CN103835781A - Combined type engine brake device - Google Patents
Combined type engine brake device Download PDFInfo
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- CN103835781A CN103835781A CN201210487373.7A CN201210487373A CN103835781A CN 103835781 A CN103835781 A CN 103835781A CN 201210487373 A CN201210487373 A CN 201210487373A CN 103835781 A CN103835781 A CN 103835781A
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Abstract
A combined type engine brake device comprises a double-air-valve actuator, a one-air-valve actuator and a brake control mechanism, wherein the double-air-valve actuator comprises a common air valve driving mechanism, the one-air-valve actuator comprises a brake air valve driving mechanism, and the brake control mechanism simultaneously controls the common air valve driving mechanism and the brake air valve driving mechanism. When the brake control mechanism is powered on, the common air valve driving mechanism is changed into a non-operation position from an operation position, the link between the double-air-valve actuator and two air valves of an engine is cut off, and common air valve movement of the engine is eliminated. Meanwhile, the brake air valve driving mechanism is changed into an operation position from a non-operation position, the one-air-valve actuator drives one of the two air valves, and brake air valve movement of the engine is generated. According to the combined type engine brake device, the brake air valve movement and the common air valve movement are controlled by the control mechanism and are not mutually interfered, respectively independent and optimized air valve stroke curves are obtained, the brake load of the engine is reduced, and the brake performance of the engine is improved.
Description
Technical field:
The present invention relates to mechanical field, relate in particular to the valve actuation field of vehicle motor, particularly for generation of the technology of engine braking valve motion, concrete is a kind of synthetic type engine braking apparatus.
Background technique:
In prior art, the technology of the dual valve actuator of vehicle motor is behaved and is known altogether, its application history of existing more than 100 year.But due to motor discharge and braking are waited to other demand, increasing motor need to, on the basis of conventional valve motion, increase the valve motion for engine braking.In fact, adopt the engine brake of engine braking valve motion to become gradually the device that commercial car (especially more than 12 tons heavy truck) motor must be joined.
Engine braking technology is also widely known by the people.Only motor temporarily need be converted to compressor.In transfer process, cut off fuel oil, in the time that approaching end, engine piston compression stroke opens valve, allow compressed gas (being air when braking) to be released, the motor energy that pressurized gas absorbs in compression stroke, can not turn back at expansion stroke subsequently steam-cylinder piston and the bent axle of motor, but dissipate by exhaust and the radiation system of motor.Final result is slowing down of effective engine braking and car speed.
In the on-board engine applicating history of more than 100 years, what dual valve actuator adopted is all connection and the driving of mechanical type or solid chain type (non-hydraulic type), and the camming movement of motor is passed to valve, produces conventional valve motion.And engine braking valve actuator is mostly connection or the driving that adopts hydraulic type, produce braking valve motion.
In prior art, braking valve actuating mechanism, in the process of braking valve motion that produces motor, is attended by the conventional valve motion of motor, and braking valve motion can not be independent of conventional valve motion, and braking ability is restricted.
Summary of the invention:
The object of the present invention is to provide a kind of synthetic type engine braking apparatus, described this synthetic type engine braking apparatus will solve the conventional valve motion, the braking valve motion that in the braking valve motion process of motor in prior art, are attended by motor can not be independent of the technical problem that conventional valve motion, braking ability are restricted.
This synthetic type engine braking apparatus of the present invention, comprise a dual valve actuator, a single valve actuator and a brake control mechanism, described dual valve actuator comprises a conventional valve actuating mechanism, described single valve actuator comprises a braking valve actuating mechanism, described conventional valve actuating mechanism and braking valve actuating mechanism are integrated in the existing component of motor, described brake control mechanism is controlled conventional valve actuating mechanism and braking valve actuating mechanism simultaneously, it is characterized in that: in the time that described brake control mechanism is connected, conventional valve actuating mechanism becomes off position from operating position, between two valves of dual valve actuator and motor, link disconnection, cancel the conventional valve motion of motor, meanwhile, braking valve actuating mechanism becomes operating position from off position, and single valve actuator drives in described two valves, produces the braking valve motion of motor.
Further, the conventional valve actuating mechanism of described synthetic type engine braking apparatus is solid chain type driving mechanism or hydraulic type driving mechanism.
Further, the braking valve actuating mechanism of described synthetic type engine braking apparatus is solid chain type driving mechanism or hydraulic type driving mechanism.
Further, the braking valve actuating mechanism of described synthetic type engine braking apparatus and conventional valve actuating mechanism are integrated in the air valve bridge of motor.
Further, the braking valve actuating mechanism of described synthetic type engine braking apparatus is integrated in the rocking arm of motor.
Further, the dual valve actuator of described synthetic type engine braking apparatus also comprises conventional cam and the conventional rocking arm of motor, when described conventional valve actuating mechanism is during in operating position, two valves that move through conventional rocking arm and pass to motor of described conventional cam, produce the conventional valve motion of motor.
Further, single valve actuator of described synthetic type engine braking apparatus also comprises brake cam and brake rocker arm, when described braking valve actuating mechanism is during in operating position, the brake rocker arm that moves through of described brake cam passes in described two valves, produces the braking valve motion of motor.
Further, the brake cam of described synthetic type engine braking apparatus contains compression releasing brake boss, EGR boss, exhaust releasing brake boss and the anti-boss that fills of exhaust.
Further, the compression releasing brake boss of described synthetic type engine braking apparatus is positioned at the near of motor, described EGR boss is positioned near the air inlet lower dead center of motor, described exhaust releasing brake boss is positioned near the exhaust top dead center of motor, and the anti-boss that fills of described exhaust is between compression releasing brake boss and exhaust releasing brake boss.
Working principle of the present invention is: in the time that needs motor is converted to braking valve motion from conventional valve motion, the brake control mechanism of motor is connected, conventional valve actuating mechanism becomes off position from operating position, between two valves of dual valve actuator and motor, link disconnection, lose the conventional valve motion of motor; Meanwhile, braking valve actuating mechanism becomes operating position from off position, and single valve actuator drives a valve in two valves by braking valve actuating mechanism, produces the braking valve motion of motor.In the time not needing to brake valve motion, the brake control mechanism of motor disconnects, conventional valve actuating mechanism becomes operating position from off position, and dual valve actuator drives two valves of motor by conventional valve actuating mechanism, produces the conventional valve motion of motor; Meanwhile, braking valve actuating mechanism becomes off position from operating position, between single valve actuator and valve, links disconnections, the braking valve motion of cancellation motor.
The present invention compares with prior art, and its effect is actively with obvious.Brake control mechanism of the present invention is controlled conventional valve actuating mechanism and braking valve actuating mechanism simultaneously, in producing the braking valve motion of motor, eliminate the conventional valve motion of motor, conventional valve motion and the mutual noninterference of braking valve motion, obtained independently, performance better brakes valve motion.
Accompanying drawing explanation:
Fig. 1 be an embodiment of synthetic type engine braking apparatus of the present invention at brake control mechanism in disconnecting schematic diagram when (oil extraction) state.
Fig. 2 be an embodiment of synthetic type engine braking apparatus of the present invention at brake control mechanism in connecting schematic diagram when (fuel feeding) state.
Fig. 3 is that the brake control mechanism of synthetic type engine braking apparatus of the present invention is in disconnecting the schematic diagram of (oil extraction) state.
Fig. 4 is that the brake control mechanism of synthetic type engine braking apparatus of the present invention is in connecting the schematic diagram of (fuel feeding) state.
Fig. 5 is second embodiment's of synthetic type engine braking apparatus of the present invention structural arrangement schematic diagram.
Embodiment:
Embodiment 1:
Fig. 1, Fig. 2, Fig. 3 and Fig. 4 are used for describing embodiment one.
As depicted in figs. 1 and 2, the brake control mechanism 50 of synthetic type engine braking apparatus of the present invention is in connecting the position of (fuel feeding) and disconnection (oil extraction).Solenoid valve 51 in figure is two-position three way type.In the time that the positive and negative electrode 55 and 57 of brake control mechanism 50 is connected (Fig. 1), the valve body 58 of solenoid valve 51 is opened oil-feed port 111 downwards, close oil drain out 222, the low-pressure oil (lubricant oil) of motor flows to conventional valve actuating mechanism 100 and braking valve actuating mechanism 100b(Fig. 4 from fluid passage simultaneously).In the time that the positive and negative electrode 55 and 57 of brake control mechanism 50 disconnects (Fig. 2), the valve body 58 of solenoid valve 51 is upwards closed oil-feed port 111, open unloading port 222 simultaneously, the low-pressure oil (lubricant oil) of motor stops flowing to conventional valve actuating mechanism 100 and braking valve actuating mechanism 100b(Fig. 3), on the contrary from fluid passage and the outside oil extraction of oil drain out 222.
As shown in Figure 3, when brake control mechanism 50 is in the time disconnecting (oil extraction) position (Fig. 2), the conventional valve actuating mechanism 100 of dual valve actuator 200 is in operating position.In Fig. 3, dual valve actuator 200 comprises conventional cam 230, tappet roller 235, conventional rocking arm 210, conventional valve clearance regulating system, conventional valve actuating mechanism 100 and air valve bridge 400.Conventional valve clearance regulating system comprises adjusting screw 110, tighten up nut 105 and resemble foot pad 114, two valves 301 and 302 of motor are positioned at below air valve bridge 400 both sides, be biased on the valve seat 320 of engine cylinder-body 500 by the valve spring 311 and 312 of motor, stop gas to flow between engine cylinder and outlet pipe 600.Conventional rocking arm 210 is arranged on conventional pitman arm shaft 205 rock typely, and one end of conventional rocking arm 210 is connected with conventional cam 230 by roller 235, and conventional cam 230 has a conventional boss 220 on interior basic circle 225; The other end of conventional rocking arm 210 is connected with the conventional valve actuating mechanism 100 in air valve bridge 400.
In Fig. 3, conventional valve actuating mechanism 100 comprises piston (or plunger) 260, piston spring 277, one or more lockup piston (or plunger) 160 and the locking spring 177 of the center hole 290 that is positioned at air valve bridge 400.The lockup piston 160 in the horizontal piston hole 190 that is positioned at air valve bridge 400 is pushed the annular groove 275 on piston 260 by locking spring 177, stoped the relative movement between piston 260 and air valve bridge 400, formed a kind of solid link (or mechanical linkages).Two valves 301 and 302 that move through conventional rocking arm 210, conventional valve actuating mechanism 100 in operating position and air valve bridge 400 and pass to motor of conventional cam 230, it is is periodically opened and closed, produce the conventional valve motion 20 of motor, for routine (igniting) running of motor.
In this simultaneously, the braking valve actuating mechanism 100b of the single valve actuator 200b in Fig. 3 is in off position.Single valve actuator 200b comprises brake cam 230b, tappet roller 235b, brake rocker arm 210b, auxiliary valve clearance regulating system and braking valve actuating mechanism 100b.Auxiliary valve clearance regulating system comprises adjusting screw 110b and tightens up nut 105b.It is upper that brake rocker arm 210b is arranged on brake rocker arm axle 205b rock typely, and secondary spring 198b is biased in one end of brake rocker arm 210b on brake cam 230b by roller 235b.Braking valve actuating mechanism 100b in the other end of brake rocker arm 210b and air valve bridge 400 is adjacent.Brake cam 230b has one or more (in Fig. 3 being two) braking boss 232 and 233 on interior basic circle 225b.
Braking valve actuating mechanism 100b in Fig. 3 comprises that brake piston (or plunger) 160(in the horizontal piston hole 190 of a side of the air valve bridge 400 that is positioned at valve 301 tops is the lockup piston of conventional valve actuating mechanism 100 simultaneously), brake spring 177(is the locking spring of conventional valve actuating mechanism 100 simultaneously) and positioning means.Positioning means is made up of the groove 137 on brake piston 160 and the pin 142 being fixed on air valve bridge 400, with deciding the stroke of brake piston 160, and prevents its rotation simultaneously.Brake spring 177 pushes piston 160 in the piston hole 190 of air valve bridge 400, brake piston 160 not operation surface 145 is above positioned at below adjusting screw 110b, form the gap 132 between piston 160 and brake rocker arm 210b, disconnected linking between single valve actuator 200b and valve 301, the motion of brake cam 230b can not pass to valve 301(cancels or has lost the braking valve motion 10 of motor).
As shown in Figure 4, when brake control mechanism 50 is in the time connecting (fuel feeding) position (Fig. 1), the conventional valve actuating mechanism 100 of dual valve actuator 200 is in off position.The machine oil of motor is by the oil duct 211 and 212 in conventional pitman arm shaft 205, oil duct 213 and 214 in conventional rocking arm 210, oil duct 115 in valve clearance adjusting screw 110 enters oil duct 215 and the annular groove 275 in piston 260, oil pressure overcomes the active force of locking spring (brake spring) 177, lockup piston (brake piston) 160 is interior toward extrapolation from the horizontal piston hole 190 of air valve bridge 400, depart from the annular groove 275 on piston 260, allow the relative movement between piston 260 and air valve bridge 400, disconnect linking between two valves 301 and 302 of dual valve actuator 200 and motor, the motion of conventional cam 230 can not transmitted two valves 301 and 302(cancellations or lost the conventional valve motion 20 of motor).Piston spring 277 is placed in above the spring seat 278 being fixed on air valve bridge 400, and piston 260 is setovered upwards, contacts all the time with conventional rocking arm 210, plays the anti-effect flying off.
Meanwhile, the braking valve actuating mechanism 100b of the single valve actuator 200b in Fig. 4 is in operating position.When the machine oil of motor overcomes the active force of brake spring (locking spring) 177, brake piston (lockup piston) 160 departed to annular groove piston 260 275 from piston hole 190 is interior to extrapolation time, brake piston 160 operating surface 140 has above moved on to below adjusting screw 110b, piston 160 gap 132 is above eliminated, be connected to form solid with brake rocker arm 210b and link (or mechanical linkages), brake cam 230b moves through brake rocker arm 210b, braking valve actuating mechanism 100b and air valve bridge 400 pass to a valve 301 in two valves, produce the braking valve motion 10 of motor.
Embodiment 2:
As shown in Figure 5, the another kind of arrangement mode of conventional rocking arm 210 and brake rocker arm 210b in compound engine braking device of the present invention.The conventional rocking arm 210 of dual valve actuator 200 and the brake rocker arm 210b of single valve actuator 200b are arranged on same pitman arm shaft abreast, on conventional pitman arm shaft 205.The working principle of the present embodiment and operating method are identical with embodiment one, are not described in detail in this.
In a word, compound engine braking device of the present invention, by a brake control mechanism 50, is controlled the conventional valve actuating mechanism 100 of dual valve actuator 200 and the braking valve actuating mechanism 100b of single valve actuator 200b simultaneously.When brake control mechanism 50 is in the time disconnecting (oil extraction) position (Fig. 2), the conventional valve actuating mechanism 100 of dual valve actuator 200 is in operating position, and the braking valve actuating mechanism 100b of single valve actuator 200b is in off position (Fig. 3), 301 and 302, two valves of motor produce conventional valve motion, do not brake valve motion.When brake control mechanism 50 is in the time connecting (fuel feeding) position (Fig. 1), the conventional valve actuating mechanism 100 of dual valve actuator 200 is in off position, and the braking valve actuating mechanism 100b of single valve actuator 200b is in operating position (Fig. 4), two valves 301 and 302 of motor lose conventional valve motion, and one of them valve 301 produces braking valve motion.
Also have, the braking valve actuating mechanism 100b of the conventional valve actuating mechanism 100 of dual valve actuator 200 of the present invention and single valve actuator 200b is integrated in the air valve bridge 400 of motor, and simultaneously by a brake control mechanism control, simple in structure, reduce cost, increase reliability, avoided the increase of motor height and weight.
The braking valve motion of motor of the present invention and conventional valve motion mutual noninterference, brake cam 230b can contain compression releasing brake boss, EGR boss, exhaust releasing brake boss and the anti-boss that fills of exhaust.Compression releasing brake boss is positioned at the near of motor, EGR boss is positioned near the air inlet lower dead center of motor, exhaust releasing brake boss is positioned near the exhaust top dead center of motor, and the anti-boss that fills of exhaust is between compression releasing brake boss and exhaust releasing brake boss.In the time that motor need to be braked, brake control mechanism 50 is arranged on to connection (fuel feeding) position (Fig. 1), conventional valve actuating mechanism 100 becomes off position (Fig. 4) from operating position, between exhaust valve actuator 200 and two exhaust valves 301 and 302, link disconnection, cancel the conventional valve motion of motor.In this simultaneously, braking valve actuating mechanism 100 becomes operating position from off position, and four motions that boss produces above brake cam 230b, all pass to 301 in two exhaust valves, produces engine braking motion.This braking valve motion that there is no conventional valve motion, is conducive to improve engine braking performance, reduces engine braking load.
Above-mentioned explanation has comprised a lot of concrete mode of executions, and this should not be regarded as limitation of the scope of the invention, but as representing concrete illustrations more of the present invention, many other develop all and likely therefrom produce.For instance, the compound engine braking device showing here, not only can be for generation of the braking valve motion of engine braking, also can be for generation of other valve motion such as EGRs.
In addition, the compound engine braking device showing here, not only can be used for overhead cam engine, also can be used for push rod/pushing type motor; Not only can be used for driving exhaust valve, also can be used to drive into valve.
Further, the dual valve actuator or the single valve actuator that show here, can be not only rocker arm body, can be also housing structure etc.; Can be not only mechanical type (or solid chain type), can be also hydraulic type.
In addition, the conventional valve actuating mechanism showing here can be not only solid chain type driving mechanism, can be also hydraulic type driving mechanism; Equally, braking valve actuating mechanism not only can be consolidated chain type driving mechanism, can be also hydraulic type driving mechanism.Conventional valve actuating mechanism or braking valve actuating mechanism not only can be integrated in air valve bridge, also can be integrated in rocking arm, or be placed in casing etc.
Also have, kind and the mounting type of conventional valve actuating mechanism or braking valve actuating mechanism can be varied, its component also can adopt different forms, and such as the shape of piston (plunger), shape, the shape of annular groove etc. of spring, the lockup piston of cylindricality can be also lock ball.Lockup piston and brake piston not necessarily share, and can be also component separately, different; Locking spring and brake spring can be also different two or more springs.Operating surface on brake piston and not operation surface etc. can be inclined-plane or other action face.
In addition, the two-position three way magnetic valve 51 of engine braking control mechanism 50 can be also the control mechanism of other form, such as two-position two-way solenoid valve.
Therefore, scope of the present invention should not decided by above-mentioned concrete illustration, but is decided by affiliated claim and the suitable right of law thereof.
Claims (9)
1. a synthetic type engine braking apparatus, comprise a dual valve actuator, a single valve actuator and a brake control mechanism, described dual valve actuator comprises a conventional valve actuating mechanism, described single valve actuator comprises a braking valve actuating mechanism, described conventional valve actuating mechanism and braking valve actuating mechanism are integrated in the existing component of motor, described brake control mechanism is controlled conventional valve actuating mechanism and braking valve actuating mechanism simultaneously, it is characterized in that: in the time that described brake control mechanism is connected, conventional valve actuating mechanism becomes off position from operating position, between two valves of dual valve actuator and motor, link disconnection, cancel the conventional valve motion of motor, meanwhile, braking valve actuating mechanism becomes operating position from off position, and single valve actuator drives in described two valves, produces the braking valve motion of motor.
2. synthetic type engine braking apparatus as claimed in claim 1, is characterized in that: described conventional valve actuating mechanism is solid chain type driving mechanism or hydraulic type driving mechanism.
3. synthetic type engine braking apparatus as claimed in claim 1, is characterized in that: described braking valve actuating mechanism is solid chain type driving mechanism or hydraulic type driving mechanism.
4. synthetic type engine braking apparatus as claimed in claim 1, is characterized in that: described conventional valve actuating mechanism and braking valve actuating mechanism are integrated in the air valve bridge of motor.
5. synthetic type engine braking apparatus as claimed in claim 1, is characterized in that: described braking valve actuating mechanism is integrated in the rocking arm of motor.
6. synthetic type engine braking apparatus as claimed in claim 1, it is characterized in that: described dual valve actuator also comprises conventional cam and the conventional rocking arm of motor, when described conventional valve actuating mechanism is during in operating position, two valves that move through conventional rocking arm and pass to motor of described conventional cam, produce the conventional valve motion of motor.
7. synthetic type engine braking apparatus as claimed in claim 1, it is characterized in that: described single valve actuator also comprises brake cam and brake rocker arm, when described braking valve actuating mechanism is during in operating position, the brake rocker arm that moves through of described brake cam passes in described two valves, produces the braking valve motion of motor.
8. synthetic type engine braking apparatus as claimed in claim 7, is characterized in that: described brake cam contains compression releasing brake boss, EGR boss, exhaust releasing brake boss and the anti-boss that fills of exhaust.
9. synthetic type engine braking apparatus as claimed in claim 8, it is characterized in that: described compression releasing brake boss is positioned at the near of motor, described EGR boss is positioned near the air inlet lower dead center of motor, described exhaust releasing brake boss is positioned near the exhaust top dead center of motor, and the anti-boss that fills of described exhaust is between compression releasing brake boss and exhaust releasing brake boss.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210487373.7A CN103835781B (en) | 2012-11-26 | 2012-11-26 | Combined type engine brake device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210487373.7A CN103835781B (en) | 2012-11-26 | 2012-11-26 | Combined type engine brake device |
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| CN103835781A true CN103835781A (en) | 2014-06-04 |
| CN103835781B CN103835781B (en) | 2017-04-19 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201210487373.7A Expired - Fee Related CN103835781B (en) | 2012-11-26 | 2012-11-26 | Combined type engine brake device |
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Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105089731A (en) * | 2015-09-08 | 2015-11-25 | 朱志超 | Valve transmission set capable of achieving stepless variable valve lift and variable valve timing |
| CN106089348A (en) * | 2016-08-23 | 2016-11-09 | 潍柴动力股份有限公司 | A kind of air valve bridge and include the electromotor of this air valve bridge |
| CN110107373A (en) * | 2019-04-23 | 2019-08-09 | 东风商用车有限公司 | A kind of the engine air raft of pontoons structure and its control method of lift range variable |
| CN112696247A (en) * | 2019-10-07 | 2021-04-23 | 现代自动车株式会社 | Compression release engine brake |
| DE102021124460A1 (en) | 2021-09-22 | 2023-03-23 | Schaeffler Technologies AG & Co. KG | Arrangement for fastening an actuator for actuating a switchable valve contact carrier for a valve train of an internal combustion engine |
| DE102021124458A1 (en) | 2021-09-22 | 2023-03-23 | Schaeffler Technologies AG & Co. KG | Valve contact carrier for a valve train of an internal combustion engine and rocker arm arrangement for a valve train of an internal combustion engine |
| DE102021124457A1 (en) | 2021-09-22 | 2023-03-23 | Schaeffler Technologies AG & Co. KG | Valve contact carrier for a valve train of an internal combustion engine, actuator for switching such a valve contact carrier and rocker arm arrangement for a valve train of an internal combustion engine |
| DE102021124456A1 (en) | 2021-09-22 | 2023-03-23 | Schaeffler Technologies AG & Co. KG | Valve contact carrier for a valve train of an internal combustion engine, actuator for switching such a valve contact carrier and rocker arm arrangement for a valve train of an internal combustion engine |
| DE102022108259A1 (en) | 2022-04-06 | 2023-10-12 | Schaeffler Technologies AG & Co. KG | Assembly unit for a switchable valve train of a heavy-duty internal combustion engine |
| DE102022109898A1 (en) | 2022-04-25 | 2023-10-26 | Schaeffler Technologies AG & Co. KG | Assembly for a variable valve train of a heavy-duty internal combustion engine, with a switchable bridge and with at least one e-actuator |
| DE102022113655A1 (en) | 2022-05-31 | 2023-11-30 | Schaeffler Technologies AG & Co. KG | Structural unit for a variable valve train of a heavy-duty internal combustion engine with a rocker arm acting on a switchable bridge |
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Cited By (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105089731B (en) * | 2015-09-08 | 2017-12-08 | 朱志超 | The valve train group of electrodeless lift range variable and VVT can be achieved |
| CN105089731A (en) * | 2015-09-08 | 2015-11-25 | 朱志超 | Valve transmission set capable of achieving stepless variable valve lift and variable valve timing |
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| CN106089348A (en) * | 2016-08-23 | 2016-11-09 | 潍柴动力股份有限公司 | A kind of air valve bridge and include the electromotor of this air valve bridge |
| CN110107373A (en) * | 2019-04-23 | 2019-08-09 | 东风商用车有限公司 | A kind of the engine air raft of pontoons structure and its control method of lift range variable |
| CN112696247A (en) * | 2019-10-07 | 2021-04-23 | 现代自动车株式会社 | Compression release engine brake |
| DE102021124460A1 (en) | 2021-09-22 | 2023-03-23 | Schaeffler Technologies AG & Co. KG | Arrangement for fastening an actuator for actuating a switchable valve contact carrier for a valve train of an internal combustion engine |
| DE102021124458A1 (en) | 2021-09-22 | 2023-03-23 | Schaeffler Technologies AG & Co. KG | Valve contact carrier for a valve train of an internal combustion engine and rocker arm arrangement for a valve train of an internal combustion engine |
| DE102021124457A1 (en) | 2021-09-22 | 2023-03-23 | Schaeffler Technologies AG & Co. KG | Valve contact carrier for a valve train of an internal combustion engine, actuator for switching such a valve contact carrier and rocker arm arrangement for a valve train of an internal combustion engine |
| DE102021124456A1 (en) | 2021-09-22 | 2023-03-23 | Schaeffler Technologies AG & Co. KG | Valve contact carrier for a valve train of an internal combustion engine, actuator for switching such a valve contact carrier and rocker arm arrangement for a valve train of an internal combustion engine |
| DE102022108259A1 (en) | 2022-04-06 | 2023-10-12 | Schaeffler Technologies AG & Co. KG | Assembly unit for a switchable valve train of a heavy-duty internal combustion engine |
| DE102022109898A1 (en) | 2022-04-25 | 2023-10-26 | Schaeffler Technologies AG & Co. KG | Assembly for a variable valve train of a heavy-duty internal combustion engine, with a switchable bridge and with at least one e-actuator |
| DE102022113655A1 (en) | 2022-05-31 | 2023-11-30 | Schaeffler Technologies AG & Co. KG | Structural unit for a variable valve train of a heavy-duty internal combustion engine with a rocker arm acting on a switchable bridge |
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| CN103835781B (en) | 2017-04-19 |
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