar, be appreciated that it can directly connect when element relates to " connection ", " attaching ", " coupling (connection) " to another element, attaching, be couple to another element, or there is intermediary element.On the contrary, when element relates to " directly connecting ", " direct attaching ", " directly coupling " to another element, there is not intermediary element.

In addition, as used herein relative terms such as " on ", " on ", " top ", " top ", D score, " bottom " in order to describe the relation of a structure shown in the drawings or part and another structure or part.Be appreciated that relative terms such as " on ", " on ", " top ", " top ", D score, " bottom " object are the different direction comprising device except the direction of indication in figure.Such as, if device in figure rotates, be described as other structures or part " on " structure or part will change direction for other structures or part " under ".Similar, if the device in figure rotates along axle, be described as other structures or part " on " structure or part will change direction for or other structures or part " adjacent " or " left side ".Similar reference character relates to similar element in full.

VVA system embodiment: VVA system embodiment represents COMM communication, actuating method, analysis and control system and the common unique combination generating the enabling tool of VVA system.VVA system embodiment can comprise one or more enabling tool.

I. the explanation of discrete variable valve lift (DVVL) system embodiment

1.DVVL system survey

Switching rocker arrangement that is cam-actuated, discrete variable valve lift (DVVL) will be described below, this switching rocker arrangement is used the assembled hydraulic actuating of two supply hydraulic lash adjuster (DFHLA) and pressure control valve (OCV), and it is by the intake valve that is installed in model II valve mechanism.In an alternate embodiment, this layout can be applied to the combination of any air inlet on piston driven internal combustion machine or exhaust valve.

As shown in Figure 2 B, the exhaust valve mechanism in present embodiment comprises fixing rocking arm 810, single salient angle camshaft 811, standard hydraulic lash adjuster (HLA) 812 and exhaust valve 813.As shown in Fig. 2 A and Fig. 3 A-3B, the parts of intake valve mechanism comprise three salient angle camshafts 102, switch rocker arm assembly 100, have two supplies hydraulic lash adjuster (DFHLA) 100 of upper fluid flow port 506 and lower fluid flow port 512 and electric liquid solenoid oil control valve assembly (OCV) 820.OCV820 has entrance 821 and first and controls mouth 822 and the second control mouth 823.

With reference to figure 2A-2B, air inlet and exhaust valve mechanism have some geometrical shape, comprise isolated valve 813 and valve 112 isolated with DFHLA110 with HLA812.Keep common geometrical shape that DVVL system can be assembled together with model II cylinder head space that is existing or that improve slightly, use standard chain drive system simultaneously.As shown in Figure 4, the other parts that air inlet and exhaust valve mechanism have comprise valve 112, valve spring 114, valve spring retainer 116.Valve key and valve stem seal (not shown) are also total for air inlet and exhaust.By keeping common geometrical shape, using common elements to make the implementation cost of DVVL system minimize.

Intake valve organ shown in Fig. 3 A-3B works to open the intake valve 112 with high-lift cam crown of roll angle 104,106 or low lift cams crown of roll angle 108 together.High-lift cam crown of roll angle 104,106 is designed to provide the performance being equivalent to fixing intake valve mechanism, and comprises the circular part not having lift to produce, the lift part that can comprise linear lift transition and correspond to the projection of maximum lift.Low lift cams crown of roll angle 108 allows lower valve lift and early admission valve-closing.Low lift cams crown of roll angle 108 also comprises the circular part, the substantial linear part as lift transition and the projection corresponding to maximum lift that do not have lift to produce.Picture in Fig. 5 illustrates the curve of valve lift 818 relative to crank angle 817.Camshaft high lift curve 814 and fixing exhaust valve lift curve 815 are formed with low lifting curve 816 and contrast.The low lift events represented by curve 816 reduces lift and the endurance of air inlet event in partial throttling operation period, to reduce throttling loss and to realize the improvement of fuel economy.This is also referred to as early admission valve-closing, or EIVC.When needs full power runs, DVVL system becomes high lift curve 814 again, and it is similar to standard fixed lift event.Produce within a cam axle cycle from low lift to the transformation of high lift and reverse transformation.The exhaust lift event represented by curve 815 is fixed and runs with low lift or the identical mode of high lift air inlet event.

The system switched for control DVVL uses hydraulic actuating.The hydraulic control that the mode of execution that figure 6 illustrates the application's instruction uses and actuating system 800.Hydraulic control and actuating system 800 are designed to be commanded by control logic, and delivering hydraulic fluid is to mechanical latches assembly, and this mechanical latches assembly is for providing switching between high lift state and low lift condition.Controlled by control unit of engine 825 when mechanical switch procedure initialization.Shown in hydraulic control and the actuating system 800 four-cylinder II h type engine h in upright arrangement in described intake valve mechanism above, but those skilled in the art it is clear that, control and actuating system can be applied to the motor of other " models " and the cylinder of varying number.

That mentions above can combinationally use with DVVL system unit described here for some enabling tool in DVVL system described here, thus breaks unique combination, and wherein some will describe at this:

2.DVVL system enabling tool

Serve many purposes with different application for some technology in this system, they are described to the parts of DVVL system disclosed herein at this.These comprise:

2.1 pressure control valves (OCV) and oil control valve assembly

Referring now to Fig. 7-9, OCV, be a kind of control gear, its guides or direct pressurized hydraulic fluid does not switch between high lift pattern and low lift mode to cause rocking arm 100.The actuating of OVC and stopping (making it inaction) are caused by control gear signal 866.One or more OVC can be packaged in a module to form assembly.In one embodiment, OVC assembly 820 comprises two solenoid type OVC packaging together.In this embodiment, control gear provides signal 866 to OVC assembly 820, causing this assembly provides high pressure (in embodiments, the oil pressure of at least 2 bar) or low pressure is (in embodiments, 0.2-0.4 clings to) oily to oil pressure cntrol passage (gallery) 802,803, to make switching rocking arm 100 be in low lift or high lift pattern, respectively as shown in FIG. 8 and 9.This further describing of OCV assembly 820 mode of execution comprises in the following paragraphs.

2.2 pairs of supplies hydraulic lash adjuster (DFHLA)

The existence of some hydraulic lash controlling devices is the gaps in order to keep in motor.Rocking arm 100 (Fig. 4) is switched for DVVL, need the management of traditional gap, but traditional HLA device deficiency think switch provide necessary oil stream demand, stand the associated side load that applied by assembly 100 at run duration and be assembled to restricted packaging space.Describe a kind of with switch use together with rocking arm 100 compact two and supply hydraulic lash adjuster (DFHLA), it has to provide the series of parameters of low consumed optimization oil flow pressure and shape and in order to the series of parameters that manages side loads and shape.

As shown in Figure 10, ball plunger end 601 is assemblied in ball seat 502, and this ball seat allows to rotate freely in all directions.In some operating mode, this allows the side of ball plunger end 601 and possible asymmetric load, such as, when switching from high lift to low lift or vice versa.Compared with the typical pommel plunger for HLA device, DFHLA110 ball plunger end 601 by thinner material construction to stand side loads, the thickness of plunger shown in Figure 11 510.

The material selected for ball plunger end 601 can also have higher kinetic stress load allowable, such as chrome alum alloy.

Hydraulic flow path design in DFHLA110 is high flowing and low pressure loss, to guarantee the pumping loss that constant hydraulic pressure switches and reduces.As shown in Figure 11, DFHLA installs being dimensioned in the cylinder containing seat of outer sealing surface 511 within the engine.Cylinder containing seat has the closed fluid path in particular cross section region with formation in conjunction with the first oil flow channel 504.

As shown in Figure 11, preferred implementation comprises four oily head pieces 506 (only illustrating two), and they are arranged with the base portion of equidistant mode around the first oil flow channel 504.In addition, two the second oil flow channels 508 are arranged around ball plunger end 601 in equidistant mode, and are communicated with the first oil flow channel 504 by oily head piece 506 fluid.Oil head piece 506 and being dimensioned to of the first oil flow channel 504 have location (area), and separate around the body of DFHLA110, to guarantee flow from the even fluid of the first oil flow channel 504 to the three oil flow channel 509 and make pressure drop minimize.3rd oil flow channel 509 be dimensioned to the oil stream of combining from multiple second oil flow channel 508.

2.3 diamond like carbon coating (DLCC)

Describe a kind of diamond like carbon coating (DLCC) coating, this coating can reduce the friction between processed part, and provides necessary wear-resisting and load characteristic simultaneously.Coating material like known class and method, when using together with VVA system, they are all not enough to meet some demands.Such as, 1) enough hardness, 2) there is applicable load bearing capacity, 3) chemically stable in running environment, 4) being applied to temperature is no more than in the technique of parts annealing temperature, 5) engine life demand is met, and 6) friction of reduction is provided compared to the steel on steel interface.

A kind of DLC coating process meeting the uniqueness of the demand is described.The DLC coating selected is from containing hydrogen amorphous or similar material.DLC coating comprises the several layers shown in Figure 12.

1. first layer is chromium adhesive layer 701, and it is as the bonding agent between metal receiving surface 700 and lower one deck 702.

2. the second layer 702 is chromium nitrides, and it is that interface between parent metal receiving surface 700 and DLC coating adds ductility.

3. third layer 703 is chromium carbides and contains hydrogen amorphous combination, and it makes DLC coating be attached to chromium nitride layer 702.

4. the 4th layer 704 comprises containing hydrogen amorphous, and it provides hard function wear interface.

The combination thickness of layer 701-704 between 2-6 micrometers.DLC coating can not be applied directly to metal receiving surface 700.In order to meet durability demand and suitably be attached to metal receiving surface 700 in order to the first chromium adhesive layer 701, mechanically apply very special surface finish (polishing) to matrix receiving surface 700.

2.4 inductions and measurement

Can use utilize sensor to carry out information gathering to examine switch mode, identification error conditioned disjunction provide analysis for the information of switch logic and timing.Below describing can by some sensing device used.

2.4.1 two supply hydraulic lash adjuster (DFHLA) is mobile

Variable valve actuation (VVA) Technology design is use COMM communication such as DVVL to switch rocking arm or cylinder deactivation (CDA) rocking arm change valve lift curve at motor run duration.When using these devices, the state of valve lift is the important information confirming successful handover operation or detect error condition/fault.

Use DFHLA manages gap and supplies flow of pressurized liquid for switching in the VVA system adopting switching rocker arm assembly such as DCA or DVVL.As shown in cross section in figure 10, adjusting (describing in detail in the following paragraphs) to the normal gap of DVVL rocker arm assembly 100 makes ball plunger 601 keep contacting with inner arm 122 containing seat during high lift and low lift operation.Ball plunger 601 is designed to move as required when load changes between high lift state and low lift condition.The measurement result 514 of the movement contrasted with known running state in Figure 13 can determine interstitial site state.In one embodiment, non-contact switch 513 is outer between body and ball plunger cylinder part at HLA.Second example can comprise hall effect sensor, and this hall effect sensor is mounted to allow to measure the changes of magnetic field being moved 514 generations by some.

2.4.2 valve stem moves

Variable valve actuation (VVA) Technology design is use COMM communication such as DVVL to switch rocking arm at motor run duration to change valve lift curve.The state of valve lift is the important information confirming successful handover operation or detect error condition/fault.In order to this function can use valve stem position and relative movement sensor.

The state that VVA switches and the mode of execution determining whether to occur switch failure is monitored shown in Figure 14,14A.According to an aspect of the utility model instruction, the straight line motion of its mechanical valve 872 coupled of institute can be converted to corresponding electrical signal by linear variable differential transducer (LVDT) type transducer.LVDT linear position sensor easily obtains, and it can measure the little movement to a few millionths inch to several inches.

Figure 14 A illustrates the parts of the typical LVDT be arranged in valve stem guide 871.LVDT internal structure comprises primary air (winding) 899, and this primary air is between the secondary coil 897,898 of a pair of identical winding.In embodiments, coil 897,898,899 is wrapped in the hollow depression be formed in valve guide body 871, and this hollow depression is defined by thin segment 878, first end wall 895 and the second end wall 896.In this embodiment, valve guide body 871 is that position is fixed.

Referring now to Figure 14,14A and 14B, the moving element of this LVDT device is independently can the tubulose armature of magnetic-permeable material, also referred to as core body 873.In embodiments, core body 873 uses that any suitable method and rapidoprint are such as iron causes valve 872 bar.

Core body 873 axially moves freely at primary air 899 and secondary coil 897,898 inside, and is mechanically couple to valve 872, and the position of this valve is measured.Core body 873 and valve guide 871 do not have physical contact in hole.

In operation, the alternating current that the primary air 899 of LVDT is applied in suitable amplitude and frequency carrys out energy supply, is known as elementary excitation.Consequent magnetic flux is coupled to adjacent secondary coil 897 and 898 by core body 873.

As shown in fig. 14 a, if the midway of core body 873 between secondary coil 897,898, then equal magnetic flux is coupled to each secondary coil, makes the voltage of inducting in each coil 897,898 equal.In core body 873 position, this benchmark midway-and it is called zero point, it is zero substantially that difference voltage exports.

Core body 873 is arranged to the two ends extending past coil 899.As shown in Figure 14B, if core body 873 displacement distance 870 is so that closer to coil 897 compared with coil 898, then more magnetic flux is coupled to coil 897 and less magnetic flux is coupled to coil 898, thus causes non-vanishing difference voltage.Measure movement direction and position that difference voltage can indicate valve 872 by this way.

In the second mode of execution shown in Figure 14 C and 14D, above-mentioned LVDT device is revised by removal second coil 898 (Figure 14 A).After coil 898 is removed, in coil 897, the voltage of induction will change relative to the end position 874 of core body 873.Wherein in the movement direction of known valve 872 and the mode of execution on opportunity, only need a secondary coil 897 to measure amount of movement.As mentioned above, core body 873 part of valve can use multiple method to make and location.Such as, the welding of end position 874 can join Ni-based non-core material to iron-based core material, use the physics of diameter to reduce to come retaining tips position 874 to change the magnetic flux of special position, maybe can insert the blank of iron and be located at end position 874.

Be appreciated that according to disclosure, LVDT sensor element near location, valve guide 871 top, can be dissipated under this point with allowable temperature in an example.And this position can higher than the typical soldering point made for valve stem, weld seam can move or as mentioned above.Core body 873 relative to secondary coil 897 position with to induct how many voltage in proportion.

LVDT sensor in the above-mentioned use of engine operation, there are some advantages, comprise 1) without friction run-during normal use, there is no Mechanical Contact between the core body 873 of LVDT and coil block.The mechanical life more grown also is caused without friction.2) close to unlimited resolution-because LVDT runs with electromagnetic coupling principle in without friction structure, therefore can measure the little change of core body position, only be limited to the resolution of noise in LVDT signal conditioner and output display.This feature also causes significant repeatability.3) environment robustness-produce sane, durable sensor for the material and constructing technology assembling LVDT, this sensor is suitable for different environmental conditionss.Coil 897,898,899 can enter in valve guide body 871 by epoxy encapsulation after engaging, and produces moistureproof and moisture resistance preferably, can carry out larger vibration load and high level of vibration equally.In addition, this coil block can seal with grease proofing and corrosion protection environment.4) zero point repeatable-above described in, the position at the zero point of LVDT is highly stable and repeatably, even if in the operating temperature range of its non-constant width.5) disappearance rubbed during fast dynamic response-conventional operation allows LVDT response quickly to change core body position.The dynamic response of LVDT sensor is only limited to the less inertia effect caused by core component quality.As a rule, the response of LVDT sensed system is by the characteristics determined of signal conditioner.6) definitely output-LVDT is absolute output unit, instead of increment output unit.This means when the loss of energy, the position data exported from LVDT can not be lost.When measuring system is restarted, the output value meeting of LVDT is the same with before generation power cut-off.

Above-mentioned valve stem position transducer uses LVDT type transducer to determine the position of valve stem at motor run duration.Sensor can be any known sensor technology, comprises hall effect sensor, can follow the trail of valve stem position and will monitor that the electronics of ECU, optics and mechanical pick-up device are reported in position.

2.4.3 component locations/movement

Variable valve actuation (VVA) Technology design is use COMM communication such as DVVL to switch rocking arm at motor run duration to change valve lift curve.The change of switching state also can change the position of constituent elements in VVA assembly, and described position is absolute position in assembly or position respect to one another.Design and implementation change in location can measure to monitor the state that VVA switches, and determine whether there is switch failure possibly.

With reference now to Figure 15-16, example DVVL switches rocker arm assembly 100 can be configured to have accurate non-contact sensor 828 for measuring relative movement, action or distance.

In one embodiment, movable sensor 828 near first end 101 (Figure 15) so that for high lift or low lift mode assessment outer arm 120 relative to the movement of known location.In this embodiment, movable sensor 828 comprises the coil around permanent magnetism core body, and locating and orienting becomes by measuring when iron material detects movement through the change of its known magnetic field magnetic flux.Such as, when the outer arm tie-rod 875 of magnetic (iron material) is through the permanent magnetic field of position transducer 828, magnetic flux density is adjusted, comprise in coil induct AC voltage and with exporting close to proportional electricity tie-rod 875.Adjustment voltage is imported into control unit of engine (ECU) (describing in following paragraph), and wherein processor uses logic and calculates and starts rocker arm assembly 10 handover operation.In embodiments, it can be binary that voltage exports, and namely voltage signal does not exist or exist instruction high lift or low lift.

Can see, position transducer 828 can be placed into the movement of measuring miscellaneous part in rocker arm assembly 100.In this second embodiment, sensor 828 can be placed in the second end 103 of DVVL rocker arm assembly 100 (Figure 15) to assess the position of inner arm 122 relative to outer arm 120.

3rd mode of execution can place sensor 828 directly to assess the position of breech lock 200 in DVVL rocker arm assembly 100.Breech lock 200 and sensor 828 when being in kayser state (high lift pattern) relative to being engaged with each other and fixing, and can separate when non-kayser (low lift) operates.

Also movement can be detected by use sense induction sensor.Sensor 877 can be hall effect sensor, and this sensor is mounted to allow measure mobile or do not move, the movement of such as valve stem 112 or do not move.

2.4.4 pressure characteristic

Variable valve actuation (VVA) Technology design is use COMM communication such as DVVL to switch rocking arm at motor run duration to change valve lift curve.Such as regulate fuel/air to mix increase oil consumption mileage, decreasing pollution because latch mode important input-this ECU that is ECU can make it perform different functions or regulate idling and quick-friedly to shake, so need the measuring device for confirming successful handover operation or detection erroneous condition or fault or system to correctly control.In some cases, in order to abidance by rule, switching state is needed to report and error notification.

In the mode of execution comprising hydraulic actuating DVVL system 800-as shown in Figure 6, the change of switching state provides distinguishing hydraulic pressure switch fluids pressure characteristic.Owing to needing hydrodynamic pressure to produce the necessary hydraulic pressure rigidity of starting and switching, and because hydraulic fluid is limited by concrete passage and chamber geometry, may be used for so produce the Characteristic pressures feature expectedly can determining kayser or non-kayser state or switch failure.Some measuring pressures can be described and by the embodiment of measurement result compared with known and acceptable Operational Limits.Can the single handover event of several milliseconds be continued by the hydrodynamic pressure on the several switching cycle of inspection or assessment and analyze pressure measurements in macroscopic aspect.

Referring now to Fig. 6,7 and 17, example chart (Figure 17) illustrates when switching rocking arm 100 and running with high lift or low lift and switch between high lift and low lift, cylinder one valve lift height change 882 in time.Corresponding data for hydraulic pressure switched system shows for same time ratio (Figure 17), comprise the oil pressure 880 in the upper channel 802,803 using pressure transducer 890 to measure, and for opening and closing the electric current 881 of solenoid valve (solenoid valve) 822,823 in OVC assembly 820.Can see, the analysis level of this macroscopic aspect is clearly shown that OCV switch current 881, between pilot pressure 880 and lift 882 in the correlation of all state run durations.Such as, switched by instruction in the time 0.1, OCV, as shown in the electric current 881 of increase.When OCV switches, the pilot pressure 880 of increase causes high lift to low lift handover event.When on one or more complete switching cycle during evaluation operation, comprise OCV and the proper handling for the subtense angle of the pressure fluid transporting system of rocker arm assembly 100 can be evaluated.Other independent measurement result such as above-mentioned valve stem can be used to move to strengthen the determination of switch failure.Can see, these analyses can perform for the OCV of any amount of air inlet and/or exhaust valve for controlling one or more cylinder.

Use similar approach, but the data measured on Microsecond grade during being used in switching and analyze, enough detailed pilot pressure information (Figure 17 A, 17B) can be provided successfully to switch or switch failure with independent evaluations, and need not directly measure valve lift or latch pin moves, in the embodiment using the method, by comparing and measuring pressure transient and determining switching state at the known running state pressure transient of test period development, and stored in ECU for analysis.Figure 17 A and 17B illustrate for generation of in DVVL system for switching the example test data of the known operating pressure transient state of rocking arm.

Test system comprises four switching rocker arm assemblies 100 as shown in fig. 3, OCV assembly 820 (Fig. 3 B), two upper oil pressure cntrol passages 802,803 (Fig. 6-7) and the closed-loop system in order to the temperature and pressure that controls hydraulic actuating fluid in control channel 802,803.Each control channel provides hydraulic fluid to control two rocker arm assemblies 100 with the pressure of rule.Figure 17 A illustrates when the energising of OCV solenoid valve is to start from high lift to the effective single test run display data during switching of low lift condition.Install and measure that instrument moves 1003 to measure breech lock, pressure 1001 in pressure 880 in control channel 802,803, OCV electric current 881, hydraulic fluid supply 804 (Fig. 6-7) and latch gap and cam clearance.The order of event is as described below:

0ms-ECU firing current 881 switches to be energized to OCV solenoid valve.

10ms-, as shown in pressure diagram 880, is enough to the pressure in control channel to regulate uprise to the solenoidal switch current 881 of OCV.

10-13ms-is along with hydraulic fluid is from control channel 802,803 supply 804 (Fig. 6-7) inflow, and supply pressure diagram 1001 is reduced to below the pressure that regulated by OCV.Responsively, pressure 880 increases fast in control channel 802,803.As shown in latch pin moving curve 1003, latch pin starts mobile.

13-15ms-supplies pressure diagram 1001 and gets back to stable non-adjustment state when fluid stable.Pressure 880 in control channel 802,803 increases to the more high pressure regulated by OCV.

15-20ms-, when pressurized hydraulic fluid promotes breech lock complete return (latch pin moving curve 1002), produces pressure 880 to increase/reduce transient state in control channel 802,803, and under OCV does not regulate pressure flow of pressurized and pressure stability.Pressure spike 1003 is features of this transient state.

Can see pressure diagram 880 in the specified pressure transient state of 12ms and 17ms, this pressure diagram overlaps with unexpected change of position latching 1002.

Figure 17 B illustrates when OCV solenoid valve dead electricity is to start effective single test run display data when switching from low lift to high lift state.The order of event is as described below:

0ms-ECU close current 881 is to make OCV solenoid valve dead electricity.

5ms-OCV solenoid moves enough far away to cause adjusted lower pressure, and hydraulic fluid enters (pressure diagram 880) in control channel 802,803.

5-7ms-is when OCV is adjusted to lower pressure, and the pressure in pressure channel 802,803 reduces fast as shown in curve 880.

7-12ms-is when overlapping with low pressure force 1005, and pressure lower in pressure channel 802,803 starts breech lock and moves, as shown in breech lock moving curve 1002.When late spring 230 (Figure 19) compression and hydraulic fluid in mobile breech lock engaging space time pressure diagram 880 transient state started.

12-15ms-, when having been moved by the latch pin shown in latch pin moving curve 1002, is reintroduced back to the pressure transient as shown in pressure diagram 880.

Pressure stability in 15-30ms-control channel 802,803 regulates under pressure, as shown in pressure diagram 880 at OCV.

As mentioned above, can find out in 7-10ms and 13-20ms specified pressure transient state from pressure diagram 880, this is consistent with the unexpected change of position latching 1002.

As above and described in following paragraph, hydraulic channel, hole, gap and the fixed geometry configuration of chamber and the rigidity of late spring are variable, this with for changing hydraulic response and the mechanical switch velocity correlation of regulated flow of pressurized pressure.Pressure diagram 880 in Figure 17 A and 17B describes a kind of DVVL run in tolerance interval and switches rocker arm system.Be in operation, the special speed (slope of curve) of pressure increase or reduction is with the time of the above-mentioned event suitable operation characteristic that is feature.The example of erroneous condition comprises: the time shifting of pressure events illustrates the slow deterioration of breech lock response time, the change (pressure diagram slope variation) of event generation rate, or the whole reduction of pressure events amplitude.Such as, increase lower than expecting pressure in the 15-20ms period and represent that breech lock is not retracted completely, critical transformation may be caused.

Test data in these embodiments is with the fuel temperature measurement of the oil pressure of 50psi and 70 degrees Celsius.A series of tests in different running environment can provide the database of indicatrix, so that by ECU for switching diagnosis.

The following describes and use pressure measurements to diagnose the additional embodiment of switching state.DFHLA110 is as shown in Figure 3A used for not only managing gap but also supply hydraulic fluid, and this hydraulic fluid is for activating the VVA system using and switch rocker arm assembly such as CDA or DVVL.As shown in the sectional view of Figure 52, the normal gap adjustment for DVVL rocker arm assembly 100 makes ball plunger 601 keep contacting with the containing seat of interior arm component 622 at high lift and low lift run duration.When assembling within the engine completely, DFHLA110 is in fixed position, and inner rocker arm assembly 622 exists the rotary motion around bulb point of contact 611 simultaneously.When switching between high lift and low lift condition, rotary motion and the ball plunger load 615 of inner rocker arm assembly 622 change in size.Ball plunger 601 is designed to compensate when load and mobile change move.

Instantly, when control channel 805 is communicated with end opening 512 and chamber 905 (Figure 11), the equilibrant force of ball plunger load 615 is provided for by the hydraulic fluid pressure in this lower control channel.As shown in figs. 6-7, be in and do not regulate the hydraulic fluid of pressure to pass into lower control channel 805 from engine cylinder cap.

In embodiments, pressure converter is placed in hydraulic channel 805, the slack adjuster parts of this hydraulic channel supply DFHLA110.Pressure converter may be used for the transient pressure change monitored in hydraulic channel 805, and this hydraulic channel is supply slack adjuster when changing from high lift state to low lift condition or from low lift condition to high lift state-transition.By monitoring pressure characteristic when being switched to another kind of pattern from a kind of pattern, variable valve actuation system can be worked as and detect this system when breaking down in any one position.Pressure characteristic curve-be illustrated as in an embodiment pressure relative to millisecond time-characteristic shape comprising amplitude, slope and/or other parameters is provided.

Such as, Figure 17 C illustrates the chart of intake valve lift profile curve 814,816 relative to the time of millisecond, adds the chart of hydraulic channel pressure diagram 1005,1005 relative to same time ratio.Pressure diagram 1006 and valve lift profile curve 816 correspond to low lift condition, and pressure diagram 1005 and valve lift profile curve 814 correspond to high lift state.

During steady state operation, there is periodic characteristics in pressure characteristic curve 1005,1006, there is the unique peak value 1007,1008 caused when DFHLA compensates alternately ball plunger load 615, described alternately ball plunger load be when cam promote downwards rocker arm assembly with compression valve spring (Fig. 3 A) and along with valve spring extend valve lift is provided to close valve time and the formation when cam is on the basic circle not having lift to produce.As shown in Figure 17 C, transient pressure peak value 1006,1007 corresponds respectively to the summit of low lift and both high lift 816,814.When hydraulic system pressure is stablized, recover steady state pressure indicatrix 1005,1006.

As above with described in following paragraph, the fixed geometry configuration of DFHLA hydraulic channel, hole, gap and chamber is variable, and this is relevant with pressure transient to the hydraulic response for given hydraulic fluid pressure and temperature.Pressure characteristic curve 1005,1006 in Figure 17 C describes a kind of DVVL run in tolerance interval and switches rocker arm system.In operation, some speed (slope of curve) of pressure increase or reduction, summit force value and summit pressure are with the feature of the time of the handover event proper handling that is feature relative to the time of maximum lift equally.The example of erroneous condition can comprise the time shifting of pressure events, change (pressure diagram slope variation), unexpected less desirable pressure transient or the whole reduction of pressure events amplitude of event occurrence rate.

A series of tests in different running environment can provide by ECU for switching the database of the indicatrix of diagnosis.One or several value of pressure can be used based on system configuration and vehicle instruction.The pressure trajectories monitored can to determine when system malfunctions compared with standard trajectory.

3. switching controls and logic

3.1 motors are implemented

DVVL hydraulic fluid system is described below, and this system switches rocking arm 100 with the DVVL shown in controlled pressure conveying motor fluid to Fig. 4, and this system can be arranged on the intake valve in four in model II valve mechanism.In substituting mode of execution, this hydraulic fluid transporting system can be applied to any combination of piston actuated internal-combustion engine upper air or exhaust valve.

The 3.2 hydraulic fluid transporting systems of leading to rocker arm assembly

With reference to figure 3A-3B, 6 and 7, hydraulic fluid system switches rocking arm 100 (Fig. 4) with controlled pressure to DVVL and carries motor fluid.In this arrangement, motor fluid is regulated to be fed into supply passage 805 under HLA from the non-pressure of cylinder head 801.As shown in Figure 3A, this fluid is always communicated with lower supply entrance 512 fluid of DFHLA, and at this place, it is for performing the adjustment of normal hydraulic lash.The non-pressure come from cylinder head 801 regulates motor fluid to be also supplied to oil control valve assembly entrance 821.As previously mentioned, the OCV assembly 820 for this DVVL mode of execution comprises the solenoid valve of two independent actuation, and this solenoid valve regulates the oil pressure from co-portal 821.The hydraulic fluid come from OCV assembly 820 first control outlet 822 is supplied to the first upper channel 802, and the hydraulic fluid come from the second control mouth 823 is supplied to the second upper channel 803.One OCV determines lift mode for cylinder one and two, and the 2nd OCV determines lift mode for cylinder three and four.Describe as shown in Figure 18 with in following paragraph, the actuating of the valve in OCV assembly 820 is guided by control unit of engine 825, this unit uses such logic, this logic based on the information detecting for special physical configuration, switch window and operational condition group and store, the cylinder of such as some and specific oil temperature.That comes from upper channel 802,803 is introduced into DFHLA suitable for reading 506 through pressure controlled hydraulic fluid, is passed to switches rocker arm assembly 100 at this place by passage 509.As shown in Figure 19, hydraulic fluid is communicated with switching rocker arm assembly 100 by the first oil passage 144, and is communicated with latch pin assembly 201 by the second oil passage 146, is used to start the switching between high lift and low lift condition at this place.

The air removing accumulation in upper channel 802,803 keeps hydraulic pressure rigidity and minimized vibrations to be very important in the pressure increase period.Breech lock traveling time during pressure rise time directly affects handover operation.Passive type air vent 832,833 shown in Fig. 6 adds the high point in upper channel 802,803 to, the air venting of accumulation to be entered the cylinder head air space below valve cap.

3.2.1 the hydraulic fluid for low lift mode is carried

Referring now to Fig. 8, DVVL system, be from idle to 3500rpm in low lift mode.The sectional view of rocker arm assembly 100 and three salient angle cams 102 shows low lift and runs.The critical piece of the assembly shown in Fig. 8 and 19 comprise inner arm 122, roller bearing 128, outer arm 120, slide block 130,132, breech lock 200, late spring 230, pivotal axis 118 and idle running torque spring (lostmotiontorsionspring) 134,136.Run for low lift, when the solenoid valve in OCV assembly 820 is energized, the oil pressure that do not regulate of >=2.0 bar is supplied to switching rocker arm assembly 100 through control channel 802,803 and DFHLA110.This pressure causes breech lock 200 to be retracted, and unlocks inner arm 122 and outer arm 120, and allows them independently mobile.The slide block 130,132 on outer arm 120 is kept in touch at high-lift cam crown of roll angle 104,106 (Fig. 3 A).This so-called idle running.Because low lift cam profile 816 (Fig. 5) is for early stage valve-closing, switches rocker arm assembly 100 and must be designed to absorb the everything come from high-lift cam crown of roll angle 104,106 (Fig. 3 A).The power come from idle running torque spring 134,136 (Figure 15) guarantees that outer arm 120 and high lift lobe 104,106 (Fig. 3 A) keep in touch.Low lift lobe 108 (Fig. 3 A) contacts the roller bearing 128 on inner arm 122, is opened at each low lift early stage valve-closing molded line 816 (Fig. 5) valve.

3.2.2 the hydraulic fluid for high lift pattern is carried

With reference to Fig. 9, DVVL system for run from idling to 7300rpm in high lift pattern.The sectional view display high lift of rocker arm assembly 100 and three salient angle cams 102 runs.The critical piece of assembly illustrates in Fig. 9 and 19, comprise inner arm 122, roller bearing 128, outer arm 120, slide block 130,132, breech lock 200, late spring 230, pivotal axis 118 and idle running torque spring 134,136.

Solenoid valve dead electricity in OCV assembly 820 is running by high lift.Late spring 230 makes breech lock 200 stretch out, locking inner arm 122 and outer arm 120.The similar fixing rocking arm of the arm be blocked works.Symmetrical high lift lobe 104,106 (Fig. 3 A) contacts the slide block 130 (132 do not illustrate) on outer arm 120, inner arm 122 is rotated around DFHLA100 pommel 601, and opens valve 112 (Fig. 4) each both high lift 814 (Fig. 5).During this period of time, switching rocking arm 100 is supplied to through control channel 802,803 from the adjusted oil pressure of 0.2-0.4 bar.The oil pressure maintaining 0.2-0.4 bar keeps oil passage be full of but do not make breech lock 200 retract.

In high lift pattern, two functions of physical supply of DFHLA are important to guaranteeing that the appropriate gap of valve mechanism under maximum engine speed compensates.Lower channel 805 in Fig. 9 makes cylinder head oil pressure be communicated to lower DFHLA mouth 512 (Figure 11).The low portion design of DFHLA is as normal fluid pressure rocker compensating gear.DFHLA110 mechanism design for guaranteeing that hydraulic pressure has enough pressure, to avoid inflating and to be full of fluid under remaining on all engine speeds.Keep hydraulic pressure rigidity and suitable valve function within the system.

The form of Figure 20 outlines the pressure state in high lift and low lift mode.Also show the hydraulic pressure separating from rocker arm assembly switching function to DFHLA normal clearance compensate function.In high lift pattern (breech lock stretches out and engages), motor is started, because this is default mode.

3.3 Operational Limits

The key factor run in DVVL system is the reliable control switched from high lift pattern to low lift mode.DVVL valve actuation system only can switch between modes within the time of predetermined window.As mentioned above, started by the signal from the control unit of engine (ECU) 825 (Figure 18) using logic from high lift pattern to low lift mode switching and inverse operation, the information that this logical analysis stores, such as, for the switch window of specific physical configuration, storage running condition and the processing data by sensor collection.Switch window duration is determined by DVVL system physical configuration, comprises the breech lock response time intrinsic in number of cylinders, the number of cylinders controlled by single OCV, cylinder lift duration, engine speed and hydraulic control and mechanical system.

3.3.1 the data of collecting

Real time sensor information comprises the input from any amount sensor, example DVVL system 800 as shown in Figure 6.Sensor can comprise 1) valve stem displacement 829, its linear variable differential of use in one embodiment transducer (LVDT) is as described above measured, 2) action/position 828 and the position latching 827 of hall effect sensor or motion detector is used, 3) the DFHLA displacement 826 of proximity switch, hall effect sensor or other devices is used, 4) oil pressure 830,5) oil temperature 890.Camshaft rotation position and speed directly can collect or infer from engine rotation speed sensor.

In the VVA system of hydraulic actuating, oil temperature impact is used for the rigidity of the hydraulic system switched in systems in which, such as CDA and VVL.If oil temperature is excessively cold, its viscosity slows down switching time, causing trouble.This pass ties up in Figure 21-22 and illustrates for example DVVL switching rocker arm system.Oil temperature provides information the most accurately accurately, and this oil temperature takes from the sensor 890 shown in Fig. 6, and this sensor is near using point instead of motor fluid crankcase.In one embodiment, the oil temperature monitored near pressure control valve (OCV) in VVA system must be more than or equal to 20 degrees Celsius, to start low lift (non-kayser) operation with the hydraulic pressure rigidity needed.Measurement result can take from any amount of commercially available parts, such as thermocouple.Pressure control valve is further described in US2010/0018482 disclosed in 28, on January of U.S. Patent application US2010/0089347 and 2010 disclosed in 15 days April in 2010, and these two documents include reference in this entirety.

Sensor information is sent to control unit of engine (ECU) 825 using as real time execution parameter (Figure 18).

3.3.2 the information stored

3.3.2.1 switch window algorithm

Mechanical switch window:

The shape of each salient angle of three salient angle cams shown in Fig. 4 comprises the base circle portion 605,607,609 not having lift to produce, and for producing the transition portion of mechanical clearance before lift events, and makes the lift part of valve 112 movement.Switch rocking arm 100 for the example DVVL be arranged in system 800 (Fig. 6), during the load of moving when breech lock not stoping it, the switching between high lift and low lift can occur over just basic circle run duration.In the following paragraphs this mechanism is further described.What basic circle ran illustrates in Figure 5 without lift part 863.DVVL system 800 is 20 DEG C in oil temperature and switches in single cam axle with the speed within 3500 motor rpm above.Switching outside timing window or predetermined fluid condition may cause critical change event, this event is when the switching ability to bear of the load on valve actuator switching part or engine valve higher than structural design, the transformation of engine valve position when certain point of engine cycle.Critical change event may cause the damage of valve mechanism and/or other engine components.Switch window can be further defined as and change pressure in control channel and from the endurance reaching camshaft crankangle required when retracted position moves breech lock and inverse operation.

As previously mentioned with shown in Fig. 7, DVVL system has single OCV assembly 820, and this assembly comprises two independent solenoid valves controlled.First valve controls the first upper channel 802 pressure and determines lift mode for cylinder one and two.Second valve controls the second upper channel 803 pressure and determines lift mode for cylinder three and four.Figure 23 illustrates the intake valve timing (lift order) for this OCV assembly 820 (Fig. 3 B) configuration relative to the camshaft angle being the four in upright arrangement of (2-1-3-4) for cylinder starting sequence.The high lift intake valve molded line of cylinder 2 851, cylinder 1, cylinder 3 853 and cylinder 4 854 is depicted as the ratio of lift and degree in crank angle at diagram top.The valve lift time of corresponding cylinder is plotted in the ratio as lift time zone 855,856,867 and 858 lift and degree in crank angle in bottom.Also illustrate for individual cylinder without lift basic circle operation area 863.Aforementioned switch window must be defined as mobile breech lock in a cam axle, and wherein each OCV is configured to once control two cylinders.

Mechanical switch window can by being familiar with and improving breech lock moving optimised.With reference to Figure 24-25, the machine configurations switching rocker arm assembly 100 provides two different situations allowing to increase effective switch window.Be called that the first situation that high lift breech lock limits occurs time in place for breech lock 200 locking in high lift pattern when the load by applying for opening valve 112.Be called that the second situation that low lift breech lock limits occurs in the low lift mode of non-kayser when outer arm 120 stops breech lock 200 to extend to outer arm less than 120.These situations are described below:

High lift breech lock limits:

Figure 24 illustrates that wherein breech lock 200 engages the high lift event of outer arm 120.When valve overcomes the power that applied by valve spring 114 and opens, power is delivered to outer arm 120 from inner arm 122 by breech lock 200.When spring 114 power is transmitted by breech lock, breech lock 200 becomes and is locked in extended position.In this case, when attempting to be switched to low lift mode from high lift pattern, being not enough to by the hydraulic pressure switching OCV applying the power overcoming locking breech lock 200, thus preventing this breech lock from retracting.This situation by terminate in high lift event and unload breech lock 200 basic circle 863 (Figure 23) operation start before allow apply pressure expand total switch window.When power discharges on breech lock 200, handover event can start immediately.

Low lift breech lock restriction:

Figure 25 illustrates that wherein breech lock 200 is retracted into the low lift operation in low lift mode.In the lift part of event, outer arm 120 stops breech lock 200, prevents it from stretching out, even if OCV switches, hydraulic fluid pressure reduces to get back to high lift kayser state.This situation allowed release pressure to expand total switch window before terminating in high lift event to start with basic circle 863 (Figure 23) operation.Once arrival basic circle, late spring 230 can make breech lock 200 extend.Total switch window is increased by release pressure before basic circle.When camshaft rotates to basic circle, switching can start immediately.

Figure 26 describes information same as shown in Figure 23, but the transition period mechanical switch process between low lift and high lift state that also superposed completes the time that each step needs.The representative of these steps switches the element of mechanical switch intrinsic in rocker arm assembly.As shown in figure 23, the starting sequence of motor is presented at top and corresponds to reference to the degree in crank angle of cylinder two along intake valve molded line 851,852,853,854.When intake cam salient angle is on basic circle 863, breech lock 200 must be moved (being called as mechanical switch window).Because solenoid valve each in OCV assembly 820 controls two cylinders, switch window must timing with on their basic circle time accept two cylinders.Cylinder two gets back to basic circle in 285 crank angle degree.Movement must be completed by 690 degree in crank angles before being latched in the next lift of cylinder two.Similar, cylinder one is got back to basic circle at 465 degree and must complete switching by 150 degree.Can see, the switch window of cylinder one and two is slightly different.Can see, an OCV electricity trigger started switching before cylinder one air inlet lift events, and the 2nd OCV electricity trigger started before cylinder four air inlet lift events.

Carry out worst case analysis to define the switching time that maximum switch speed is in fig. 26 3500rpm.Notice that motor can run under higher 7300rpm speed, but, do not allow pattern to switch at more than 3500rpm.Total switch window of cylinder two is 26 milliseconds, and is divided into two-part: 7 milliseconds of high lift/low lift breech lock binding hours 861, and 19 milliseconds of mechanical switch times 864.10 milliseconds of mechanical response times 862 are consistent to all cylinders.15 milliseconds of breech lock binding hours 861 are oversize concerning cylinder one, because OCV switching is started when the air inlet lift events of cylinder one, and breech lock is limited mobile.

Some machineries and hydraulic pressure restraining factors must be applicable to meeting total switch window.First, the critical transitions 860 caused by the switching do not completed before next air inlet lift events must be avoided.Secondly, test data shows, and at bottom line motor oil temperature 20 DEG C, the maximum switching time of mobile breech lock is 10 milliseconds.As shown in figure 26,19 milliseconds of mechanical switch 864 that can be used on basic circle are had.Switch mechanical response 862 meeting generation in first 10 milliseconds because all test datas all show, do not need the mechanical switch time 864 of whole 19 milliseconds.The combination of machinery and hydraulic pressure restraining factors defines the worst case switching time of 17 milliseconds, and it comprises breech lock binding hours 861 and adds breech lock mechanical response time 862.

DVVL switches rocker arm system and is designed to have nargin to complete switching 9 milliseconds of nargin.In addition, 9 milliseconds of nargin can allow to switch higher than the pattern under the speed of 3500rpm.Cylinder three and four correspond to cylinder one with two identical switching time, unlike the stage shown in Figure 26.Because the time changed being energized to control channel oil pressure from OCV keeps measurable, although ECU can easily calibrate to consider this variable, the electric switching time activated in OCV assembly needed for solenoid valve is not counted in current analysis.

As Fig. 4 and 25A, if camshaft rotates and breech lock 200 move timing with load at an edge breech lock 200-wherein it to be only partly bonded on outer arm 120-timing consistent, then may produce critical conversion.Once high lift event starts, breech lock 200 can slide and be disengaged with outer arm 120.Upon such an occurrence, the inner arm 122 accelerated by the power of valve spring 114 causes the impact between roller bearing 128 and low lift cam lobes 108.Critical conversion is not supposed to, because it can cause the out of control and impact to system of the moment of rocker arm assembly 100 and valve motion.DDVL switches rocking arm and is designed to meet the life-span being worth critical switching occurs.

3.3.2.2 the Operational Limits stored

Operational Limits comprises the information of storage, and this information is controlled for switch logic by ECU825 (Figure 18), and the data of collecting during the extend testing described based on following paragraph.Some examples of known service data are described: in an embodiment, 1) the minimum oil temperature of needs 20 degrees Celsius is switched from high lift state to low lift condition, 2) the minimum oil pressure being greater than 2 bar should be present in engine sump for handover operation, 3) breech lock response changes with oil temperature according to Figure 21-22 drawing data switching time, 4) as shown in figure 17 and above, what caused by hydraulic pressure handover operation predictable pressure change can occur in upper channel 802, determined by pressure transducer 890 in 803 (Fig. 6), 5) as shown in Figure 5 and above, relative to degree in crank angle (time) and based on lift profile 814, the known valve of 816 moves can be preset and be stored.

3.3 control logic

As implied above, DVVL switching can occur over just the little predetermined window time durations under certain operating conditions, and outside timing window, switch DVVL system may cause critical change event, this event can cause valve mechanism and/or other failure of engine components.Due to engine condition such as oil pressure, temperature, discharge and load possibility Rapid Variable Design, high speed processor can be used to analyze real time status, they and known Operational Limits are relatively characterized work system, according to result to determine when to switch, and sends switching signal.These operations per secondly can carry out hundreds of or thousands of times.In embodiments, this computing function can by application specific processor or by being called that the existing multifunctional steam vehicle control of control unit of engine (ECU) carries out.Typical case ECU has the input section for analog-and digital-data, comprises the processing section of microprocessor, programmable storage and random access memory, and may comprise the output section of relay, switch and beacon actuating.

In one embodiment, control unit of engine (ECU) 825 shown in Fig. 6 and 18 receives input from multiple sensor, and such as valve stem displacement 829, action/position 828, position latching 827, DFHLA move 826, oil pressure 830 and oil temperature 890.The data of the running temperature such as allowed given engine speed and pressure (Figure 20) and switch window (Figure 26 and described in other sections) store in memory.The information of real-time collecting contrasts with the information stored subsequently and analyzes to switch timing for ECU825 and control provides logic.

After input is analyzed, control signal outputs to OCV820 with initialization handover operation by ECU825, and this regularly to be avoided critical conversion to meet engine performance target simultaneously, such as, can improve fuel economy and reduce discharge.If needed, ECU825 also reminds driver's erroneous condition.

4.DVVL switches rocker arm assembly

4.1 assembly explanations

Disclose and a kind of switch rocking arm, it is hydraulically activated by pressure fluid and for engagement cam.Outer arm and inner arm are configured to the valve of transmission action to internal-combustion engine.Bolt lock mechanism comprises breech lock, sleeve pipe and orientation member.Hole in sleeve pipe engages receptacle and inner arm, and provide opening for orientation member, this orientation member is used for providing correct orientation for breech lock relative to sleeve pipe and inner arm.Sleeve pipe, breech lock and inner arm have the reference mark of the optimal orientation for determining breech lock.

Example switches rocking arm 100 and can be configured to together with three salient angle cams 10 as shown in Figure 4 at run duration.Alternative, similar swing arms mode of execution can be configured to work together with other cam design of such as two salient angle cams.Switch rocking arm 100 and the mechanism for keeping hydraulic lash to adjust with for supply hydraulic pressure switch fluids to inner arm 122 mechanism together with construct.In embodiments, two supply hydraulic lash adjuster (DFHLA) 110 performs two kinds of functions.Valve 112, spring 114 configure too with spring retainer 116 together with assembly.Cam 102 has the first and second high lift lobe 104,106 and low lift lobe 108.Switch rocking arm and there is outer arm 120 and inner arm 122, as shown in figure 27.At run duration, high lift lobe 104,106 contacts outer arm 120, and low lift lobe contact inner arm 122.Salient angle causes the periodicity of outer arm 120 and inner arm 122 to move downward.Downward action is delivered to valve 112 by inner arm 122, thus opens valve.Rocking arm 100 is changeable between high lift pattern and low lift mode.In high lift pattern, outer arm 120 snaps to inner arm 122.At motor run duration, high lift lobe periodically promotes outer arm 120 downwards.Because outer arm 120 snaps to inner arm 122, high lift action is sent to inner arm 122 and further to valve 112 from outer arm 120.When rocking arm 100 is in its low lift mode, outer arm 120 does not snap to inner arm 122, and the high lift motion therefore presented by outer arm 120 is not delivered to inner arm 122.Replace, low lift lobe contacts outer arm 120 and produces the low lift motion being delivered to valve 112.When unlocking from inner arm 122, outer arm 120 around axle 118 pivotable, but does not transmit action to valve 112.

Figure 27 illustrates that example switches the perspective view of rocking arm 100.Switch rocking arm 100 only to provide by way of example, be appreciated that the configuration of the switching rocking arm 100 of disclosure theme is not limited to the configuration of switching rocking arm 100 shown in this figure.

As shown in Figure 27, switch rocking arm 100 and comprise the outer arm 120 with the first outer webs 124 and the second outer webs 126.Inner arm 122 is placed between the first outer webs 124 and the second outer webs 126.Inner arm 122 and outer arm 120 are all arranged on pivotal axis 118, the first end 101 of the contiguous rocking arm 100 of this pivotal axis, and inner arm 122 is fixed to outer arm 120 by it, also allow inner arm 122 relative to the rotary freedom of outer arm 120 around pivotal axis 118 simultaneously.Except having the illustrated embodiment of the independent pivotal axis 118 be installed on outer arm 120 and inner arm 122, pivotal axis 118 can be a part for outer arm 120 or inner arm 122.

Rocking arm 100 shown in Figure 27 has roller bearing 128, and this roller bearing is configured to the low lift lobe in center of joint three salient angle cam.First and second slide blocks 130,132 of outer arm 120 are configured to the first and second high lift lobe 104,106 shown in index map 4.First and second torque spring 134,136 functions be by high lift lobe 104,106 be shifted after on bias voltage outer arm 120.The design of this rocking arm provides spring excessive torque feature.

First and second excess of stroke limiters 140,142 of outer arm prevent the overwind of torque spring 134,136, and the overstress on restraining spring 134,136.When outer arm 120 in low lift mode reaches its maximum rotation, excess of stroke limiter 140,142 contacts inner arm 122 on the first and second oil ducts 144,146.At this point, the interference between excess of stroke limiter 140,142 and oil duct 144,146 stops any of outer arm 120 to be rotated down further.Figure 28 represents the top view of rocking arm 100.As shown in figure 28, excess of stroke limiter 140,142 stretch out from outer arm 120 to inwall 122 with the oil duct 144 of inwall 122,146 overlapping, guarantee the interference between excess of stroke limiter 140,142 and oil duct 144,146 thus.As shown in figure 29, this illustrates the sectional view that 29-29 along the line intercepts, and the profile design of the contact surface 143 of limiter 140 becomes the sectional shape of coupling oil duct 144.This contributes to being evenly distributed of power when limiter 140,142 contacts with oil duct 144,146.

When outer arm 120 arrives its maximum rotation as mentioned above in low lift mode, breech lock stop member 90 shown in Figure 15 prevents breech lock from stretching out and incorrect locking.This feature can be configured to as required, be suitable for the shape of outer arm 120.

Figure 27 illustrates the perspective view of looking above rocker arm assembly 100, according to the torque spring 134,136 of a mode of execution of the application's instruction shown in it.Figure 28 is the plane view of the rocker arm assembly 100 of Figure 27.This design shows the rocker arm assembly 100 with torque spring 134,136, and torque spring 134,136 reels around axle 118 separately.

Switch that rocker arm assembly 100 is sufficiently compact does not sacrifice performance or durability to be assemblied between limited engine air.Traditional torque spring that the circular metal silk being met the torque demand of this design by its size reels is too wide in some embodiments and can not be assemblied in the spring compartment 121 of permission between outer arm 120 and inwall 122, as shown in figure 28.

4.2 torque spring

The Design and manufacture technique of present description torque spring 134,136, it is formed has the substantially rectangular compact design wiry be made up of structural material that selecting.

Referring now to Figure 15,28,30A and 30B, torque spring 134,136 is constructed by roughly trapezoidal wire 397.Wire 397 is allowed to be deformed into rectangular shape when this trapezoidal shape is designed to apply power during coiling process.After torque spring 134,136 is wound, generates shape wiry and can be described as being similar to first wire 396 with substantially rectangular cross section.In Figure 28, two torque springs 134,136 mode of execution is shown along the cross section of line 8, is described as multiple coil 398,399 in cross section.In a preferred embodiment, wire 396 has rectangular cross sectional shape, and it has two elongate sides, is expressed as vertical side 402,404 and bottom 403 at this.The Mean length ratio of the vertical side 402 of the coil of wire and the Mean length of vertical side 403 and top 401 and bottom 403 can be less than 1 any value.The spring coil that this ratio reels along coil of wire axis of bending 400 than the circular metal silk at the top 401 and bottom 403 Mean length that are equaled the coil of wire 398 by diameter produces more large rigidity.In substituting mode of execution, cross section metal filament shape is the roughly trapezoidal shape with larger top 401 and less bottom 403.

In this configuration, when the coil of wire is wound, the elongate sides 402 of each coil of wire against the elongate sides 402 of the previous coil of wire, thus makes torque spring 134,136 keep stable.Above-mentioned shape keeps all coils of wire at vertical position with arranging, and mutually crosses or angulation when preventing them under stress.

When rocker arm assembly 100 runs, substantially rectangular or trapezoidal torque spring 134,136-when they bend around axle 400 as shown in Figure 30 A, 30B and Figure 19-produce high component stress, particularly in the tensile stress of upper face 401.

For meeting life requirement, material is employed together with the combination of technology.Such as, torque spring 134,136 can be made up of the material comprising chrome alum alloyed steel, adopts this design to improve intensity and durability.

Torque spring 134,136 also can be cooled with spring described in tempering fast by heating.It reduce residual stress.

Impact the surface manufacturing torque spring 134,136 wires 396,397 used with projectile, or " shot-peening processing (shotpeening) " is to add the surface of wire 396,397 by compressive residual stress.Wire 396,397 is wound into torque spring 134,136 subsequently.Because they are processed by shot-peening, the torque spring 134,136 produced can bear larger tensile stress than by the same spring not carrying out shot blast.

4.3 torque spring seats

Switching rocker arm assembly 100 can be enough compact to be assemblied in having minimum influence in limited engine air surrounding structure.

Switch rocking arm 100 and provide torque spring seat, this torque spring seat has the maintenance feature formed by described adjacent component.

With reference to Figure 27,19,28 and 31, as shown in figure 31, the assembly of outer arm 120 and inner arm 122 forms spring seat 119.This comprises and keeps feature 119 to the entirety of the end of the torque spring 134,136 in Figure 19.

Torque spring 134,136 can move freely along the axis of pivotal axis 118.When fully assembled, the first and second lugs 405,406 on inner arm 122 keep the inner 409,410 of torque spring 134,136 respectively.The first and second excess of stroke limiters 140,142 on outer arm 120 are assembled into and prevent rotation and the outer end 407,408 keeping torque spring 134,136 respectively, and do not have excessive constraint or increase material and parts.

4.4 outer arm

The specific load optimization that the design of outer arm 120 is expected for run duration, and it is to being applied by other devices or its deviation may being caused to go out its specification from the moment in other directions and bending opposing.The example of inoperative load can be by process or machining causes.Clutch features or surface construction, in parts, are designed to auxiliary clamp and maintenance technique when grinding slide block, need crucial step to keep parallel between slide block when slide block holding member is fixed and is not out of shape.Figure 15 illustrates the perspective view of another rocking arm 100.First clamping lug 150 protrudes below the first slide block 130.Similarly, the second clamping lug (not shown) is positioned at below the second slide block 132.In the fabrication process, during grinding slide block 130,132, fixture gripper lug 150 is passed through.Active force is applied to clamping lug 150, and outer arm 120 is limited in appropriate location by this power, just as the assembled state of the part as rocker arm assembly 100.These surfaces of grinding need slide block 130,132 to keep being parallel to each other and outer arm 120 is indeformable.The distortion of outer arm 120 may be occurred in when the clamping clamping lug 150 place prevents under other clampings are arranged.Such as, in the clamping of clamping lug 150 place, preferred overall clamping, to outer arm 120, contributes to eliminating any mechanical pressure extruding mutually the generation of outer end arms 124,126 when clamping.In another embodiment, the position of clamping lug 150, directly under slide block 130,132, causes the almost nil extremely minimum moment of moment produced by lapping machine contact force on outer arm 120.In some applications, the other parts in outer arm 120 may be needed to apply pressure, so that minimization deformation.

4.5DVVL assembly operating

Figure 19 illustrates the exploded view of the switching rocking arm 100 of Figure 27 and 15.With reference to Figure 19 and 28, upon assembly, roller bearing 128 is parts of pin roll-type assembly 129, and pin roll-type assembly 129 can have the pin 180 be arranged between roller bearing 128 and roller bearing 182.Roller bearing 182 is installed to inner arm 122 by roller bearing through hole 183,184.

Roller assembly 129 for transmitting the spinning movement of low lift cams 108 to inner rocker arm 122, and then transfer operation to the valve 112 of non-kayser state.Pivotal axis 118 is installed to inner arm 122 at first end 101 place of rocking arm 100 by the axle collar 123 and is installed to outer arm 120 by pivotal axis through hole 160,162.Outer arm 120 produces around pivotal axis 118 relative to the idle running rotation of inner arm 122 in non-kayser state.Lost motion represents that outer arm 120 is relative to the motion of inner arm 122 in non-kayser state in this case.In non-kayser state, the spinning movement of the first and second high lift lobe 104,106 of cam 102 is not transmitted in this action to valve 112.

Other configurations except roller assembly 129 and slide block 130,132 also allow from cam 102 transfer operation to rocking arm 100.Such as, smooth non rotating surface (not shown) such as slide block 130,132 can be placed on to engage low lift lobe 108 on inner arm 122, and roller assembly can be installed to rocking arm 100 with from high lift lobe 104,106 transfer operation to the outer arm 120 of rocking arm 100.

Referring now to Fig. 4,19 and 12, as mentioned above, the switching rocking arm 100 of example uses three salient angle cams 102.

Compact to design for making, dynamic load is designed near without switching rocking arm as far as possible, and during high lift mode operation, slide block 130,132 is used as surface to contact cam lobe 104,106.Other design example of frictional ratio that slide block produces at run duration is as many in roller bearing, the friction between the first shoe surface 130 and the first high lift lobe 104, adds the friction between the second slide block 132 and the second high lift lobe 106, causes engine efficiency to lose.

When rocker arm assembly 100 is in high lift pattern, the full load of valve opening event is applied to slide block 130,132.When rocker arm assembly 100 is in low lift mode, the load that valve opening event is applied to slide block 130,132 is very little, but exists.Example switches the as narrower than most of existing slide block interface in contacted the width described with cam lobe 104,106 by shoe edge length 710,711 of each slide block of packaging constraint requirements 130,132 of rocking arm 100.This causes the component load higher than most of slide block interface and pressure.Friction causes the excessive wear to cam lobe 104,106 and slide block 130,132, may cause parts premature failure when combining higher load.In the switching rocker arm assembly of example, the coating of such as diamond-like coating is used on the slide block 130,312 on outer arm 120.

Diamond-like coating (DLC) makes the operation of the switching rocking arm 100 of example reduce friction, and simultaneously for shoe surface 130,132 provides necessary wearing and tearing and load characteristic.Can be readily seen that, the advantage of DLC coating can be applied to any parts surface of this assembly or other assemblies, such as, pivotal axis surface 160,162 on outer arm 120 shown in Figure 19.

Although there is similar cladding material and technique, but they are all not enough to the demand meeting following DVVL rocker arm assembly: 1) enough hardness, 2) there is suitable load bearing capacity, 3) chemically stable in running environment, 4) be suitable for wherein temperature and be no more than the technique of the annealing temperature of outer arm 120,5) engine life demand is met, with 6) friction of reduction is provided compared with the steel on steel interface.Before described DLC coating process meets above listed demand, and is applied to shoe surface 130,132, and shoe surface 130,132 is ground to final precision by the emery wheel material that described shoe surface use is the research and development of DLC coatings applications and speed.Shoe surface 130,132 is polished to specific surface roughness equally, uses the one in several technology, such as steam honing or particulate sandblasting.

4.5.1 hydraulic fluid system

Hydraulic pressure breech lock for rocker arm assembly 100 must be configured to and be assembled in tight space, meets handoff response time demand and minimum oil pumping loss.Fluid is directed along fluid path under controlled pressure, and to provide the mode of starting the required power of latch pin switching and speed to apply controlled volume.Hydraulic channel needs specific gap and size, has suitable hydraulic pressure rigidity and the handoff response time of generation to make system.The design of hydraulic system must with other co-operation comprising switching mechanism such as biasing spring 230.

In switching rocking arm 100, fluid is conveyed through array of fluid and is communicated with chamber and arrives latch pin assembly 201, or any other hydraulic actuating latch pin mechanism.As mentioned above, Hydraulic Power Transmission System, from the oily head piece 506 in DFHLA110, is introduced into controlled pressure at this mouthful of fluid or other hydraulic fluids.COMM communication such as solenoid pressure regulating valve can be used.After leaving ball plunger end 601, oil or other pressure fluid are directed through the first oil passage 144 and the second oil passage 146 of above-mentioned inner arm from this single position, this inner arm has the hole that to be of a size of minimum pressure when fluid flows through from ball seat 502 and to decline-as shown in Figure 10, arrives the latch pin assembly 201 in Figure 19.

For inner arm 122 being snapped to the latch pin assembly 201 of outer arm 120 shown in Figure 19, this latch pin assembly 201 is near the second end 103 of rocker arm assembly 100 in said embodiment, and this latch pin assembly 201 is depicted as to be included in high lift pattern and stretches out and inner arm 122 be fixed to the latch pin 200 of outer arm 120.In low lift mode, breech lock 200 is retracted in inner arm 122, allows the lost motion of outer arm 120.Oil pressure is for controlling the movement of latch pin 200.

As shown in figure 32, a mode of execution display of latch pin assembly, oil passage 144,146 (shown in Figure 19) is communicated with by fluid opening 280 fluid with chamber 250.

Depending on the needs of operating mode, fluid by with the pressure feed of certain limit to fluid opening 280 and latch pin assembly 201.

As Figure 33 can find out, once pressurization fluid is introduced in chamber 250, breech lock 200 is retracted in hole 240, allows outer arm 120 to carry out idle running relative to inner arm 122 and rotates.Fluid can transmit between the first overall periphery 205 and surface 241, from the first chamber 250 to the second chamber 420, as shown in figure 32.

Some fluid passing hole 209 are discharged and are got back to motor, enter inner arm 122.When biasing spring gets back to the high lift state of kayser, along with the stretching, extension of this biasing spring 230, residue fluid is pushed back by hydraulic path.Can understand, similar flow path may be used for the locking mechanism that the normal non-kayser of bias voltage runs.

The combination of the similar standard flowed by gap, tolerance, hole dimension, chamber size, spring design and control oil, the latch pin component design management latch pin response time.Such as, latch pin design can comprise some features, as having active hydraulic area with the two diameter pins run in the tolerance within the scope of setting pressure, the sealing surface or the oil-feed chamfering that are designed to limit oil pump loss.

Referring now to Figure 32-34, breech lock 200 is included in the confined space DESIGNED FEATURE providing several functions:

1, breech lock 200 uses the first roughly periphery 205 and second roughly periphery 206.First roughly the diameter that has of periphery 205 than second, roughly the diameter of periphery 206 is large.When pin 200 and sleeve pipe 210 fit together in hole 240, form chamber 250 when not using any optional feature.It is noted that this space is communicated with fluid opening 280 fluid.In addition, the oil pressure-can be controlled to provide necessary power that the region-combination of pressing surfaces 422 is transmitted, to make pin 200 move, compress biasing spring 230 and be switched to low lift mode (non-kayser).

2, the first space roughly between periphery 205 and adjacent hole wall 241 minimizes for making the fluid amount flowing into the second chamber 420 from chamber 250.When fluid is roughly carried from chamber 250 to the second chamber 420 between periphery 205 and surface 241 first, first roughly periphery 205 and surface 241 between gap must be moved freely by closely controlling to allow pin 200, and do not have fluid reveal and fluid pumping loss of being correlated with.

3, packaging restriction requires the distance minimization along the mobile axis of pin 200.In some running environment, existing fluid sealing surface 424 may be not enough to control the flow of the fluid roughly carried to the second chamber 420 from chamber 250 between periphery 205 and surface 241 first.A kind of annular seal surface is described.When breech lock 200 is retracted, it touches hole wall 208 in its rear surface 203.In a preferred embodiment, the rear surface 203 of breech lock 200 has flat annular or sealing surfaces 207, and this surface is approximately perpendicular to the first and second substantial cylindrical hole walls 241,242 and is parallel to hole wall 208.Flat annular surface 207 forms sealing against hole wall 208, which reduces by sealing from the oil liquid leakage of chamber 250, sealing by breech lock 200 first roughly barrel surface 205 and first roughly cylindrical bore wall 241 formed.The separation resistance that the area size of sealing surfaces 207 is designed to make to be caused by sealing surfaces 207 shown in Figure 32 and the oil film between hole wall 208 is minimum, keeps sealing to prevent compressed oil liquid from flowing between sealing surfaces 207 and hole wall 208 and tap hole 209 simultaneously.

4, in the mode of execution of a latch pin 200, oil-feed surface 426, such as chamfered section, provides initial press surface area, starts to allow to accelerate to switch and overcomes the separation resistance caused by the oil film between pressing surfaces 422 and sleeve end 427.The size of chamfered section and angle make switching easily start, and the oil pressure change accidental activation that can not occur due to normal operation period.In the mode of execution of second latch pin 200, the radial direction of a series of castellations 428-as shown in figure 34 arrange-provides initial press surface area, and it is designed and sized to and allows to accelerate to switch start and overcome the separation resistance caused by the oil film between pressing surfaces 422 and sleeve end 427.

Oil-feed surface 426 can also by reduce to the demand of disagglutinating action power between pressing surfaces 422 and sleeve end 427 reduce switch needed for pressure and pumping loss.These relations can be expressed as the incremental improvements to handoff response and pumping loss.

When fluid flows through previously described switching rocker arm assembly 100 hydraulic system, oil pressure and the relation between oily flow path region (area) and length greatly limit the reaction time of hydraulic system, and this also directly affects the handoff response time.Such as, if high-voltage oil liquid at full speed enters larger space, its speed reduces at once, thus reduces its hydraulic pressure reaction time or intensity.These scopes being used in particular for operating the relation switching rocker arm assembly 100 can calculate.A kind of relation such as can be described below: the fluid of 2 bar pressures is supplied to chamber 250, remove-transmit a power at this chamber place oil pressure-pressurized surface area, this is made every effort to overcome and takes biasing spring 230 power, and in 10 milliseconds, start the switching from snapping to the operation of non-kayser.

Cause the hydraulic pressure strength that is applicable to and response time-wherein minimized pumping loss can calculate from the system design variables-the scope of characteristic relation can limit as follows:

The internal diameter of oil passage 144,146 and from ball seat 502 to the length in hole 280

Hole 280 diameter and length

The area of pressing surfaces 422

The volume of chamber 250 in all running statees

The volume of the second chamber 420 in all running statees

By first roughly barrel surface 205 and surface 241 between space produce section area

The length of sealing surface 424

The area of flat annular surface 207

The diameter in hole 209

The oil pressure supplied by DFHLA110

The rigidity of biasing spring 230

The section area of flow channel 504,508,509 and length

The area on oil-feed surface 426 and quantity

The quantity of castellations 428 and section area.

In described switching rocking arm 100, the breech lock response time of hydraulic pressure installation is described for the condition of certain limit above, such as:

Oil temperature: 10 DEG C to 120 DEG C

Fluid type: 5w-20weight

These conditions cause the oil viscosity of the certain limit affecting the breech lock response time.

4.5.2 latch pin mechanism

Otherwise the latch pin mechanism 201 of rocker arm assembly 100 provides from high lift to low lift and mechanical switch mode.Latch pin mechanism can be set to usually be in non-kayser or kayser state.Some preferred implementations can be described.

In one embodiment, for inner arm 122 is snapped to outer arm 120-can see near the second end 103 of rocking arm 100-latch pin assembly 201 shown in Figure 19, it comprises latch pin 200, sleeve pipe 210, locating stud 220 and late spring 230.Latch pin assembly 201 is set to the inner side being arranged on inner arm 122 in hole 240.As described below, in the rocking arm 100 assembled, breech lock 200 stretches out in high lift pattern, inner arm 122 is fixed to outer arm 120.At low lift mode, breech lock 200 is retracted in inner arm 122, allows the lost motion of outer arm 120.As mentioned before, provide switching oil pressure by the first and second oil passage 144,146, to control breech lock 200 whether kayser.Plug 170 inserts in port hole 172, to form the compression seal of close first and second oil passage 144,146 and to allow them to flow through fluid to locking mechanism 201.

Figure 32 illustrate along the line 32 in Figure 28,33-32,33 the sectional view of the bolt lock mechanism 201 being in kayser state.Breech lock 200 is placed in hole 240.Breech lock 200 has spring eye 202, wherein inserts biasing spring 230.Breech lock 200 has rear surface 203 and front surface 204.Breech lock 200 also has the first roughly barrel surface 205 and second roughly barrel surface 206.First roughly barrel surface 205 there is the diameter that roughly barrel surface 206 is large than second.Spring eye 202 is roughly concentric with surface 205,206.

Sleeve pipe 210 have one with the first roughly outer surface 211 of substantial cylindrical that has a common boundary of cylindrical bore wall 241 and substantial cylindrical internal surface 215.Hole 240 has first roughly cylindrical bore wall 241 and diameter the second roughly cylindrical bore wall 242 that roughly cylindrical bore wall 241 is large than first.The substantial cylindrical outer surface 211 of sleeve pipe 210 and first of breech lock 200 roughly barrel surface 205 engage first roughly cylindrical bore wall 241 to form compression seal.In addition, the substantial cylindrical internal surface 215 of sleeve pipe 210 also with second of breech lock 200 roughly barrel surface 206 form compression seal.Be in operation, these sealings make oil pressure be formed in chamber 250, and this chamber is around the second roughly barrel surface 206 of breech lock 200.

The default location of breech lock 200-shown in Figure 32-be latched position.Spring 230 from hole 240 outside bias voltage breech lock 200 to latched position.The oil pressure being applied to chamber 250 makes breech lock 200 retract and makes it to move to non-latched position.Other configurations are also possible, such as spring 230 bias voltage breech lock 200 in non-latched position, and between hole wall 208 and rear surface 203, the applying of oil pressure causes breech lock 200 to extend outward to kayser outer arm 120 from hole 240.

In kayser state, breech lock 200 makes the latch surface 214 engaging arms engaging surface 213 of outer arm 120.As shown in figure 32, outer arm 120 is prevented from moving down and by breech lock 200 actuation to inner arm 122.Oriented feature 212 adopts the form of passage, and locating stud 221 is sold opening 217 by first and stretched into this passage in outside from inwall 122 by the second pin opening 218 in sleeve pipe 210 subsequently.Locating stud 221 is normally solid and level and smooth.Retainer 222 makes pin 221 in position.Locating stud 221 prevents breech lock 200 from excessively rotating in hole 240.

As mentioned before, and see Figure 33, once introduce pressurization fluid in chamber 250, breech lock 200 is just retracted in hole 240, allows outer arm 120 to carry out idle running relative to inner arm 122 and rotates.Outer arm 120 subsequently no longer latched 200 preventions moves down, and has lost motion.Pressurization fluid is incorporated into chamber 250 by fluid opening 280, and this fluid opening is communicated with oil passage 144,146 fluid.

Figure 35 A-35F illustrates some holding devices for locating stud 221.In Figure 35 A, pin 221 is have uniform thickness cylindrical.Push-tight ring 910 as shown in Figure 35 C is arranged on the depression 224 be arranged on sleeve pipe 210.Pin 221 inserts in ring 910, causes tooth 912 to be out of shape also fixing pin 221 and arrives ring 910.Then because ring 910 is enclosed in depression 224 by inner arm 122, pin 22 is secured in place.In another embodiment, as shown in Figure 35 B, pin 221 has groove 902, and the tooth 912 of ring 910 is pressed in this groove so that ring 910 is fixed to pin 221.In another mode of execution shown in Figure 35 D, pin 221 has groove 904, and the E clip 914 as shown in Figure 35 E or the arc E clip 914 as shown in Figure 35 F can be inserted in this groove, so that relative to inner arm 122 by position for pin 221.In another embodiment, metallic coil may be used for replacing punching press ring.At assembly process, E clip 914 is placed in depression 224, and is in the some place that sleeve pipe 210 is inserted into inner arm 122, and locating stud 221 inserts through clip 910 subsequently.

The breech lock 200 of example shown in Figure 36.Breech lock 200 is roughly divided into head portion 290 and body part 292.Front surface 204 stretches out convex surface.This surface configuration extends and the chance that suitably engages with outer arm 120 of the arm engaging surface 213 increasing breech lock 200 towards outer arm 120.Arm engaging surface 213 comprises the surface of general planar.Arm engaging surface 213 extends to the second boundary 286 from first border 285 with the second roughly barrel surface 206 and extends to the border 233 with surface 232 from the border 287 with front surface.Arm engaging surface 213 extend from surface 232 on the direction of the longitudinal axis A of breech lock 200 part farthest substantially equidistant between the first border 285 and the second boundary 286.On the contrary, arm engaging surface 213 on the direction of the longitudinal axis A of breech lock 200, extend nearest part generally within the first border 285 and the second boundary 286 from surface 232.Front surface 204 needs not to be convex surface, and can be V-arrangement surface, or some other shape.This arranges latch enable 200 rotation larger in hole 240, improves the possibility of the arm engaging surface 213 of breech lock 200 and the suitable joint of outer arm 120 simultaneously.

The bolt lock mechanism 201 of alternative form illustrates in Figure 37.The limit plug (directed plug) 1000 of the cup-shaped plug form of hollow is press-fitted in collar aperture 1002, and carrys out positioning latch 200 by stretching in locating features 212, excessively rotates relative to sleeve pipe 210 to prevent breech lock 200.As discussed further below, by providing the features making breech lock 200 can rotate in sleeve pipe 200, adjustment tank (alignment slots) 1004 contributes to breech lock 200 and to be positioned in sleeve pipe 210 and to be finally positioned in inner arm 122.Adjustment tank 1004 can, as a kind of features, utilize this features that breech lock 200 is rotated, and measures its relative bearing (orientation).

With reference to Figure 38-40, the exemplary method that assembling switches rocking arm 100 is as follows: limit plug 1000 is press-fitted in collar aperture 1002, and breech lock is inserted the substantial cylindrical internal surface 215 of sleeve pipe 210.

Latch pin 210 turns clockwise subsequently until locating features 212 arrives plug 1000, and the interference between this point patterns portion 212 and plug 1000 prevents from further rotating.Then take measurement of an angle A1, and as shown in figure 38, it corresponds to the angle between arm engaging surface 213 and sleeve benchmark 1010,1012, and this sleeve reference vehicular aligns in collar aperture 1002.Adjustment tank 1004 can also as the reference line of breech lock 200, and keyway 1014 can also as the reference be positioned on sleeve pipe 210.Latch pin 200 is rotated counterclockwise subsequently until locating features 212 arrives plug 1000, thus prevents from further rotating.Visible in Figure 39, measure the second angle A 2, it corresponds to the angle between arm engaging surface 213 and sleeve pipe benchmark 1010,1012.In order to obtain A1 and A2, also rotating along pointer subsequently counterclockwise is also allow.As shown in figure 40, once be inserted in inner arm 122, sleeve pipe 210 and pin assemblies 1200 rotate an angle A measured between inner arm benchmark 1020 and sleeve pipe benchmark 1010,1012, thus cause arm engaging surface 213 relative to inner arm 122 horizontal orientation, as shown in inner arm benchmark 1020.The amount A rotated should be chosen to be the possibility making breech lock 200 engage outer arm 120 and maximize.Such embodiment is when measuring from inner arm benchmark 1020, with the half angle gyrator assembly 1200 of the difference of A2 and A1.Other amounts adjusting A in the scope of the present disclosure are also possible.

The section of the alternate embodiments of pin 1000 is shown in Figure 41.At this, pin 1000 is hollow, and part surrounds internal volume 1050.Pin has the first wall 1030 of substantially cylindrical and the second wall 1040 of substantially cylindrical.The first wall 1030 of substantially cylindrical has diameter D1, and this diameter D1 is greater than the diameter D2 of the second wall 1040.In the mode of execution of shown in Figure 41, edge 1025 moves downwards through in sleeve pipe 210 for banking pin 1000 sells opening 218.In the second mode of execution shown in Figure 42, press fit banking pin 1000 moves downwards through in sleeve pipe 210 sells opening 218.

Breech lock embodiment as above utilizes smooth fitting surface engage during handover operation or be disengaged, and because herein is provided predictable contact area, this region has the relatively low contact stress for component.As above-mentioned, the parts that this pin designing requirement is extra and feature, to guarantee suitable orientation during operation, which increase complexity and the cost of rocker arm assembly manufacture and assembling process.

Another breech lock embodiment combines round or other is nonplanar (non-flat forms) latch pin, and described latch pin eliminates the demand to providing pin orientation.Think in the past, in order to utilize round or nonplanar rocking arm breech lock, fitting surface can require the bending fitting surface of expensive high tolerance " grinding ", or the breech lock seat of radius closely latch pin radius.Slightly too small seat may cause adhesion, delayed release, and may cause the bight of slam latch seat.Excessive breech lock seat allows that too much transverse direction (side direction) is mobile.As described below, stamping process can be utilized produce and not ask the circle of grinding or nonplanar breech lock embodiment.

In the illustrated example, for the breech lock round veritably with nonplanar breech lock frame, the needs of this breech lock directed in the rocking arm residing for breech lock are eliminated.By eliminating the demand of directed breech lock, assembling part and risk can be eliminated.

Described method also can reduce or eliminate such demand, that is, sort out breech lock, inner arm and outer arm with the clearance requirement met for given rocker arm assembly.This realizes by regulating latch gap at the end of assembling process.

Use description to manufacture the method that make use of rocker arm assembly that is round or nonplanar breech lock embodiment below.As has been noted, described method changes fitting surface by stamping process.

The utility model adopts nonplanar breech lock, such as, have the breech lock of circular cross-section, this circular cross section with from planar cross-sectional change and come breech lock seat be combined.The utility model comprises the design that can realize the bending fitting surface mating breech lock requirement, and does not need grinding process.Described method changes described fitting surface by stamping process.By using the breech lock round veritably with nonplanar breech lock frame, eliminate the needs of the rocking arm be arranged at breech lock this breech lock directed.By eliminating the demand of directed breech lock, the parts in assembly and assembling risk can be eliminated.

Described method can reduce or eliminate the demand sorted out by breech lock and demand inner arm and outer arm sorted out.This realizes by regulating latch gap at the end of assembling process.

This specification explains the VVL rocker arm assembly with normally unlocking latch position at this.Described method also may be used for cylinder deactivation rocker arm assembly, and other switches rocker arm assembly.Rocker arm assembly partly fits together with mounted roller bearing.Now not yet breech lock is installed.

As shown in Figure 134 and Figure 135, investment casting the second end 103 of outer arm 120, and by smooth for breech lock seat 214 punching press.

Next, outer arm will be arranged on the securing means with 3-point, under the pivoting hole make it be supported in below arm, being located immediately on arm both sides.Described outer arm will be positioned at the middle part of breech lock fitting surface subsequently by rotatable positioning member, provide 3-point and arrange.Therefore described outer arm will be located immediately at these some tops by angle of rotation clamping piece, thus can not make part distortion.

To carry out machining to pivoting hole now.Next, will heat-treat described outer arm.To polish pivoting hole now.

Pivoting hole is after this by milled.Parts are installed on the securing means, wherein sell the pivoting hole through outer arm 120 and the datum hole be positioned in fixing device.Outer arm 120 also by being resisted against on the rotation corner post that is located immediately under the breech lock pad surface of punching press, again providing 3 positions and eliminating part distortion.In described fixing device, stop rod will be machined into applicable height simultaneously and with pivoting hole axis being parallel.Now, outer arm will be positioned on pivoting hole and stop rod, in order to complete grinding final on slider pad.Present by assembling two arms.By spring fitting on inner arm spring stack, then assemble two arms, pivot pin is installed.

Figure 134 illustrates that see from its second end 103, that sections fit is good switching rocker arm assembly 100.This illustrates bottom side upwards, makes it possible to the transverse arm 439 seeing bottom.Interior arm component 622 (also shown in Figure 44 and Figure 45) suspends downwards.This illustrates latch hole 240 (this latch hole is also shown in Figure 19,33).

The end 103 of outer arm 120 also illustrates breech lock backstop 90 (Figure 15 illustrates another view of breech lock backstop 15).Point out as above-mentioned, the art methods of machining breech lock seat is only carried out on outer arm 120, and independent of other parts instead of measure as assembly.Because outer arm 120 carries out machining independently, therefore during measuring, do not consider the connection with other parts.In method and apparatus of the present utility model, alternatively process and measure the switching rocker arm assembly 100 assembled or partly assemble.Therefore, the breech lock coming from assembly is measured, instead of measure the breech lock coming from single parts.Figure 135 illustrates the perspective view of the switching rocker arm assembly with latch bar 199, and wherein latch bar 199 is inserted latch hole 240 and stretched out from this hole.Latch bar 199 is made up of the material harder than the material making breech lock seat 214.Switch rocker arm assembly 100 and be in locked position, stretch out at this position latch pin (herein, latch bar 199) and abut against on breech lock seat 214.

Figure 136 illustrates the manufacture fixing device 310 pointing to the complete manufacture switching rocker arm assembly 100.Particularly, it by be used for formed Figure 134,135 breech lock seat 214 in impression or recess time keep switch rocker arm assembly 100.

Be placed in the fixing device shown in Figure 136 by switching rocker arm assembly 100 now, this fixing device has the post for simulating ball plunger and the post for simulating valve top.Manufacture fixing device 310 shown in this embodiment is 3 assembling sets.This fixing device has bearing support 311, and the size and dimension of this bearing support is designed to the structure of support latch pin or analogous shape when switching rocker arm assembly and being installed in manufacture fixing device 310.Be provided with the valve roofbolt 315 for supporting the first end (101 of Figure 15) switching rocker arm assembly, and for supporting the valve roofbolt 313 of the second end (103 of Figure 15) switching rocker arm assembly.

Inner arm will to be resisted against on goalpost stick harness 315 and to be directed to opposite side by valve top post from side.Latch bar 199 has tight slip and is pressed in latch hole 240 and the size then slided in inner arm 122.Latch bar 199 will be stretched out from inner arm 122 (such as, stretching out about 10mm).Thus latch bar 199 will be resisted against on the carbide bearing support 311 of the plane be positioned in manufacture fixing device 310.Now, rocker arm assembly 100 is supported, as shown in Figure 137 by ball plunger 315 and the seat latch bar 199 be located on bearing support 311.

Rocker arm assembly 100 is controlled by goalpost stick harness 315 and valve top post 313 in both sides.Now, by be located immediately at above latch surface and press machine 317 at outer arm 120 top to outer arm 120 apply load (this press machine can be hydraulic pressure, screw or the controlled dynamic forces press machine of other form).This load will increase until reach correct latch gap always.The breech lock seat 214 of outer arm 120 has the recess of accurate punching press now in surface, and this recess just in time mates with latch pin (in Fig. 8,9 200).

Figure 137 is the unassembled view of the outer arm 120 after process, and breech lock seat 214 is shown.By forming described recess, latch pin (in Fig. 8,9 200) no longer has point cantact, and breech lock seat 214 will have the enough low contact stress level do not lost efficacy with operation.Because breech lock seat is formed together with the switching rocker arm assembly 100 almost to assemble completely, it should be understood that, switching rocker arm assembly 100 only needs latch pin is inserted to complete assembling process.After this in breech lock seat 214, impression is formed.The unassembled view of the outer arm in Figure 137 is only provided for the impression be manufactured in breech lock seat 214 is shown.

It is below the example of the step performing described method.

1, fitting surface is worn into the breech lock seat 214 of plane.

2, by outer arm 120, load is applied in latch bar 199 (it is carbide pin preferably), this latch bar analog latch pin, this latch pin is positioned in the latch hole 240 of inner rocker arm 122, with punching press in breech lock seat 214, cutting or formation impression (carbide pin/bar also can be made up of any material being suitable for punching press/cutting process).

3, this needs manufacture fixing device 310 to be kept at a pressure that by assembly.

4, load is increased until form distortion or the string degree of depth of the expectation for expecting gap in breech lock seat 214.

5, the vestige through outer arm 120 is measured with each delta duty, and record and preservation Trace Data.

6, described vestige should be obtained with each load at penetralia edge and middle pad region.

7, the latch assembly 200 of inner arm 122 with standard circular is re-assemblied.

8, cam clearance and gap are measured to verify assembly and whether meet regulation.

4.6DVVL pack clearance manages

Describe the DVVL shown in a kind of control chart 4 and switch three or more gap width of rocker arm assembly 100 or the method in design space.The method can comprise the design profile of certain limit manufacturing tolerances, wear allowance and cam lobe/rocking arm contact surface.

The explanation of DVVL pack clearance

Example rocker arm assembly 100 shown in Fig. 4 has one or more gap width, and these must be kept one or more positions in assembly.Three salient angle cams 102 shown in Fig. 4 comprise three cam lobes, the first high lift lobe 104, second high lift lobe 106 and low lift lobe 108.Cam lobe 104,106,108 has the molded line comprising basic circle 605,607,609 respectively, and described basic circle is depicted as circular and concentric with camshaft.

Switching rocking arm 100 shown in Fig. 4 is designed to have small―gap suture two positions.Primary importance-illustrate in Figure 43-be latch gap 602, it is the distance between breech lock pad surface 214 and arm engaging surface 213.Latch gap 602 ensures that breech lock 200 is not subject to load and can moves freely when switching between high lift and low lift mode.As Fig. 4,27, shown in 43 and 49, second example in gap is the distance between the first slide block 130 and the first high-lift cam salient angle basic circle 605, and it is expressed as camshaft gap 610.When contacting low lift cams basic circle 609 at low lift run duration roller bearing 128 as shown in figure 49, Contact and the associated friction loss of slide block 130,132 and their respective high-lift cam salient angle basic circles 605,607 are eliminated in camshaft gap 610.

In low lift mode, the power of torque spring 134,136 is also prevented to be sent to DFHLA110 in basic circle 609 run duration camshaft gap 610.This allows DFHLA110 to run as the standard rocker arm assembly with normal fluid pressure backlash compensation, and wherein the backlash compensation part of DFHLA directly provides from engine oil pressure passageway.As shown in figure 47, the rotation stop 621,623 that this action is switched in rocker arm assembly 100 promoted, described stop member prevents outer arm 120 enough far away rotatably due to the power contact high lift lobe 104,106 of torque spring 134,136.

As shown in Figure 43 and 48, total mechanical clearance is camshaft gap 610 and latch gap 602 sum.And valve event should be affected.High-lift cam spindle-type line comprises opening and closing domatic 661 to compensate total mechanical clearance 612.Minimum change in total mechanical clearance 612 is important to retention target in whole engine life.Gap is kept, aborning the strict error controlling total mechanical clearance 612 at particular range.Because component wear relates to the change of total mechanical clearance, in the life-span of whole mechanism, allow the component wear of low degree.A large amount of durability shows to pass through distributed wear allowance and total mechanical direct clearance terminates still in the specific limit to test.

With reference to chart shown in Figure 48, in the gap of millimeter at the longitudinal axis, be arranged on transverse axis in the camshaft angle of spending.The linear segment 661 of valve lift molded line 660 illustrate relative to given camshaft angle change in the constant variation of the distance of millimeter, and the region that closing speed wherein between contact surface is constant is shown.Such as, at the linear segment 661 of valve lift molded line curve 660, when rocker arm assembly 100 (Fig. 4) switches from low lift mode to high lift pattern, the closed distance between the first slide block 130 and the first high lift lobe 104 (Figure 43) represents constant speed.Use constant velocity region decreases the impulsive load owing to accelerating.

As shown in figure 48, during constant speed valve lift molded line curve 660 without lift part 661 in apneustic lift occur.If reduce by improved system design, manufacture or packaging technology or strictly control total backlash, then the time demand of the linear speed part of valve lift molded line reduces, this provide engine management advantage, such as, allow valve earlier to open or air door operation consistent between motor.

As Figure 43,47 and 48, design and the assembling change of individual component or sub-component can produce gap width matrix, and these values meet and switch timing specification and to reduce the constant speed of described needs above Zone switched.Such as, what latch pin 200 auto-alignment mode of execution can comprise needs 10 microns minimizes latch gap 602 so that the features worked.Be configured to the latch gap 602 that can be designed as needs 5 microns without the breech lock 200 of the improvement of auto-alignment features.This design modification decreases the total backlash of 5 microns, and reduce valve lift molded line 660 need without lift 661 part.

Latch gap 602 shown in Figure 43 and camshaft gap 610 can be described for the mode using other modes to contact any design modification of the switching rocker arm assembly 100 of three salient angle cams 102 similar in Fig. 4.In one embodiment, the slide block of similar 130 is used to substitute roller bearing 128 (Figure 15 and 27).In this second embodiment, the roller of 128 is similar to for alternative slide block 130 and slide block 132.Other mode of executions are also had to have the combination of roller and slide block.

Gap manages, test

As following paragraph describes, for managing the Design and manufacture method in gap for expecting that the certain limit of running environment is tested and verify, to simulate the operation normally running and represent high stress environment.

The durability that DVVL switches rocking arm is assessed in conjunction with wear testing by duration performance (opening and closing that such as valve is suitable).The DVVL by quantifying of wearing and tearing switch material on rocking arm particularly in the loss of DLC coating and system the relative quantity of mechanical clearance assess.As previously discussed, latch gap 602 (Figure 43) must move between interior outer arm with latch enable pin, high and low lift can be made to run when being ordered by engine electronic control unit (ECU).DVVL switches on rocking arm and can reduce effectively without domatic 661 (Figure 48) of lift for the increase in the gap of any reason, causes the acceleration that valve mechanism is high.Relative to the wearing and tearing specification assumes of mechanical clearance for allowing limit structure parts to keep required dynamic performance in the later stage in life-span.

Such as, as shown in figure 43, the total backlash that the wearing and tearing in rocker arm assembly between contact surface can change latch gap 602, camshaft gap 610 and produce.The wearing and tearing affecting these each values can describe as follows: the interface wearing and tearing 1) between roller bearing 128 (Figure 15) and cam lobe 108 (Fig. 4) reduce total backlash, 2) between slide block 130,132 (Figure 15) and cam lobe 104,106 (Fig. 4), the wearing and tearing of sliding interface increase total backlash, 3) wearing and tearing between breech lock 200 and breech lock pad surface 214 increase total backlash.Because bearing interface wearing and tearing reduce the interface wearing and tearing increase total backlash of total backlash and breech lock and slide block, therefore whole wearing and tearing cause minimized clean total backlash change in the whole life-span of rocker arm assembly.

4.7DVVL assembly is dynamic

The inertia of conventional rocker, weight distribution and rigidity are optimised, and for relating to the dynamic stability of run duration, valve tip loads and the motion speed of particular range of valve spring compression and active force.Example shown in Fig. 4 switches rocking arm 100 and has the designing requirement identical with conventional rocker, is wherein applied with additional restriction by the quality of the increase of assembly and switching function.Other factors also must be considered, comprise the impulsive load because pattern handoff error causes and sub-component Functional Requirement.Reducing quality and inertia but effectively can not carrying out the design that in holding structure rigidity and opposing key area, stress material requested distributes causes parts depart from specification or become over-stress, and both is all the situation causing poor performance of handoffs and too early component failure.DVVL rocker arm assembly 100 shown in Fig. 4 must be stabilized in 3500rpm at low lift mode and in high lift pattern, be stabilized in 7300rpm to meet performance requirement.

As Fig. 4,15,19 and 27, DVVL rocker arm assembly 100 intensity all evaluated in low lift and high lift pattern.At low lift mode, inner arm 122 conveying capacity is to open valve 112.The motor packaging space surplus of inner arm 112 and functional parameter do not need the high structure optimized, because inner arm rigidity is greater than the rigidity of the fixing rocking arm in same application.In high lift pattern, outer arm 120 works with transmitting forces to open valve 112 together with inner arm 122.Finite element analysis (FEA) technology show, outer arm 120 is the parts of being obedient to most, as in Figure 50 with the maximum region of vertical missing 670 shown in exemplary plot.The mass distribution of these parts and stiffness optimization are concentrated on the vertical section height increasing outer arm 120 between slide block 130,132 and breech lock 200.The design restriction of the upper molded line of outer arm 120 is based on the gap between outer arm 120 and the scanning molded line of high lift lobe 104,106.The design restriction of the lower molded line of outer arm 120 is based on the gap to valve spring retainer 116 in low lift mode.In described design, optimize distribution of material constraint conditio reduce vertical missing and increase rigidity, in one embodiment, be greater than 33% of initial designs.

As shown in Figure 15 and 52, DVVL rocker arm assembly 100 is designed to, when it around during ball plunger point of contact 611 pivotable of DFHLA110 by making inertia minimize towards the quality of sidepiece 101 bias assembly as far as possible.This causes the assembly being provided with two larger quality, and pivotal axis 118 and torque spring 134,136 are positioned near the sidepiece 101 of DFHLA110.By being in the pivotal axis 118 of this position, breech lock 200 is positioned at the end 103 of DVVL rocker arm assembly 100.

Figure 55 is the chart comparing DVVL rocker arm assembly 100 rigidity and other standards rocking arm in high lift pattern.For the application DVVL rocker arm assembly 100, there is the rigidity lower than fixing rocking arm; But, in the existing scope of the rocking arm that its rigidity uses in the similar valve mechanism configuration produced now.The inertia of DVVL rocker arm assembly 100 is approximately the twice of the inertia of fixing rocking arm, but its inertia only a little higher than similar valve mechanism produced now arranges the intermediate value of the rocking arm of middle use.Whole effective masses of intake valve mechanism-comprise many DVVL rocker arm assembly 100-than fixing intake valve mechanism large 28%.These rigidity, quality and inertia values need to optimize each parts and sub-component to guarantee to minimize inertia and maximum rigidity, meet operating energy loss standard simultaneously.

4.7.1DVVL assembly dynamically describes in detail

The critical piece comprising total inertia of rocker arm assembly 100 is shown in Figure 53.They are interior arm component 622, outer arm 120 and torque springs 134,136.As indication, the function requirement of interior arm component 622, such as its hydraulic fluid bang path and its latch pin mechanism shell, need the structure harder than fixing rocking arm for identical application.In the following description, interior arm component 622 is considered to single parts.

The plan view of rocker arm assembly 100 in Fig. 4 is shown with reference to Figure 51-53, Figure 51.Figure 52 is the sectional view along Figure 51 center line 52-52, and the load contact point of rocker arm assembly 100 is shown.The three salient angle cam 102 distributing cam loads 616 of rotating to roller bearing 128 or-depending on operating mode-to slide block 130,132.Ball plunger end 601 and valve tip 613 provide contrary power.

In low lift mode, interior arm component 622 transmits cam loads 616 to valve tip 613, extrusion spring 114 (Fig. 4), and opens valve 112.In high lift pattern, outer arm 120 is together with interior arm component 622 kayser.In this case, outer arm 120 transmits cam loads 616 to valve tip 613, extrusion spring 114, and opens valve 112.

With reference now to Figure 4 and 52, total inertia of rocking arm 100 is determined by the inertia sum of its critical piece, and calculates when they rotate around ball plunger point of contact 611.In the rocker arm assembly 100 of example, critical piece can be defined as torque spring 134,136, interior arm component 622 and outer arm 120.When total inertia increases, the dynamic load on valve tip 613 increases, and system dynamic stability declines.In order to minimize valve tip load and maximize dynamic stability, the quality of all rocker arm assemblies 100 is by towards ball plunger point of contact 611 bias voltage.Can the amount of biased quality be needed to limit the desirable strength of given cam loads 616, valve tip 614 and ball plunger load 615 by rocker arm assembly 100.

See now Figure 4 and 52, when they are at high lift or low lift condition, the rigidity of rocker arm assembly 100 is determined by the composite rigidity of interior arm component 622 and outer arm 120.Finite element analysis (FEA) or other analytical methods can be used to calculate and visualization the rigidity value at given position any on rocker arm assembly 100, it is characterized in that the chart of rigidity relative to the position along measurement axle 618.In a similar manner, the rigidity of outer arm 120 and interior arm component 622 can use finite element analysis (FEA) or other analytical methods to calculate respectively and visualization.Example describes 106 and shows rigidity these results analyzed relative to the series of features chart of the position along measurement axle 618.As description other before, Figure 50 illustrates the chart of the maximum deflection of outer arm 120.

Referring now to Figure 52 and 56, finite element analysis (FEA) or other analytical methods can be used to calculate to the pressure in region and the deviation of giving any on rocker arm assembly 100, and feature is relative to along the chart of position measuring axle 618 for the pressure of given cam loads 616, valve tip 614 and ball plunger load 615 and deviation.In a similar fashion, the pressure of outer arm 120 and interior arm component 622 and deviation can use finite element analysis (FEA) or other analytical methods to calculate respectively.In Figure 56, exemplary description shows for the pressure of given cam loads 616, valve tip 614 and ball plunger load 615 and deviation relative to along the series of features graphic analyses result of position measuring axle 618.

4.7.2DVVL assembly dynamic analysis

For pressure and variance analysis, just the load situation shown in Figure 52 and value describe loading condition.Such as, in the kayser rocker arm assembly 100 in high lift pattern, cam loads 616 is applied to slide block 130,132.Cam loads 616 is by valve tip load 614 and ball plunger load 615 reaction.First distance 632 is the distances measured between valve tip load 614 and ball plunger load 615 along measurement axle 618.Second distance 634 is the distances measured between valve tip load 614 and camshaft load 616 along measurement axle 618.Load percentage is that second distance 634 is divided by the first distance 632.In order to dynamic analysis, consider that multiple value and operating conditions are for analyzing and possible optimization.These can comprise three salient angle camshaft interface parameterss, torque spring parameter, total mechanical clearance, inertia, valve spring parameter and DFHLA parameter.

For assessment of design parameter can be described as:

Referring now to Fig. 4,51,52,53 and 54, based on given set of design parameters, general design method is described.

1, in step one 350, along measurement axle arrangement component 622,120,134 and 136, with towards ball plunger point of contact 611 bias voltage quality.Such as, torque spring 134,136 can be positioned at 2mm place on the left of ball plunger point of contact, and interior arm component 622 pivoting axis 118 can be positioned at 5mm place, right side.Outer arm 120 can align with pivotal axis 118 and place, as shown in Figure 53.

2, in step 351, given parts are arranged, total inertia is calculated to rocker arm assembly 100.

3, in step 352, what evaluation means was arranged is functional.Such as, confirm that torque spring 134,136 can provide required rigidity to contact cam 102 to keep slide block 130,132 at its special position, and do not increase quality.In another embodiment, parts are arranged and must be determined with assembling within Package size restriction.

4, in step 353, the result of appraisal procedure 351 and 352.If valve tip load 614 and the minimum essential requirement of dynamic stability under selected engine speed are not satisfied, again in step 351 and 352, are set up iteration at parts cloth and analyze.When valve tip load 614 and dynamic stability, the minimum essential requirement under selected engine speed is satisfied, to rocker arm assembly 100 calculation deviation and stress.

5, in step 354, calculated stress and deviation.

6, in step 356, evaluation error and stress.If the minimum essential requirement of deviation and stress is not satisfied, then proceed to step 355, and improve part design.When design iteration completes, get back to step 353 and reappraise valve tip load 614 and dynamic stability.When valve tip load 614 and dynamic stability, the minimum essential requirement under selected engine speed is satisfied, calculation deviation and stress in step 354.

7, with reference to Figure 55, when the condition of stress, deviation and dynamic stability is satisfied, result is a possible design 357.Analysis result can illustrate possible design and arrange in the plotted curve of rigidity relative to inertia.This diagram provides the acceptable value of the certain limit as region 360 indication.Figure 57 shows three independently can accept design.Amplification is come, and acceptable inertia/stiffness region 360 also limits the feature of individual critical piece 120,622 and torque spring 134,136.

Referring now to Fig. 4,52,55, as mentioned above, if each critical piece of rocker arm assembly 100-comprise outer arm 120, interior arm component 622 and torque spring 134,136 all satisfied specific design criteria for inertia, pressure and deviation, then successfully design is implemented.Successfully be designed to each primary clustering and produce unique characteristic.

In order to describe, select three functional DVVL rocker arm assemblies 100, their shown in Figure 57 and satisfied certain rigidity/inertia standards.These assemblies are each comprises three critical pieces: torque spring 134,136, outer arm 120 and interior arm component 622.In order to this analyzes, the example as Figure 58 A-58C describes, to can being described as of the scope of the possible inertia values of each critical piece:

Torque spring group, design one, inertia=A; Torque spring group, design two, inertia=B; Torque spring group, design three, inertia=C.

The torque spring group inertia scope calculated around pommel plug top (in Figure 59 equally with X instruction) limits by being worth the scope that A, B and C define.

Outer arm, design one, inertia=D; Outer arm, design two, inertia=E; Outer arm, design three, inertia=F.

The outer arm inertia scope calculated around pommel plug top (in Figure 59 equally with X instruction) limits by being worth the scope that D, E and F define.

Interior arm component, design one, inertia=X; Interior arm component, design two, inertia=Y; Interior arm component, design three, inertia=Z.

The interior arm component inertia scope calculated around pommel plug top (in Figure 59 equally with X instruction) limits by being worth the scope that X, Y and Z define.

The scope of this component inertia value then produces the unique arrangement of critical piece (torque spring, interior arm component and outer arm).Such as, in this design, torque spring tends to very near plug top, pommel 611.

With reference to Figure 57-61, the inertia for individual component calculates and the load request tight association in assembly, because the mass distribution optimization making the minimized expectation of inertia need in parts, to manage the stress in key area.Each in above-mentioned three successful design, the scope for the value of rigidity and mass distribution can be described below:

Design one for outer arm 120, mass distribution can be drawn to the distance of end B relative to along parts from end A.In an identical manner, outer arm 120 design two and the outer arm 120 mass distribution value that designs three also can illustrate.

Region in this assembly between two extreme mass distribution curves can be defined as the scope of the eigenvalue of outer arm 120.

Design one for outer arm 120, Stiffness Distribution can be drawn from end A to the distance of end B relative to the distance along parts.In an identical manner, outer arm 120 design two and outer arm 120 rigidity value that designs three also can illustrate.

Region in this assembly between two extreme Stiffness Distribution curves can be defined as the scope of the eigenvalue of outer arm 120.

Outer arm 120 along axle and the rigidity relevant with orientation to its action of run duration and mass distribution Expressive Features value, and amplification is come Expressive Features shape.

5. design verification

5.1 breech lock responses

The breech lock response time of example DVVL system uses the breech lock response test platform 900 shown in Figure 62 to verify, to switch in the mechanical switch window guaranteeing the aforementioned regulation that rocker arm assembly is described in fig. 26.For scope from 10 DEG C to 120 DEG C to affect the oil temperature recording responses time of Varying Oil Viscosity.

Breech lock response test platform 900 utilizes produces specialized hardware, comprises OCV, DFHLA and DVVL and switches rocking arm 100.In order to simulated engine fluid condition, oil temperature is controlled by external heat or cooling system.Oil pressure is supplied by external pump and adjustment in use device controls.Measure in the control channel of oil temperature between OCV and DFHLA.Breech lock moves and uses displacement transducer 901 to measure.

The breech lock response time uses the special SRFF of multiple production to measure.Test uses the machine oil of 5w-20 to carry out.When from low lift mode to high lift pattern with from high lift pattern to low lift mode switching, the response time is recorded.

Figure 21 details the breech lock response time when being switched to high lift pattern from low lift mode.Be measured as at the maximum response time of 20 DEG C and be less than 10 milliseconds.Figure 22 details the mechanical response time when being switched to low lift mode from high lift pattern.Be measured as at the maximum response time of 20 DEG C and be less than 10 milliseconds.

Carry out the conclusion display of adaptive switched research, the switching time of breech lock is the major function of oil temperature, due to the change of oil viscosity.The viscosity temperature relation of the similar machine oil of slope of breech lock response curve.

Handoff response conclusion shows, breech lock move a camshaft rotary mode within 3500 motor rpm is switched enough fast.When temperature is down to below 20 DEG C, the response time starts remarkable increase.Be 10 DEG C and following in temperature, do not reduce 3500rpm and switch to require and carry out switching in a camshaft rotates to be impossible.

It is all sane that SRFF to be designed under high engine speed for the height shown in table 1 and low lift mode.High lift pattern can be run within 7300rpm, and has " breaking " rate request of 7500rpm.To break the short stroke be defined as more high engine speed.In high lift pattern, SRFF is by normal kayser, thus high lift pattern does not rely on oil temperature.Low lift operating mode focuses on the fuel economy that component load operates in period within 3500rpm, wherein except 7500rpm " breaks " speed requirement also had except speed more than 5000rpm.As test, SRFF can be unlocked by hydraulic pressure for oil temperature 200 DEG C or more systems.Be reduced to 10 DEG C to carry out testing to guarantee to operate in 20 DEG C.Durability results shows, and it is all sane for designing for the engine speed of whole service scope, lift mode and oil temperature.

Table 1

In order to realize closing intake valve in advance and SRFF based on DVVL system designs, improves and verifies and completes for model II valve mechanism.This DVVL system is improved fuel economy by running in two modes and does not damage performance.In low lift mode, reduce pump circulation loss, simultaneously by use standard intake valve molded line retention in high lift pattern by closing intake valve in advance.The geometrical shape of the conventional model II air inlet of this systematic conservation and exhaust valve mechanism, for being used in in-line four cylinder petrol engine.Be minimized by using general components and standard chain drive system implementation cost.The SRFF based system of model II is used to allow this hardware of various engines serial application by this way.

This DVVL system-it to be arranged in intake valve mechanism-all to meet in high lift and low lift mode and to switch for pattern and the Key performance targets of dynamic stability.The handoff response time allows pattern to switch under the oil temperature more than 20 DEG C and the engine speed within 3500rpm in a cam rotates.The optimization of SRFF rigidity and inertia, allows system at low lift mode dynamic stability to 3500rpm and at high lift pattern dynamic stability to 7300rpm in conjunction with suitable valve lift Profile Design.The validation test display DVVL system that production specialized hardware completes exceeds durability target.Acceleration system aging test is in order to prove that durability exceedes target life objective.

5.2 durability

The discharge requirement in working life of car demand fulfillment 150000 miles.It is sane to guarantee that product exceedes legal requirements ground that this research sets the stricter target of 200000 miles.

Valve mechanism is 200000 miles of targets to the requirement of life test end.This mileage target must be converted to valve actuation to define valve mechanism life requirement.In order to determine the quantity of valve event, assumed average car speed and average engine speed vehicle ages must be exceeded.For this embodiment, the average vehicle speed of 40 miles per hour and the mean engine speed of 2200rpm can be selected for car.Camshaft speed run under the engine speed of half and valve often enclose camshaft rotate activated once, cause test request 3.3 hundred million valve event.Test builds is being piloted engine with on non-starting arrangement.Not that operation is piloted engine test for 5000 hours, but mostly test and report the result and concentrate on non-starting arrangement shown in Figure 63 to carry out meeting the test of 3.3 hundred million valve events.Comparing starting with non-result of starting test, corresponding to valve mechanism wear results, for non-starting arrangement life test provides confidence level dry straightly.

5.2.1 accelerated ageing

Before operation Engine Block Test, need to carry out accelerated test to show deferring to the multiple-motor life-span.Therefore, device to test carried out before starting test.Higher velocity test is designed to accelerate valve mechanism wearing and tearing thus it can complete within the less time.Set up the association of test, thus to bear results within the time of about 1/4th relative to operating speed multiplication mean engine speed and basic equal with valve mechanism attrition value.Therefore, following equation is strictly deferred in valve mechanism wearing and tearing:

${\mathrm{VE}}_{Accel}~{\mathrm{VE}}_{in-use}{\left(\frac{{\mathrm{RPM}}_{avg-test}}{{\mathrm{RPM}}_{avg-inuse}}\right)}^2$

Wherein, VE _accelthe valve event of accelerated ageing test period requirement, VE _in-usethe valve event required in normal use test, RPM _avg-testthe mean engine speed for accelerated test, RPM _avg-inusethe mean engine speed for use test.

Develop a patented high speed durability test circulation, this circulation has the mean engine speed of about 5000rpm.Each circulation has the high speed stage in the high lift pattern of about 60 minutes, the low-speed stage then in the low lift mode of about other 10 minutes.This is cycled to repeat 430 times to complete 7,200 ten thousand valve events under the wear rate accelerated, and this equals 3.3 hundred million events of proof load level.The standard valve mechanism product comprising pin and roller bearing has been used successfully in automobile industry for many years.This test loop focuses on DLC coating slide block, and wherein in high lift pattern, the valve lift event of about 97%, on slide block, is left to circulate in for 2,000,000 times on low lift roller bearing, as shown in table 2.These test conditions consider a valve mechanism life-span of circulating equal with 430 accelerated tests.Test display, ignore wearing and tearing and gap change, SRFF through six motor actual lives be durable.

Table 2: durability test, valve event and target

Acceleration system aging test is the key of display durability, can also complete the test of some specific functions to show the robustness of various running state simultaneously.

Table 2 comprises the main durability test combined with the object of each test.Above-mentioned acceleration system aging test display about 500 hours or about 430 test loop.Run about 500 hours of switch test assess breech lock and torque spring weares and teares.Same, also carry out critical conversion testing with ageing component further in the coarse of the outer arm from part kayser and the switching of abuse, thus it can slide into low lift mode during high lift event.Carry out critical conversion testing structure to be presented at the robustness under the extreme condition that caused by unsuitable vehicle maintenance.This critical conversion testing is difficult to reach and requires that accurate oil pressure cntrol is with part kayser outer arm in testing experiment.This operation undesirably uses because oil pressure cntrol controls beyond window.Multiple idle running test is carried out with due to low oil lubrication accelerated wear test in conjunction with cold start operation.The fluid test used is carried out equally at high speeds.Finally, bearing and torque spring test are to guarantee parts durability.All tests meet the motor actual life requirement of 200000 miles, this at secure context higher than the requirement of 150000 miles of car actual life.

All durability tests are performed with specific oil-filled grade.General to passenger car applications, the oil-filled rate range that great majority test has is between the total gas content of about 15%-20% (TGC).This content changes along with engine speed, and this grade is quantified as from idling up to 7500rpm engine speed.Also carry out excessive oil-filled test, it has the oil-filled grade of 26%TGC.These tests perform with SRFF, and they meet dynamically and the test of performance of handoffs.The conclusion paragraph that is described in detail in of dynamic performance testing is described.Perform oil-filled grade and expand grade to show product robustness.

5.2.2 device for testing endurance

Durability test platform shown in Figure 63 comprise have additional engine Oil-temperature control system 905 by the prototype 2.5L four cylinder engine of motoring.Camshaft location is by being monitored by the encoder 902 of the precise coder 802S outside of camshaft actuated.The angular velocity of camshaft uses digital magnetoelectric tachometric transducer (model Honeywell584) 904 to measure.Oil pressure in control channel and hydraulic channel uses the monitoring of KuliteXTL piezo-electric pressure sensor.

5.2.3 device for testing endurance controls

The set-up of control system of fixture is for controlling engine speed, oil temperature and valve lift condition and verifying that expection lift function realizes.The performance of valve mechanism is measured valve displacement to assess close to probe 906 by using non-intrusion type BentleyNevada3300XL.Close to probe with the valve lift within 1.5 times of camshaft angle resolution measurement 2mm.This is closing velocity and the reprocessing analyzed and submit necessary information to confirm valve lift state and data of beating.The test of setting up comprises valve displacement and follows the trail of, this tracking be recorded to represent under idling speed SRFF base condition and for determining the principal mode line 908 shown in Figure 64.

Figure 17 illustrates system diagnostics window, and it represents for diagnosing one of valve-closing displacement to switch circulation.OCV controls by causing the control system of OCV armature movement, and this moves as shown in by OCV current locus 881.In fluid control channel, the pressure in OCV downstream increases, as shown in pressure diagram 880; Therefore, actuated latch pin causes the change of state from high lift to low lift.

Figure 64 illustrates valve-closing tolerance 909 and the relation testing the principal mode line 908 determined.The last 2mm being calibrated to measure lift close to probe 906 used, the longitudinal axis wherein in Figure 64 illustrates the last 1.2mm of lift.2.5 " camshaft angle tolerance establishes the change from the valve mechanism compression under high engine speed allowed in lift around principal mode line 908, to prevent from recording wrong fault.Set up detection window to determine whether valvetrain system has anticipated deviation.Such as, more Zao camshaft angle more acutely can be caused to close than expection valve-closing, thus cause the valve bounce due to less desirable excess speed.These anomalies can be detected around the detection window of principal mode line and tolerance.

5.2.4 durability test plan

Perform design failure pattern and impact analysis, to determine SRFF failure mode.Similarly, mechanism is determined with the grade of system and subtense angle.This information for improvement of with assessment SRFF to the durability of different operating conditions.As shown in Figure 65, test-types is divided into four classifications, comprising: performance verification, subsystem testing, limit test and acceleration system aging.

Shown in Figure 65 to the key test level of durability.The performance that performance verification test display SRFF requires application, and be the first step in durability checking.Subsystem testing assessment life of product cycle period specific function and wear interface.Limit test makes SRFF stand harsh user and operational limit.Finally, accelerated ageing test is the integration testing of comprehensive assessment SRFF.The success of these tests demonstrates the durability of SRFF.

Performance verification

-tired & rigidity

SRFF tests through cyclic loading to guarantee that fatigue life exceedes application load by larger design margin.Valve mechanism performance relies on the rigidity of system unit to a great extent.To measure the rigidity of rocking arm with test design and guarantee acceptable dynamic performance.

-valve mechanism is dynamic

The explanation of valve mechanism dynamic test and performance describe in conclusion section.Test relates to the strain combined with measurement valve closing velocity and measures SRFF.

Subsystem testing

-switch durability

Switch durability test by making SRFF at kayser, non-kayser and getting back to the total 3,000,000 times (Figure 24 and 25) that to circulate between kayser state and assess switching mechanism.The main purpose of test is assessment locking mechanism.Obtain other durability information when considering torque spring, due to test loop 50% in low lift.

-torque spring durability and fatigue

Torque spring is the one-piece element switching the driven device of roller finger wheel.Torque spring allows outer arm to run under idle running, keeps in touch high-lift cam crown of roll angle simultaneously.Perform torque spring durability test so that the durability of the torque spring under evaluation operation load.The torque spring durability test torque spring be arranged in SRFF carries out.The fatigue life of torque spring under torque spring Fatigue test assessment high stress level.Be defined as successfully when end torque spring load loss is less than 15% in the life-span.

-idling speed durability

Idling speed durability simulates the limit lubricating condition caused by low oil pressure and high oil temperature.Test for assessment of slide block and bearing, valve tip to valve pallet and seat to the wearing and tearing of ball plunger.Lift condition keeps being constant in high or low lift in whole test process.To make regular check on the total mechanical clearance of interval measurement, and it is the primary appraisal of wearing and tearing.

Limit test

-hypervelocity

Switch rocking arm failure mode to comprise and lose lift condition and control.SRFF is designed to run with the maximum cam axle speed of 3500rpm in low lift mode.When causing the less desirable inefficacy of low lift condition, SRFF comprises the design protection to those more speeds.Test fatigue life of low lift is carried out under 5000rpm.Motor breaks to test and carries out under 7500rpm high lift state and low lift condition.

-cold starting durability

The ability standing 300 engine starts circulation from the initial temperature of-30 DEG C of cold starting durability test assessment DLC.Usually, the cold climate motor started at these tem-peratures comprises engine cylinder heater.This is selected extremely to test to show robustness and repeat 300 times on motorization motor fixture.This thermometrically DLC coating stands the ability of the lubrication of the reduction caused by low temperature.

-critical conversion durability

SRFF is designed to switch on the basic circle of camshaft and latch pin does not contact outer arm.Under unsuitable OCV timing or the event lower than the minimum control channel oil pressure needed for full latch pin stroke, latch pin still may move in the beginning of next lift.The inappropriate position of latch pin may cause the part of latch pin and outer arm to engage.In the part joint event of latch pin and outer arm, outer arm may cause producing between roller bearing and low lift cam lobes impacting by landing latch pin.Critical conversion durability is bad use test, and it creates conditions to quantize robustness and is less desirable in the life time of vehicle.Critical conversion testing makes SRFF stand 5000 subcritical change event.

The bearing endurance of-acceleration

Acceleration bearing endurance is the life test for assessment of the bearing life completing critical conversion testing.This test is for determining whether the effect of critical conversion testing shortens the life-span of roller bearing.Test the time running to have reduced under the radial load increased.New bearing is stood performance and the wearing and tearing of critical conversion testing by side by side testing to show test bearing.Carry out vibration measurement in whole process and analyzed the beginning to detect bearing damage.

The fluid test of-use

The system aging test accelerated and idling speed durability test molded line use the fluid with 20/19/16ISO grade to carry out.This fluid takes from motor in the drain period.

The system aging accelerated

The system aging test accelerated, for assessment of the overall durability of rocker arm assembly, comprises the sliding interface between camshaft and SRFF, locking mechanism and low lift bearing.Come measurement mechanical gap to make regular check on interval, and mainly measure wearing and tearing.Figure 66 illustrates the testing scheme assessing SRFF in the system aging test loop accelerated.Mechanical clearance is measured and FTIR measurement allows to carry out the sound research of SRFF and DLC coating entirety separately.Finally, parts are disassembled to try hard to understand the source of any change when mechanical clearance is from test.

Figure 67 is the pie chart of the dependence test time represented SRFF durability test, and test comprises total about 15700 hours.The information that acceleration system aging test provides each test hour maximum, due to accelerator in a test and cause to the combination load of SRFF total testing time 37% distribution.Due to the endurance of the length of each test, idling speed durability (low speed, low lift and low speed, high lift) test accounts for 29% of total testing time.Switch durability carry out testing for multiple life-span and take the total testing time of 9%.Owing to being difficult to reach the thermal cycle times needed for critical conversion and cold starting durability, critical conversion and cold starting durability test need the plenty of time.The quantification of data is not only critical conversion and cold starting time itself according to the cumulative time of carrying out these pattern needs.Remaining subtense angle and limit test need the total testing time of 11%.

Valve mechanism is dynamic

Valve mechanism dynamic behavior determines performance and the durability of motor.Dynamic performance is determined by assessment closing velocity and the bounce-back of the valve when valve gets back to valve seat.Resistance strain gauge provides about system load relative to the information of camshaft angle on engine speed envelope.Resistance strain gauge is applied to inner arm and outer arm at the position of uniform pressure.Figure 68 illustrates the resistance strain gauge being attached to SRFF.Outer arm and inner arm are equipped with instrument with monitor strain, thus the load capacity on verification SRFF.

Carry out valve mechanism dynamic test to assess the performance capability of valve mechanism.Test and normally and under limit mechanical gap width carrying out.Normal condition is, carries out the velocity scanning of 1000-7500rpm, each engine speed record 30 valve handover events.Dynamic data reprocessing allows to calculate valve closing velocity and valve bounce-back.Resistance strain gauge instruction attached on the interior outer arm of SRFF, is enough to the separation prevented between " pump is got " of valve mechanism parts or HLA in the load of all engine speed lower shake-changing arms.When HLA compensation valve bounce-back or valve mechanism deviation are to cause valve to stay open on camshaft basic circle, generation got by this pump.Minimum, maximum and average closing velocity is illustrated the distribution understanding whole engine speed range.High lift closing velocity illustrates in Figure 67.The closing velocity of high lift meets design object.The scope of value changes with about 250mm/s between a minimum and a maximum under 7500rpm, and safety remains within target simultaneously.

Figure 69 illustrates the closing velocity of low lift cams spindle-type line.Occur within normally operating in 3500rpm, wherein closing velocity remains on below 200mm/s, and for low lift, it is in design margin safely.In the hypervelocity condition that low lift mode system is 5000rpm, wherein maximum closing velocity is lower than the limit.Valve closing velocity design object meets high lift pattern and low both lift modes.

Critical conversion

Critical conversion testing is undertaken by latch pin being remained on the transition point engaged with outer arm shown in Figure 27.Latch portion ground engages outer arm, and this illustrates that outer arm is thrown off from latch pin with the opportunity of the moment causing outer arm to control loss.The bearing impact low lift cams crown of roll angle of inner arm.The tested some of SRFF, this quantity is considerably beyond the quantity of critical conversion, and described critical conversion is the working life to show SRFF robustness expected in vehicle.The critical conversion testing assessment wearing and tearing of locking mechanism during clear-latch and the bearing durability had an impact from critical switching.

Critical conversion testing use is similar to vehicularized motor shown in Figure 63 and carries out.Slack adjuster control channel adjustment critical pressure.Motor runs under constant speed and pressure changes around critical pressure with the retardation phenomenon of coupled system.Critical conversion is defined as the valve being greater than 1.0mm and declines.Typical SRFF valve falling head distribution is shown in Figure 70.It should be noted that more than 1000 subcritical conversions to occur lower than 1.0mm, this list display but be not counted in test and complete.Figure 71 shows the distribution of critical photograph for camshaft angle.Exceed top lift largest cumulative to produce immediately, remaining is uniformly distributed substantially.

Locking mechanism and bearing are in the monitored wearing and tearing of whole test.The typical wear (Figure 73) of outer arm compares with new parts (Figure 72).Critically to convert once required, check the operation that rocking arm is correct and test terminates.Shown edge abrasion has no significant effect kayser function, and total mechanical clearance such as most of breech lock frame shows negligible wearing and tearing.

Subtense angle

The specific function of subsystem testing assessment SRFF rocking arm and wear interface.Switch function in the life expectancy of whole SRFF of durability evaluating locking mechanism and wearing and tearing.Similarly, idling speed durability makes bearing and slide block stand the condition of the worst condition comprising low lubrication and 130 DEG C of oil temperatures.Torque spring durability test has circulated by making torque spring stand about 2,500 ten thousand times.In whole test, torque spring load is measured to measure degeneration.Further conformity does not exceed the design maximum load loss acquisition of 15% to 100,000,000 circulations by extension test.Figure 74 show test start and at the end of outer arm on torque spring load.100,000,000 times circulation after, there is little load loss of about 5%-10%, its lower than 15% accepted target and show the enough load of outer arm to four engine lives.

The system aging accelerated

The system aging test accelerated is the comprehensive durability test as duration performance benchmark.Test represents the cumulative damage of extreme terminal use.The average approximately 5000rpm of test loop, and there is constant speed and accelerate molded line.The time of each circulation terminates as follows: 28% steady state, and circulate between 15% low lift and high and low lift, all the other under acceleration conditions.The result display of test, in the test intermediate gap of a life cycle, change accounts for 21% of the wearing and tearing specification of rocking arm.The system aging test accelerated comprises 8 SRFF, expands past standard life to determine the wear pattern of SRFF.Once through standard sustained period, the total mechanical clearance measurement of every 100 test loop records.

The result that the system aging accelerated is measured shows in Figure 75, and display wearing and tearing specification exceeds 3.6 times of life-spans.Test continues and completes six life time and do not lose efficacy.Extend testing illustrates the linear change through initial damages after date mechanical clearance to multiple life-span.The dynamic performance of system is degenerated due to the total mechanical clearance increased, but functional performance is still complete in six engine lives.

5.2.5 durability test result

Carry out each test of discussing in test plan and provide result summary.The result of dynamic, the critical conversion durability of valve mechanism, torque spring durability and final acceleration system aging test is illustrated.

Accelerated ageing test is stood to prove robustness and to be illustrated schematically in table 3 in conjunction with specific function test SRFF.

Table 3: durability is summarized

Durability amounts to according to engine life and equals 200000 miles of assessments, and it provides and exceedes required 150000 miles of rich surpluses required.The object of project proves at least one engine life of all tests display.Main durability test is the system aging test accelerated, and it represents the durability of at least six engine lives or 1,200,000 miles.This test is also carried out together with the fluid used, and the robustness of an engine life is shown.Crucial operating mode is switchover operation between high and low lift.Switch durability test and show at least three times of engine lives or 600,000 miles.Similarly, torque spring is sane at least four times of engine lives or 800,000 miles.Other test show needles are at least one engine life of critical conversion, hypervelocity, cold starting, bearing robustness and dry run condition.DLC coating is sane for all conditions, and it illustrates the minimal wear of polishing, as shown in Figure 76.As a result, a large amount of test display SRFF robustness is good, exceeds 200000 miles of working lifes.

5.2.6 durability test conclusion

The DVVL system comprising SRFF, DFHLA and OCV demonstrates robustness at least 20000 miles, and 200000 miles exceed 150000 miles of safe clearances required.Durability test display is aging to the acceleration system of at least six times of engine lives or 1,200,000 miles.This SRFF is to use fluid and to add that gas and oil shows equally be sane.The switching function of SRFF is sane at least 3 times of engine lives or 600000 miles of displays.All subsystem testing display SRFF exceed an engine life of 200000 miles steadily.

Critical conversion testing demonstrates the robustness to 5000 events or at least one engine life.Under this condition produces oil pressure conditions beyond normal operation range, and the harsh event caused as outer arm landing breech lock thus SRFF forwards inner arm to.Even if condition is harsh, the condition display of SRFF to such type is sane.This event can not occur in bulk article.Test result display SRFF is sane to these conditions when critical conversion produces.

SRFF reaches 7300rpm and burst speed condition to engine speed and proves sane to the passenger car applications of 7500rpm.Igniter motor test has consistent abrasion condition with the Engine Block Test that misfires described in this chapter.It is sane that DLC coating on outer arm slide block shows through whole service condition.Therefore, SRFF design is applicable to four-cylinder passenger car applications, and object reduces motor pumping loss raising fuel economy under running at partial load motor.This technology can extend to other application comprising six cylinder engine.It is sane that SRFF shows under the certain situation far exceeding automotive needs.Diesel engine application can consider other improvement with process increase engine loading, oil contamination and engine life requirement.

5.3 slide blocks/DLC coating abrasion

5.3.1 wear testing plan

This part describes the test plan of the durability for studying DLC coating on wear characteristic and outer arm slide block.Target is the relation set up between design code and process parameter and the durability how affecting slide block interface separately.Three key factors in this slide block interface are: camshaft lobe, slide block and valve mechanism load.Each element has needs to be included in factor in test plan to determine the impact on DLC Coating Durability.Being described in detail as follows of each assembly:

The width at camshaft-regulation high-lift cam crown of roll angle is to ensure to remain in camshaft lobe at motor run duration slide block.This comprises and increases by heat the axial position that causes and change or change due to the size manufactured.As a result, whole width of slide block can contact camshaft lobe and not have camshaft lobe to become to depart from the risk of slide block.The shape (molded line) being applicable to the salient angle of valve lift characteristics is also based upon in the improvement of camshaft and SRFF.This makes to need to consider about two factors of DLC Coating Durability: first is salient angle material, and second is the surface finishment of camshaft lobe.Test plan is included in salient angle with different surface conditions test cast iron and steel camshaft lobe.First comprises the camshaft lobe prepared by grinding action (grinding).Second is the surface finishment condition (polishing) improving salient angle after polishing operation.

Slide block-slide block molded line is designed to valve lift and the dynamic particular requirement of valve mechanism.Figure 77 be SRFF top slide block and contact high lift lobe between the diagram of contact relation.Owing to expecting the change manufactured, there is angular alignment relation in this contact surface, it is shown in Figure 77 with the schedule of proportion amplified.Consider various aligned condition, crown surface reduces the risk that edge loads slide block.But crown surface adds the complexity of manufacture, therefore the impact of crown surface on coating interface performance is added in test plan to determine its necessity.

Figure 77 show on camshaft surface titled with as method for selecting.Based on expecting that the hertz stress that load and hat change calculates the guidance be used in test plan.Between two blocks (comprising angle), the tolerance needs of alignment are attached to the change regulation expecting hat.The required output of test is how actual understanding changes the slide block alignment angles affecting DLC coating.Stress calculation is used to provide 0.2 degree of out-of-alignment desired value.These calculate for reference only point.Test plan adopts three values, and these values comprise the angle between slide block: < 0.05 degree, 0.2 degree, 0.4 degree.The parts of angle below 0.05 degree think that the flat and parts of 0.4 degree represent the twice of calculating reference point.

The second factor on the slide block of assessment is needed to be the surface finishment of slide block before DLC coating.The process step of slide block comprises the grinding action of formation slide block molded line and the polishing step for DLC coating formation surface.The final surface finishment of the slide block of each step impact before application DLC coating.Test plan is introduced the contribution of each step and is provided result with the final specification of the surface finishment after setting up for the process specification of grinding and polishing step.Test plan adopts as the surface finishment after grinding and polishing.

Valve mechanism load-last factor is the load of the slide block run by valve mechanism.Calculate to provide and a kind ofly change the mode that valve mechanism loads to stress levels.The durability of camshaft lobe and DLC coating is based on each stress levels stood before failure.Camshaft lobe material should be defined in the scope of 800-100MPa (moving contact stress).This scope considers standard design pressure.In order to accelerated test, the stress levels in test plan is set in 900-1000MPa and 1125-1250MPa.These values represent the standard design stress of upper half part and the standard design stress of 125% respectively.

Test plan comprises six factors to prove the durability of DLC coating on slide block: (1) camshaft lobe material, (2) shape of camshaft lobe, (3) surface condition of camshaft lobe, (4) angular alignment of slide block and camshaft lobe, the surface finishment of (5) slide block and (6) are applied to stress on coating slide block by opening valve.The element emphasized in this part and the overview of factor illustrate in Table 1.

Table 1: test plan element and factor

5.3.2 component wear test result

The target of test determines the Relative Contribution of each factor to the durability of slide block DLC coating.The major component of test configuration comprises minimizing of two factors in test plan.Slide block 752 shown in Figure 78 is connected to the rocker arm support 753 on test sample 751.All configurations all test the relevant comparative allowing each factor under two stress levels.The scope of beginning assay intervals of testing be 20-50 hour and in needs long-time observation result time be increased to 300-500 h apart.When sample exists DLC coating loss or suspends test when camshaft lobe surface has significant change.Test under pressure rating is higher than the impact of applying the accelerator required.As a result, the assessment of described engine life is conservative estimation and dependent interaction for proving Testing factors.Sample completes a life-span and is described to enough on test bench.Sample exceeds three life-spans and does not have DLC loss to think perfectly.Test result is divided into two-part so that discuss.The result of cast iron cam shaft is discussed by first portion, and second checks the result from steel camshaft.

The test result of cast iron cam shaft

First test uses cast iron cam shaft salient angle and contrasts shoe surface degree of finish and two angular alignment configurations.Result is presented in table 2 below.This table outlines the combination comprising the slide block in conjunction with angle and surface condition using cast iron cam shaft test.Each be combined in design maximum and 125% design maximum loading condition under test.The value listed represents the engine life quantity that each combination of test period reaches.

Table 2: cast iron test list and result

All there is slabbing (peeling off) in the camshaft of test, this causes end of test.Great majority formed slabbing before half engine life.Slabbing is in more high load components and exist on design maximum load component more serious.Analyze the ability that display two kinds of loads exceed camshaft.Cast iron cam shaft salient angle often uses in the application together with the roller elements comprising similar load level; But at this sliding interface, described material is not applicable selection.

Enough inspection intervals are frequently to study the effect of surface finishment to the durability of coating.The sample of grinding skin degree of finish in testing very early stand DLC coating loss.Sample shown in Figure 79 A describes the typical sample of early stage DLC coating loss in testing.

Scanning electron microscope (SEM) analyzes the character of breaking of display DLC coating.Metal surface below DLC coating can not provide enough supports for coating.The metal that coating obviously combines than it is harder.Therefore, if parent metal is significantly out of shape, the possible result of DLC is broken.Sample performance polished is before coating good until camshaft lobe starts slabbing.Under design maximum load, carry out the best result of sample for cast iron cam shaft that is straight, polishing is 0.75 times of life-span.

The test result of steel camshaft

Next group test adopts steel salient angle camshaft.The overview of testing combination and the results are shown in table 3.Camshaft lobe is tested with four kinds of different configurations: (1) surface finishment is grinding and has flat salient angle, (2) surface finishment is grinding and has crown salient angle, (3) polishing and have minimum crown salient angle and (4) polishing and have the crown salient angle of nominal.Slide block on sample polishing and at three angle measurements before DLC coating: (angle is less than 0.05 degree) that (1) is flat, the angle of (2) 0.2 degree and the angle of (3) 0.4 degree.The load set of all camshafts is the design maximum level of design maximum or 125%.

Table 3: the test list of steel camshaft and result

Set has the test sample of the flat steel camshaft lobe of grinding and 0.4 degree of angle sample in 125% design (calculated) load level not more than a life-span.Sample test under maximum design pressure continues a life-span but there is same function in coating.The sample performance of 0.2 degree of peace is better but be no more than the twice life-span.

Then this test is carried out grinding, flat steel camshaft lobe and is comprised 0.2 degree of sample of angle and straight sample.Time requirement on observation 0.2 degree of sample before coating loss is 1.6 times of life-spans.Flat sample slightly reaches 1.8 times of life-spans working time.On flat sample, the pattern of DLC loss has uneven maximum loss on the outside of surface of contact.On outside surface of contact, the loss of coating shows that the stress applied by slide block is uneven on its width.This phenomenon is known as " edge action ".The solution reducing by two alignment element edge upper stresses an element increases crown profile wherein.Use in the application of SRFF on camshaft, add crown profile.

Next group test adopts crown minimum value in conjunction with 0.4,0.2 degree and flat polishing slide block.This setting confirms to increase the crown positive role to camshaft.In 125% maximum load, 0.4 degree of sample brings up to 1.3 times of life-spans from 0.75.Equally loaded flat parts are existed and brings up to 2.2 times of life-span less improvement from 1.8.

Last test group comprises the sample of all three angles and is processed with the polished steel camshaft lobe of the crown value of standard.In these results most marked difference be camshaft hat and slide block to camshaft lobe angular alignment between interaction.Flat with 0.2 degree of sample under two load level more than three times of life-spans.0.4 degree of sample does not exceed the twice life-span.Figure 79 B shows the typical case with the sample that 0.2 degree of angle is tested under design maximum load.

These results confirm as follows: it is effective that the reference value of (1) cam hat reaches 0.2 degree time flat in the angular alignment of minimizing slide block; (2) will be stable under the design maximum load of application and 125% design maximum load, (3), when in conjunction with slide block polishing and camshaft lobe hat, the durability of polishing camshaft lobe to DLC coating contributes.

Each test result contributes to understanding stress better to be affected in the durability of DLC coating.Result is shown in Figure 80.

Use the early stage test of cast iron cam shaft salient angle in the sliding interface under design (calculated) load, do not exceed the engine life of half.Next improvement produces in the form identifying " edge action ".Increase crown to polishing camshaft lobe, there is the better acceptable angular alignment understood, improve Coating Durability more than three times of life-spans.Result proves the design margin between the test result observed and the design maximum stress used in each engine life estimated.

Surface finishment is reported at most in from grinding coating sample to the transition of polishing coating sample on the impact of DLC Coating Durability.As shown in Figure 81, the test of slide block grinding coating is no more than 1/3rd engine lives.The improvement of the surface finishment of slide block provides the better load bearing ability of the substrate below coating and improves the whole durability of coating slide block.

The result come from cast iron and the test of steel camshaft provides following: (1) slide block is to the specification of the angular alignment of camshaft, (2) clear evidence is that angular alignment specification and camshaft lobe are preced with consistent, (3) when exceeding design maximum load, in the specification of aiming at design for camshaft lobe hat and slide block, the maintenance of DLC coating is complete, (4) after slide block grinding, polishing operation is needed, (5) for the process specification of grinding action, (6) specification of the surface finishment of the front-slider of coating and the polishing operation of (7) steel camshaft lobe contribute to the durability of DLC coating on slide block.

5.4 slide block manufactures improve

5.4.1 slide block manufacture improves explanation

Outer arm uses machining foundry goods.For the surface finishment before the Angulation changes of slide block and coating, there is set target from the mach prototype part of strand raw material.The improvement of product grinding and glossing produces test simultaneously, and describes in Figure 82.The improvement of test result to the manufacturing process of outer arm slide block provides feedback and guides.Parameter in technique adjusts based on the result of testing and new machining sample is assessed subsequently on test fixture.

This section describes slide block from sample to the manufacturing process process of SRFL outer arm.

First step development grinding process is to assess different machines.Test run is based upon in three different grinding machine.Each machine uses identical ceramic cubic boron nitride (CBN) emery wheel and emery wheel.Select CBN emery wheel to be because it can improve the conformity of parts to parts for (1), (2) in the application requiring slight errors, improve accuracy and (3) raise the efficiency by producing more fragments between emery wheel circulation compared to aluminium oxide.Each machine uses identical feed rate grinding one group of sample and often through once removing the material of identical amount.Fixture is set and allows the grinding of test continuous print.Sample is tested, because sample polishing and testing wearing on rig.The method is by keeping providing the mode of justice to assess lapping machine as the parameter that fixture, emery wheel and emery wheel are constant.

Measure after often organizing sample collection.The angular measurement of slide block uses LeitzPPM654 coordinatometer (CMM) to obtain.Surface finish measurement carries out on MahrLD120 profilograph.Figure 83 illustrates that slider angles controls the result relative to lapping machine equipment.Result more than line is noticeable generation coating performance degeneration part.The parts of this angle of target area display test do not have difference in life test.Target is not met for two lapping machines for the angle at sample top slide block.Very good by contrasting the 3rd performance.The test result come by wearing rig confirms that sliding interface is responsive to the angle more than this target.Be combined in the lapping machine test of leading portion discussion and test the selection contributing to manufacturing equipment.

The measurement result of Figure 84 general introduction surface finishment of same sample when angle data are as shown in Figure 83.Specification for the surface finishment of slide block is set up with these results of testing.Surface finish display more than restraining line reduces durability.

Two identical lapping machines (A and B) do not meet surface finishment target yet.The target of surface finishment is formulated based on parts net change of surface finishment in glossing of given type.From grinding process as the sample exceptional value, after glossing, remain exceptional value.Therefore, in grinding action, control surface degree of finish is very important, can produce the slide block of satisfied final surface finishment after polishing before coating.

Each machine is looked back and measures.In angle measurement, lapping machine A and B has change with the form of each pad.The emery wheel vertically movement when its grinding slide block of result hint.In this types of mills, vertical emery wheel moves the whole rigidity relating to machine.Machine stiffness also can affect the surface finishment of grinding parts.The specification that the rigidity that the slide block of grinding outer arm identifies to the lapping machine C required by test fixture confirms.

This empirical learning has arrived the outer arm that grinding sample uses the fixture grinding SRFF improved.But outer arm has visibly different challenge.It is rigidity that outer arm is designed on the direction that activated by camshaft lobe at it.Outer arm does not have this rigidity on slide block width direction.

Clamp needs (1) to control each slide block and not bias voltage, and each slide block of (2) rigid support is to resist the power that applied by grinding and (3) reliably repeat this process in production in enormous quantities.

The improvement of outer arm fixture is from hand-operated clamping BOB(beginning of block).Each correction of fixture is attempted remove bias voltage from damping mechanism and reduce the change of grinding skin.Figure 85 describes the result that jig Design is improved, and it keeps outer arm during slide block grinding action.

By the surface finish quality being improved to crucial SRFF outer arm slide block specification of test plan group with form tolerance settings border in angle.Research grinding action surface finishment is on the impact of final surface finishment after producing polishing and for middle IWS International Workman Standard constituting criterion.These parameters are improved for building equipment and member gripper to ensure to guarantee coating performance when high yield.

5.4.2 slide block manufacture improves

Conclusion

DLC coating structure on SRFF slide block, in the DVVL system comprising DFHLA and OCV parts, which show the good robustness and durability that exceed car life requirements.Although DLC coating is for multi industries, be limited to the product in automobile air valve mechanism market.This work identification and quantize the manufacture process of the effect of surface finishing before DLC coatings applications, the stress level of DLC and slide block.The display of this technology is suitable and satisfied to the continuous manufacture of SRFF slide block.

In whole life test, surface finishment is crucial to maintenance DLC coating on slide block.Test result display produces early failue when surface finishment is too coarse.Emphasize the situation far exceeding life cycle test requirements surface finish level herein.The method keeps DLC complete on the top of the Ni-based layer of chromium, thus SRFF parent metal can not expose contact camshaft lobe material.

Stress level on DLC slide block is identified equally and proves.The needs to shoe edge Angle ambiguity are emphasized in test.Illustrate due to manufacturing tolerances be increased to camshaft lobe crown give edge load effect increase a large amount of robustnesss.Setting is used for the specification of Angle ambiguity and is presented at and exceeds in life-span life requirement test result.

Also find that the material of camshaft lobe is important factor at sliding interface.Packing instructions based on DVVL system SRFF are needed robustness to tackle to reach to the sliding contact stress of 1000MPa.Tackle these stress levels, need high-quality Steel material to split to avoid the camshaft lobe endangering the sliding interface life-span.Find that there is steel camshaft material, final system that is crown and polishing exceeds life-span life requirement.

The technique of producing slide block and DLC in a large amount of manufacturing process is described.Crucial manufacture improves the fixture concentrating on equipment for grinding selection and Grinding wheel and the maintenance SRFF outer arm for the manufacture of slide block grinding process.The manufacturing process selected selects display robustness to meet the specification of the guarantee durability sliding interface of engine life.

DLC coating on slide block demonstrates and exceeds life requirements, and it is consistent with the result of system DVVL.DLC coating on outer arm slide block demonstrates robustness through operating conditions.As a result, SRFF design is applicable to four cylinder passenger car applications, object gets loss raising fuel economy by reducing engine pump under the operation of partial load motor.The DLC coating sliding interface of DVVL demonstrates durability and VVA technology is used in the application of different engine valve.

II. single salient angle cylinder deactivation system (CDA-1L) system embodiment explanation

1.CDA-1L SYSTEM SUMMARY

CDA-1L (Figure 88) is that compact actuated by cams formula list salient angle cylinder deactivation (CDA-1L) switches rocking arm 1100, and it to be arranged on piston driven internal combustion machine and to combine two supply hydraulic lash adjuster (DFHLA) 110 and fluid control valve (OCV) 822 activated.

With reference to Figure 11,88,89 and 100, CDA-1L arrange and comprise four critical pieces: fluid control valve (OCV) 822, two supply hydraulic lash adjuster (DFHLA), CDA switch rocker arm assembly (being also called SRFF-1L) 1100, single salient angle cam 1320.Acquiescence configuration is normal lift (kayser) position, and in this position, the inner arm 1108 of CDA-1L rocking arm 1100, together with outer arm 1102 kayser, causes engine valve to be opened and allows cylinder to run as standard valve mechanism.DFHLA110 has two fluid mouths.Lower fluid mouth 512 provides backlash compensation, and with standard HLA supply engine fluid similarly.Upper fluid mouth 506 is called switching pressure port, and it provides passage between from the breech lock 1202 in the controlled oil pressure of OCV822 and SRFF-1L.As indication, when breech lock engages, in SRFF-1L1100, inner arm 1108 opens engine valve with the same the operation together of the accurate rocking arm of outer arm 1102 image scale.Without lift (non-kayser) position, inner arm 1108 and outer arm 1102 independently can move to make cylinder deactivation.

As shown in Figure 88 and 99, comprise a pair idle running torque spring 1124 with the position of bias voltage inner arm 1108, thus this inner arm keeps continuous contact camshaft lobe 1320 always.Idle running torque spring 1124 requires than the preload using the design of multiple salient angle higher to promote the continuous contact between camshaft lobe 1320 and inner arm roller bearing 1116.

Figure 89 illustrates in SRFF-1L1100 inner arm 1108 and outer arm 1102 detailed drawing along breech lock 1202 mechanism and roller bearing 1116.The function of SRFF-1L1100 design keeps similar packaging, and reduces the complexity of camshaft 1300 compared to the configuration with more than one salient angle, and such as, the separation for each SRFF position can be removed without lift lobe.

As shown in Figure 91, complete CDA system 1400 for a cylinder comprises an OCV822, two SRFF-1L rocking arms 1100 are for exhaust, two SRFF-1L rocking arms 1100 for air inlet, for each SRFF-1L1110 a DFHLA110 and drive single salient angle camshaft 1300 of each SRFF-1L1100.In addition, CDA1400 system is designed to make SRFF-1L1100 and DFHLA110 be identical for air inlet and exhaust.It is this that to arrange in four the SRFF-1L rocker arm assemblies 1100 allowing single OCV822 simultaneously to switch needed for cylinder deactivation each.Finally, system by from ECU825 Electronic control so that OCV822 normal lift mode and without lift mode between switch.

The engine arrangement of SRFF-1L1100 is used to show in Figure 90 A and 90B for an exhaust and an intake valve.The packaging group of SRFF-1L1100 is similar to the packaging of standard valve mechanism.Cylinder head needs to change to provide the supply of fluid from lower channel 805 to OCV822 (Figure 88,91).In addition, second (on) oil passage 802 needs the switching port 506 connecting OCV822 and DFHLA110.Base engine cylinder cap framework keeps identical, thus valve center line, camshaft centerline and DRHLA110 center line keep constant.Because these three center lines are kept relative to standard valve mechanism, and due to SRFF-1L1110 keep compact, cylinder head height, length and width almost do not change compared to standard valvetrain system.

2.CDA-1L system enabling tool

Some technology used within the system have for the multiple application in different application, and they are described as the parts of DVVL system disclosed herein at this.They comprise:

2.1 fluid control valves (OCV)

As what describe in part above, and as Figure 88,91, shown in 92 and 93, fluid control valve (OCV) 822 be guide or not direct pressurized hydraulic fluid with cause rocking arm 100 normal lift mode and without lift mode between the control gear that switches.OCV by intelligent control, such as, uses the control signal sent by ECU825.

2.2 pairs of supplies hydraulic lash adjuster (DFHLA)

There is many hydraulic lash controlling devices for maintaining motor intermediate gap.Rocking arm 100 (Fig. 4) is switched for DVVL, conventional gap is needed to control, but traditional HLA device deficiency is thought to switch provides required fluid demand, it needs to stand associated side load that run duration applies by assembly 100 and is applicable to restricted packaging space.Describe a kind of compact two supplies hydraulic lash adjuster 110 (DFHLA) used together with switching rocking arm 100, it has one group and optimizes the parameter of oil flow pressure and shape for providing with low consumption, and one group for managing parameter and the shape of side loads.

As shown in Figure 10, ball plunger end 601 is assemblied in ball seat 502, directively to allow rotates freely.This allows the side of the ball plunger end 601 in some operator scheme and may asymmetric load, on the contrary such as when switching from high lift to low lift or.Contrary with the typical pommel plunger for HLA device, DFHLA110 ball plunger end 601 uses thinner material construction to resist side loads, figure 11 illustrates plunger thickness 510.

The material selected for ball plunger end 601 can also have higher allows kinetic stress load, such as chrome alum alloy.

In DFHLA110, hydraulic flow path design is for high-pressure flow and low drops, to guarantee that constant hydraulic pressure switches and reduces pumping loss.DFHLA is arranged in the in-engine cylinder containing seat be dimensioned to relative to outer surface 511 sealing, as shown in Figure 11.Cylinder containing seat is combined to be formed the closed fluid path with particular cross section region with the first oil flow channel 504.

As shown in Figure 11, preferred implementation comprises four oily head pieces 506 (only illustrating two), and they are arranged with the substrate of equidistant mode around the first oil flow channel 504.In addition, two the second oil flow channels 508 are arranged around ball plunger end 601 in equidistant mode, and are communicated with the first oil flow channel 504 by fluid mouth 506 fluid.Fluid mouth 506 and the first oil flow channel 504 are with location dimensional fits and separate around DFHLA110 body, to guarantee from the first oil flow channel 504 to the three oil flow channel 509 fluid Uniform Flow and pressure drop is minimum.3rd oil flow channel 509 be designed and sized to the oil stream of combining from multiple second oil flow channel 508.

2.3 detect and measure

Use that the information of sensor collection may be used for verification switch mode, identification error conditioned disjunction provides information analysis and for switch logic and timing.Can find out, detection and the measurement mode of execution of previously described applicable DVVL system can also be applied to CDA-1L system.Therefore, the valve position used in DVVL and/or motion detect and logic also can be used in CDA system.Similarly, for DVVL system, detection in the determination of position/action of being used in rocking arm or rocking arm relative position/action relative to each other and logic also may be used in CDA system.

2.4 torque spring design and implementations

Sane torque spring 1124 design provides the moment larger than the design of routine known rocking arm, keeps high reliability simultaneously, the operation that this design makes CDA-1L system can run through all dynamic operationals to keep appropriate.Describe in the Design and manufacture of torque spring 1124 paragraph below.

3. switching controls and logic

3.1 motors are implemented

CDA-1L mode of execution can comprise any amount of cylinder, such as 4 and 6 single-row cylinder arrangements and 6 or 8 cylinder in V-arrangements.

The hydraulic fluid transporting system of 3.2 to rocker arm assembly

As shown in Figure 91, hydraulic fluid system switches rocking arm 1100 with controlled pressure conveying motor fluid to CDA-1L.In this is arranged, be fed into DFHLA110 without pressure controlled motor fluid by lower oil passage 805 from cylinder head 801.This fluid is always communicated with end opening 512 fluid of DFHLA110, is used for carrying out the adjustment of conventional hydraulic gap at this place.Oil control valve 822 is also supplied to without pressure controlled motor fluid from cylinder head 801.From OCV822 and the hydraulic fluid be supplied under controlled pressure is supplied to oil passage 802.The lift mode of each CDA-1L rocking arm 1100 assembly is determined in the switching of OCV822, and this assembly comprises the CDA cylinder deactivation system 1400 for given cylinder.As described in following paragraph, the actuating of OCV valve 822 by control unit of engine 825 use based on the cylinder of the information-such as some special physical configuration, switch window and sequence of maneuvers condition being detected and stores and specific oil temperature-logic carry out.Be introduced into DFHLA110 suitable for reading 506 from the pressure regulator solution hydraulic fluid of upper channel 802, at this place, it is passed to switching rocker arm assembly 1100.Hydraulic fluid is communicated to latch pin 1202 assembly through rocker arm assembly 1100, is used to start normal lift and without the switching between lift condition at this fluid of this place.

In upper channel 802, remove accumulation air keeps hydraulic pressure rigidity and minimized vibrations to be important in the pressure increase period.The pressure increase period directly affect handover operation during breech lock traveling time.Passive bleeding point 832 shown in Figure 91 is added to the high point in upper channel 802, to be entered by the air venting of accumulation in the cylinder head air space below valve cap.

3.2.1 the hydraulic fluid for normal lift mode is carried

Figure 92 A-92B illustrates that SRFF-1L1100's does not wherein have electrical signal to the default location of OCV822, the following system of enable operation and the cross section of parts: OCV822 in normal lift mode are also shown, DFHLA110, late spring 1204, breech lock 1202, outer arm 1102, cam 1302, roller bearing 1116, inner arm 1108, valve pad 1140 and engine valve 112.Unadjusted engine oil hydraulic fluid in lower channel 805 be communicated with DFHLA110 backlash compensation (under) mouth 512 be can carry out standard clearance compensation.OCV822 is adjusted to the oil pressure of oil passage 802, and on this, oil passage supplies fluid to suitable for reading 506 when not having ECU825 electrical signal with 0.2-0.4 bar subsequently.This force value is lower than needing compression latch spring 1204 with the pressure of mobile latch pin 1202.This force value is full of fluid for keeping fluid loop and does not have air, so that the system responses needed for realizing.Cam 1320 salient angle contact roller bearing, makes outer arm 1102 around DFHLA110 ball base rotary to open and close valve.When breech lock 1202 is engaged, SRFF-1L function class is similar to standard RFF rocker arm assembly.

3.2.2 carry for the hydraulic fluid without lift mode

Figure 93 A, B and C illustrate the detailed drawing of SRFF-1L1100 in cylinder deactivation (without lift mode) period.Control unit of engine (ECU) 825 (Figure 91) provide a signal to OCV822 thus oil pressure be supplied to breech lock 1202 cause its retract, as shown in Figure 93 B.The pressure of breech lock of needing to retract completely is 2 bar or higher.Torque spring 1124 (Figure 88,99) preload higher in this single salient angle CDA mode of execution makes camshaft lobe 1320 can work as when it occurs in empty moving and keeps in touch inner arm 1108 roller bearing 1116, and engine valve keeps closing as shown in Figure 93 C.

3.3 Operational Limits

The key factor running CDA system 1400 (Figure 91) is normal lift mode and without the reliable control switched before lift mode.CDA valve actuation system 1400 only can be switched between modes in scheduled time window.As mentioned above, low lift mode and inverse operation is switched to by starting from the signal of the control unit of engine (ECU) 825 (Figure 91) using logic from high lift pattern, the information that this logical analysis stores, such as the switch window of specific physical configuration, the operating conditions of storage and the processing data by sensor collection.Switch window duration is determined by CDA system physical configuration, and this physical configuration comprises the breech lock response time intrinsic in number of cylinders, the number of cylinders controlled by single OCV, valve lift duration, engine speed and hydraulic control and mechanical system.

3.3.1 data are collected

Real time sensor information comprises the input from any amount of sensor, such as, example CDA-1L system 1400 shown in Figure 91.As previously mentioned, sensor can comprise 1) valve stem displacement 829, linear variable differential transducer (LVDT) is used to measure in one embodiment, 2) action/position 828 and the position latching 827 of hall effect sensor or motion detector is used, 3) DFHLA of proximity switch, hall effect sensor or other devices is used to move 826,4) oil pressure 830 and 5) oil temperature 890.Camshaft rotation position and speed directly can be collected or derive from engine rotation speed sensor.

In the VVA system of hydraulic actuating, oil temperature impact is used for the rigidity of the hydraulic system switched in the system of such as CDA and VVL.If fluid is excessively cold, its viscosity slows down switching time, causing trouble.This temperature relation describes and is used for example CDA-1L switching rocking arm 1100 system 1400 in Figure 96.Oil temperature provides information accurately accurately, and this oil temperature adopts the sensor 890 shown in Figure 91 to obtain in one embodiment, and this sensor is positioned at and uses point neighbouring but not be positioned at motor fluid crankcase.In one embodiment, the oil temperature in CDA system 1400 is monitored near pressure control valve (OCV) 822, and this oil temperature must be more than or equal to 20 degrees Celsius and operate without lift (non-kayser) to start with the hydraulic pressure rigidity of needs.Measurement can adopt any amount of commercially available parts, such as thermocouple.Fluid control valve further describes in US2010/0018482 disclosed in 28, on January of U.S. Patent application US2010/008937 and 2010 disclosed in 15 days April in 2010, and these two sections of documents are incorporated herein by reference in this entirety.

Sensor information is as real time execution parameters input control unit of engine (ECU) 825.

3.4 information stored

3.4.1 switch window algorithm

SRFF require from normal lift to without lift (cylinder deactivation) on the contrary state and pattern switching.To guarantee that suitable motor runs during switching requires to occur in and is less than a cam axle.Pattern switching can occur over just when the basic circle 1322 (Figure 101) that SRFF is in cam 1320 is upper.Between valve lift state switch can not occur in when breech lock 1202 (Figure 93) be loaded and move be limited time.Breech lock 1202 must be controlled to prevent breech lock 1202 from sliding in the transition period completely and between part joint.The opportunity that the switch window recognition mode that the electromechanical latch response time intrinsic in CDA system 1400 (Figure 91) is combined switches.

Expectation function parameter based on the SRFF of CDA system 1400 is analogous to the V-type of producing now and switches roller lift device.Normal lift and without the mode switching set between lift for synchronous with camshaft 1300 rotational position during occurring in basic circle 1322 event.SRFF default location is set as normal lift.Also V-type CDA product systems are similar to according to the oil stream that SRFF controls.

Critical conversion is defined as the unexpected event may worked as and occur when latch portion engages, and it causes valve partly to promote or sharply rolls back valve seat down.When switching command is performed during the parameter and camshaft location synchronism switching of aforementioned oil temperature, engine speed, this situation is unlikely.Critical change event impacts load to DFHLA110, its may require the DFHLA of high strength-as previous section describe-using as enabled systems parts.

Basic synchronism switching for CDA system 1400 is described in Figure 94.Exhaust valve molded line 1450 and intake valve molded line 1452 are plotted as the function of camshaft angle.Required switch window is defined as the time sum of following action need: 1) OCV822 valve supply pressurization fluid, 2) hydraulic system pressure overcomes biasing spring 1204 and causes breech lock 1202 Mechanical Moving, and 3) on the contrary from without lift to normal lift and the breech lock 1202 that needs of patten transformation move completely.In this exhaust embodiment, switch window is opened once exc. just existence again until be vented beginning period 1454.Breech lock 1202 keeps being limited during exhaust lift event.The timing window of the critical conversion 1456 described in detail in the following paragraphs can be caused to be indicated in Figure 94.Switch window for air inlet can describe relative to air inlet lift profile in a similar manner.

Breech lock preload

CDA-1L rocking arm 1100 switching mechanism is designed to apply hydraulic pressure to breech lock 1202 after latch gap is absorbed, and causes function not change.This design parameter allows hydraulic pressure to be started in upper oil passage 822 by OCV822 during intake valve lift events.Once intake valve lift profile 1452 gets back to basic circle 1322 no-load condition, breech lock just completes it and moves to specific kayser or non-kayser pattern.This design parameter helps to maximize variable switch window.

Relative to the hydraulic response time of temperature

Figure 96 illustrates the dependence of breech lock 1202 response time to the oil temperature of use SAE5W-30 fluid.Breech lock 1202 response time reflection breech lock 1202 from normal lift (kayser) move to without lift (non-kayser) on the contrary position or endurance.At 20 DEG C of oil temperatures and 3 bar oil pressure breech lock 1202 response time requirement ten milliseconds in switching pressure port 506.At uniform pressure condition and Geng Gao running temperature such as 40 DEG C, the breech lock response time reduces to 5 milliseconds.The hydraulic response time is used for determining switch window.

Variable Valve Time

With reference to Figure 94 and 95, some camshaft drive systems are designed to have larger phase place authority/actuating range relative to camshaft angle than the drive system of standard.This technology can be described as Variable Valve Time, and when determining to consider together with engine speed when allowing the switch window endurance 1454.

Valve lift molded line indicates in Figure 95 with the figure that camshaft angle changes, and describes the impact of Variable Valve Time on the switch window endurance 1454.Exhaust valve lift molded line 1450 and intake valve lift profile 1452 show the typical recycling (also see Figure 94) not having and cause without the Variable Valve Time ability of switch window 1455, and exhaust valve lift molded line 1460 and intake valve lift profile 1462 display have the typical recycling of the Variable Valve Time ability caused without switch window 1464.The embodiment of this Variable Valve Time causes increasing without switch window 1458 endurance.Suppose that the Variable Valve Time ability of 120 crank angle continues between exhaust and admission cam shaft, then under 3500rpm engine speed, time remaining conversion 1458 is 6 milliseconds.

Figure 97 is the chart affecting variation switching time that display calculated and measured due to temperature and cam phase.This chart based on scope from 420 crank angle with minimum overlay 1468 camshaft phase to the switch window of 540 crank angle of camshaft phase with Maximum overlap 1466.For the normal engine running temperature of 40 DEG C-120 DEG C, the breech lock response time display of 5 milliseconds on the graph.From ECU825 switching signal start until hydraulic pressure be enough to cause breech lock 1202 move measure hydraulic response variation 1470.Based on using the CDA system 1400 of OCV hydraulic control oil pressure to study, about 10 milliseconds of maximum change.Oil pressure, temperature and the voltage to OCV822 in motor are considered in this hydraulic response change 1470.The phase position with minimum overlay 1468 provides the available switching time of 20 milliseconds under 3500rpm engine speed, and total breech lock response time is 15 milliseconds, represents and switches available time and the surplus of 5 milliseconds between breech lock 1202 response time.

Change switching time that is that Figure 98 illustrates calculating equally and the impact due to temperature and cam phase that is that measure.Illustrate based on scope from 420 crank angle with minimum overlay 1468 camshaft phase to the switch window of 540 crank angle with Maximum overlap 1466 camshaft phase.For the cold engine running temperature of 20 DEG C, the breech lock response time of 10 milliseconds is presented in this diagram.Hydraulic response change 1470 is started until hydraulic pressure enough causes breech lock 1202 moves and measure from ECU825 switching signal.Based on using the CDA system 1400 of OCV hydraulic control oil pressure to study, about 10 milliseconds of maximum change.Oil pressure, temperature and the voltage to OCV822 in motor are considered in this hydraulic response change 1470.The phase place with minimum overlay 1468 provides the available switching time of 20 milliseconds under 3500rpm engine speed, and total breech lock response time is 20 milliseconds, and this represents the design margin switching available time and reduce between breech lock 1202 response time.

3.4.2 the Operational Limits stored

These variablees comprise engine configurations parameter, such as, with expectation breech lock response time and the Variable Valve Time of running temperature change.

3.5 control logic

As implied above, CDA switches the little predetermined window time durations occurred over just under certain operating conditions, and outside timing window, switches CDA system may cause critical change event, and this can cause damaging to valve mechanism and/or other engine components.Because engine condition such as oil pressure, temperature, discharge and load may repeat change, high speed processor can be used to analyze real time status, by them compared with characterizing the known Operational Limits of work system, be in harmonious proportion result to determine when to switch, and send switching signal.These operations can hundreds of time or thousands of times of execution per second.In embodiments, this computing function can by application specific processor or by being called that the existing multipurpose automobile control system of control unit of engine (ECU) is carried out.Typical case ECU has for the input section of analog-and digital-data, the processing section comprising microprocessor, programmable storage, random access memory and output section, and this output section may comprise relay, switch and warning lamp and activate.

In one embodiment, the control unit of engine (ECU) 825 shown in Figure 91 receives input from multiple sensor, and such as valve stem displacement 829, action/position 828, position latching 827, DFHLA move 826, oil pressure 830 and oil temperature 890.The data of the running temperature such as allowed given engine speed and pressure, switch window store in memory.The information of real-time collecting contrasts with the information stored and analyzed to switch timing for ECU825 and control provides logic subsequently.

After input is analyzed, control signal is transferred to OCV822 with initialization handover operation by ECU825, and this operation regularly to avoid critical change event to meet engine performance target simultaneously, such as, can improve fuel economy and reduce discharge.If needed, ECU825 also reminds driver's erroneous condition.

4.CDA-1L rocker arm assembly

Figure 99 illustrates the perspective view of example CDA-1L rocking arm 1100.CDA-1L rocking arm 1100 only provides in an illustrative manner, is appreciated that the configuration of the CDA-1L rocking arm 1100 of the application's theme is not restricted to the configuration comprising CDA-1L rocking arm 1100 shown in the figure.

As shown in Figure 99 and 100, CDA-1L rocking arm 1100 comprises the outer arm 1102 with the first outer webs 1104 and the second outer webs 1106.Inner arm 1108 is placed between the first outer webs 1104 and the second outer webs 1106.Inner arm 1108 has the first inner webs 1110 and the second inner webs 1112.Inner arm 1108 and outer arm 1102 are both installed to the pivotal axis 1114 of the first end 1101 of contiguous rocking arm 1100, and inner arm 1108 is fixed to outer arm 1102 simultaneously also when rocking arm 1110 is rotating freely angle without allowing during lift condition around this pivotal axis 1114 pivotable by this pivotal axis.Except the mode of execution that shown having is installed to the independent pivotal axis 1114 of outer arm 1102 and inner arm 1108, pivotal axis 1114 can also be integrated into inner arm 1102 or outer arm 1108.

CDA-1L rocking arm 1100 has bearing 1190, this bearing is included in the roller 1116 be arranged between the first inner webs 1110 and the second inner webs 1112 in bearing shaft 1118, at rocking arm normal operation period, this roller is used for from the cam (not shown) conveying capacity rotated to rocking arm 1110.Bearing shaft 1118 is installed roller 1116 allows bearing 1190 to rotate around axle 1118, and this axle 118 is for reducing contacting by the cam rotated and roller 1116 friction produced.As described here, roller 1116 is rotatably fixed to inner arm 1108, and this inner arm then can rotate around pivotal axis 1114 relative to outer arm 1102 under certain condition.In said embodiment, bearing shaft 1118 is installed to inner arm 1108 and extends through the bearing axial trough 1126 of outer arm 1102 in the bearing axis hole 1260 of inner arm 1108.When using bearing shaft 1118, other configurations are also possible, and such as bearing shaft 1118 does not extend through bearing axial trough 1126 but is still arranged in the bearing axis hole 1260 of inner arm 1108.

When rocking arm 1110 is in without lift condition, when the lift part (in Figure 101 1324) of cam starts the roller 1116 of contact bearing 1190, inner arm 1108 relative to the downward pivotable of outer arm 1102, thus extrudes outer arm downwards.Axial trough 1126 allows bearing shaft 1118 and therefore inner arm 1108 and bearing 1190 move down.Along with cam continues to rotate, the lift part of cam leaves the roller 1116 of bearing 1190, thus because bearing shaft 1118 is by bearing shaft torque spring 1124 upwards bias voltage and allow bearing 1190 to move up.Shown bearing shaft spring 1124 is the torque springs being fixed to the bearing 1150 be positioned on outer arm 1102 by spring retainer 1130.Second end 1103 of the contiguous rocking arm 1100 of torque spring 1124 is fixed and has the spring arm 1127 contacted with bearing shaft 1118.When bearing shaft 1118 and spring arm 1127 move down, bearing shaft 1118 is slided along spring arm 1127.The pivotal axis 1114 of the first end 1101 of the fixing torque spring of second end 1103 with contiguous rocking arm 1100 of rocking arm 1100, contiguous rocking arm and the configuration of bearing shaft 1118 between pivotal axis 1114 and axle spring 1124 decrease the quality near the first end 1101 of rocking arm.

As shown in Figure 101 and 102, valve stem 1350 also contacts this rocking arm 1100 near the first end 1101 of rocking arm 1100, therefore the Mass lost quality of whole valve mechanism (not shown) that reduces of first end 1101 place of rocking arm 1100, thus decrease the required power of the speed that changes valve mechanism.It should be noted that other spring configuration can be used for bias voltage bearing shaft 1118, such as single continuous spring.

Figure 100 illustrates the decomposition view of CDA-1L rocking arm 1100 in Figure 99.The decomposition view of Figure 100 and the assembled view of Figure 99 illustrate bearing 1190, comprise the pin roll-type bearing of the substantial cylindrical roller 1116 be combined with pin 1200, and this bearing can be installed in bearing shaft 1118.Bearing 1190, for transmitting the spinning movement of cam to rocking arm 100, transmits action to valve stem 1350, such as, in configuration shown in Figure 101 and 102 then.As shown in Figure 99 and 100, bearing shaft 1118 can be arranged in the bearing axis hole 1260 of inner arm 1108.In this configuration, the axial trough 1126 of outer arm 1102 hold bearing shaft 1118 and allow bearing shaft 1118 to carry out lost motion and when rocking arm 1100 without during lift condition by extend inner arm 1108." idle running " motion not can think the motion of rotary motion to valve of transmitting cam of rocking arm.In said embodiment, dally and to be embodied relative to the pivot movement of outer arm 1102 around pivotal axis 1114 by inner arm 1108.

Except other settings of bearing 1190 also allow from cam transmission action to rocking arm 1100.Such as, the flat surperficial without spin (not shown) with the interface of camshaft lobe (in Figure 101 1320) can be arranged near the region of bearing 1190 shown in Figure 99 or one-body molded to inner arm 1108 at relative inner arm 1108 and rocking arm 1100.This surface without spin can comprise the friction pad be formed on surface without spin.In another embodiment, substituting bearing, such as, have the bearing of multiple concentric roller, may be used for effectively substituting bearing 1190.

With reference to Figure 99 and 100, resemble foot 1140 and be arranged on pivotal axis 1114 between the first and second inner webs 1110,1112.Pivotal axis 1114 is installed in interior pivot axis hole 1220 and outer pivot axis hole 1230 near the first end 1101 of rocking arm 1100.The lip 1240 be formed on inwall 1108 prevents resembling foot 1140 and rotates around pivotal axis 1114.Resemble the end that foot 1140 engages valve stem 1350, as shown in Figure 102.In an alternate embodiment, can remove and resemble foot 1140, instead, can be placed on pivotal axis 1114 with the interface surface of the termini-complementary of valve stem 1350.

Figure 101 and 102 illustrates that rocking arm 1100 is relative to the side view of cam 1300 and front elevation respectively, and this cam has lift lobe 1320, and this lift lobe has basic circle 1322 and lift part 1324.Roller 1116 is depicted as contact lift lobe 1320.Two supply hydraulic lash adjuster (DFHLA) 110 contacts this rocking arm 1100 near the second end 1103 of rocking arm, and applies to upward pressure rocking arm 1100, particularly outer rocker arm 1102, reduces valve clearance simultaneously.First end 1101 contact that valve stem 1350 closes on rocking arm 1100 resembles foot 1140.In normal lift condition, rocking arm 1100 promotes valve stem 1350 periodically downwards, and this is for opening corresponding valve (not shown).

4.1 torque spring

As mentioned below, rocking arm 1100 can stand slack adjuster 110 excessive pump without lift condition is got, and this is beginning due to excessive oil pressure, unsteady state condition or other reason.When the fluid that pressurizes is full of its inside, this can cause the increase of the effective length of slack adjuster 110.This situation may occur such as during engine cold starting, if not on inspection, needs the cost plenty of time self to solve, and even can cause permanent engine damage.In this case, breech lock 1202 can not actuator rocker arm 1100 until normal running length got back to by slack adjuster 110.In this case, slack adjuster applies upward pressure to outer arm 1102, makes outer arm 1102 near cam 1300.

Sky on SRFF-1L moves torque spring 1124 and is designed to provide enough power to keep roller bearing 1116 contacting camshaft lift lobe 1320 without lift run duration, guarantee that the controlled acceleration of inner arm sub-component and deceleration and inner arm 1108 are to controlled the returning of latched position, retain latch gap simultaneously thus.Pump situation of getting requires the additional force that stronger torque spring 1124 is got to compensate self-pumping.

The rectangular metal silk cross section of torque spring 1124, for reducing packaging space, keeps the low moment of inertia of assembly and provides enough depth of sections to support running load.Stress calculation described below and FEA, testing authentication are for developing torque spring 1124 parts.

The Design and manufacture technique of torque spring 1124 (Figure 99) is described, and this technique is formed has the compact design substantially rectangular wiry be made up of structural material that selecting.

With reference to Figure 30 A, 30B and 99, torque spring 1124 is constructed by the wire 397 of roughly trapezoidal shape.Wire 397 is allowed to be deformed into substantially rectangular when this trapezoidal shape is designed to apply power during coiling process.After torque spring 1124 is wound, the shape wiry formed can be described as being similar to first wire 396 with substantially rectangular cross section.Figure 99 illustrates two torque spring mode of executions, and it is shown as cross section is multi-coil 398,399.In a preferred embodiment, wire 396 has rectangular cross sectional shape, it have two elongate sides-this be expressed as vertical side 402,404, top 401 and bottom 403.The Mean length of sidepiece 402,404 of the coil of wire and the ratio of top 401 and bottom 403 can be less than 1 any value.It is large that this ratio makes the rigidity along coil of wire axis of bending 400 be greater than the spring coil rigidity reeled by the circular metal silk with the diameter equal with the Mean length of bottom 403 with the top 401 of the coil of wire 398.In substituting mode of execution, cross section metal filament shape has roughly trapezoidal shape, and it has larger top 401 and less bottom 403.

In this configuration, when the coil of wire is wound, the elongate sides 402 of each coil of wire against the elongate sides 402 of the previous coil of wire, thus makes torque spring 1124 keep stable.Shape and layout keep all coils of wire at vertical position, mutually cross or align when preventing them under stress.

When rocker arm assembly 1100 runs, substantially rectangular or trapezoidal torque spring 1124-when they bend around the axis 400 shown in Figure 30 A and 30B-produce high partial pressure, the tensile stress particularly on upper face 401.In order to meet life requirement, material is employed together with the combination of technology.Such as, torque spring can be made up of the material comprising chrome alum alloyed steel, improves intensity and durability together with this design system.Torque spring can cool by heating with fast with tempering spring.It reduce remainder stress.Impact the surface for the formation of the wire 396,397 of torque spring with projectile, or use " shot-peening processing " to process the residual stress in the surface of wire 396,397.Wire 396,397 is wound into torque spring 134,136 subsequently.Owing to being processed by shot-peening, the torque spring formed can bear larger tensile stress than the same spring not carrying out shot blast.

4.2 torque spring seats

As illustrated in graph 100, knob 1262 stretches out from the end of bearing shaft 1118 and forms groove 1264, and spring arm 1127 is placed in this groove 1264.In a replacement scheme, the spring fitting pin (not shown) that can use hollow bearing axle 1118 and be separated, this spring fitting pin comprise such as mounting spring arm 1127, the features of such as knob 1262 and groove 1264.

4.3 outer arm components

4.3.1 bolt lock mechanism describes

For optionally stopping the mechanism of rocking arm 1100 shown in Figure 100, this mechanism is visible near the second end 1103 of rocking arm 1100 in the illustrated embodiment, and this mechanism is shown as and comprises breech lock 1202, late spring 1204, spring retainer 1206 and clip 1208.It is inner that breech lock 1202 is configured to be arranged on outer arm 1102.Late spring 1204 to be placed in breech lock 1202 and by late spring retainer 1206 and clip 1208 in position.Once install, late spring 1204 is just towards the first end 1101 bias voltage breech lock 1202 of rocking arm 1100, thus latch enable 1202, particularly contact segment 1210 engage inner arm 1108, prevent inner arm 1108 from moving relative to outer arm 1102 thus.When breech lock 1202 engages inner arm by this way, rocking arm 1100 is in normal lift condition, and will from cam transmission action to valve stem.

In the rocking arm 1100 assembled, breech lock 1202 normal lift and without lift condition between alternately.When such as applying by mouth 1212 oil pressure being enough to the biasing force of offsetting late spring 1204, rocking arm 1100 can enter without lift condition, and this mouthful 1212 is configured to allow oil pressure to be applied to the surface of breech lock 1202.When applying oil pressure, the second end 1103 towards rocking arm 1100 promotes breech lock 1202, makes the breech lock 1202 engaged with inner arm 1108 regain thus and allows inner arm to rotate around pivotal axis 1114.In normal lift with without in both lift condition, the straight section 1250 of directed folder 1214 is in plat surface 1218 place engages receptacle 1202.Directed folder 1250 is arranged in folder hole 1216, therefore keeps the horizontal orientation of straight section 1250 relative to rocking arm 1100.The orientation of plat surface 1218 is also restricted to level by this, thus along suitable direction orientation breech lock 1202 to engage inner arm 1108 consistently.

4.3.2 latch pin design

As shown in Figure 93 A, B, C, the breech lock 1202 of SRFF-1L rocking arm 1100 is retracted in outer arm 1202 in without lift mode, simultaneously inner arm 1108 followup cam axle lift lobe 1320.Under certain condition, can cause the situation shown in Figure 103 from without lift mode to the transition of normal lift mode, breech lock 1202 stretched out before inner arm 1108 gets back to the position of breech lock 1202 normal engagement.

Features of rejoining adds SRFF to be stopped to prevent wherein inner arm 1108 and is trapped in the situation of the position of breech lock less than 1202.Optimize inner arm domatic 1474 and breech lock domatic 1472 with contact when inner arm 1108 breech lock domatic 1472 time provide the mild breech lock 1202 to retracted position to move.This design is avoided being changed the bolt lock mechanism caused by the pressure switching pressure port 506 (Figure 88) and is damaged.

As what describe in the previous paragraph relating to DVVL rocker arm assembly and operation, multiple breech lock embodiment can be applied to allow the reliable operation of bolt lock mechanism during operational condition, comprise and there is breech lock that is round or other nonplanar shape.

4.4 system packagings

SRFF-1F design concentrates on and minimizes the change of valve mechanism packaging compared to standardized product layout.Important design parameter comprises cam lobe relative to the relative displacement of SRFF ball bearing and axially aligning between steel camshaft and aluminium cylinder lid.Steel and aluminium parts have different thermal expansion coefficient, and described thermal expansion can relative to SRFF-1F switching cam crown of roll angle.

Figure 104 A and Figure 104 B shows single camshaft salient angle respectively relative to the proper alignment of SRFF-1L1100 outer arm 1102 and bearing 1116 and bad alignment.Proper alignment display camshaft lift lobe 1320 is in the centre of roller bearing 1116.Single camshaft salient angle 1320 and SRFF-1L1100 are designed to avoid the edge load 1428 on roller bearing 1116 and avoid camshaft lobe 1320 to contact 1480 outer arms 1102.In many salient angles CDA configuration, remove camshaft reduce the requirement that tight manufacturing tolerances, camshaft lobe width and position assembling are controlled without lift lobe, Camshaft Manufacturing Engineering is similar to be used in the technique of the standard cams axle on model II motor.

The hydraulic operation of 4.5CDA-1L bolt lock mechanism

As previously mentioned, it is term for describing this situation that pump is got, and in this situation, HLA exceedes the size of its expection work, thus anti-air-stop gate gets back to its seat during basic circle event.

The power of rolling and referring on follower assembly (RFF) 1496 is applied to during the below of Figure 105 illustrates Standard Gases door system and camshaft basic circle event.Hydraulic lash adjuster power 1494 is the combinations of hydraulic lash adjuster (HLA) 1493 power and the HLA inner spring power produced by oil pressure in backlash compensation mouth 1491.Cam reaction force 1490 is between camshaft 1320 and RFF bearing.Reaction force 1492 is between RFF1496 and valve 112 bar head.Must counteracting forces in case the anti-air-stop gate 112 of valve spring force 1492 be not intended to open.If the valve reaction force 1492 produced by HLA power 1492 and cam reaction force 1490 exceed the power of taking a seat of the valve 112 that needs to take a seat, so lifting stayed open at basic circle run duration valve 112, this is less desirable.The description of standard fixed arm system does not comprise dynamic operation load.

Design SRFF-1L1100 also considers that the pump when system is in without lift mode is got in addition.When SRFF-1L1100 is in without lift mode, the pump of DFHLA110 is got and wherein inner arm 1108 can be caused can not to get back to the situation that breech lock 1202 can be re-engaged the position of inner arm 1108.

When SRFF-1L1100 is in normal lift mode, SRFF-1L1100 is similar to standard RFF1496 (Figure 105) reaction.Keeping required latch gap to prevent pump from getting to switch SRFF-1L1100 simultaneously, except needing to make inner arm 1108 turn back to except the warping force of its kayser engagement positio, also solving to overcome HLA active force 1494 by applying additional force from torque spring 1124.

Figure 106 A-106B shows the equilibrium of forces be applied to when system is in without lift mode on SRFF-1L1100: produced by the oil pressure of backlash compensation mouth 512 (Figure 88) and add the DFHLA power 1499 of piston spring power 1498, cam reaction force 1490 and torque spring power 1495.The torsion 1495 produced by spring 1124 is converted to the reactive spring force 1500 acted on inner arm 1108 by bearing shaft 1118 and spring arm 1127.

Torque spring 1124 in SRFF-1L rocker arm assembly 1100 is designed to provide enough power, to keep roller bearing 1116 to contact camshaft lift lobe 1320 during without lift mode, guarantee acceleration and the deceleration of control inner arm 1108 sub-component thus and make inner arm 1108 return latched position, retaining latch gap 1205 simultaneously.The torque spring 1124 being used for SRFF-1L1100 design when system is in without lift mode designs the oil pressure change also considering backlash compensation mouth 512 place.Oil pressure regulates the load request that can reduce torque spring 1124, and this acts directly on spring sizes.

Figure 107 represents the requirement of oil pressure in backlash compensation pressure port 512.Only require when system is in without lift mode to limit oil pressure to SRFF-1L.Consider synchronism switching as previously described, to the temperature limiting lower than 20 DEG C without lift mode.

4.6CDA-1L pack clearance manages

Figure 108 A-108B illustrates the latch gap 1205 of SRFF-1L1100.For single salient angle CDA system, total mechanical clearance 1505 is reduced to single latch gap 1205 and is worth, and this is contrary with latch gap 1205 sum with the camshaft gap 1504 designed for the CDA with more than one salient angle.The distance between breech lock 1202 and inner arm 1108 to the latch gap 1205 of SRFF-1L1100.

Figure 109 compare be designed for three salient angle SRFF and single salient angle SRFF-1L camshaft on open slope (openingramp).

By eliminating camshaft gap for the design of single salient angle SRFF-1L.The elimination in camshaft gap 1504 allows to optimize camshaft lift profile further, and this optimization reduces 1510 by making lift slope and therefore allows the lift events more grown to carry out.The camshaft of SRFF-1L is opened slope 1506 and is opened slope 1506 relative to the camshaft used needed for the similar Design of many salient angles and reduce up to 36%.

In addition, mechanical clearance change on SRFF-1L improves 39% than similar three lobe design, this is the elimination due to camshaft gap and correlated characteristic, correlated characteristic is such as the manufacturing tolerances of camshaft without lift lobe Base radius, and the salient angle needed for slide block to slide block and slide block to roller bearing parallelism is deviate from.

4.7CDA-1L assembly is dynamic

4.7.1 describe in detail

SRFF-1L rocking arm 1100 and system 1400 (Figure 91) are designed to the dynamic stability requirement meeting whole engine operating range.SRFF rigidity and moment of inertia (MOI) is analyzed designs for SRFF.The MOI of SRFF-1L assembly 1100 measures around the pivotal axis 1114 (Figure 99) of the running shaft through the SRFF seat contacted with DFHLA110.Rigidity is measured in interface between cam 1320 and bearing 116.Figure 110 illustrates the curve of the rigidity of measurement relative to the assembly MOI calculated.Relation between the rigidity of SRFF-1L and MOI and contrasting for the carrying out of the standard RFF of the Type II motor of current production.

4.7.2 analyze

Perform design and finite element analysis (FEA) iteration for several times, to hold maximum strength at the DFHLA of SRFF and to reduce MOI.The DFHLA that quality stiffening element is placed in SRFF holds to minimize MOI.One of parts the heaviest in torque spring 1124-SRFF assembly-near SRFF running shaft location.Locking mechanism is also located near DFHLA.The vertical portion height increasing SRFF makes MOI minimize to increase intensity simultaneously.

SRFF design uses the load information optimization come from dynamic model.The key input parameter analyzed comprises valve mechanism layout, the quality of SRFF element, moment of inertia, rigidity (being estimated by FEA), mechanical clearance, valve spring load and speed, DFHLA shape and piston spring and valve lift molded line.Next, by changing system to meet predetermined dynamic object relative to the laterostigmatal effective mass optimal stiffness of CDASRFF.Laterostigmatal effective mass represents that MOI is relative to the pivotal point of SRFF and the ratio of square distance between valve and SRFF.The dynamic performance tested describes in the following paragraphs.

5. design verification and test

5.1 valve mechanism dynamic result

It is important that the dynamic performance of valve mechanism meets in Engine Durability and performance objective in control vibration noise (NoiseVibrationandHarshness, NVH) simultaneously.Valve mechanism dynamic part ground is affected by the rigidity of SRFF parts and MOI.The MOI of SRFF is calculated, and rigidity is estimated by COMPUTER AIDED ENGINEERING (CAE) technology.Dynamic valve event is also affected by multiple factor, obtains guarantee so carry out testing in controlling at high speed valve.

Monitoring engine testing apparatus is used to valve mechanism dynamics.Cylinder head is equipped before test.Fluid is heated to and represents real engine condition.From idling speed to 7500rpm, carry out sweep rate, record data are defined as engine speed.Dynamic performance is determined by assessment valve closing velocity and valve resilience.SRFF-1L strain contact object is monitoring load.Valve spring load keeps constant in make fixed system consistent.

Figure 111 describes the closing velocity of taking a seat as a result of intake valve.Need for eight continuous events with the data of display relative to minimum, the average and maximum speed of engine speed.Target velocity is shown as the top speed of seating velocity general in industry.Target seating velocity keeps up to about 7500 motor rpm, it illustrates the acceptable Dynamic controlling to motorcar engine application.

5.2 torque spring checkings

Torque spring is the critical component of SRFF-1L design, particularly during high speed operation.Spring carries out Proof of Concept to verify robustness.Three elements of spring design are tested for inspection concept.First, load loss is recorded under the condition circulated at the height of running temperature.Load on spring loss, or lax, represents the decline to load on spring at the end of test from test.Load loss is also by applying maximum pressure grade and making parts stand high temperature record (proof).The second, under worst condition and circulation, test durability and spring checking fatigue life, and described load loss.Finally, the function by using minimum load spring and checking to fetch checking lost motion springs at the not pump of all operating conditions period DFHLA in CDA pattern.

In engine oil pendular ring border, the test of based target fixture makes torque spring circulate under engine operating temperatures.Torque spring with the application cycle of complete stroke under the highest preload condition to represent the stress of worst condition.Circulation desired value is set as 2,500 ten thousand times and 5,000 ten thousand circulations.Torque spring is also through setting test of being heated, and in this test, they are loaded into the highest application stress, keep 50 hours and sensing lead loss at 140 DEG C.

Figure 112 summarizes the load loss of loop test and heat setting test.All parts are through 8% maximum load loss, and design object is set in 10% maximum load loss simultaneously.

Result shows the maximum load loss of 8% and meets design object.Many tests demonstrate minimum load loss close to 1%.Safe to all tests of load loss in design guidance policy.

Robustness got by pump during 5.3 cylinder deactivations

Torque spring 1124 (Figure 99) is designed to prevent HLA pump from getting to retain latch gap 1205 (Figure 108 A) when system is run during without lift mode.Testing apparatus is designed to the engine oil pressure at backlash compensation pressure port place to maintain pattern and switches in the oil temperature and engine speed condition scope that require.

Carry out demonstration test to prove that torque spring 1124 keeps the ability of latch gap 1205 (Figure 108 A) at desired conditions.Test is carried out on monitored motor, has the instrument for measurement clearance compensatory pressure mouth 512 (Figure 88) and the switching valve at pressure port 506 (Figure 88) place and CDASRFF action, oil pressure and temperature.

Lower limit lost motion springs is for simulating worst condition.This test performs under the 3500rpm representing maximum switch speed.Two running temperatures are thought of as 58 DEG C and 130 DEG C.Test result shows, and when pressure ratio application requires high 25%, pump is got.

Figure 113 is presented at 58 DEG C in the minimum pump pressure power 1540 that exhaust side records.For the pump pressure power of exhaust at air inlet at 58 DEG C and 130 DEG C and 130 DEG C higher than the pump pressure power of exhaust side at 58 DEG C.SRFF, at switch mode, has normal lift events and without lift mode event.To salient angle close to for detecting valve event, to verify at the SRFF mode state of switching pressure port 506 under corresponding pressure.Pressure in backlash compensation mouth 512 increases gradually, and monitoring is from without the switching of lift condition to normal lift condition.Pressure when system finishing switches is registered as pump pressure power 1540.To SRFF-1L design, when oil pressure remains on 5 bar or avoids pump to get oil pressure lower than security of system during 5 bar.The fatigue design surplus condition simulating worst condition is carried out in Concept Testing under the moment torque spring of high restriction especially.The Concept Testing that high capacity torque spring carries out meets required design object.

The checking of mechanical clearance during 5.4 switching durability

Mechanical clearance control is important to valve mechanism dynamic stability and is kept in the life time of whole motor.Have breech lock load and normal lift mode and without lift mode between the test that switches be considered to the wearing and tearing that are appropriate to verify bolt lock mechanism and performance.Switch durability by from joining that unengaged position switches breech lock to, the SRFF that circulates in without lift mode, make breech lock joint inner arm and SRFF circulated in normal lift to test.A circular in definition is for throwing off and being re-engaged breech lock subsequently and running SRFF in two kinds of patterns.The durability target switched is 3,000,000 circulations.3000000 cyclic representation equals an engine life.An engine life is defined as 200,000 miles that equal reliably more than 150,000 miles of standards.Parts the highest switch speed target of 3500 motor rpm tested with simulate switch during worst condition dynamic load.

Figure 114 illustrates the change of the mechanical clearance at test period periodic test point.This test is based upon on one group of six cylinder engine fixture.Often organize three cylinders and corresponding four SRFF-1L of each cylinder, 12 molded line are shown altogether.The mechanical clearance change of 0.020mm is asserted design wear down target.All SRFF-1L are presented at the safety clearance wear allowance lower than wear down target under equal vehicle ages.This test extends to more than 25% of lifetime goal at parts close to time of maximal clearance variation targets value.

For SRFF-1L, the valve mechanism in equal engine life dynamically, checking got by torque spring load loss, pump and mechanical clearance all meets re-set target.Valve mechanism dynamically-with regard to closing velocity-be reliably positioned at the limit under the maximum engine speed of 7200rpm and the speed limit higher than 7500rpm.The load loss of LMS load loss display 8%, it is reliably within the design object of 10%.Carry out pump and get test display, SRFF-1L design correctly runs under the given target oil pressure of 5 bar.Finally, the mechanical clearance change in equal motor lift is reliably within design object.SRFF-1L meets all designing requirements for cylinder deactivation in spark ignition passenger car application.

6. conclusion

Cylinder deactivation is proved to be method car gasoline vehicle being improved to fuel economy.Complete the design of the single salient angle SRFF based on cylinder deactivation system, improvement and change, provide by reducing pumping loss and run the ability that part cylinder improves fuel economy under more high burning efficiency.System is by keeping identical center line to carry out the basic framework of protective standard model II valve mechanism to engine valve, camshaft and slack adjuster.Engine cylinder cap needs in cylinder head, increase OCV and fluid control mouth, changes to deactivation mode to allow SRFF from normal lift mode hydraulic cutting.System needs the corresponding OCV of each cylinder, and is usually configured with four identical SRFF for air inlet and exhaust, the wherein corresponding DFHLA of each SRFF.

SRFF-1L design provides the solution reducing system complexity and cost.The most important enabling tool of SRFF-1L design is the amendment to idle running torque spring.LMS be designed to normal lift mode and without both lift modes during maintain continuous contact between single salient angle camshaft and SRFF.Although this torque spring requires packaging spaces many a little, whole system becomes simpler by elimination three salient angle camshaft.The axis accumulation of SRFF-1L reduces from three salient angle CDA designs, due to not on outer arm slide block and with the interface of inner arm on increase the external cam crown of roll angle on the attached load in edge opportunity.The rocking arm rigidity levels of SRFF-1L is similar to standard production rocking arm.

Moment of inertia by heavier parts are directly being landed in the hub switch side on DFHLA to minimize, described heavier parts and bolt lock mechanism and torque spring.To obtain better valve mechanism dynamic by minimizing laterostigmatal effective mass for this feature.System and checking are carried out for the engine speed of the 3500rpm during the engine speed of the 7200rpm during standard lift mode and deactivation mode.Parts are also verified by least one engine life at least equaling 200,000 motor miles.

Although present disclosure describes different aspect of the present utility model, although and these aspects be described in some details, this is not to retrain application or restriction this application claims instruction by any way scope is such details.Other advantages and improvement it will be apparent to those skilled in the art that.Therefore, the instruction of the application, in its broad sense, is not restricted to specific detail and shown and described embodiment.Therefore, can make from such details and do not depart from claimant of the present utility model and require to instruct the change within spirit and scope.In addition, aforementioned aspect is illustrative, does not have single feature or element for being necessary with all possible combination of accompanying claim herein.

III.VVA motor and cylinder head are arranged

1. switch rocker arm assembly

1.1 illustrate-general engine structure

Figure 115 and 116 describes the part engine cylinder cap assemblies with the Dual Over Head Camshaft internal-combustion engine of exhaust cam of conventional model II.For clarity, exhaust cam rocking arm, valve and partial-air admission valve camshaft are removed.It is noted herein that the utility model is equal to other engine design being applied to and having similar device and structure.

Multiple cam tower 10 protrudes upward, and has 13 parts at the bottom of the cam tower protruded upward from cylinder head.At the bottom of cam tower, the upside of 13 has semi-cylindrical canyon.

Cam tower cap 11 to be bolted at the bottom of cam tower 13.Cam tower cap 11 has similar semi-cylindrical canyon down, thus when cam tower cap 11 to be bolted at the bottom of cam tower 13, depression generates the circular cam depression 321 holding camshaft.Camming recess 321 size and structural design are that fixing air inlet and exhaust cam shaft still allow them to rotate freely.

Spark plug tube 20 in the utility model between cam tower 10 and the center line 21 be parallel to through cylinder head center.Spark plug tube 20 extends downwardly through cylinder head and enters in each cylinder top, and is designed to hold spark plug.

1.2VVA switches rocking arm and arranges

1.2.1 be arranged symmetrically with

Illustrate that this engine cylinder cap assemblies in Figure 115 and 116 has enough spaces to hold as previously mentioned and the lift range variable of symmetry (VVL) rocker arm assembly 100.

VVL rocker arm assembly 100 is for other parts of this specification.But, be appreciated that these aspects of the present utility model may be used for being arranged in cylinder head and in one end of rocker arm assembly and have other different rocker arm assemblies closely spaced.

This VVT rocker arm assembly 100 is by having the camshaft actuated of three salient angles to each cylinder.In Figure 115 and 116, remove camshaft, but retain intermediate cam salient angle 324 and external cam salient angle 326.Of the present utility model in this, shown rocker arm assembly 100 has to inner 101 (or first ends 101) and 103 (or second ends 103) outward.Term " inwardly " relates to the direction of inwardly center line 21, and " outwards " relates to outwards away from the direction of center line 21.

As shown in Figure 116, can find out, VVL rocker arm assembly 100 is supported to inner 101 by hydraulic lash adjuster 340.103 be resisted against on valve stem 350 outward.

When middle cam lobe 342 rotates and is pressed downwardly onto on VVL rocker arm assembly 100, it causes 103 promoting valve stem 350 downwards and opening the poppet valve being connected to valve stem 350 outward of VVL rocker arm assembly 100.When interior breech lock runs for high-voltage oil liquid to it by carrying, VVL rocker arm assembly 100 causes valve and promotes according to the shape of external cam salient angle 326.This is described further below in conjunction with Figure 117.

1.2.2 unsymmetrical arrangement

In Figure 117, torque spring 135,137 makes VVL rocker arm assembly 100 wider at first end compared with standard rocker arm assembly with spring strut 141,143.The design of VVL rocker arm assembly 100 (with CDA rocking arm) is wider and can only be assemblied in some cylinder head than standard rocking arm.Have enough spaces in cylinder head shown in Figure 115 and 116, but in some engine cylinder cover, not from the enough space of other structure example as cam tower or spark plug tube, this DVVL rocking arm 100 can not use.

As implied above, redesign/amendment cylinder head, cam driver and gear mechanism are unusual Expenses Costs.Equally, many different manufactures may make equipment based on cylinder head standard design, make it be difficult to amendment or change cylinder head.

Therefore, the utility model can be embodied in design especially and has in the VVA rocker arm assembly of small―gap suture cylinder head to coordinate.

In many Cylinder head designs, determine only in the shortage space, side of rocking arm.Usually, the shortage in space may appear at rocking arm near spark plug tube 20 side to inner 101.Therefore, be feasible to redesign packaged VVL rocker arm assembly 100, thus the width of obstruction side can not wider than the width of standard rocking arm.

Result is the rocker arm assembly producing amendment, has in the cylinder head of obstruction on the right side of rocker arm assembly or the left side of rocker arm assembly.In the rocker arm assembly of left side, most of functional element moves on to left side from right side.Equally, right side is formed as the width with reduction.

Similarly, right side rocker arm assembly is designed to use when having obstruction in left side.Similarly, structure moves on to right side from left side, and left side is formed as on left side, producing increase gap to compensate obstruction.Jointly, they are called the rocker arm assembly of improvement.

According to the improvement rocker arm assembly 400 composition graphs 118-122 explanation of the novelty of an aspect of the present utility model.

Figure 118 is according to an aspect of the present utility model, the perspective view showing the left side improvement rocker arm assembly 400 of lift range variable.

Figure 119 is the plan view of the improvement rocker arm assembly 400 of Figure 110.

Figure 120 is the side view of the improvement rocker arm assembly 400 of Figure 118-119.

Figure 121 is that the improvement rocker arm assembly of Figure 118-120 holds the end elevation seen from its hinge (first).

Figure 122 is that the improvement rocker arm assembly of Figure 118-121 holds the end elevation seen from its breech lock (second).

Improvement rocker arm assembly 400 for describing object shown here is lift range variable (VVL) rocker arm assemblies.But cylinder deactivation (CDA) rocker arm assembly or other rocker arm assemblies-they use torque spring at first end 408 or otherwise have first (or hinged) end 408 of widening-all fall in scope of the present utility model.

The method of operation of this rocker arm assembly be very similar to rocker arm assembly as shown in Figure 117 and VVLRockerApplication as above-it at this all by reference to introducing.The rocker arm assembly 400 improved uses the inner structure 410 be assemblied in external structure 420.But the rocker arm assembly of this improvement is used in be had in the cylinder head in less gap near rocker arm assembly.Improve rocker arm assembly 400 except function aspects disclosed herein, also comprise some decoration aspects.

Inner structure 410 can have the axle recess 413 through its first end 408.External structure 420 also can have the axle recess 433 through its first end 408.When roller axle recess 413,433 aligns with the inner structure 410 in external structure 420, axle 434 can be fixed through axle recess 413,433, to allow inner structure 410 relative to external structure 420 around axle 434 pivotable.

Hinder external structure on side 405 420-when it extends towards first end 408 from the second end 409-can offset towards without hindrance side 407, produce the first Offset portion 428.This skew can be can produce the bending of less width or angled side arm at first end 408 place.Compared to standard VVL or CDA rocker arm assembly, this first Offset portion 428 can provide additional clearance on obstruction side 405.This can allow the rocker arm assembly 400 improved to be fitted into cylinder head working therewith, and this cylinder head has narrow obstruction region, such as Figure 132,133 obstruction region 600.

External structure on without hindrance side 407 420-when it extends from the second end 409 towards first end 408-can outwards offset away from improvement rocker arm assembly 400, produce the second Offset portion 429.Compared to standard VVL or CDA rocker arm assembly, this second Offset portion 429 can provide extra gap on without hindrance side 407, to allow joint second torque spring 437.This can allow to improve power that rocker arm assembly 400 applies appropriate amount with relative to external structure 420 bias voltage inner structure 410.In alternative aspect of the present utility model, single larger torque spring may be used for replacing two or more torque springs shown here.

Improve rocker arm assembly 400 and use the latch assembly 500 with latch pin 510, latch pin 510 can keep inner structure 410 together with external structure 420 thus they move as a rocking arm.Latch assembly 500 can be activated by fluid control valve (not shown), and fluid control valve can provide the oil pressure of increase by the cup 448 of pivotable on hydraulic lash adjuster 340.This further illustrates in conjunction with Figure 126,127.

Owing to having two (or multiple) torque springs 435,437 (or single larger torque spring) and there is no torque spring in obstruction side 405 on without hindrance side 407, the inner structure 410 of rocker arm assembly and external structure 420 there is torsional forces.Therefore the play amount around axle 434 can be adjusted to ensure that improving rocker arm assembly 400 suitably works.

When use two torque springs 435,437, torque spring 435 is considered to right side spring and opposite direction along torque spring 437 reels.The more invalid spring forces of these different springs.

If only use single torque spring, when in designing and external structure 410,420 time need the extra warping force of consideration.

For two torque spring and the design of single torque spring, interior and relative intensity that is external structure 410,420 can be adjusted to reduce bending, to ensure proper property.In addition, each structure can be configured to provide suitable intensity and structure along the weight distribution of their length, is minimized under starting to run required speed simultaneously and needs pivotable to improve the inertial force of rocker arm assembly 400.Comprise many ornamental aspects different from disclosed functional aspect herein with external structure 410,420 in described.

Figure 122 display is held when latch pin is at extended position and is kept the breech lock key seat 485 of this latch pin 501.Latch pin 501 and breech lock key seat 485 can keep the inner structure 410 be assemblied in external structure 420.Even if latch pin is depicted as circle, it also can have the smooth end of corresponding smooth seat.Latch pin 501 and breech lock key seat 485 can have allow they be adapted at together with any complementary shape.

Figure 123 be the external structure of display first and second offset area 428,429 from the plan view viewed from top.That can find out from the external structure of the rocker arm assembly of Figure 117 here is different.The first outer webs 421 near first end 408 can deflect into left side to hold the obstruction on the right side of rocker arm assembly 400 first end.Similar, the second outer webs 422 also can deflect into left side to hold the obstruction on the right side of rocker arm assembly 400 first end, when they extend from the second end 409 to first end 408, keeps the distance that the first and second outer webs are roughly mutually the same.This can produce skew (counteracting) region 428 and 429.

Figure 124 be the external structure of Figure 123 from the planimetric map viewed from bottom, it also shows the first and second offset areas 428,429.This also shows lower cross arm 439.Owing to improving the asymmetrical design of rocker arm assembly 400, lower cross arm 439 can be illustrated as gaining in strength with neutralization power and helping prevent may produce in addition bending.

The breech lock key seat 485 illustrated in conjunction with upper Figure 122 also shows from this view.

Figure 125 is the side view of the external structure 420 according to one side of the present utility model.First outer webs 421 and the first Offset portion 428 visible in this view.

Figure 126 is the perspective view on the top of inner structure 410 according to one side of the present utility model.

Figure 127 is the perspective view of the bottom of the inner structure 410 of Figure 126.Axle recess 413 is depicted as and can holds axle 434 and pivotable can connect inner structure 410 to external structure 420.In Figure 126 and 127, ball axis hole 483 and 484 can hold roller axle (not shown) to keep roller 415.In Figure 127, cup 448 can hold the hydraulic lash adjuster 340 of Figure 116.Hydraulic lash adjuster (340 of Figure 116) has the oil stream come from fluid control valve (not shown).Cup 448 can be connected to the inner gateway providing fluid to passage 444 and 446.Oil passage can be connected to latch assembly 500 by inner gateway.The oil pressure being greater than threshold pressure provided by fluid control valve can cause latch assembly 500 to switch.Latch pin (501 of Figure 120-122) can be set to its normal position (having low oil pressure) at retracted position.When the oil pressure being greater than threshold value is fed into breech lock, it can switch stretches out latch pin (501 of Figure 120-122).This is " normally non-kayser " configuration.

Alternative, under low oil pressure, latch pin can normally at extended position.When oil pressure is increased to more than threshold value, latch pin can be retracted.This is " normal kayser " design.

Figure 128 is that the inner structure of Figure 126-127 is from the view viewed from top.

Figure 129 is that the inner structure of Figure 126-128 is from the view viewed from bottom side.

In Figure 129, show valve pole socket 417.Valve pole socket 417 extrudes engine air valve rod, thus when improve rocker arm assembly 400 pivotable time actuate valves.

Figure 130 is that the inner structure 410 of Figure 126-129 holds the end elevation seen from hinge (first).

Figure 131 is that the inner structure 410 of Figure 126-130 holds the end elevation seen from breech lock (second).

Spring strut 447 is shown in Figure 128-131.The first one or more torque springs 435,437 to be assemblied on spring strut 447 and to be held in place by this spring strut.Also single larger torque spring can be used, for alternative first and second torque springs 435,437.

Figure 132 is the perspective view that the improvement rocker arm assembly 400 of Figure 118-122 presents when being installed in cylinder head.

As Figure 115 and 116, for clarity sake remove parts.The most significantly, the shaft portion each engine valve to the camshaft of three salient angles is removed.Intermediate cam salient angle 324 and an external cam salient angle 326 are shown.Because a side salient angle does not show, the second slide block 426 is visible.As described in above VVL rocking arm application, the second slide block can ride in external cam salient angle 326.

Camshaft passes through and passes cam tower 10 to fix.Can know at this and see, spark plug tube 20 can interference standard CDA or VVL rocker arm assembly in obstruction region 600.The first Offset portion 428 improving rocker arm assembly 400 is hindering region 600 near spark plug tube 20.Due to the width that it reduces, can be assemblied in now this and cover and play function and do not collide spark plug tube 20.

Figure 133 is the perspective view at another visual angle of the improvement rocker arm assembly 400 of Figure 118-122, and this is the perspective view that it presents when being arranged in cylinder head.

Which show the same structure as Figure 120, but from top and viewed from the viewpoint of cylinder head center line, observe and improve the without hindrance side 407 of rocker arm assembly 400.Intermediate cam salient angle 324 depresses roller 415.

First Offset portion 428 is shown near hindering region 600 near spark plug tube 20, to provide required gap.

Second Offset portion 429 is also shown as torque spring 435,437 and provides additional space.

Although present disclosure describes different aspect of the present utility model, although and these aspects be described in some details, this is not to retrain application or restriction this application claims instruction by any way scope is such details.Other advantages and improvement it will be apparent to those skilled in the art that.Therefore, the instruction of the application, in its broad sense, is not restricted to specific detail and shown and described embodiment.Therefore, can make from such details and do not depart from claimant of the present utility model and require to instruct the change within spirit and scope.In addition, aforementioned aspect is illustrative, does not have single feature or element for being necessary with all possible combination of accompanying claim herein.

Claims (8)

1. switch a rocker arm assembly, comprising:

Multiple rocking arm and additional structure, they link together and have manufacturing tolerances, and described manufacturing tolerances causes mechanical clearance;

With the breech lock of latch pin and breech lock seat, described breech lock seat is suitable for receiving and fixing described latch pin, and it is characterized in that, described breech lock seat comprises:

Recess, this recess has the shape with the shape complementarity of latch pin, the degree of depth of described recess be chosen to compensate mechanical clearance at least partially to form predetermined gap.

2. for switching a latch assembly for rocker arm assembly, it is characterized in that, described latch assembly comprises:

Nonplanar latch pin; With

Breech lock seat, this breech lock seat comprises the recess of punching press, and this recess is positioned at the position that this latch pin (200) touches with this breech lock seated connection, and described recess has the shape with the shape complementarity of described latch pin.

3. latch assembly according to claim 2, is characterized in that, described latch pin has cylinder form, and described recess is the bending recess with the cylinder form complementation of described latch pin.

4. a manufacturing equipment, this manufacturing equipment has:

Base portion;

Goalpost stick harness, this goalpost stick harness upwards extends from described base portion and has the size and dimension identical with the hydraulic lash adjuster of preset engine (HLA);

Valve roofbolt, this valve roofbolt upwards extends from described base portion and has the size and dimension identical with the valve stem of preset engine, and this valve roofbolt is identical with orientation relative to the position of the hydraulic lash adjuster of described preset engine, height with described valve stem with directed relative to the position of described goalpost stick harness, height;

Bearing support;

It is characterized in that, the size and dimension manufacturing fixing device is designed for receiving the switching rocker arm assembly be designed in described preset engine.

5. manufacturing equipment according to claim 4, is characterized in that, described goalpost stick harness and described valve roofbolt are suitable for receiving described switching rocker arm assembly.

6. manufacturing equipment according to claim 4, is characterized in that, switching rocker arm assembly to be processed has breech lock, and this breech lock is installed to latch pin in latch hole and a breech lock seat with one; This manufacturing equipment also comprises:

Latch bar, this latch bar is placed in described latch hole, so that this latch bar leans against on breech lock pad when described switching rocker arm assembly is installed on the gentle door roofbolt of described goalpost stick harness, the hardness of described latch bar is obviously greater than the hardness of described breech lock seat, and the diameter of described latch bar is identical with described latch pin.

7. manufacturing equipment according to claim 4, is characterized in that, this manufacturing equipment also comprises:

Pressure piece, this pressure piece is pressed on the second end of this switching rocker arm assembly when described switching rocker arm assembly is arranged on the gentle door roofbolt of described goalpost stick harness, is pressed in described breech lock seat, forms impression thus in breech lock seat for by described latch bar.

8. an economic switching rocker arm assembly, this switching rocker arm assembly has predetermined gap and is configured with its tolerance and designs large parts than prior art, and described rocker arm assembly comprises:

First rocking arm, this first rocking arm is manufactured with and designs large tolerance than prior art, and has first end and the second end;

Second rocking arm, this second rocking arm is manufactured with and designs large tolerance than prior art, and has the first end be pivotally connected to the first end of the first rocking arm;

Roller bearing on first rocking arm, this roller bearing to be suitable for riding on cam and to activate this first rocking arm;

Breech lock, the breech lock seat that this breech lock has the latch pin on the second end of the rocking arm being arranged in the first and second rocking arms and is positioned on the second end of another rocking arm, this breech lock runs when locking, these rocking arms relative to each other to be fixed, and allows these rocking arms pivotable independently of each other when unlocking;

It is characterized in that, described breech lock seat has recess, this recess is configured as receiving described latch pin, and being dimensioned to gap that compensation increases at least partially and forming predetermined gap of this recess, the gap of this increase is caused by the manufacturing tolerances increased.