CN110925045A

CN110925045A - Hydraulically-controlled engine brake actuating mechanism and application method thereof

Info

Publication number: CN110925045A
Application number: CN201911394557.7A
Authority: CN
Inventors: 吴春华
Original assignee: Shanghai Mansong Technology Center
Current assignee: Quanzhou Sifang Yunji Technology Co ltd
Priority date: 2019-12-30
Filing date: 2019-12-30
Publication date: 2020-03-27
Anticipated expiration: 2039-12-30
Also published as: CN110925045B

Abstract

The invention discloses an engine brake actuator for hydraulic braking, comprising a rocker arm body, a control unit and an execution unit are arranged on the rocker arm body, the axis of the control unit is perpendicular to the rotation direction of the rocker arm body, and the The unit includes an actuating piston adjusting screw, an actuating piston, and an actuating piston limiting guide bush, the actuating piston includes an actuating piston upper body and an actuating piston lower body, the head of the actuating piston adjusting screw faces downward, and the actuating piston limiting guide bush is The actuator is slidably connected to the actuating piston adjusting screw, an actuating piston spring is arranged between the actuating piston limiting guide sleeve and the head of the actuating piston adjusting screw, the actuating piston upper body is sleeved on the actuating piston adjusting screw, and the actuating piston adjusting screw is The lower body of the piston is fixed with the upper body of the execution piston from the bottom, and the top of the execution piston is connected to the high pressure oil passage of the execution piston, which can control the lift of the exhaust valve during braking, and does not affect the lift of the exhaust valve at all when not braking. the executive body.

Description

Hydraulically-controlled engine brake actuating mechanism and application method thereof

Technical Field

The invention belongs to the field of valve driving of automobile engines, and particularly relates to a hydraulically-controlled engine brake actuating mechanism and an application method thereof.

Background

With the rapid development of the logistics industry, the efficiency requirement for transporting heavy trucks is higher and higher. The truck speed is increased and the safety requirements are higher. When the traditional brake in the engine cylinder is not assembled, the brake pedal of the automobile needs to be used more frequently, and accidents often occur due to the failure of the brake pedal. In order to improve the safety of the truck, auxiliary braking can be added to the whole truck to reduce the use frequency of the brake pedal, so that the brake pedal is ensured to be in a recent use state at a critical moment. The auxiliary brake comprises a hydraulic retarder, an eddy current retarder and in-cylinder braking of the engine. The first two of them have too high cost and limited working conditions. Have not been widely used. However, the engine brake is integrated in the engine and the service life of the engine is the same, so the engine brake is the most suitable auxiliary brake mode from the aspects of cost, quality and function.

The so-called in-cylinder engine braking is to use a vehicle to back up the engine, convert the high-speed motion of the vehicle into the compressed air energy of the engine, and consume the compressed air energy along with the exhaust heat energy of the engine. Therefore, to achieve maximum in-cylinder engine braking, the exhaust valve is opened at the end of engine air intake to form exhaust gas backflow to increase the air intake amount, and compressed air is exhausted near the top dead center of compression. To achieve opening of the exhaust valve at a fixed time, an actuator is required to achieve this function.

The existing executing mechanisms for in-cylinder braking are mainly divided into mechanical valve driving and hydraulic valve driving. The mechanical valve is driven, the whole structure is rigid transmission force, and the impact force of the system is large. In the hydraulic valve driving, due to the compressibility of hydraulic oil, a system can absorb certain impact, so that the impact of the system is reduced, and the reliability is improved.

For example, chinese patent application No. 200820072612.1 discloses an engine brake execution unit, which is characterized in that: the exhaust rocker arm control valve comprises an exhaust rocker arm control valve spring seat, an exhaust rocker arm control valve spring, an exhaust rocker arm control valve plunger, a one-way valve assembly, an exhaust rocker arm brake plunger spring, an exhaust rocker arm brake plunger and two elastic retainer rings, wherein the rocker arm is internally divided into an upper cavity and a lower cavity; the lower cavity of the rocker arm is firstly provided with a one-way valve assembly which is arranged at the top of the lower cavity of the rocker arm in an interference fit manner, then is provided with an exhaust rocker arm brake plunger spring, then is provided with an exhaust rocker arm brake plunger, and finally is fixed in the lower cavity by an elastic retainer ring through a hole. The exhaust rocker arm brake plunger can be downwards extruded for a certain distance during braking and cannot slide, and when the tappet is jacked up by the brake lift of the camshaft, 2 valves can be simultaneously opened to realize engine braking; when the brake is not applied, the brake plunger of the exhaust rocker arm can slide up and down, and the sliding amount can offset the valve lift generated by the brake lift of the camshaft, namely the camshaft cannot open the valve in the brake lift.

However, because the directions of the motion axes of the control valve plunger and the brake plunger are consistent, the rocker arm swings in a reciprocating manner continuously, and the control valve plunger is easily influenced by the motion inertia force of the rocker arm, so that the required control position is unstable, and the reliability and the braking power are influenced; in addition, the initial position of the brake plunger cannot be adjusted as required; the extension of the brake plunger when the brake is opened can only be controlled by the position of the elastic check ring, the control precision is difficult to improve, and the two factors influence the lift of the brake valve, so that the improvement and the consistency of the brake power are also influenced.

Disclosure of Invention

Aiming at the defects of the prior art, the invention provides an actuating mechanism which can control the lift of an exhaust valve during braking and does not influence the lift of the exhaust valve at all during non-braking.

In order to achieve the purpose, the invention provides the following technical scheme: a hydraulic braking engine braking actuating mechanism comprises a rocker arm body, wherein a control unit and an actuating unit are arranged on the rocker arm body,

the control unit comprises a one-way valve assembly and a control piston assembly,

the check valve assembly comprises a check valve body and a check valve sealing seat, the check valve sealing seat is fixedly connected with the check valve body, a through hole is formed in the check valve sealing seat, a check valve is arranged in the check valve body, a check valve spring is arranged on one side, back to the check valve sealing seat, of the check valve, the check valve abuts against the through hole of the check valve sealing seat, an oil flow hole is formed in the check valve body, and an execution piston high-pressure oil duct communicated with the oil flow hole is formed in the rocker arm body;

the control piston assembly comprises a control piston and a control piston push rod, the control piston push rod is fixedly connected with the control piston, the control piston push rod extends into a through hole of the check valve sealing seat, one side of the control piston, which is back to the control piston push rod, is provided with a control piston inner spring, an oil filling space is reserved between the control piston and the check valve sealing seat, and a brake oil inlet hole communicated with the oil filling space is formed in the rocker arm body;

the one-way valve assembly and the control piston assembly are coaxial, and the axial line is vertical to the rotation direction of the rocker arm body;

the execution unit comprises an execution piston adjusting screw rod, an execution piston and an execution piston limiting guide sleeve, the execution piston comprises an execution piston upper body and an execution piston lower body, the head of the execution piston adjusting screw rod faces downwards, the inner side of the execution piston limiting guide sleeve is connected to the execution piston adjusting screw rod in a sliding mode, an execution piston spring is arranged between the execution piston limiting guide sleeve and the head of the execution piston adjusting screw rod, the execution piston upper body is sleeved on the execution piston adjusting screw rod from top to bottom, the execution piston lower body is fixed with the execution piston upper body from bottom, the top of the execution piston limiting guide sleeve is abutted to the execution piston upper body through the execution piston spring, and the top of the execution piston is communicated with an execution piston high-pressure oil duct.

And the actuating piston adjusting screw rod is in threaded connection with the rocker arm body.

Furthermore, the top end of the execution piston adjusting screw rod extends out of the rocker arm body, and the top end of the execution piston adjusting screw rod is connected with an execution piston adjusting nut.

Furthermore, a first-stage cavity and a second-stage cavity are arranged at the position, corresponding to the control piston, of the rocker arm body, the diameter of the second-stage cavity is larger than that of the first-stage cavity, the control piston is located in the first-stage cavity, the inner spring of the control piston extends into the first-stage cavity from the second-stage cavity, the outer spring of the control piston is arranged in the second-stage cavity, the diameter of the inner ring of the outer spring of the control piston is smaller than that of the first-stage cavity, and the diameter of the outer ring of the outer spring of the.

Further the secondary cavity communicates with the outside.

Furthermore, the oil injection space is formed by arranging a groove on the check valve sealing seat, the groove is positioned on one surface, facing the control piston, of the check valve sealing seat, and the groove is communicated with the through hole and the brake oil inlet hole.

Further, the one-way valve body is fixedly connected with the one-way valve sealing seat through threads, and the one-way valve sealing seat is fixedly connected with the rocker arm body through threads.

The application method of the engine brake actuating mechanism of the hydraulic brake is characterized in that the rocker arm body is an independent brake rocker arm, and the brake rocker arm and the exhaust rocker arm assembly are arranged side by side and connected to the same exhaust rocker arm elephant foot assembly.

An application method of a hydraulic braking engine braking actuator is characterized in that a rocker body is an exhaust rocker arm assembly, and a control unit and an execution unit are integrated in the exhaust rocker arm assembly.

Compared with the prior art, the invention has the beneficial effects that: when braking, the actuating piston moves downwards to a fixed position and cannot slide, and the lift of the exhaust valve is limited; when the brake is not performed, hydraulic oil at the execution unit reflows, the execution unit releases pressure, the execution piston spring jacks up the limiting guide sleeve and the execution piston, the execution piston is located at the highest position, the lift of the exhaust valve cannot be influenced, and meanwhile, the reciprocating swing of the rocker arm cannot influence the control unit; the actuating piston adjusting screw rod at the actuating unit can adjust the initial position of the actuating piston, and the clearance between the actuating piston limiting guide sleeve and the head of the actuating piston adjusting screw rod can accurately control the extending amount of the actuating piston, so that the optimal braking lift of the exhaust valve can be obtained during braking, and the optimal braking power can be obtained.

Drawings

FIG. 1 is a cross-sectional view of the control piston and check valve in a position when the brake is closed;

FIG. 2 is a cross-sectional view of the control piston and check valve in position when the brake is on;

FIG. 3 is a cross-sectional view of the check valve assembly;

FIG. 4 is a perspective view of a check valve assembly;

FIG. 5 is a cross-sectional view of the actuator piston in an initial position (brake oil not entering the actuator unit);

FIG. 6 is a cross-sectional view of the actuator piston in a compressed position in a positive power state;

FIG. 7 is a cross-sectional view of the actuator piston actuating the valve to open during a braking condition;

FIG. 8 is a schematic structural view of a hydraulically-braked engine brake actuator;

FIG. 9 is a side view of the brake actuator in the application of a dedicated brake rocker arm;

FIG. 10 is a top view of the brake actuator on a dedicated brake rocker arm application;

FIG. 11 is a side view of the brake actuator in a brake integrated exhaust rocker arm application;

FIG. 12 is a top view of the brake actuator on a brake integrated exhaust rocker arm application.

Reference numerals: 1. a rocker arm body; 2. a one-way valve assembly; 3. a control unit; 4. a check valve spring; 5. a one-way valve; 6. a one-way valve body oil cavity; 7. an implement piston high pressure oil gallery; 8. an execution unit; 9. a check valve body; 10. a one-way valve seal seat; 11. a control piston push rod; 12. a brake oil inlet hole; 13. a control piston; 14. a control piston outer spring; 15. a control valve piston inner spring; 16. an air escape opening; 17. a control piston shim; 18. a control piston circlip; 19. an execution piston high-pressure oil chamber; 20. executing a piston adjusting screw; 21. an actuator piston adjusting nut; 22. an actuator piston upper body; 23. an actuator piston spring; 24. an execution piston limiting guide sleeve; 25. an actuating piston lower body; 26. an exhaust valve; 27. an exhaust valve sliding pin; 29. an exhaust rocker elephant foot assembly; 30. a rocker shaft mounting bolt; 31. a brake rocker arm biasing leaf spring; 32. positioning pins; 33. an actuator piston; 34. a brake cam; 35. a brake rocker arm assembly; 36. a rocker shaft assembly; 37. an exhaust rocker arm assembly; 39. an exhaust cam; 40. an intake rocker arm assembly; 41. a through hole; 42. a groove; 43. and the oil flow hole.

Detailed Description

Embodiments of the hydraulically braked engine brake actuator of the present invention will be further described with reference to fig. 1 to 12.

In the description of the present invention, it should be noted that, for the terms of orientation, such as "central", "lateral (X)", "longitudinal (Y)", "vertical (Z)", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", etc., indicate that the orientation and positional relationship are based on the orientation or positional relationship shown in the drawings, and are only for the convenience of describing the present invention and simplifying the description, but do not indicate or imply that the referred device or element must have a specific orientation, be constructed and operated in a specific orientation, and should not be construed as limiting the specific scope of the present invention.

Furthermore, if the terms "first" and "second" are used for descriptive purposes only, they are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features. Thus, a definition of "a first" or "a second" feature may explicitly or implicitly include one or more of the features, and in the description of the invention, "a number" or "a number" means two or more unless explicitly specified otherwise.

A hydraulic braking engine braking actuator comprises a rocker arm body 1, a control unit 3 and an actuating unit 8 are arranged on the rocker arm body 1,

the control unit 3 comprises a one-way valve assembly 2 and a control piston 13 assembly,

the check valve assembly 2 comprises a check valve body 9 and a check valve sealing seat 10, the check valve sealing seat 10 is fixedly connected with the check valve body 9, a through hole 41 is formed in the check valve sealing seat 10, a check valve 5 is arranged in the check valve body 9, a check valve spring 4 is arranged on one side, back to the check valve sealing seat 10, of the check valve 5, the check valve 5 abuts against the through hole 41 of the check valve sealing seat 10, a flow oil hole 43 is formed in the check valve body 9, and an execution piston high-pressure oil duct 7 communicated with the flow oil hole 43 is formed in the rocker arm body 1;

the control piston 13 assembly comprises a control piston 13 and a control piston push rod 11, the control piston push rod 11 is fixedly connected with the control piston 13, the control piston push rod 11 extends into a through hole 41 of the one-way valve sealing seat 10, one side of the control piston 13, which is opposite to the control piston push rod 11, is provided with a control piston inner spring 15, an oil injection space is reserved between the control piston 13 and the one-way valve sealing seat 10, and the rocker arm body 1 is provided with a brake oil inlet hole 12 communicated with the oil injection space;

the one-way valve assembly 2 and the control piston 13 assembly are coaxial, and the axial line is vertical to the rotation direction of the rocker arm body 1; as shown in fig. 10 and 12, i.e. the axis of the check valve assembly 2 and the control piston 13 assembly is parallel to the rocker shaft.

The execution unit 8 comprises an execution piston adjusting screw 20, an execution piston 33 and an execution piston limiting guide sleeve 24, the execution piston 33 comprises an execution piston upper body 22 and an execution piston lower body 25, the head of the execution piston adjusting screw 20 faces downwards, the inner side of the execution piston limiting guide sleeve 24 is connected to the execution piston adjusting screw 20 in a sliding mode, an execution piston spring 23 is arranged between the execution piston limiting guide sleeve 24 and the head of the execution piston adjusting screw 20, the execution piston upper body 22 is sleeved on the execution piston adjusting screw 20 from top to bottom, the execution piston lower body 25 is fixed with the execution piston upper body 22 from bottom, the execution piston spring 23 enables the top of the execution piston limiting guide sleeve 24 to abut against the execution piston upper body 22, and the top of the execution piston 33 is communicated with an execution piston high-pressure oil channel 7.

In this embodiment, the lower actuator piston body 25 and the upper actuator piston body 22 are fixed to each other by interference fit.

As shown in fig. 2, a check valve body oil chamber 6 is arranged in the check valve body 9, the check valve 5 is arranged in the check valve body oil chamber 6, and the oil flow hole 43 is communicated with the check valve body oil chamber 6 and the execution piston high-pressure oil passage 7; as shown in fig. 3 and 4, it is preferable that a ring groove is formed on an outer wall of the check valve 5, the ring groove communicating the oil flow hole 43 and the actuating piston high-pressure oil passage 7, and it is not necessary to align the oil flow hole 43 with the actuating piston high-pressure oil passage 7 at the time of installation.

In the state shown in fig. 1 and 2, the check valve assembly 2 is located above, the control piston 13 assembly is located below, the check valve assembly 2 is fixedly connected with the rocker body 1, the control piston 13 is in sealing sliding connection with the rocker body 1, and the control piston push rod 11 is in interference connection with the control piston 13.

As shown in fig. 5, 6 and 7, the actuator unit 8 in the present embodiment has the actuator piston 33 sealingly slidably connected to the rocker arm body 1, and an actuator piston high-pressure oil chamber 19 is formed between the actuator piston upper body 22 and the rocker arm body 1, and the actuator piston high-pressure oil chamber 19 communicates with the actuator piston high-pressure oil passage 7.

The specific working principle is as follows:

when the brake is started: as shown in fig. 2, the brake oil enters the oil filling space from the brake oil inlet hole 12, the control piston 13 carries the control piston push rod 11 to move downward under the action of the brake oil pressure, so that the control piston push rod 11 is separated from the check valve 5, the brake oil pushes away the check valve 5 to enter the check valve body oil cavity 6 from the through hole 41 along with the gradual entry of the brake oil, enters the execution piston high-pressure oil passage 7 through the oil flow hole 43 and the ring groove, and enters the execution unit 8 through the execution piston high-pressure oil passage 7; as shown in fig. 7, the brake oil fills the high-pressure oil chamber 19 of the actuating piston at the actuating unit 8, the brake oil pressure acts on the upper body 22 of the actuating piston, the hydraulic thrust generated thereby pushes the entire actuating piston 33 downward by the upper end of the actuating piston limiting guide 24 against the elastic force of the spring 23 of the actuating piston, and the lower end of the upper end of the actuating piston limiting.

As shown in FIG. 7, when the rocker arm body 1 rotates towards the exhaust valve 26, the actuating piston 33 pushes the exhaust valve sliding pin 27 and the exhaust valve 26, due to the action of the spring force of the exhaust valve 26, the actuating piston 33 reversely compresses the brake oil in the actuating piston high-pressure oil chamber 19 to form high-pressure oil, the high-pressure oil enters the one-way valve body oil chamber 6 formed by the one-way valve 5 through the actuating piston high-pressure oil channel 7 and presses the one-way valve 5 on the one-way valve sealing seat 10 to form a sealed high-pressure oil chamber, so that the actuating piston 33 cannot slide continuously, and the exhaust valve 26 can be opened.

When the brake is closed, no brake oil comes out from the brake oil inlet hole 12, the control piston 13 pushes the check valve 5 away from the check valve sealing seat 10 through the control piston push rod 11 under the action of the control piston inner spring 15, as shown in the state of fig. 1, under the action of the execution piston spring 23, the execution piston 33 and the execution piston limit guide sleeve 24 move upwards, so that the brake oil in the execution piston high-pressure oil chamber 19 enters the brake oil inlet hole 12 through a gap formed by the separation of the check valve 5 and the check valve sealing seat 10, the brake oil is discharged back to an oil inlet channel, a high-pressure oil chamber cannot be formed in the execution piston high-pressure oil chamber 19, and the execution piston 33 is at the highest point, as shown in the states of fig. 5 and 6, when the rocker arm body 1 rotates towards the exhaust valve 26, the exhaust valve 26 cannot.

In this embodiment, the actuating piston adjusting screw 20 is preferably in threaded connection with the rocker arm body 1, the top end of the actuating piston adjusting screw 20 preferably extends out of the rocker arm body 1, and the top end of the actuating piston adjusting screw 20 is connected with an actuating piston adjusting nut 21.

The actuating piston adjusting screw 20 has an operating hole at its top end, which may be a polygonal hole to facilitate the rotation of the actuating piston adjusting screw 20 with a tool.

According to the opening degree of the exhaust valve 26 that needs to be opened, that is, the lift of the exhaust valve 26 is controlled, the braking lift of the exhaust valve 26 is determined by the lowest position of the actuation piston 33 at the time of initiation of braking and the amount of extension of the actuation piston 33 at the time of braking; the lowest position of the actuating piston 33 can be set by adjusting the actuating piston adjusting nut 21 and the actuating piston adjusting screw rod 20 in the braking test; such as moving the actuator piston adjusting screw 20 a certain distance downwards or moving the actuator piston adjusting screw 20 a certain distance upwards to obtain the optimal lowest position of the actuator piston 33, i.e. the braking lift of the exhaust valve 26 at the optimal braking power.

This embodiment is preferred the rocking arm body 1 corresponds control piston 13 department and is provided with one-level cavity and second grade cavity, and the diameter of second grade cavity is greater than the diameter of one-level cavity, control piston 13 is located the one-level cavity, and control piston inner spring 15 extends to in the one-level cavity by the second grade cavity, be provided with control piston outer spring 14 in the second grade cavity, control piston outer spring 14's inner circle diameter is less than the diameter of one-level cavity, and control piston outer spring 14's outer lane diameter is greater than the diameter of one-level cavity.

As shown in fig. 1 and 2, the first-stage cavity is closer to the check valve assembly 2 than the second-stage cavity, the first-stage cavity is located above the second-stage cavity, the second-stage cavity is communicated with the outside, a control piston elastic check ring 18 is arranged on the inner wall of the second-stage cavity, a control piston gasket 17 is arranged above the control piston elastic check ring 18, an air leakage opening 16 is formed in the control piston gasket 17 to enable the second-stage cavity to be communicated with the outside, and the control piston inner spring 15 and the control piston outer spring 14 are both abutted to the control piston gasket 17.

When the brake is closed, high-pressure oil does not exist in the oil injection space, the brake piston and the brake piston push rod move upwards under the action of the spring in the brake piston, and the top end of the spring outside the brake piston abuts against the top of the secondary cavity; when the brake is opened, the brake oil is filled into the oil filling space to form high-pressure oil, the brake piston overcomes the elastic force of the spring in the brake piston to slide downwards, when the brake piston reaches the secondary cavity, the bottom end of the brake piston contacts the spring outside the brake piston, and the spring outside the brake piston can be used for buffering pressure waves during oil inlet.

In the preferred embodiment, the oil filling space is formed by forming a groove 42 in the check valve seal seat 10, the groove 42 is located on a surface of the check valve seal seat 10 facing the control piston 13, and the groove 42 communicates the through hole 41 and the brake oil inlet hole 12.

As shown in fig. 3 and 4, two grooves 42 are formed on a surface of the check valve seal seat 10 facing the control piston 13, the two grooves 42 radially penetrate the check valve seal seat 10, at least one end of one groove 42 is communicated with the brake oil inlet 12, although more grooves 42 may be formed, or other shapes may be formed, as shown in fig. 1, when the control piston 13 reaches a high point, the control valve is pushed open, and the brake oil flows back to the brake oil inlet 12 through the through hole 41 and the grooves 42.

In the embodiment, the check valve body 9 is preferably fixed to the check valve sealing seat 10 in a threaded manner, and the check valve sealing seat 10 is fixed to the rocker arm body 1 in a threaded manner.

Referring to fig. 9 and 10, in a method for applying a hydraulic brake engine brake actuator, the rocker arm body 1 is a separate brake rocker arm assembly 35, and the brake rocker arm assembly 35 and the exhaust rocker arm assembly 37 are arranged side by side and connected to the same exhaust rocker arm elephant foot assembly 29.

The brake rocker biasing leaf spring 31 biases the brake rocker against the brake cam 34 in normal contact with the brake cam 34, and brake lift on the brake cam 34 is transmitted through the brake rocker to the actuator unit 8.

After the brake rocker arm is installed, the lash between the actuator piston 33 and the exhaust valve slide pin 27 is set by the actuator piston adjustment screw 20 and the actuator piston adjustment nut 21.

When the brake is opened, the actuating mechanism is acted, the high-pressure oil chamber 19 of the actuating piston forms a high-pressure chamber, and the actuating piston 33 pushes the exhaust valve 26 to be opened; when the brake is closed, the actuator does not work, the brake oil in the high-pressure oil chamber 19 of the actuator piston is discharged back to the oil inlet passage from the brake oil inlet hole 12, and the actuator piston 33 is reset to the high point.

Wherein the brake rocker arm biasing leaf spring 31 is fixed on the rocker shaft assembly 36 by the rocker shaft mounting bolt 30, and the brake rocker arm biasing leaf spring 31 is prevented from being separated from the brake rocker arm by the positioning pin 32 on the brake rocker arm, thereby ensuring that the brake rocker arm is in a normal contact state with the brake cam 34.

As shown in fig. 11 and 12, in a method for applying a hydraulic braking engine brake actuator, the rocker arm body 1 is an exhaust rocker arm assembly 37, and the control unit 3 and the actuator unit 8 are integrated in the exhaust rocker arm assembly 37.

Adjacent the exhaust rocker arm assembly 37 in fig. 12 is an intake rocker arm assembly 40.

In this case, the exhaust rocker arm assembly 37 is the rocker arm body 1, wherein the braking lift on the exhaust cam 39 is transmitted to the actuator via the exhaust rocker arm assembly 37. When the brake is opened, the actuating mechanism is acted, the high-pressure oil chamber 19 of the actuating piston forms a high-pressure chamber, and the actuating piston 33 pushes the exhaust valve 26 to be opened; when the brake is closed, the actuator does not work, the brake oil in the high-pressure oil chamber 19 of the actuator piston is discharged back to the oil inlet passage from the brake oil inlet hole 12, and the actuator piston 33 is reset to the high point.

The actuating mechanism of the invention is easy to be arranged on various engines, and the hydraulic driving mechanism occupies small space.

The above description is only a preferred embodiment of the present invention, and the protection scope of the present invention is not limited to the above embodiments, and all technical solutions belonging to the idea of the present invention belong to the protection scope of the present invention. It should be noted that modifications and embellishments within the scope of the invention may occur to those skilled in the art without departing from the principle of the invention, and are considered to be within the scope of the invention.

Claims

1. A hydraulic braking engine braking actuating mechanism comprises a rocker arm body and is characterized in that a control unit and an actuating unit are arranged on the rocker arm body,

2. The hydraulically braked engine brake actuator as set forth in claim 1, wherein: the execution piston adjusting screw is in threaded connection with the rocker body.

3. The hydraulically braked engine brake actuator as set forth in claim 2, wherein: the top end of the execution piston adjusting screw rod extends out of the rocker arm body, and the top end of the execution piston adjusting screw rod is connected with an execution piston adjusting nut.

4. The hydraulically braked engine brake actuator as set forth in claim 1, wherein: the rocker arm body is provided with one-level cavity and second grade cavity corresponding to control piston, and the diameter of second grade cavity is greater than the diameter of one-level cavity, control piston is located the one-level cavity, and control piston inner spring extends to the one-level cavity by the second grade cavity in, be provided with control piston outer spring in the second grade cavity, the inner circle diameter of control piston outer spring is less than the diameter of one-level cavity, and control piston outer spring's outer lane diameter is greater than the diameter of one-level cavity.

5. The hydraulically braked engine brake actuator as set forth in claim 4, wherein: the secondary cavity is communicated with the outside.

6. The hydraulically braked engine brake actuator as set forth in claim 1, wherein: the oil injection space is formed by arranging a groove on the one-way valve sealing seat, the groove is positioned on one surface, facing the control piston, of the one-way valve sealing seat, and the groove is communicated with the through hole and the brake oil inlet hole.

7. The hydraulically braked engine brake actuator as set forth in claim 6, wherein: the one-way valve body is fixedly connected with the one-way valve sealing seat through threads, and the one-way valve sealing seat is fixedly connected with the rocker body through threads.

8. A method of applying a hydraulically braked engine brake actuator as claimed in any one of claims 1 to 7, characterized in that: the rocker arm body is an independent brake rocker arm, and the brake rocker arm and the exhaust rocker arm assembly are arranged side by side and connected to the same exhaust rocker arm elephant foot assembly.

9. A method of applying a hydraulically braked engine brake actuator as claimed in any one of claims 1 to 7, characterized in that: the rocker body is an exhaust rocker assembly, and the control unit and the execution unit are integrated in the exhaust rocker assembly.