EP3039256A1 - Method for optimizing response time of hydraulic latch-pin in cylinder deactivation rocker arm - Google Patents
Method for optimizing response time of hydraulic latch-pin in cylinder deactivation rocker armInfo
- Publication number
- EP3039256A1 EP3039256A1 EP14840581.4A EP14840581A EP3039256A1 EP 3039256 A1 EP3039256 A1 EP 3039256A1 EP 14840581 A EP14840581 A EP 14840581A EP 3039256 A1 EP3039256 A1 EP 3039256A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- latch
- response time
- rocker arm
- ref
- major
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
- F01L13/0005—Deactivating valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/12—Transmitting gear between valve drive and valve
- F01L1/18—Rocking arms or levers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L2303/00—Manufacturing of components used in valve arrangements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L2305/00—Valve arrangements comprising rollers
Definitions
- the present disclosure relates generally to switching roller finger followers and more specifically to methods for optimizing response times of a latch pin for a cylinder deactivation rocker arm.
- a switching roller finger follower or switching rocker arm allows for control of valve actuation by alternating between two or more states, usually involving multiple arms, such as in inner arm and outer arm.
- Switching rocker arms can be used in variable valve actuation (WA) systems to improve engine fuel economy.
- WA variable valve actuation
- a method for optimizing response time of a latch in a cylinder deactivation rocker arm assembly is provided.
- the latch is configured to move between an engaged position with an inner arm of the rocker arm assembly and a retracted position.
- Remarck Ref. No. 431 1 -000161/WO/POA outer diameter (L1 ) of the latch is determined.
- An installed length (L2) of a spring biasing the latch is determined.
- a clearance (L3) between L1 and a major inner diameter of an outer arm of the rocker arm assembly is determined.
- a radial clearance (L4) between a cage coupled to the outer arm and a major inner diameter of the latch is determined.
- a minor diameter (L5) of the latch is determined.
- a relationship between the response time of the latch and L1 , L2, L3, L4 and L5 is established. At least one of the L1 , L2, L3, L4 and L5 impacts the response time more than a remainder of the L1 , L2, L3, L4 and L5.
- Components of the cylinder deactivation rocker arm assembly are selected based on the relationship.
- the response time can be an ON response time required for the latch to move from the inner arm and enable switching to a cylinder deactivation mode.
- L4 has a greater impact on response time than L1 , L2 and L3.
- L5 has a greater impact on response time than L1 , L2 and L3.
- the relationship is established by the following equation:
- ON Response time (ms) 22.1431 + 1.2675 * L1 - 1.28 * L2 - 0.2625 * L3 - 8.8762 * L4 + 8.1951 * L5 + 0.55 * L1 * L2 - 2.825 * L1 * L4 - 2.77 * L1 * L5 + 0.655 * L2
- the response time is an OFF response time required for the latch to move from the retracted position to the engaged position.
- L1 can have a greater impact on response time than L2, L3, L4 and L5.
- L4 can have a greater impact on response time than L2, L3 and L5.
- L5 can have a greater impact on response time than L2 and L3.
- the relationship is established by the following equation:
- a method for optimizing ON and OFF response times of a latch in a cylinder deactivation rocker arm assembly is provided.
- the latch moves between an engaged position with an inner arm of the rocker arm assembly and a retracted position.
- the method includes determining a major outer diameter (L1 ) of the latch.
- An installed length (L2) of a spring biasing the latch is determined.
- the ON response time is required for the latch to move from the inner arm and enable switching to a cylinder deactivation mode.
- L4 can have a greater impact on response time than L1 , L2 and L3.
- L5 can have a greater impact on response time than L1 , L2 and L3.
- L5 can have a greater impact on response time than L1 , L2 and L3.
- the ON Response time is established by the following equation:
- ON Response time (ms) 22.1431 + 1.2675 * L1 - 1.28 * L2 - 0.2625 * L3 - 8.8762 * L4 + 8.1951 * L5 + 0.55 * L1 * L2 - 2.825 * L1 * L4 - 2.77 * L1 * L5 + 0.655 * L2
- the OFF response time is required for the latch to move from the retracted position to the engaged position.
- L1 can have a greater impact on response time than L2, L3, L4 and L5.
- L4 can have a greater impact on response time than L2, L3 and L5.
- L5 can have a greater impact on response time than L2 and L3.
- the OFF response time is established by the following equation:
- FIG. 1 is a front perspective view of an exemplary switching rocker arm constructed in accordance to one example of the present disclosure; Eaton Ref. No. 13-ECD-744PCT
- FIG. 2 is a partial sectional view of a switching mechanism of the switching rocker arm of FIG. 1 and shown with the valve in lift mode with the latch engaged;
- FIG. 3 is a partial sectional view of the switching rocker arm of FIG. 2 and shown with the valve in cylinder deactivation mode with the latch disengaged;
- FIG. 4 is a partial cross-sectional view of the switching rocker arm of FIG. 1 and shown with the latch engaged with the inner arm;
- FIG. 5 is a partial cross-sectional view of the switching rocker arm of FIG. 1 and shown with the latch in a retracted position and in contact with the cage;
- FIG. 6A is a partial cross-sectional view of the switching rocker arm showing the latch moving from the engaged position to the retracted position
- FIG. 6B is an end view of the cage and latch of the switching rocker arm of FIG.
- FIG. 7 is a free body diagram of the latch during motion toward the cage
- FIG. 8 is a free body diagram of the latch during motion away from the cage
- FIG. 9A is a partial cross-sectional view of the switching rocker arm of FIG. 1 according to an exemplary baseline design
- FIG. 9B is a cross-sectional view taken along line A-A of FIG. 9A;
- FIG. 10A is a partial cross-sectional view of the switching rocker arm of FIG.
- FIG. 10B is ac cross-sectional view taken along line A-A of FIG. 10A;
- FIG. 1 1 is a graph illustrating an effect of clearance on diameter (L3) between the latch and the outer arm;
- FIG. 12 is a graph illustrating an effect of radial clearance (L4) between the latch and the cage.
- FIG. 13 is a graph illustrating an effect of contact length (L6) between the latch and the outer arm.
- the following teachings are directed toward methods for optimizing response time of a latch in a switching rocker arm. Specifically, the following discussion provides methods of optimizing latch response time or the time for the latch to move such that the switching rocker arm can shift from lift mode to deactivation mode and vice-versa. Eaton Ref. No. 13-ECD-744PCT
- the SRFF assembly 10 can be a compact cam-driven single-lobe cylinder deactivation (CDA) switching rocker arm 12 installed on a piston-driven internal combustion engine, and actuated with the combination of a duel- feed hydraulic lash adjusters (DFHLA) 14 and oil control valves (OCV) 16.
- CDA compact cam-driven single-lobe cylinder deactivation
- the SRFF assembly 10 can be engaged by a single lobe cam 20.
- the switching rocker arm 12 can include an inner arm 22, an outer arm 24.
- the default configuration is in the normal-lift (latched) position where the inner arm 22 and the outer arm 24 are locked together, causing an engine valve 26 to open and allowing the cylinder to operate as it would in a standard valvetrain.
- the DFHLA 14 has two oil ports.
- a lower oil port or lash compensator pressure port 28 provides lash compensation and is fed engine oil similar to a standard HLA.
- An upper oil port 30, referred as the switching pressure port, provides the conduit between controlled oil pressure from the OCV 16 and a latch 32 (FIG. 2).
- the latch 32 When the latch 32 is engaged, the inner arm 22 and the outer arm 24 operate together like a standard rocker arm to open the engine valve 26.
- the inner arm 22 and the outer arm 24 can move independently to enable cylinder deactivation.
- a pair of lost motion torsion springs 40 are incorporated to bias the position of the inner arm 22 so that it always maintains continuous contact with the camshaft lobe 20.
- the torsion springs 40 are secured to mounts located on the outer arm 24 by spring retainers 44.
- the lost motion torsion springs 40 require a higher preload than designs that use multiple lobes to facilitate continuous contact between the camshaft lobe 20 and an inner arm roller bearing 50.
- the engine valve 26 can include a valve seat 54 and a valve guide 56.
- a valve spring 58 can bias to valve seat 54 away from the outer arm 24.
- the OHV 16 can be an electronically controlled ON/OFF valve that receives an electrical signal from an engine control unit (ECU) 70.
- Engine oil is supplied to the OCV 16.
- the OCV 16 is hydraulically connected to the DFHLA 14.
- the inner arm 22 is pivotally coupled to the outer arm 24 at a pivot axle 76. The connection at the Eaton Ref. No. 13-ECD-744PCT
- Remarck Ref. No. 431 1 -000161/WO/POA pivot axle 76 allows the inner arm 22 to swing in relation to the outer arm 24.
- the latch 32 is installed at the end pivot side of the outer arm 24, above the DFHLA 14, with a purpose of providing a secondary connection between the inner arm 22 and the outer 24.
- a latch compression spring 80 biases the latch 32 in the extended position engaging the inner arm 22.
- the latch compression spring 80 is captured at one end by the latch 32 and at the other end by a cage 82 which is permanently joined with the outer arm 24.
- the lost motion springs 40 maintain the camshaft lobe 20 in permanent contact with the roller bearing 50 located in the inner arm 22.
- the balance between the oil pressure in the switching pressure port and the force of the latch compression spring 80 is pushing the latch 32 to engage or disengage the inner arm 22 and the outer arm 24.
- Lift mode can occur at engine speeds up to 7200 rpm and all operating temperatures.
- the oil pressure in the switching port can be regulated to 0.2 bar to 0.4 bar.
- the latch 32 is in the extended position and engaged with the inner arm 22.
- Cylinder deactivation or no lift mode can be available on engine speeds up to 3500 rpm and oil temperatures of 20 degrees Celsius or higher.
- the no lift mode is triggered by an electric signal from the ECY 70 to the OCV 16, which increases the oil pressure in the switching pressure port above 2.0 bar. The increase in pressure retracts the latch 32 to disengage the inner arm 22.
- oil pressure at 20 degrees Celsius is above 4.0 bar.
- 2.0 bar oil pressure is practical at temperatures above 100 degrees Celsius. As a result, the oil pressure at cold temperature can be 3 bar.
- FIG. 2 a cross-section of the SRFF assembly 10 during lift mode will be described.
- the oil pressure in the switching pressure port is 0.2 to 0.4 bar.
- the latch 32 is extended and engaged with the inner arm 22.
- the SRFF assembly 10 inner arm 22 and outer arm 24 are linked together working as a single body similar to a standard rocker arm.
- the camshaft rotational motion is transferred to the valve 26 through the inner arm 22 and the outer arm 24.
- the valve 26 opens and closes based on the lift profile of the camshaft lift lobe 20.
- Eaton Ref. No. 13-ECD-744PCT Eaton Ref. No. 13-ECD-744PCT
- the electric signal from the ECU 70 energizes the OCV 16 to pressurize the switching port with engine oil pressure.
- a minimum of 2.0 bar is needed to overcome the latch spring 80 preload force, compressing the latch spring 80 and moving the latch 32 in the retracted position, disengaging the inner arm 22 from the outer arm 24.
- the SRFF assembly 10 can include a gap between the latch 32 and the inner arm 22 called latch lash. The lash allows the latch 32 to move in and out of the outer arm 24 based on the oil pressure in the switching port and when the camshaft is on the base circle. The absence of the connection between the latch 32 and the inner arm 22 results in camshaft rotational motion transfers to the inner arm 22 only that rotates around the pivot axle 76. Camshaft motion is not transferred to the valve 26 that remains at rest on the valve seat 54.
- the CDA switching rocker arm 12 can enable switching from lift mode to deactivation mode and vice versa.
- Dual overhead cam engines have one OCV 16 that provides input to four SRFF assemblies 10 (two for intake valves and two for exhaust valves).
- the sequence of activating and deactivating the valves is important for proper function of the engine.
- the preferred sequence from switching from lift mode to deactivation is to deactivate the SRFF's connected to the exhaust valves first, entrapping the exhaust gas inside the cylinder, and then, deactivating the SRFF's connected to the intake valves.
- the exhaust valves are activated first to relieve the pressure from the entrapped gas held in the cylinder during deactivation cycles.
- the SRFF's connected to the intake valves are activated, allowing the intake valves to open at nearly atmospheric pressure.
- Exhaust gas being trapped inside the cylinder during the deactivation cycles is beneficial because it reduces the pumping loses and keeps the deactivated cylinder warm, maintaining the engine thermal efficiency.
- Switching between modes is required within one camshaft revolution and the sequence of switching the intake and exhaust is important and must be maintained for proper engine function. Exceeding the switching time for one of the SRFF can result in switching the SRFF in the wrong sequence.
- the window available for switching is defined as the time that the hydraulic pressure can change modes and the latch mechanical movement can be complete to Eaton Ref. No. 13-ECD-744PCT
- Remarck Ref. No. 431 1 -000161/WO/POA create the change from deactivation to activation and vice-versa. Mode switching occurs when the SRFF is on camshaft base circle condition when the latch 32 is under load from the inner arm 22 and can move freely.
- Latch response time is defined as the time for the latch 32 to move such that the SRFF can shift from lift to deactivation mode and vice-versa.
- the time required for the latch 32 to move from the inner arm 22 and enable switching the SRFF to deactivation mode is referred to as "ON responseā.
- the movement of the latch 32 is enabled by energizing the OCV 16. This increases the pressure in the switching pressure port to engine oil pressure. The increase in pressure overcomes the force in the latch spring 80 moving the latch 32 from the engaged to the retracted position.
- the latch 32 is shown in the engaged position.
- the latch 32 is in the engaged position when the latch 32 front surface is in contact with the inner arm 22.
- the increase in the oil pressure in the switching pressure port moves the latch 32 a distance D1 from the engaged position to the retracted position.
- the distance D1 can be 1.86mm.
- the latch 32 is shown in the retracted position. In the retracted position, the latch 32 is in contact with the cage 82. The latch 32 is completely inside the outer arm 24 and the connection between the inner am 22 and the latch 32 is discontinued. The inner arm 22 remains free to pivot during the deactivation cycles.
- the OCV 16 is de-energized when no signal is sent to the OCV 16.
- the oil pressure in the switching pressure port is regulated to 0.2 bar to 0.4 bar. This pressure is insufficient to overcome the compressed spring force, moving the latch 32 to the extended position.
- the time for the latch 32 to travel from the retracted position to a partially engaged position is referred to herein as "OFF response".
- FIGS. 6A and 6B the latch 32 is shown in transit from the engaged position to the retracted position.
- FIG. 6A shows a cross-section along the axis of the latch travel.
- FIG. 6B represents a cross-section through a plane perpendicular to the direction of the latch movement.
- the oil residing between the latch inside pocket and the cage 82 creates a back pressure if the oil cannot quickly exit the SRFF through the hole located in the cage when the latch 32 moves to the disengaged position.
- An oil escape route 100 is formed between the latch 32 and the cage 82.
- FIG. 7 illustrates a free body diagram of the latch 32 during motion toward the cage 82.
- the force that drives latch motion is the hydraulic force due to pressure from the OCV 16 at latch close end towards major outer diameter, F pa i.
- Forces that oppose latch motion are viscous friction due to fluid between the latch 32 and the outer arm 24, Fviscousi and F V iscous2, the latch spring compression force, F sp hng, hydraulic force at latch close end toward minor diameter F pa 2, and the hydraulic force acting on the latch 32 from the open end F pa 3.
- the latch displacement, x is derived from Newton's second law of motion, with m being the latch mass identified in the following equation:
- FIG. 8 illustrates a free body diagram of the latch 32 during this motion wherein the forces that drive latch motion are the latch spring preload force, F sp hn g , hydraulic force at latch close end towards minor OD, F pa 2 and the hydraulic force acting on the latch 32 from the open end, F pa 3.
- the forces that drive latch motion are the latch spring preload force, F sp hn g , hydraulic force at latch close end towards minor OD, F pa 2 and the hydraulic force acting on the latch 32 from the open end, F pa 3.
- FIGS. 9A and 10A illustrate cross-sections through the SRFF 12 in the direction of latch movement for a baseline design (FIG. 9A) and an optimized design (FIG. 10A).
- FIGS. 9B and 10B illustrate respective cross-sections perpendicular to the latch axis of movement with the latch 32 between the engaged and retracted Eaton Ref. No. 13-ECD-744PCT
- a latch major outside diameter (OD) L1 an installed length L2 of the spring 80.
- a clearance between the latch major OD and the outer arm 24 bore major inside diameter (ID) L3.
- latch major OD, L1 The ON response time reduces with increasing in latch major OD, L1 due to increases in the area available for pressure that results in hydraulic force F pa i.
- the OFF response time increases as diameter increases due to higher hydraulic force acting on the latch major OD, L1.
- a back pressure of 0.4 bar max is available in the switching pressure port during the latch motion from the disengaged position to the engaged position.
- the rate at which the pressure in the switching port drops plays a role in the OFF response.
- the spring preload contributes effectively to the latch motion only after the pressure drops to a minimum pressure. Consequently before the pressure drops to minimum pressure, the dynamics of OCV interaction with latch and fluid path are important for accurate prediction of OFF response.
- the dynamics of OCV are influenced by latch major diameter, due to its frontal interaction.
- the effects of spring installed length L2 will now be described.
- the variation in spring load varies with L2.
- the installed length L2 affects the spring preload force.
- the larger the spring installed length the lesser is the spring force.
- the ON response decreases with increase in installed length due to lower resistance offered by the spring during motion from the engaged position to the disengaged position.
- the OFF response decreases with lesser spring installed length, due to larger preload in the spring which is the driving force during motion from the disengaged position to the engaged position.
- Remarck Ref. No. 431 1 -000161/WO/POA major OD, L1 and the outer arm major ID has an influence on the ON and the OFF response.
- the OFF response decrease with increase in clearance on the diameter L3, due to increased flow at the latch open end increasing pressure F pa 3.
- the ON response decreases until the clearance reaches a predetermined distance such as 0.12mm.
- the response time subsequently increases.
- an increase in clearance up to 0.12 mm decreases viscous friction force and hence the ON response decreases. Beyond the 0.12 mm, the leakage is high and therefore very low hydraulic force acting on the latch major OD, L1 , resulting in increased ON response.
- FIG. 12 shows the effect of the radial clearance between the cage 82 and the latch major ID for ON and OFF response times.
- the ON time decreases with increases in the radial clearance because lesser opposing force F pa 3 due to pressure generated at the cavity volume L7.
- the OFF response follows similar physics in the latch motion during the return travel. The response of the OFF response is steeper compared to the ON response slope.
- latch minor diameter L5 The ON response increases with increase in latch minor diameter L5 due to the relative increase in hydraulic force F pa 2 compared to F pa i which gives a resistive force for the retracted motion of the latch 32.
- the OFF response decreases with larger minor diameter due to combined effect of spring force F sp hn g and hydraulic force F pa 2 acting in the same direction.
- Remarck Ref. No. 431 1 -000161/WO/POA length L6 and chamber volume L7 parameters do not affect the response times compared to other parameters.
- a quantitative transfer function yielding a relationship between control factors affecting output response is provided.
- Five control factors have influence on response time: latch major OD (L1 ), spring installed length (L2), clearance on diameter (L3), radial clearance (L4), and latch minor ID (L5).
- Transfer functions were developed from analyzing output results for ON and OFF response times. The effect of the factor is directly proportional to the magnitude of the associated coefficient. Higher magnitude of coefficient, the stronger the change in response.
- the coefficients of radial clearance (L4) and latch minor OD (L5) in the following equation show a strong influence and contribution of (-40%) and (+37%) respectively.
- ON Response (ms) 22.1431 + 1 .2675 * L1 - 1 .28 * L2 - 0.2625 * L3 - 8.8762 * L4 + 8.1951 * L5 + 0.55 * L1 * L2 - 2.825 * L1 * L4 - 2.77 * L1 * L5 + 0.655 * L2 * L4 - 0.6050 * L2 * L5 - 0.4875 * L3 * L4 - 4.035 * L4 * L5
- OFF Response (ms) 19.731 + 15.8987 * L1 + 1.17163 * L2 - 1.53 * L3 - 7.6401 * L4 - 4.405 * L5 + 1.3375 * L1 * L2 - 10.265 * L1 * L4 - 1.837 * L1 * L5 - 1.005 * L2 * L5 + 1.7875 * L4 * L5
- the latch major OD (L1 ), spring installed length (L2), latch minor OD (L5) are in inverse relationship with respect to ON and OFF response time.
- a response optimizer function was developed to understand the effect of different experimental settings on the ON and OFF response times with the purpose to explore sensitivity of ON and OFF responses with changes in the input variables.
- the function determines the best possible combination of the input variables, L1 to L5 that generated the shortest ON and OFF response time.
- the optimization objective was to minimize both response times and an arbitrary target of 12.0 ms was chosen to provide robustness to design variations.
- the two transfer functions derived earlier, an optimal combination of the design variables was found to minimize the ON and OFF response simultaneously. The following ideal dimensions were provided after optimization for the best ON and OFF response time.
- the design methods set forth herein move toward the level 1 for L2, L3 and L4 and level 0 for L1 and L5.
- the optimized design is shown in FIGS. 10A and 10B where like reference numbers with an "A" suffix are used to denote like components.
- the optimized design includes changes to the latch 32A, the cage 82A and the spring installed length L2 to reduce the response time and balance the ON and OFF response. Optimized values were found for the factors L1 to L5. Packaging considerations restricted the changes of the latch major OD (L1) and the latch minor diameter (L5). The following design changes were made: L2 was decreased by 3.87% to balance the ON/OFF response. L3 was increased by 44% to reduce the viscous friction forces during latch movement and reduces both response times. L4 was increased by 53%. The optimized design modified the cage minor OD and increased latch ID. Further, as can be appreciated, the ON and OFF Response time equations provided by the instant methods can be used when selecting components of the SRFF assembly 10. Eaton Ref. No. 13-ECD-744PCT
- FIG. 1 A plurality of different embodiments of the present disclosure is shown in the Figures of the application. Similar features are shown in the various embodiments of the present disclosure. Similar features have been numbered with a common reference numeral and have been differentiated by an alphabetic suffix. Also, to enhance consistency, the structures in any particular drawing share the same alphabetic suffix even if a particular feature is shown in less than all embodiments. Similar features can be structured similarly, operate similarly, and/or have the same function unless otherwise indicated by the drawings or this specification. Furthermore, particular features of one embodiment can replace corresponding features in another embodiment or can supplement other embodiments unless otherwise indicated by the drawings or this specification.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
Abstract
Description
Claims
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
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US201361872624P | 2013-08-30 | 2013-08-30 | |
US201361872621P | 2013-08-30 | 2013-08-30 | |
US201361898475P | 2013-11-01 | 2013-11-01 | |
PCT/US2014/053689 WO2015031887A1 (en) | 2013-08-30 | 2014-09-02 | Method for optimizing response time of hydraulic latch-pin in cylinder deactivation rocker arm |
Publications (3)
Publication Number | Publication Date |
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EP3039256A1 true EP3039256A1 (en) | 2016-07-06 |
EP3039256A4 EP3039256A4 (en) | 2017-04-19 |
EP3039256B1 EP3039256B1 (en) | 2018-03-21 |
Family
ID=52587411
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP14840581.4A Not-in-force EP3039256B1 (en) | 2013-08-30 | 2014-09-02 | Method for optimizing response time of hydraulic latch-pin in cylinder deactivation rocker arm |
Country Status (4)
Country | Link |
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US (1) | US20160169064A1 (en) |
EP (1) | EP3039256B1 (en) |
CN (1) | CN105378236B (en) |
WO (1) | WO2015031887A1 (en) |
Families Citing this family (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2017053898A1 (en) * | 2015-09-25 | 2017-03-30 | Eaton Corporation | Cylinder deactivation control and methods |
CN108431390B (en) | 2016-01-19 | 2022-03-18 | ä¼é”æęŗč½åØåęéå ¬åø | Cylinder deactivation and engine braking for thermal management |
EP3445956B1 (en) * | 2016-04-21 | 2021-01-06 | Eaton Intelligent Power Limited | Valve train assembly |
CN109415956B (en) * | 2016-05-12 | 2021-08-03 | ä¼é”æęŗč½åØåęéå ¬åø | Rocker arm |
US11187162B2 (en) | 2016-08-17 | 2021-11-30 | Eaton Intelligent Power Limited | Extended coast and controlled deceleration using cylinder deactivation |
CN115263580A (en) | 2016-08-17 | 2022-11-01 | ä¼é”æęŗč½åØåęéå ¬åø | Gear selection with cylinder deactivation |
EP4062038A1 (en) * | 2019-11-20 | 2022-09-28 | Eaton Intelligent Power Limited | Latch assembly, latching device, and rocker arm |
KR20230173470A (en) | 2022-06-17 | 2023-12-27 | ķėģėģ°Øģ£¼ģķģ¬ | CDA Rocker Arm System with Oil Double Supply Line and Method thereof |
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US5431133A (en) * | 1994-05-31 | 1995-07-11 | General Motors Corporation | Low mass two-step valve lifter |
US6588394B2 (en) * | 2000-09-22 | 2003-07-08 | Delphi Technologies, Inc. | Model-based control of a solenoid-operated hydraulic actuator for engine cylinder deactivation |
US20050188930A1 (en) * | 2004-02-18 | 2005-09-01 | Best Richard R. | Valve deactivation device |
US6966291B1 (en) * | 2004-10-28 | 2005-11-22 | Delphi Technologies, Inc. | Latch timing mechanism for a two-step roller finger cam follower |
US7484487B2 (en) * | 2005-11-21 | 2009-02-03 | Eaton Corporation | Dual lift rocker arm latch mechanism and actuation arrangement therefor |
US7121241B1 (en) * | 2006-01-10 | 2006-10-17 | Eaton Corporation | Valve control system including deactivating rocker arm |
WO2011116329A2 (en) * | 2010-03-19 | 2011-09-22 | Eaton Corporation | Switching rocker arm |
US9488075B2 (en) * | 2011-11-06 | 2016-11-08 | Eaton Corporation | Latch pin assembly; rocker arm arrangement using latch pin assembly; and assembling methods |
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2014
- 2014-09-02 EP EP14840581.4A patent/EP3039256B1/en not_active Not-in-force
- 2014-09-02 CN CN201480037996.1A patent/CN105378236B/en not_active Expired - Fee Related
- 2014-09-02 WO PCT/US2014/053689 patent/WO2015031887A1/en active Application Filing
-
2016
- 2016-02-25 US US15/053,231 patent/US20160169064A1/en not_active Abandoned
Non-Patent Citations (1)
Title |
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See references of WO2015031887A1 * |
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Publication number | Publication date |
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WO2015031887A1 (en) | 2015-03-05 |
US20160169064A1 (en) | 2016-06-16 |
CN105378236B (en) | 2018-10-12 |
EP3039256A4 (en) | 2017-04-19 |
EP3039256B1 (en) | 2018-03-21 |
CN105378236A (en) | 2016-03-02 |
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