CN110344909B - Electric engine braking device - Google Patents

Electric engine braking device Download PDF

Info

Publication number
CN110344909B
CN110344909B CN201910758421.3A CN201910758421A CN110344909B CN 110344909 B CN110344909 B CN 110344909B CN 201910758421 A CN201910758421 A CN 201910758421A CN 110344909 B CN110344909 B CN 110344909B
Authority
CN
China
Prior art keywords
plunger
hole
sliding
rocker arm
engine
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.)
Active
Application number
CN201910758421.3A
Other languages
Chinese (zh)
Other versions
CN110344909A (en
Inventor
俞黎明
俞振寰
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Zhejiang Liming Zhizao Co ltd
Original Assignee
Zhejiang Liming Zhizao Co ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Zhejiang Liming Zhizao Co ltd filed Critical Zhejiang Liming Zhizao Co ltd
Priority to CN201910758421.3A priority Critical patent/CN110344909B/en
Priority to PCT/CN2019/103248 priority patent/WO2021031230A1/en
Priority to EP19908081.3A priority patent/EP3800332B1/en
Publication of CN110344909A publication Critical patent/CN110344909A/en
Application granted granted Critical
Publication of CN110344909B publication Critical patent/CN110344909B/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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
    • F01L13/06—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for braking
    • F01L13/065—Compression release engine retarders of the "Jacobs Manufacturing" type
    • 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
    • F01L1/181—Centre pivot rocking arms
    • 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
    • F01L1/26—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder
    • F01L1/267—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder with means for varying the timing or the lift of the 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
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/06—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for braking
    • 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
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/20—Valve-gear or valve arrangements actuated non-mechanically by electric means
    • 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
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • F01L1/053—Camshafts overhead type
    • 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
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/08—Shape of cams
    • 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
    • F01L1/46—Component parts, details, or accessories, not provided for in preceding subgroups
    • F01L2001/467—Lost motion springs
    • 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
    • F01L2013/10—Auxiliary actuators for variable valve timing
    • F01L2013/103—Electric motors
    • 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
    • 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
    • F01L2800/00—Methods of operation using a variable valve timing mechanism
    • F01L2800/05—Timing control under consideration of oil condition
    • 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
    • F01L2800/00—Methods of operation using a variable valve timing mechanism
    • F01L2800/06—Timing or lift different for valves of same cylinder
    • 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
    • F01L2800/00—Methods of operation using a variable valve timing mechanism
    • F01L2800/10—Providing exhaust gas recirculation [EGR]
    • 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
    • F01L2820/00—Details on specific features characterising valve gear arrangements
    • F01L2820/01—Absolute values
    • 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
    • F01L2820/00—Details on specific features characterising valve gear arrangements
    • F01L2820/03—Auxiliary actuators
    • F01L2820/031—Electromagnets

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)

Abstract

An electric engine brake device. The method is characterized in that: including control mechanism and electric drive mechanism, control mechanism includes the casing, carries out plunger, slip subassembly includes slider, first elastic component, transmission plunger, second elastic component, the transmission plunger has the first position that will set up completely in the slider and stretches out the slider and connect slider and casing into integrative second position, electric drive mechanism includes actuating motor, slide grillage, slide, contact leaf spring, actuating motor can promote the slide along slide grillage to slide, drive contact leaf spring promotes and carries out the plunger and slide, drive transmission plunger removal and make it keep in the second position. The engine braking control device has the advantages that the electric driving mechanism and the control mechanism are arranged, the motor is used for controlling, the existing engine oil is used as a working or driving control medium, the reliability risk caused by the engine oil is eliminated, the engine braking use area is increased, the engine braking entering and exiting time is shortened, the fuel consumption is reduced, and the engine braking performance is graded and finer.

Description

Electric engine braking device
Technical Field
The invention relates to a medium and heavy diesel and natural gas engine, in particular to an electric engine braking device.
Background
The mountain area of China is numerous, the mountain area is large, the mountain area is about 69 percent of the total area of China, a heavy truck is used for braking frequently in a mountain area on a downhill road section, a driver can absorb larger energy in a short time by using the service brake, but the surface temperature of a friction pair between a brake drum and a brake shoe is increased along with the increase of the braking time, the friction coefficient is reduced, and finally, the dangerous condition of the reduction of the braking efficiency and even the braking failure is caused, so that serious traffic accidents are caused. In order to improve the driving safety of heavy commercial vehicles, an auxiliary braking system needs to be added on the basis of service braking to ensure that the vehicle has a constant braking force in the downhill process.
Auxiliary braking systems for vehicles are mainly divided into two categories: retarder and engine braking system. The engine braking system is widely used due to the advantages of simple structure, convenient installation, low price and the like.
The engine braking technology is that a driver lifts an accelerator pedal in the running process of an automobile, releases a clutch, and utilizes compression resistance generated in the compression stroke of the engine and the action of air inlet and outlet resistance and friction force on braking force formed by driving wheels to brake the automobile. The engine braking technology is divided into three types of compression engine braking, air leakage type engine braking and partial air leakage type engine braking. Compression engine braking is opening an exhaust valve or auxiliary valve near compression top dead center; the bleeder type engine brake is to open the exhaust valve throughout the engine cycle; partial bleeder engine braking is the opening of the exhaust valve for the majority of the engine cycle. The application of the engine braking technology effectively reduces the use frequency of the service brake, and when the whole vehicle is used on steep roads such as downhill slopes, rugged mountain roads and the like, the engine braking can be avoided, and the temperature of the friction plate of the brake is increased, so that the braking force is reduced and even is disabled due to long-time use of the brake.
The engine braking device is capable of providing one or more auxiliary valve lifts for implementing an engine braking function. There are several patents related to the application of this technology, mainly including one or several additional auxiliary lifts outside the main lift of the cam, and also adding a cam specially used for braking, the engine braking device can make the auxiliary lift active (implement engine braking function) or make it inactive according to the requirement of engine operation.
Patent CN200980158946.8 is a dedicated rocker arm engine brake applied by jacobs vehicle systems company, and discloses a system for actuating engine exhaust valves, the system including a rocker shaft having a control fluid supply passage, and an exhaust rocker arm pivotally mounted on the rocker shaft. The engine brake rocker arm may have: a central opening, a hydraulic passage connecting the central opening with the control valve, and a fluid passage connecting the control valve with the actuator piston assembly.
Patent CN201080019296.1 is a jacob vehicle system application for a lost motion variable valve actuation system for engine braking and early exhaust valve opening, which may include a first cam having a compression release lobe and an early exhaust valve opening lobe connected to a hydraulic lost motion system having a first rocker arm. A hydraulically actuated piston may be selectively extended from the hydraulic lost motion system to provide compression release actuation or early exhaust valve opening actuation to the exhaust valve. The hydraulically actuated piston may be provided in a fixed housing as a slave piston in a master-slave piston circuit or, alternatively, be slidably disposed in the rocker arm as a hydraulic piston.
Patent CN200910140026.5 is an engine brake device with a valve assist control unit and method for engine braking, filed by german commercial vehicle division, the exhaust valve of which is connected to the camshaft by means of a mechanical connection comprising a hydraulic valve assist control unit. The hydraulic valve assist control unit holds the exhaust valve in a temporarily open position. The hydraulic valve auxiliary control unit can be switched on and off by means of an auxiliary oil circuit which is additionally arranged with respect to the main oil circuit of the internal combustion engine.
The engine braking patents all use engine oil as a medium for transmitting the motion law of the valve, and the motion law of the braking valve is greatly dependent on some characteristics of the engine oil, such as the lift of the braking valve is lost when the air content of the engine oil is too high, thereby affecting the braking performance. In addition, when the temperature of the engine oil is too low and the viscosity of the engine oil is too high, the normal operation of engine braking is also affected. Therefore, the engine brake technology requires that the engine oil temperature is higher than a certain limit value (such as 40 ℃) so that the engine brake can be inserted, and thus the service condition of the engine brake can be limited. And further, as engine braking driven by engine oil is adopted, the intervention and withdrawal time of the engine braking is generally longer (more than 0.4 s), so that the switching process of the engine braking and the ignition state is influenced, and the transient switching process of the engine is unstable.
Disclosure of Invention
In order to overcome the defects of the background technology, the invention provides an electric engine braking device.
The invention adopts the technical scheme that: an electric engine brake device comprising
A rocker shaft;
a camshaft disposed in parallel with the rocker shaft and having an exhaust cam and an auxiliary cam disposed adjacently;
The exhaust valve comprises a first exhaust valve, a second exhaust valve and a valve bridge transversely arranged on the first exhaust valve and the second exhaust valve;
An exhaust rocker arm rotatably mounted on the rocker shaft, the front end of the exhaust rocker arm being in corresponding contact with the valve bridge, and the rear end of the exhaust rocker arm being in corresponding contact with the exhaust cam;
An auxiliary rocker arm rotatably mounted on the rocker arm shaft and disposed adjacent to the exhaust rocker arm with its rear end corresponding to the auxiliary cam;
an elastic member capable of holding the auxiliary rocker arm in contact with the auxiliary cam;
The sliding pin is arranged in the valve bridge, one end of the sliding pin is contacted with the first exhaust valve, and the other end of the sliding pin penetrates through the valve bridge;
the control mechanism is arranged at the front end of the auxiliary rocker arm and corresponds to the sliding pin, and comprises a shell, an execution plunger and a sliding assembly, wherein a first transverse hole and a longitudinal groove are formed in the shell, the lower end of the longitudinal groove is open, the upper end of the longitudinal groove penetrates through the first transverse hole and is intersected with the first transverse hole, the execution plunger is arranged in the first transverse hole in a sliding manner, the sliding assembly is arranged in the longitudinal groove in a sliding manner, one end of the execution plunger extends out of the first transverse hole, the other end of the execution plunger abuts against the sliding assembly, the sliding assembly comprises a sliding block, a first elastic piece, a transmission plunger and a second elastic piece, the sliding block is in circumferential limiting axial sliding fit with the longitudinal groove, the lower end of the sliding block extends downwards out of the longitudinal groove, a second transverse hole corresponding to the first transverse hole is further arranged on the sliding block, the first elastic piece can drive the sliding block to move downwards and enable the second transverse hole to coincide with the first transverse hole, the length of the transmission plunger is smaller than or equal to the length of the second transverse hole, the second elastic piece can drive the second plunger to move towards the second end face and enable the second end face to be completely flush with the second end face of the second plunger to be arranged in the second end face opposite to the first end of the piston;
The electric driving mechanism comprises an executing motor, a sliding plate frame, a sliding plate and a contact leaf spring, wherein the sliding plate frame is arranged above the auxiliary rocker arm, the sliding plate and the rocker arm shaft are arranged in parallel and are arranged on the sliding plate frame in a sliding mode, the contact leaf spring is arranged on the sliding plate and is in corresponding contact with the executing plunger, and the output end of the executing motor is in linkage fit with the sliding plate to push the sliding plate to slide along the sliding plate frame.
The upper end of the longitudinal groove is provided with a spring groove, the lower end of the longitudinal groove is provided with a first limiting ring, the sliding block is in a convex shape, the lower end of the sliding block penetrates through the first limiting ring and is in limiting fit with the first limiting ring, the first elastic piece is a spring and is arranged in the spring groove, and two ends of the first elastic piece are respectively propped against the shell and the sliding block.
The second transverse hole is a stepped hole and sequentially comprises a large hole, a middle hole and a small hole, and the small hole is the same as the first transverse hole; the transmission plunger is matched with the small hole, a first annular boss matched with the middle hole is formed on the outer ring of the transmission plunger and is in a cross shape, a second limiting ring is installed in the large hole and is in limiting fit with the first annular boss of the transmission plunger, the second elastic piece is a spring and is sleeved outside the transmission plunger, and two ends of the second elastic piece respectively abut against the sliding block and the first annular boss.
The execution plunger outer ring is provided with a second annular boss which is in a cross shape integrally, a third limiting ring is arranged at the end part of the first transverse hole, and the execution plunger penetrates through the third limiting ring to extend out of the first transverse hole and is in limiting fit with the third limiting ring through the second annular boss.
The front end of the auxiliary rocker arm is provided with a longitudinal hole, a longitudinal guide groove is formed in the side wall of the longitudinal hole, the upper end of the longitudinal hole is provided with an adjusting bolt, and the lower end of the longitudinal hole is provided with a fourth limiting ring; the shell is arranged in the longitudinal hole in a sliding way, the execution plunger extends out of the auxiliary rocker arm through the longitudinal guide groove, and the sliding block extends downwards to the lower part of the longitudinal hole through the fourth limiting ring; and a third elastic piece is arranged between the fourth limiting ring and the shell, and the third elastic piece can drive the shell to keep contact with the adjusting bolt.
The two longitudinal guide grooves are symmetrically arranged on the side wall of the longitudinal hole; two guide bosses are arranged on two sides of the shell, and the whole shell is in a cross shape; the guide bosses are correspondingly arranged in the longitudinal guide grooves, and the first transverse holes penetrate through the two guide bosses.
The actuating motor is a rotating motor, an actuating rod which is perpendicular to the actuating motor is arranged on an output shaft of the actuating motor, an actuating hole which is matched with the actuating rod is formed in the sliding plate, and the actuating rod penetrates through the actuating hole.
The actuating motor is a linear motor, and the sliding plate is provided with a guide frame corresponding to the output end of the actuating motor; and a reset elastic piece is arranged between the sliding plate frame and the contact leaf spring.
The working process of the engine braking device comprises the following steps:
when the engine works normally, the execution motor does not work, the transmission plunger is in a first position under the action of the second elastic piece, the sliding block and the shell are in an unlocked state, when the auxiliary cam lift drives the auxiliary rocker arm to rotate, the sliding pin is in contact with the sliding block, the sliding block is driven to overcome the elastic force of the first elastic piece to move upwards, the elastic force of the first elastic piece is insufficient to drive the sliding pin to realize exhaust, the movement of the exhaust valve is not influenced, and the normal work of the engine is ensured.
When the engine is braked, the motor is executed, the slide plate and the contact leaf spring push the execution plunger to act, the execution plunger pushes the transmission plunger to enter the second transverse hole, meanwhile, the transmission plunger moves against the elastic force of the second elastic piece and stretches out of the second transverse hole to be in a second position, so that the slide block and the shell are in a locking state, and when the auxiliary cam lift drives the auxiliary rocker arm to rotate, the slide block is contacted with the slide pin and drives the slide pin to realize the movement opening of the first exhaust valve, thereby realizing the purpose of engine braking.
When the engine returns to normal operation, the motor is executed, the sliding plate and the contact leaf spring are reset, the transmission plunger returns to the first position under the action of the second elastic piece, the execution plunger is pushed out of the second transverse hole, the sliding block and the shell are in an unlocked state, when the auxiliary cam lift drives the auxiliary rocker arm to rotate, the sliding pin is contacted with the sliding block, the sliding block is driven to overcome the elastic force of the first elastic piece to move upwards, the elastic force of the first elastic piece is insufficient to drive the sliding pin to realize exhaust, the movement of the exhaust valve is not influenced, and the normal operation of the engine is ensured.
The beneficial effects of the invention are as follows: 1. Eliminating reliability risks brought by using engine oil: the engine braking device is driven by an electric control mechanism, so that the problems of unstable idle speed and white smoke generation caused by the false start of a braking function due to high viscosity and high pressure of engine oil when the engine is started are solved;
2. Increasing engine brake application area: the existing hydraulic or fixed chain engine brake uses engine oil as a working medium, so that certain requirements on the engine oil temperature and the engine oil pressure are met, and if the engine oil temperature is more than 40 ℃, the engine brake can be interposed, so that the engine brake is limited to be used when the whole vehicle is just started, and the electric control mechanism is used for driving and is not limited by the conditions, and the engine brake can be used at any time after the whole vehicle is started;
3. the engine brake entering and exiting time is obviously shortened: the traditional hydraulic or fixed chain engine brake uses engine oil as a working medium or a driving control medium, so that the entering and exiting time of the engine brake is long and generally needs 0.2 to 0.4s, and the engine brake device can complete switching of positive work and negative work in one rotation of a cam shaft by using an electric control mechanism, thereby improving the entering and exiting speed of the engine brake by 4 to 5 times.
4. The fuel consumption of the engine is reduced: the electric control mechanism does not need engine oil as a driving medium, and the engine oil demand and the oil supply capacity of an engine oil pump can be properly reduced, so that the reduction of fuel consumption is facilitated.
Drawings
Fig. 1 is a schematic front view of an engine brake device according to an embodiment of the present invention.
Fig. 2 is a schematic view of a partial perspective view of an engine brake device according to an embodiment of the present invention.
FIG. 3 is a schematic diagram of an auxiliary rocker arm and control mechanism according to an embodiment of the present invention.
Fig. 4 is a cross-sectional view of the control mechanism of the embodiment of the present invention in a first position.
Fig. 5 is a cross-sectional view of the control mechanism of the embodiment of the present invention in a second position.
FIG. 6 is a cross-sectional view of the control mechanism of the present invention after the first elastic member is compressed by the movement of the slider when the control mechanism is in the first position.
Fig. 7 is a schematic structural view of an auxiliary rocker arm according to an embodiment of the present invention.
Fig. 8 is a cross-sectional view of a housing according to an embodiment of the present invention.
Fig. 9 is a bottom view of the housing according to the embodiment of the present invention.
FIG. 10 is a cross-sectional view of a slider according to an embodiment of the present invention.
Fig. 11 is a bottom view of a slider according to an embodiment of the present invention.
Fig. 12 is a schematic view of a transfer plunger according to an embodiment of the present invention.
Fig. 13 is a cross-sectional view of an actuator plunger according to an embodiment of the present invention.
Fig. 14 is a schematic structural diagram of an embodiment of the present invention.
Fig. 15 is a schematic structural view of a skateboard rack according to an embodiment of the present invention.
Fig. 16 is a schematic structural view of a skateboard according to an embodiment of the invention.
Fig. 17 is a schematic view of a contact leaf spring according to an embodiment of the present invention.
Fig. 18 is a schematic structural view of a motor driving mechanism according to another embodiment of the present invention.
Fig. 19 is a schematic structural view of a motor base according to another embodiment of the present invention.
FIG. 20 is a schematic view of a skateboard deck according to another embodiment of the present invention.
FIG. 21 is a schematic view of a skateboard according to another embodiment of the present invention.
Fig. 22 is a schematic structural view of a guide frame according to another embodiment of the present invention.
Detailed Description
Embodiments of the invention are further described below with reference to the accompanying drawings:
As shown in fig. 1-2, an engine brake device includes a rocker shaft 1, a camshaft 2, an exhaust valve 3, an exhaust rocker arm 4, an auxiliary rocker arm 5, an elastic member 6, a slide pin 7, a control mechanism 8, and an electric drive mechanism 9.
The rocker shaft 1 is arranged in parallel with the cam shaft 2, the cam shaft 2 is provided with an exhaust cam 21 and an auxiliary cam 22 which are adjacently arranged, and the rotation of the cam shaft 2 can drive the exhaust cam 21 and the auxiliary cam 22 to rotate at the same time.
The exhaust valve 3 comprises a first exhaust valve 31, a second exhaust valve 32 and a valve bridge 33 transversely arranged on the first exhaust valve 31 and the second exhaust valve 32, wherein both the first exhaust valve 31 and the second exhaust valve 32 adopt mushroom valves for controlling the flow of gas between a combustion chamber and an intake and exhaust manifold in the engine.
The exhaust rocker arm 4 is rotatably mounted on the rocker shaft 1, and the front end of the exhaust rocker arm 4 is in corresponding contact with the valve bridge 33 and the rear end is in corresponding contact with the exhaust cam 21, so that the exhaust rocker arm 4 can rotationally oscillate around the rocker shaft 1 under the combined action of the exhaust cam 21 and the exhaust valve 3 as the camshaft 2 rotates, thereby enabling the exhaust stroke of the exhaust valve 3 through the exhaust cam 21 and the exhaust rocker arm 4.
The rear end of the exhaust rocker arm 4 is provided with a first roller 41 through a first roller shaft, the first roller 41 is in contact with the exhaust cam 21, and the exhaust cam 21 and the first roller 41 form rolling fit, so that friction between the exhaust cam 21 and the exhaust rocker arm 4 is greatly reduced, abrasion is reduced, and service life is prolonged.
The front end of the exhaust rocker arm 4 is further provided with an adjusting bolt 43, an image angle 42 and a fastening nut 44, the image angle 42 is pressed and installed at the lower end of the adjusting bolt 43 through a special tool, the image angle 42 can freely rotate in a certain rotation angle, the upper end of the adjusting bolt 43 protrudes from the top of the front end of the exhaust rocker arm 4 and is locked and fixed through the fastening nut 44, connection is firmer and more reliable, the image angle 42 is in contact with the valve bridge 33, and the contact effect with the valve bridge 33 is guaranteed along with the swinging action of the exhaust rocker arm 4 due to the higher degree of freedom of the image angle 42, so that the working stability is guaranteed.
The auxiliary rocker arm 5 is rotatably mounted on the rocker shaft 1 and is disposed adjacent to the exhaust rocker arm 4, and the rear end of the auxiliary rocker arm 5 corresponds to the auxiliary cam 22 and is pressed into contact with the auxiliary cam 22 by the elastic member 6, so that the auxiliary cam 22 can drive the auxiliary rocker arm 5 to swing rotationally along the rocker shaft 1 when the camshaft 2 rotates.
Likewise, a second roller 57 can be installed at the rear end of the auxiliary rocker arm 5 through a second roller shaft, the second roller 57 is in contact with the auxiliary cam 22, rolling fit is formed between the auxiliary cam 22 and the second roller 57, friction force between the auxiliary cam 22 and the auxiliary rocker arm 5 is greatly reduced, abrasion is reduced, and service life is prolonged.
Wherein the auxiliary cam 22 includes a base circle and one or two peaches, for example, two peaches are provided in this embodiment, which respectively include a braking peach and an EGR peach or a BGR peach, the braking peach is used to provide a braking lift, the optional EGR peach can provide an EGR lift when the engine is doing positive work, and the optional BGR peach can provide a BGR lift when the engine is braking.
In addition, there are many alternative ways of providing the elastic element 6, in this embodiment, the elastic element 6 is a spring, one end of which is fixed to the rear end of the auxiliary rocker arm 5, and the other end of which is fixed to a spring bracket (not shown) that is fixed to the engine head or other fixed component, and the elastic element 6 has a sufficient spring force to bring the engine auxiliary rocker arm 5 into contact with the auxiliary cam 22 at all times during the operation of the engine.
Of course, the auxiliary rocker arm 5 may be held in contact with the auxiliary cam 22 during engine operation by other means, such as a leaf spring, torsion spring, or the like.
The sliding pin 7 is arranged in the valve bridge 33, one end of the sliding pin is contacted with the first exhaust valve 31, the other end of the sliding pin penetrates through the valve bridge 33, and when the sliding pin 7 receives a large enough acting force, the sliding pin pushes the first exhaust valve 31 to act, so that the exhaust stroke of the first exhaust valve 31 is realized.
As shown in fig. 3-13, the control mechanism 8 is provided at the front end of the auxiliary rocker arm 5 and corresponds to the slide pin 7, and the control mechanism 8 includes a housing 81, an actuator plunger 82, and a slide assembly.
The housing 81 is formed with a first transverse hole 811 and a longitudinal groove 812, the lower end of the longitudinal groove 812 is opened, and the upper end of the longitudinal groove 812 passes through the first transverse hole 811 and intersects the first transverse hole 811.
The outer ring of the actuating plunger 82 is provided with a second annular boss 821 which is shaped like a Chinese character 'ji', the end part of the first transverse hole 811 is provided with a third limiting ring 89, the actuating plunger 82 is slidably arranged in the first transverse hole 811, and one end of the actuating plunger 82 extends out of the first transverse hole 811 after passing through the third limiting ring 89, and is in limiting fit with the third limiting ring 89 through the second annular boss 821.
The slide assembly is slidably disposed within a longitudinal recess 812, which includes a slider 83, a first resilient member 84, a transfer plunger 85, and a second resilient member 86.
The sliding block 83 and the longitudinal groove 812 form a circumferential limit axial sliding matching relationship, and through matching of 4 right-angle faces, the sliding block 83 can only slide along the longitudinal groove 812 and cannot rotate.
The upper end of the longitudinal groove 812 is provided with a spring groove 813, the lower end of the longitudinal groove 812 is provided with a first limiting ring 87, the sliding block 83 is in a convex shape, the lower end of the sliding block 83 passes through the first limiting ring 87 and is in limiting fit with the first limiting ring 87, the first elastic piece 84 is a spring and is arranged in the spring groove 813, two ends of the first elastic piece are respectively propped against the shell 81 and the sliding block 83, and the sliding block 83 can be driven to slide downwards to keep limiting contact with the first limiting ring 87.
The sliding block 83 is further provided with a second transverse hole 831 corresponding to the first transverse hole 811, and when the sliding block 83 is kept at a position contacting and limiting with the first limiting ring 87 under the action of the first elastic member 84, the second transverse hole 831 is just overlapped with the first transverse hole 811.
The second transverse hole 831 is a stepped hole and sequentially comprises a large hole 8311, a middle hole 8312 and a small hole 8313, one end close to the execution plunger 82 is a large hole 8311, and the small hole 8313 is consistent with the first transverse hole 811.
The sliding length of the transmission plunger 85 is smaller than or equal to that of the second transverse hole 831, the transmission plunger 85 is arranged in the second transverse hole 831 and is matched with the small hole 8313, a first annular boss 851 matched with the middle hole 8312 is formed on the outer ring of the transmission plunger 85, the whole transmission plunger is in a cross shape, a second limiting ring 88 is installed in the large hole 8311, the second elastic piece 86 is a spring and is sleeved outside the transmission plunger 85, two ends of the second elastic piece are respectively propped against the sliding block 83 and the first annular boss 851, and the transmission plunger 85 can be driven to slide towards the second limiting ring 88 and keep the first annular boss 851 and the second limiting ring 88 in limiting contact.
When the transfer plunger 85 is kept at the position contacting and limiting with the second limiting ring 88 under the action of the second elastic member 86, the transfer plunger 85 is completely disposed in the second transverse hole 831, and one end of the transfer plunger 85 is flush with the end surface of the second transverse hole 831.
When the execution plunger 82 is moved by an external force, the transmission plunger 85 can be pushed to move, when the execution plunger 82 is not subjected to other external forces, the transmission plunger 85 can be reset under the action of the second elastic piece 86, and meanwhile the execution plunger 82 is pushed to be reset, so that the transmission plunger 85 has a first position completely arranged in the second transverse hole 831, and the other end of the transmission plunger 85, opposite to the execution plunger 82, extends out of the second transverse hole 831 and is locked with the housing 81.
In addition, the front end of the auxiliary rocker arm 5 is provided with a longitudinal hole 51, a longitudinal guide groove 52 is formed on the side wall of the longitudinal hole 51, the upper end of the longitudinal hole 51 is provided with an adjusting bolt 53, and the adjusting bolt 53 is fixedly locked by a locking nut 56.
A fourth limiting ring 54 is further arranged at the lower end of the longitudinal hole 51; the housing 81 is slidably disposed within the longitudinal bore 51, the actuator plunger 82 extends through the longitudinal guide slot 52 out of the auxiliary rocker arm 5, and the slider 83 extends through the fourth stop collar 54 downwardly below the longitudinal bore 51.
A third elastic member 55 is further disposed between the fourth limiting ring 54 and the housing 81, and the third elastic member 55 is typically a spring, and two ends of the third elastic member are respectively abutted against the housing 81 and the fourth limiting ring 54, so as to drive the housing 81 to keep contact with the adjusting bolt 53.
Compared with the case 81 directly fixed at the front end of the auxiliary rocker arm 5, the case 81 can float up and down due to the above structure, the control mechanism 8 is driven to float up and down as a whole, and the position of the control mechanism 8 can be finely adjusted by matching the third elastic member 55 through the adjusting bolt 53, so that the adjustment of the distance between the sliding block 83 and the sliding pin 7 is realized.
Wherein, two longitudinal guide grooves 52 are symmetrically arranged on the side wall of the longitudinal hole 51, two guide bosses 814 are correspondingly arranged on two sides of the shell 81, and the shell 81 is in a cross shape as a whole; the guide bosses 814 are correspondingly disposed in the longitudinal guide grooves 52, and the first transverse holes 811 are disposed through the two guide bosses 814.
As shown in fig. 1,2 and 14-17, the electric drive mechanism 9 includes an actuator motor 91, a sled carriage 92, a sled 93, and a contact leaf spring 94.
The sliding plate frame 92 is fixedly mounted on a cylinder cover or other fixed parts of the engine, and comprises a mounting plate 921, a plurality of sliding grooves 922 are sequentially formed in the side edge of the mounting plate 921 at intervals along the length direction of the mounting plate 921, and the mounting plate 921 is arranged above the auxiliary rocker arm 5 and is parallel to the rocker arm shaft 1 in the length direction.
The sliding plate 93 has a strip structure, and is slidably engaged with the sliding groove 922 through the sliding groove 922, and the sliding plate 93 is provided with an execution hole 931 and a plurality of clamping grooves 932.
The actuating motor 91 is fixedly installed on a cylinder cover or other fixed parts of the engine through a motor base 95, the actuating motor 91 adopts a rotating motor, an actuating rod 911 which is vertically arranged on an output shaft of the actuating motor is arranged on the actuating motor, the actuating rod 911 passes through an actuating hole 931 to be arranged, and when the actuating motor 91 rotates, the actuating rod 911 can be driven to rotate, so that the sliding plate 93 can be driven to slide along the sliding groove 922.
The contact leaf spring 94 is 7-shaped, the sliding plate 93 is provided with a clamping groove 932 matched with the contact leaf spring 94, and the upper end of the contact leaf spring 94 passes through the clamping groove 932 and is bent to be in limit fit with the sliding plate 93, so that the installation is convenient.
When the engine is braked or the EGR is operated, the execution motor 91 rotates, the sliding plate 93 can be driven to slide through the execution rod 911, the sliding plate drives the contact leaf spring 94 to synchronously move, the contact leaf spring 94 is in contact with the execution plunger 82 and pushes the execution plunger 82, and the execution plunger 82 can push the transmission plunger 85 to move against the elastic force of the second elastic piece 86, so that the transmission plunger slides to the second position.
When the engine returns to normal operation, the execution motor 91 returns to the reverse direction, the slide plate 93 can be driven to slide and return through the execution rod 911, the slide plate 93 drives the contact leaf spring 94 to move, the contact leaf spring 94 is separated from the execution plunger 82, the transmission plunger 85 can return and slide to the first position under the action of the second elastic piece 86, and meanwhile the execution plunger 82 is pushed to return.
The contact leaf spring 94 is in surface contact with the actuating portion 841 of the actuating plunger 82, so that the auxiliary rocker arm 5 can ensure contact between the contact leaf spring 94 and the actuating portion 841 when rotating, and ensure that the actuating plunger 82 is kept at the first position.
In addition, the sliding plate 93 is provided with a plurality of contact leaf springs 94, and each contact leaf spring 94 is arranged at intervals and can respectively correspond to each group of engine braking devices, and each cylinder synchronously acts, so that the structure is more compact, and the braking is rapid and stable.
Fig. 18-22 show another embodiment of the electric drive mechanism 9, which comprises an actuator motor 91, a sled carriage 92, a sled 93, and a contact leaf spring 94.
The sliding plate frame 92 includes a plurality of mounting seats 923 arranged at intervals, and is fixedly mounted on a cylinder cover or other fixed parts of the engine, the mounting seats 923 are correspondingly provided with sliding grooves 922, and one mounting seat 923 at one end is further provided with a spring groove 924.
The sliding plate 93 has a strip structure, and passes through the sliding groove 922 to slidingly engage with the sliding groove 922, and one end of the sliding plate 93 corresponding to the spring groove 924 is bent to form a spring seat 933.
A return elastic member 96 is disposed between the spring seat 933 and the spring slot 924, and the return elastic member is a spring, and two ends of the return elastic member respectively abut against the spring seat 933 and the spring slot 924.
The actuating motor 91 is fixedly mounted on a cylinder cover or other fixed parts of the engine through a motor base 95, the actuating motor 91 is a linear motor, and the sliding plate 93 is provided with a guide frame 97 corresponding to the output end of the actuating motor 91.
In order to further ensure the motion stability, the motor base 95 is provided with a second sliding groove 951 corresponding to the sliding groove 922, the sliding plate 93 simultaneously passes through the second sliding groove 951, the motor base 95 is provided with a guide shaft 98, the guide frame 97 is provided with a guide hole 971 adapted to the guide shaft 98, and the guide shaft 98 passes through the guide hole 971, so that the motion is stable when the guide frame 97 translates.
When the engine is braked or the EGR is operated, the execution motor 91 rotates, the output end of the execution motor pushes the guide frame 97 to translate, the guide frame 97 drives the sliding plate 93 to slide, the sliding plate 93 drives the contact leaf spring 94 to synchronously move, the contact leaf spring 94 is in contact with the execution plunger 82 and pushes the execution plunger 82, and the execution plunger 82 can push the transmission plunger 85 to move against the elastic force of the second elastic piece 86 so as to slide to the second position.
When the engine returns to normal operation, the execution motor 91 rotates reversely, the output end is retracted, the sliding plate 93 resets at the reset elastic piece 96 and drives the contact leaf spring 94 and the guide frame 97 to reset, the transmission plunger 85 can reset and slide to the first position under the action of the second elastic piece 86, and meanwhile, the execution plunger 82 is pushed to reset.
The working process of the engine braking device comprises the following steps:
When the engine works normally, the execution motor 91 does not work, the transmission plunger 85 is in the first position under the action of the second elastic piece 86, the sliding block 83 is not locked at the moment, when the auxiliary cam 22 lifts to drive the auxiliary rocker arm 5 to rotate, the sliding pin 7 and the sliding block 83 drive the transmission sliding block 83 to move upwards against the elastic force of the first elastic piece 84, the elastic force of the first elastic piece 84 is insufficient to drive the sliding pin 7 to realize exhaust, the movement of an exhaust valve is not influenced, and the normal working of the engine is ensured.
When the engine is braked, the execution motor 91 works, the execution plunger 82 is pushed to move through the sliding plate 93 and the contact leaf spring 94, the execution plunger 82 can push the transmission plunger 85 to move against the elastic force of the second elastic piece 86, the transmission plunger is enabled to slide to the second position, the sliding block 83 is combined with the shell 81 into a whole, when the auxiliary cam 22 lifts to drive the auxiliary rocker arm 5 to rotate, the sliding block 83 contacts with the sliding pin 7, and the sliding pin 7 is driven to enable the first exhaust valve to move and open, and therefore the purpose of engine braking is achieved.
When the engine returns to normal operation, the execution motor 91 works, the sliding plate 93 and the contact leaf spring 94 are reset, the transmission plunger 85 can be reset and slide to the first position under the action of the second elastic piece 86, meanwhile, the execution plunger 82 is pushed out of the second transverse hole, the sliding block 83 and the shell 81 are not locked at the moment, when the auxiliary cam 22 lifts to drive the auxiliary rocker arm 5 to rotate, the sliding pin 7 contacts with the sliding block 83, the sliding block 83 is driven to move upwards against the elastic force of the first elastic piece 84, the movement of the exhaust valve is not influenced, and the normal operation of the engine is ensured.
Compared with the existing engine braking device adopting engine oil as a medium for transmitting the motion law of the valve, the electric engine braking device has the following advantages:
1. Eliminating reliability risks brought by using engine oil: the engine braking device is driven by an execution motor and is matched with the engine braking device through a purely mechanical linkage structure, so that the problems of unstable idling and white smoke caused by the false start of a braking function due to high engine oil viscosity and high engine oil pressure when an engine is started are solved;
2. Increasing engine brake application area: the existing hydraulic or fixed chain engine brake uses engine oil as a working medium, so that certain requirements on the engine oil temperature and the engine oil pressure are met, and if the engine oil temperature is more than 40 ℃, the engine brake can be interposed, so that the engine brake is limited to be used when the whole vehicle is just started, the motor is used for driving, and the engine brake is matched with the motor through a purely mechanical linkage structure, so that the engine brake is not limited by the conditions, and can be used at any time after the whole vehicle is started;
3. The engine brake entering and exiting time is obviously shortened: the traditional hydraulic or fixed chain engine brake uses engine oil as a working medium or a driving control medium, so that the entering and exiting time of the engine brake is long, generally 0.2-0.4 s is needed, the engine brake device is driven by an execution motor, and positive work and negative work can be switched within one rotation of a cam shaft through the cooperation of a purely mechanical linkage structure, so that the entering and exiting speed of the engine brake is improved by 4-5 times;
4. The fuel consumption of the engine is reduced: the engine is driven by the execution motor and is matched through the mechanical linkage structure, engine oil is not needed to be used as a driving medium, and the engine oil demand and the oil supply capacity of the engine oil pump can be properly reduced, so that the reduction of fuel consumption is facilitated.
In the description of the present invention, it should be noted that the terms "center", "longitudinal", "lateral", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc. indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, are merely for convenience in describing the present invention and simplifying the description, and do not indicate or imply that the apparatus or elements referred to must have a specific orientation, be configured and operated in a specific orientation, and thus should not be construed as limiting the present invention. Furthermore, the terms "first," "second," and the like, are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.
In the description of the present invention, it should be noted that, unless explicitly specified and limited otherwise, the terms "mounted," "connected," and "connected" are to be construed broadly, and may be either fixedly connected, detachably connected, or integrally connected, for example; can be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium, and can be communication between two elements. The specific meaning of the above terms in the present invention will be understood in specific cases by those of ordinary skill in the art. Furthermore, in the description of the present invention, unless otherwise indicated, the meaning of "a plurality" is two or more.
The skilled person will know: while the invention has been described in terms of the foregoing embodiments, the inventive concepts are not limited to the invention, and any modifications that use the inventive concepts are intended to be within the scope of the appended claims.

Claims (6)

1. An electric engine brake device comprising
A rocker shaft (1);
A camshaft (2) which is disposed in parallel with the rocker shaft (1) and has an exhaust cam (21) and an auxiliary cam (22) that are disposed adjacently;
an exhaust valve (3) comprising a first exhaust valve (31), a second exhaust valve (32) and a valve bridge (33) transversely arranged on the first exhaust valve (31) and the second exhaust valve (32);
An exhaust rocker arm (4) rotatably mounted on the rocker shaft (1) and having a front end in corresponding contact with the valve bridge (33) and a rear end in corresponding contact with the exhaust cam (21);
an auxiliary rocker arm (5) rotatably mounted on the rocker arm shaft (1) and disposed adjacent to the exhaust rocker arm (4), the rear end of which corresponds to the auxiliary cam (22);
an elastic element (6) capable of holding the auxiliary rocker arm (5) in contact with the auxiliary cam (22);
A slide pin (7) which is arranged in the valve bridge (33) and one end of which is contacted with the first exhaust valve (31) and the other end of which penetrates the valve bridge (33);
The method is characterized in that: and also comprises
The control mechanism (8) is arranged at the front end of the auxiliary rocker arm (5) and corresponds to the sliding pin (7), the control mechanism comprises a shell (81), an actuating plunger (82) and a sliding component, a first transverse hole (811) and a longitudinal groove (812) are formed in the shell (81), the lower end of the longitudinal groove (812) is open, the upper end of the sliding component passes through the first transverse hole (811) and is intersected with the first transverse hole (811), a spring groove (813) is formed at the upper end of the longitudinal groove (812), a first limiting ring (87) is arranged at the lower end of the longitudinal groove (812), the actuating plunger (82) is arranged in the first transverse hole (811) in a sliding mode, one end of the actuating plunger (82) extends out of the first transverse hole (811), the other end of the actuating plunger is abutted with the sliding component, the sliding component comprises a sliding block (83), a first elastic piece (84), a transmission plunger (85) and a second elastic piece (86), the sliding block (83) is in sliding fit with the longitudinal groove (812) in the circumferential direction, the sliding block (83) in a sliding mode, the sliding block (83) is in a sliding mode, the first limiting ring (83) extends downwards to the lower end of the sliding component and is matched with the first limiting ring (87) in the shape, the sliding block (83) is also provided with a second transverse hole (831) corresponding to the first transverse hole (811), the second transverse hole (831) is a stepped hole and sequentially comprises a large hole (8311), a middle hole (8312) and a small hole (8313), and the small hole (8313) is the same as the first transverse hole (811);
The first elastic member (84) is a spring and is arranged in the spring groove (813), two ends of the first elastic member are respectively abutted against the shell (81) and the sliding block (83), the sliding block (83) can be driven to move downwards and enable the second transverse hole (831) to coincide with the first transverse hole (811), the transmission plunger (85) is arranged in the second transverse hole (831) in a sliding manner, the length of the transmission plunger (85) is smaller than or equal to that of the second transverse hole (831), the transmission plunger (85) is matched with the small hole (8313), a first annular boss (851) matched with the middle hole (8312) is formed on the outer periphery of the transmission plunger (85), the second limiting ring (88) is arranged in the large hole (8311) and is in limit fit with the first annular boss (851) of the transmission plunger (85), the two ends of the second elastic member (86) are respectively abutted against the sliding block (83) and the first annular boss (851), the transmission plunger (85) can be driven to move towards the first end face (831) completely and the second end face (831) is arranged at the position flush with the first end face (82), and a second position where the transfer plunger (85) is locked with the housing (81) by extending the second transverse hole (831) from the other end of the execution plunger (82);
The electric driving mechanism (9) comprises an execution motor (91), a slide plate frame (92), a slide plate (93) and a contact leaf spring (94), wherein the slide plate frame (92) is arranged above the auxiliary rocker arm (5), the slide plate (93) is arranged in parallel with the rocker arm shaft (1) and is arranged on the slide plate frame (92) in a sliding manner, the contact leaf spring (94) is arranged on the slide plate (93) and is in corresponding contact with the execution plunger (82), and the output end of the execution motor (91) is in linkage fit with the slide plate (93) to push the slide plate (93) to slide along the slide plate frame (92).
2. The electric engine brake device of claim 1, wherein: the outer ring of the execution plunger (82) is provided with a second annular boss (821) which is in a cross shape, the end part of the first transverse hole (811) is provided with a third limiting ring (89), and the execution plunger (82) passes through the third limiting ring (89) to extend out of the first transverse hole (811) and is in limiting fit with the third limiting ring (89) through the second annular boss (821).
3. The electric engine brake device of claim 1, wherein: the front end of the auxiliary rocker arm (5) is provided with a longitudinal hole (51), a longitudinal guide groove (52) is formed in the side wall of the longitudinal hole (51), an adjusting bolt (53) is arranged at the upper end of the longitudinal hole (51), and a fourth limiting ring (54) is arranged at the lower end of the longitudinal hole (51);
The shell (81) is arranged in the longitudinal hole (51) in a sliding way, the execution plunger (82) extends out of the auxiliary rocker arm (5) through the longitudinal guide groove (52), and the sliding block (83) extends downwards below the longitudinal hole (51) through the fourth limiting ring (54);
A third elastic piece (55) is further arranged between the fourth limiting ring (54) and the shell (81), and the third elastic piece (55) can drive the shell (81) to keep in contact with the adjusting bolt (53).
4. An electric engine brake device according to claim 3, characterized in that: the two longitudinal guide grooves (52) are symmetrically arranged on the side wall of the longitudinal hole (51); two guide bosses (814) are arranged on two sides of the shell (81), and the whole shell is in a cross shape; the guide bosses (814) are correspondingly arranged in the longitudinal guide grooves (52), and the first transverse holes (811) are formed through the two guide bosses (814).
5. The electric engine brake device of claim 1, wherein: the actuating motor (91) is a rotating motor, an actuating rod (911) perpendicular to the actuating motor (91) is arranged on an output shaft of the actuating motor (91), an actuating hole (931) matched with the actuating rod (911) is formed in the sliding plate (93), and the actuating rod (911) penetrates through the actuating hole (931).
6. The electric engine brake device of claim 1, wherein: the executing motor (91) is a linear motor, and the sliding plate (93) is provided with a guide frame (97) corresponding to the output end of the executing motor (91); a reset elastic piece (96) is arranged between the sliding plate frame (92) and the contact leaf spring (94).
CN201910758421.3A 2019-08-16 2019-08-16 Electric engine braking device Active CN110344909B (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
CN201910758421.3A CN110344909B (en) 2019-08-16 2019-08-16 Electric engine braking device
PCT/CN2019/103248 WO2021031230A1 (en) 2019-08-16 2019-08-29 Electric engine braking device
EP19908081.3A EP3800332B1 (en) 2019-08-16 2019-08-29 Electric engine braking device

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN201910758421.3A CN110344909B (en) 2019-08-16 2019-08-16 Electric engine braking device

Publications (2)

Publication Number Publication Date
CN110344909A CN110344909A (en) 2019-10-18
CN110344909B true CN110344909B (en) 2024-04-26

Family

ID=68185230

Family Applications (1)

Application Number Title Priority Date Filing Date
CN201910758421.3A Active CN110344909B (en) 2019-08-16 2019-08-16 Electric engine braking device

Country Status (3)

Country Link
EP (1) EP3800332B1 (en)
CN (1) CN110344909B (en)
WO (1) WO2021031230A1 (en)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102414424A (en) * 2009-05-06 2012-04-11 雅各布斯车辆系统公司 Lost motion variable valve actuation system for engine braking and early exhaust opening
CN102414403A (en) * 2009-04-27 2012-04-11 雅各布斯车辆系统公司 Dedicated rocker arm engine brake
CN108661745A (en) * 2018-07-10 2018-10-16 浙江黎明发动机零部件有限公司 A kind of electromagnetic control type engine braking apparatus
CN109372608A (en) * 2018-11-27 2019-02-22 浙江黎明发动机零部件有限公司 A kind of electromagnetic control type engine braking apparatus
CN210289866U (en) * 2019-08-16 2020-04-10 浙江黎明智造股份有限公司 Electric engine braking device

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000291454A (en) * 1999-04-06 2000-10-17 Toyota Motor Corp Engine brake device
FR2795133B1 (en) * 1999-06-18 2002-07-12 Renault METHOD FOR CONTROLLING A COMBUSTION ENGINE WITH A VIEW TO OBTAINING AN ENGINE BRAKE EFFECT
US6957634B2 (en) * 2002-10-04 2005-10-25 Caterpillar Inc. Engine valve actuator
CN101131110A (en) * 2007-09-14 2008-02-27 中国重汽集团济南技术中心有限公司 Exhaust valve braking device
DE102008039504A1 (en) * 2008-08-23 2010-02-25 Schaeffler Kg Four-stroke internal combustion engine, has crankcase and cylinder, where one transmission element or hydraulic valve-play compensating element is attached in component inserted in transmission element
EP2766589B1 (en) * 2011-09-21 2019-01-16 Jacobs Vehicle Systems, Inc. Method and system for engine cylinder decompression
CN102444440B (en) * 2011-12-19 2013-04-10 宜兴大隆动力科技有限公司 Double-mode type full-variable valve driving system for four-cylinder internal combustion engine
DE102017129424A1 (en) * 2017-12-11 2019-06-13 Schaeffler Technologies AG & Co. KG Variable valve train of a combustion piston engine
CN109184847B (en) * 2018-08-27 2024-05-24 南京威孚金宁有限公司 Engine compression release brake valve control system and working method thereof
CN109707476B (en) * 2018-12-28 2020-07-28 潍柴动力股份有限公司 Novel brake rocker arm and control method thereof

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102414403A (en) * 2009-04-27 2012-04-11 雅各布斯车辆系统公司 Dedicated rocker arm engine brake
CN102414424A (en) * 2009-05-06 2012-04-11 雅各布斯车辆系统公司 Lost motion variable valve actuation system for engine braking and early exhaust opening
CN108661745A (en) * 2018-07-10 2018-10-16 浙江黎明发动机零部件有限公司 A kind of electromagnetic control type engine braking apparatus
CN109372608A (en) * 2018-11-27 2019-02-22 浙江黎明发动机零部件有限公司 A kind of electromagnetic control type engine braking apparatus
CN210289866U (en) * 2019-08-16 2020-04-10 浙江黎明智造股份有限公司 Electric engine braking device

Also Published As

Publication number Publication date
EP3800332B1 (en) 2022-08-17
CN110344909A (en) 2019-10-18
EP3800332A4 (en) 2021-12-08
EP3800332A1 (en) 2021-04-07
WO2021031230A1 (en) 2021-02-25

Similar Documents

Publication Publication Date Title
CN109372608B (en) Electromagnetic control type engine braking device
CN108661745B (en) Electromagnetic control type engine braking device
JPS6114335B2 (en)
CN113818943B (en) Special fixed double-piston hydraulic engine valve driving device
US6032643A (en) Decompression engine brake device of automotive internal combustion engine
CN109488411B (en) Engine brake device
CN109779716B (en) Compact movable driving fulcrum
CN208380655U (en) A kind of electromagnetic control type engine braking apparatus
CN110529216B (en) Electric control type engine braking device
CN210289866U (en) Electric engine braking device
CN110344909B (en) Electric engine braking device
CN112282888A (en) Engine braking device with continuously adjustable braking lift
CN110425016A (en) A kind of engine braking apparatus
CN210317428U (en) Engine braking device
CN210622882U (en) Electric control type engine braking device
CN110374713B (en) Engine braking device
CN110425015B (en) Hydraulic control type engine braking device
CN210396841U (en) Hydraulic control type engine braking device
CN110541762B (en) Engine brake control device with multiple driving sources
CN111828121A (en) Internal combustion engine cylinder brake device
CN210889133U (en) Engine brake control device with multiple driving sources
CN208831060U (en) A kind of electromagnetic control type engine braking apparatus
CN215761845U (en) Energy-saving and consumption-reducing engine braking device
US10876438B1 (en) Braking device for electric engine
CN203626910U (en) Exhaust brake linking mechanism for engine

Legal Events

Date Code Title Description
PB01 Publication
PB01 Publication
SE01 Entry into force of request for substantive examination
SE01 Entry into force of request for substantive examination
GR01 Patent grant
GR01 Patent grant