Engine brake rocker arm, design method and vehicle

Abstract

The present application relates to an engine brake rocker arm, a design method, and a vehicle, and relates to the technical field of engine brake rocker arms. The application includes a rocker arm body, which is rotatably arranged on a rocker arm shaft. The two ends of the rocker arm body are respectively used to abut against a brake cam and a valve assembly, and the rocker arm body is provided with an abutment boss; an elastic retaining mechanism, one end of which is connected to the abutment boss, and the other end is used to connect to the rocker arm shaft or a rocker arm shaft support. The elastic retaining mechanism is used to maintain a gap between the rocker arm body and the brake cam and the valve assembly when the rocker arm body is in a non-braking condition. Because the elastic retaining mechanism maintains a gap between the rocker arm body and the brake cam and the valve assembly when the rocker arm body is in a non-braking condition, the brake rocker arm does not move when the engine is in a non-braking condition, which greatly reduces the frequency of use and the power consumption of the engine. It also solves the problem in the prior art that the bushing of the brake rocker arm is easily side-loaded, which may affect the normal use of the engine.

Description

Technical Field

[0001] The present invention relates to the technical field of engine brake rocker arms, and in particular to an engine brake rocker arm, a design method and a vehicle. Background Art

[0002] There are two main types of engine brake rocker arms: dedicated brake rocker arms and integrated brake rocker arms with integrated exhaust rocker arm functions. For dedicated brake rocker arms, the brake piston does not extend during non-braking conditions, and the gap between the brake rocker arm and the parts on the transmission chain is large. Since the brake cam is still driving the brake rocker arm to run in vain, in order to prevent uncontrollable movements such as repeated collisions between the brake rocker arm and related parts, special parts are needed to constrain the entire movement process of the brake rocker arm. The main method currently used is to constrain the entire movement process of the brake rocker arm with special springs.

[0003] In the prior art, since the negative acceleration of the brake rocker arm driven by the brake cam is very large, and the mass of the brake rocker arm is generally very large, in order to prevent uncontrollable situations such as flying off, a spring bias with greater force is required to be arranged on the brake rocker arm to constrain the movement of the brake rocker arm.

[0004] However, since this spring force is relatively large and the spring is offset on the brake rocker arm, it is easy to generate side loads on the bushing of the brake rocker arm, causing wear. In addition, the large spring force is not conducive to the power consumption of the engine itself, which may affect the normal use of the engine. Summary of the Invention

[0005] The present application provides an engine brake rocker arm, a design method and a vehicle, which can solve the problem in the prior art that, due to the relatively large spring force and the spring being offset on the brake rocker arm, it is easy to generate side loads on the bushing of the brake rocker arm, causing wear, and the large spring force is also not conducive to the power consumption of the engine itself, which may affect the normal use of the engine.

[0006] In a first aspect, an embodiment of the present application provides an engine brake rocker arm, comprising:

[0007] A rocker arm body, which is rotatably disposed on the rocker arm shaft, with two ends of the rocker arm body respectively used to abut against the brake cam and the valve assembly, and an abutment boss is provided on the rocker arm body;

[0008] An elastic retaining mechanism, one end of which is connected to the abutment boss, and the other end is used to connect to the rocker arm shaft or rocker arm shaft support. The elastic retaining mechanism is used to maintain a gap between the rocker arm body and the brake cam and valve assembly when the rocker arm body is in a non-braking condition.

[0009] In one embodiment, the elastic retaining mechanism comprises:

[0010] A straight section, which is used to be fixedly arranged on the rocker arm shaft;

[0011] A semicircular arc segment, whose end is connected to the straight segment, is used to be wrapped around the abutment boss so that when the rocker arm body is in a non-braking condition, a gap is maintained between it and the brake cam and the valve assembly.

[0012] In one embodiment, the semicircular arc segment includes a connecting segment and a wrapping segment, the connecting segment is connected to the straight segment, the wrapping segment is used to be wrapped around the abutment boss, the outer side of the wrapping segment is aligned with the end of the abutment boss, the width of the connecting segment is the same as the width of the straight segment and is greater than the width of the wrapping segment.

[0013] In one embodiment, the abutment boss is a stepped boss, and the outer diameter of the small-diameter boss of the abutment boss matches the inner diameter of the semicircular arc segment.

[0014] In one embodiment, the elastic retaining mechanism comprises:

[0015] Two fixing bosses, one of which is arranged on the abutting boss, and the other is used to be arranged on the rocker shaft support;

[0016] The retaining spring has two ends connected to the two fixing bosses respectively.

[0017] In one embodiment, a connecting through hole is provided on the fixing boss, and connecting components are provided at both ends of the retaining spring, and the connecting components include:

[0018] a support plate connected to the end of the retaining spring and abutting against the fixing boss;

[0019] The connecting piece includes a screw and a nut. The screw is arranged on the support plate and passes through the connecting through hole. The nut is arranged on the screw and is spaced apart from the support plate and abuts against the side of the fixing boss away from the support plate.

[0020] In a second aspect, an embodiment of the present application further provides a method for designing an engine brake rocker arm, which is used to design the above-mentioned engine brake rocker arm, comprising:

[0021] Obtaining the elastic force that the elastic retaining mechanism needs to provide to maintain clearance between the rocker arm body, the brake cam, and the valve assembly when the rocker arm body is in a non-braking condition;

[0022] The size of the elastic retaining mechanism is selected based on the positional relationship of the installation points of the elastic retaining mechanism and the set gap size;

[0023] The elastic parameters of the elastic holding mechanism are obtained according to the size and elastic force of the elastic holding mechanism.

[0024] In one embodiment, after obtaining the elastic parameters of the elastic retaining mechanism according to the size and elastic force of the elastic retaining mechanism, the method further includes:

[0025] determining whether the structural stiffness of the elastic parameters of the elastic retaining mechanism meets the engine resonance requirement;

[0026] If not, the size of the selected elastic retaining mechanism is adjusted until the structural stiffness of the elastic parameters of the obtained elastic retaining mechanism meets the engine resonance requirement.

[0027] In one embodiment, after obtaining the elastic parameters of the elastic retaining mechanism according to the size and elastic force of the elastic retaining mechanism, the method further includes:

[0028] Determining the relationship between the elastic force and the push-out force of the hydraulic piston in the rocker arm body;

[0029] If the difference between the hydraulic piston pushing force and the elastic force is smaller than the set value, the size of the elastic retaining mechanism is adjusted.

[0030] In a third aspect, an embodiment of the present application further provides a vehicle comprising the above-mentioned engine brake rocker arm.

[0031] The beneficial effects of the technical solutions provided in the embodiments of the present application include:

[0032] When manufacturing this engine brake rocker arm, the rocker arm body is rotatably mounted on the rocker arm shaft. The rocker arm body's two ends are respectively configured to abut against the brake cam and valve assembly. The rocker arm body is provided with an abutment boss. An elastic retaining mechanism is connected at one end to the abutment boss and at the other end to the rocker arm shaft or rocker arm shaft support. The elastic retaining mechanism is configured to maintain clearance between the rocker arm body and the brake cam and valve assembly when the rocker arm body is in a non-braking state. The design of the elastic retaining mechanism involves first determining the elastic force required by the elastic retaining mechanism to maintain clearance between the rocker arm body and the brake cam and valve assembly when the rocker arm body is in a non-braking state. The dimensions of the elastic retaining mechanism are then determined based on the positional relationship between the elastic retaining mechanism's mounting points and the desired clearance size. Finally, the elastic parameters of the elastic retaining mechanism are determined based on the dimensions and elastic force of the elastic retaining mechanism. Because the elastic retaining mechanism maintains a gap between the rocker arm body and the brake cam and valve assembly when the rocker arm is in a non-braking condition, the brake rocker arm does not move when the engine is in a non-braking condition, which greatly reduces the frequency of use and reduces the engine power consumption. It also solves the problem in the prior art that due to the relatively large spring force and the spring offset arrangement on the brake rocker arm, it is easy to generate side loads on the bushing of the brake rocker arm, causing wear, and the large spring force is not conducive to the power consumption of the engine itself, which may affect the normal use of the engine. BRIEF DESCRIPTION OF THE DRAWINGS

[0033] In order to more clearly illustrate the technical solutions in the embodiments of the present application, the following briefly introduces the drawings required for use in the description of the embodiments. Obviously, the drawings described below are only some embodiments of the present application. For ordinary technicians in this field, other drawings can be obtained based on these drawings without any creative work.

[0034] Figure 1 This is a schematic structural diagram of an engine brake rocker arm embodiment of the present invention in a non-braking condition.

[0035] Figure 2 This is a structural schematic diagram of an engine brake rocker arm embodiment of the present invention in which a gap exists between the rocker arm body and the brake cam.

[0036] Figure 3 This is a structural schematic diagram of an engine brake rocker arm embodiment of the present invention in which a gap exists between the rocker arm body and the valve assembly.

[0037] Figure 4 This is a structural schematic diagram of a first elastic retaining mechanism in an embodiment of an engine brake rocker arm of the present invention.

[0038] Figure 5 This is a structural schematic diagram of a rocker arm body when an embodiment of an engine brake rocker arm of the present invention adopts the first elastic retaining mechanism.

[0039] Figure 6 This is a front view of the installation of a first elastic retaining mechanism in an embodiment of an engine brake rocker arm of the present invention.

[0040] Figure 7 This is a schematic side view of the installation of a first elastic retaining mechanism in an embodiment of an engine brake rocker arm of the present invention.

[0041] Figure 8 This is a schematic diagram of the installation of a second elastic retaining mechanism in an embodiment of an engine brake rocker arm of the present invention.

[0042] Figure 9 This is a schematic cross-sectional view of the installation of a second elastic retaining mechanism in an embodiment of an engine brake rocker arm of the present invention.

[0043] Figure 10 This is a structural schematic diagram of a second elastic retaining mechanism in an embodiment of an engine brake rocker arm of the present invention.

[0044] Figure 11 This is a schematic structural diagram of a rocker arm shaft support in an embodiment of an engine brake rocker arm of the present invention.

[0045] Figure 12 This is a schematic structural diagram of a rocker arm body when an embodiment of an engine brake rocker arm of the present invention adopts the second elastic retaining mechanism.

[0046] In the figure: 1. Rocker arm body; 11. Abutment boss; 12. Hydraulic piston; 13. Rocker arm shaft bushing hole; 14. Rocker arm roller; 2. Brake cam; 3. Valve assembly; 31. Valve push rod; 4. Elastic retaining mechanism; 41. Straight section; 42. Semicircular arc section; 421. Connecting section; 422. Envelope section; 43. Thickened gasket; 44. Fixed boss; 45. Retaining spring; 46. Connecting assembly; 461. Support plate; 462. Screw; 463. Nut; 5. Rocker arm shaft; 6. Rocker arm shaft support; 61. Rocker arm shaft mounting hole; 62. Camshaft mounting hole; 7. Valve yoke; 8. Exhaust rocker arm; 9. Camshaft. DETAILED DESCRIPTION

[0047] In order to enable those skilled in the art to better understand the present invention, the following will clearly and completely describe the technical solutions in the embodiments of the present invention in conjunction with the accompanying drawings. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of this application.

[0048] The embodiments of the present application provide an engine brake rocker arm, a design method, and a vehicle, which can solve the problem in the prior art that, due to the relatively large spring force and the spring being offset on the brake rocker arm, it is easy to generate side loads on the bushing of the brake rocker arm, causing wear, and the large spring force is also not conducive to the power consumption of the engine itself, which may affect the normal use of the engine.

[0049] like Figure 1 、 Figure 2 、 Figure 3 、 Figure 5 、 Figure 6 、 Figure 7 、 Figure 8 、 Figure 9 and Figure 12 As shown, on one hand, the present application provides an engine brake rocker arm, which includes:

[0050] The rocker arm body 1 is rotatably mounted on the rocker arm shaft 5. The two ends of the rocker arm body 1 are respectively used to abut against the brake cam 2 and the valve assembly 3. The rocker arm body 1 is provided with an abutment boss 11.

[0051] The elastic retaining mechanism 4 has one end connected to the abutment boss 11 and the other end used to connect to the rocker arm shaft 5 or the rocker arm shaft support 6. The elastic retaining mechanism 4 is used to maintain a gap between the rocker arm body 1 and the brake cam 2 and the valve assembly 3 when the rocker arm body 1 is in a non-braking working condition.

[0052] When manufacturing the engine brake rocker arm, the rocker arm body 1 is rotatably mounted on the rocker arm shaft 5. The two ends of the rocker arm body 1 are respectively used to abut against the brake cam 2 and the valve assembly 3. The rocker arm body 1 is provided with an abutment boss 11. An elastic retaining mechanism 4 is connected to the abutment boss 11 at one end and to the rocker arm shaft 5 or the rocker arm shaft support 6 at the other end. The elastic retaining mechanism 4 is used to maintain a gap between the rocker arm body 1 and the brake cam 2 and the valve assembly 3 when the rocker arm body 1 is in a non-braking condition. During the design process of the elastic retaining mechanism 4, the elastic force required by the elastic retaining mechanism 4 to maintain a gap between the rocker arm body 1 and the brake cam 2 and the valve assembly 3 when the rocker arm body 1 is in a non-braking condition is first determined. The size of the elastic retaining mechanism 4 is selected based on the positional relationship between the mounting points of the elastic retaining mechanism 4 and the set gap size. The elastic parameters of the elastic retaining mechanism 4 are determined based on the size and elastic force of the elastic retaining mechanism 4. Because the elastic retaining mechanism 4 maintains a gap between the rocker arm body 1 and the brake cam 2 and the valve assembly 3 when the rocker arm body 1 is in a non-braking condition, the rocker arm body 1 does not move under the non-braking condition of the engine, which greatly reduces the frequency of use and reduces the engine power consumption. It also solves the problem in the prior art that due to the relatively large force of this spring and the spring offset arrangement on the brake rocker arm, it is easy to generate side load on the bushing of the brake rocker arm, causing wear and tear, which may affect the normal use of the engine.

[0053] In this example, the piston stroke in the rocker arm body 1 should be greater than the sum of the gap between the rocker arm body 1 and the brake cam 2 and the valve assembly 3 when the rocker arm body 1 is in a non-braking condition, plus the valve lift generated by the cam lift.

[0054] In this example, the rocker arm body 1 is provided with a rocker arm roller 14, which is used to abut the brake cam 2. The rocker arm body 1 is provided with a hydraulic piston 12, which is used to abut the valve push rod 31 in the valve assembly 3. The rocker arm body 1 is provided with a rocker arm shaft bushing hole 13, which is used to allow the rocker arm shaft 5 to pass through.

[0055] like Figure 4 、 Figure 6 and Figure 7 As shown, in some optional embodiments, the elastic retaining mechanism 4 includes:

[0056] The straight section 41 is fixedly mounted on the rocker shaft 5;

[0057] The semicircular arc segment 42 has its end connected to the straight segment 41. The semicircular arc segment 42 is used to be wrapped around the abutment boss 11 so that when the rocker arm body 1 is in a non-braking condition, a gap is maintained between it and the brake cam 2 and the valve assembly 3.

[0058] In this embodiment, the structure of the elastic retaining mechanism 4 is specifically described. The elastic retaining mechanism 4 includes a straight section 41 and a semicircular arc section 42, wherein the straight section 41 is fixedly arranged on the rocker arm shaft 5, and the end of the semicircular arc section 42 is connected to the straight section 41. The semicircular arc section 42 is used to be wrapped around the abutment boss 11. The elastic force provided by the elastic retaining mechanism 4 maintains a gap between the rocker arm body 1 and the brake cam 2 and the valve assembly 3 when the rocker arm body 1 is in a non-braking condition. The structure is simple and easy to manufacture.

[0059] In this example, the straight section 41 is fixed to the rocker shaft 5 by bolts. A thickened gasket 43 is provided on the lower side of the straight section 41.

[0060] like Figure 4 、 Figure 6 and Figure 7 As shown, in some optional embodiments, the semicircular arc segment 42 includes a connecting segment 421 and a wrapping segment 422, the connecting segment 421 is connected to the straight segment 41, the wrapping segment 422 is used to wrap around the abutting boss 11, the outer side of the wrapping segment 422 is aligned with the end of the abutting boss 11, the width of the connecting segment 421 is the same as the width of the straight segment 41, and is greater than the width of the wrapping segment 422.

[0061] In this embodiment, the specific structure of the semicircular arc segment 42 is described. The semicircular arc segment 42 includes a connecting segment 421 and a wrapping segment 422, wherein the connecting segment 421 is connected to the straight segment 41, and the wrapping segment 422 is used to wrap around the abutting boss 11. The outer side of the wrapping segment 422 is aligned with the end of the abutting boss 11, and the width of the connecting segment 421 is the same as the width of the straight segment 41 and is larger than the width of the wrapping segment 422. The increase in the width of the connecting segment 421 is beneficial to the stability of the connection. Since the outer side of the wrapping segment 422 is aligned with the end of the abutting boss 11, keeping the width of the connecting segment 421 the same as the width of the wrapping segment 422 does not improve the stability, but rather there is a problem of wasting materials and installation space. The overall structure is simple and has high stability.

[0062] like Figure 4 、 Figure 5 、 Figure 6 and Figure 7 As shown, in some optional embodiments, the abutting boss 11 is a stepped platform, and the outer diameter of the small-diameter platform of the abutting boss 11 matches the inner diameter of the semicircular arc segment 42 .

[0063] In this embodiment, the abutment boss 11 is set as a stepped platform, and the outer diameter of the small diameter platform of the abutment boss 11 matches the inner diameter of the semicircular arc segment 42, so that when the rocker arm body 1 is in a non-braking condition, a gap is maintained between it and the brake cam 2 and the valve assembly 3. The entire circumference of the abutment boss 11 is a machined surface, which ensures the matching accuracy with the semicircular arc segment 42, and has a relatively low roughness, thereby reducing friction and wear of the friction pair.

[0064] like Figure 8 、 Figure 9 、 Figure 10 、 Figure 11 and Figure 12 As shown, in some optional embodiments, the elastic retaining mechanism 4 includes:

[0065] Two fixing bosses 44, one of which is provided on the abutting boss 11, and the other fixing boss 44 is used to be provided on the rocker shaft support 6;

[0066] The two ends of the retaining spring 45 are respectively connected to the two fixing bosses 44 .

[0067] In this embodiment, the structure of the elastic retaining mechanism 4 is specifically described. The elastic retaining mechanism 4 includes a retaining spring 45 and two fixed bosses 44, one of which is arranged on the abutting boss 11, and the other fixed boss 44 is used to be arranged on the rocker shaft support 6. The two ends of the retaining spring 45 are respectively connected to the two fixed bosses 44. The structure is simple and convenient for design and installation.

[0068] like Figure 8 、 Figure 10 、 Figure 11and Figure 12 As shown, in some optional embodiments, a connecting through hole is provided on the fixing boss 44, and connecting components 46 are provided at both ends of the retaining spring 45. The connecting components 46 include:

[0069] a support plate 461 connected to the end of the retaining spring 45 and abutting against the fixing boss 44;

[0070] The connecting piece includes a screw 462 and a nut 463. The screw 462 is set on the support plate 461 and passes through the connecting through hole. The nut 463 is set on the screw 462 and is spaced apart from the support plate 461 and abuts against the side of the fixing boss 44 away from the support plate 461.

[0071] In this embodiment, a connecting through hole is provided on the fixing boss 44, and connecting components 46 are provided at both ends of the retaining spring 45. The connecting component 46 includes a support plate 461 and a connecting piece, wherein the support plate 461 is connected to the end of the retaining spring 45 and abuts on the fixing boss 44. The connecting piece includes a screw 462 and a nut 463. The screw 462 is set on the support plate 461, and the screw 462 passes through the connecting through hole. The nut 463 is set on the screw 462 and is spaced apart from the support plate 461, and abuts on the side of the fixing boss 44 away from the support plate 461, which is convenient for setting the retaining spring 45 on the fixing boss 44. At the same time, if the retaining spring 45 is damaged, it is also convenient for disassembly and replacement.

[0072] In one aspect, the present application further provides a method for designing an engine brake rocker arm, which is used to design the above-mentioned engine brake rocker arm, comprising:

[0073] Obtain the elastic force that the elastic retaining mechanism 4 needs to provide to maintain clearance between the rocker arm body 1 and the brake cam 2 and the valve assembly 3 when the rocker arm body 1 is in a non-braking condition;

[0074] The size of the elastic retaining mechanism 4 is selected according to the positional relationship of the mounting points of the elastic retaining mechanism 4 and the set gap size;

[0075] The elastic parameters of the elastic holding mechanism 4 are obtained according to the size and elastic force of the elastic holding mechanism 4 .

[0076] When manufacturing the engine brake rocker arm, the rocker arm body 1 is rotatably mounted on the rocker arm shaft 5. The two ends of the rocker arm body 1 are respectively used to abut against the brake cam 2 and the valve assembly 3. The rocker arm body 1 is provided with an abutment boss 11. An elastic retaining mechanism 4 is connected to the abutment boss 11 at one end and to the rocker arm shaft 5 or the rocker arm shaft support 6 at the other end. The elastic retaining mechanism 4 is used to maintain a gap between the rocker arm body 1 and the brake cam 2 and the valve assembly 3 when the rocker arm body 1 is in a non-braking condition. During the design process of the elastic retaining mechanism 4, the elastic force required by the elastic retaining mechanism 4 to maintain a gap between the rocker arm body 1 and the brake cam 2 and the valve assembly 3 when the rocker arm body 1 is in a non-braking condition is first determined. The size of the elastic retaining mechanism 4 is selected based on the positional relationship between the mounting points of the elastic retaining mechanism 4 and the set gap size. The elastic parameters of the elastic retaining mechanism 4 are determined based on the size and elastic force of the elastic retaining mechanism 4. Because the elastic retaining mechanism 4 maintains a gap between the rocker arm body 1 and the brake cam 2 and the valve assembly 3 when the rocker arm body 1 is in a non-braking condition, the rocker arm body 1 does not move under the non-braking condition of the engine, which greatly reduces the frequency of use and reduces the engine power consumption. It also solves the problem in the prior art that due to the relatively large force of this spring and the spring offset arrangement on the brake rocker arm, it is easy to generate side load on the bushing of the brake rocker arm, causing wear and tear, which may affect the normal use of the engine.

[0077] In this example, the set gap size refers to the gap size maintained between the rocker arm body 1 and the valve assembly 3 when the rocker arm body is in a non-braking condition. The installation point position relationship of the elastic retaining mechanism 4 refers to the connection point position relationship between the elastic retaining mechanism 4 and the rocker arm body 1, as well as the connection point position relationship between the elastic retaining mechanism 4 and the rocker arm shaft 5 or the rocker arm shaft support 6.

[0078] In some optional embodiments, after obtaining the elastic parameters of the elastic retaining mechanism 4 according to the size and elastic force of the elastic retaining mechanism 4, the method further includes:

[0079] Determining whether the structural stiffness of the elastic parameters of the elastic retaining mechanism 4 meets the engine resonance requirement;

[0080] If not, the size of the selected elastic retaining mechanism 4 is adjusted until the structural stiffness of the obtained elastic parameters of the elastic retaining mechanism 4 meets the engine resonance requirement.

[0081] In this embodiment, after obtaining the elastic parameters of the elastic retaining mechanism 4 based on the size and elastic force of the elastic retaining mechanism 4, it is also necessary to determine whether the structural stiffness in the elastic parameters of the elastic retaining mechanism 4 meets the engine resonance requirements. If not, adjust the selected size of the elastic retaining mechanism 4 until the structural stiffness in the obtained elastic parameters of the elastic retaining mechanism 4 meets the engine resonance requirements to prevent safety hazards.

[0082] In this case, according to the formula: Where F is the elastic force, N r is the maximum speed of the engine camshaft 9, K is the structural stiffness of the elastic parameters of the elastic retaining mechanism 4, and M is the equivalent mass of the elastic retaining mechanism 4 on the rocker arm body 1.

[0083] In some optional embodiments, after obtaining the elastic parameters of the elastic retaining mechanism 4 according to the size and elastic force of the elastic retaining mechanism 4, the method further includes:

[0084] Determine the relationship between the elastic force and the push-out force of the hydraulic piston 12 in the rocker arm body 1;

[0085] If the difference between the pushing force of the hydraulic piston 12 and the elastic force is smaller than the set value, the size of the elastic retaining mechanism 4 is adjusted.

[0086] In this embodiment, after obtaining the elastic parameters of the elastic retaining mechanism 4 based on the size and elastic force of the elastic retaining mechanism 4, it is also necessary to determine the relationship between the elastic force and the pushing force of the hydraulic piston 12 in the rocker arm body 1. If the difference between the pushing force of the hydraulic piston 12 and the elastic force is less than the set value, the size of the elastic retaining mechanism 4 is adjusted to reduce the structural stiffness in the elastic parameters of the elastic retaining mechanism 4 to prevent obstruction of the normal operation of the hydraulic piston 12. This is equivalent to increasing the deformation of the elastic retaining mechanism 4 and reducing the structural stiffness. Since the extreme position of the movement of the hydraulic piston 12 is fixed, the obstruction that the hydraulic piston 12 still needs to overcome can be reduced.

[0087] In this example, this step is before determining whether the structural rigidity of the elastic parameters of the elastic retaining mechanism 4 meets the engine resonance requirement. The set value is a limit value that does not affect the operation of the valve push rod 31.

[0088] In this example, if adjusting the size of the elastic retaining mechanism 4 still fails to achieve the expected effect, the position relationship of the installation point of the elastic retaining mechanism 4 can also be adjusted. By changing the position relationship of the connection point between the elastic retaining mechanism 4 and the rocker arm body 1, as well as the position relationship of the connection point between the elastic retaining mechanism 4 and the rocker arm shaft 5 or the rocker arm shaft support 6, the deformation amount of the elastic retaining mechanism 4 in the non-braking condition is adjusted, thereby changing the elastic force in the elastic parameters of the elastic retaining mechanism 4.

[0089] like Figure 1 、 Figure 2 、 Figure 3 、 Figure 5 、 Figure 6 、 Figure 7 、 Figure 8 、 Figure 9 、 Figure 11 and Figure 12As shown, on the other hand, the present application also provides a vehicle, which includes the above-mentioned engine brake rocker arm.

[0090] When manufacturing the engine brake rocker arm, the rocker arm body 1 is rotatably mounted on the rocker arm shaft 5. The two ends of the rocker arm body 1 are respectively used to abut against the brake cam 2 and the valve assembly 3. The rocker arm body 1 is provided with an abutment boss 11. An elastic retaining mechanism 4 is connected to the abutment boss 11 at one end and to the rocker arm shaft 5 or the rocker arm shaft support 6 at the other end. The elastic retaining mechanism 4 is used to maintain a gap between the rocker arm body 1 and the brake cam 2 and the valve assembly 3 when the rocker arm body 1 is in a non-braking condition. During the design process of the elastic retaining mechanism 4, the elastic force required by the elastic retaining mechanism 4 to maintain a gap between the rocker arm body 1 and the brake cam 2 and the valve assembly 3 when the rocker arm body 1 is in a non-braking condition is first determined. The size of the elastic retaining mechanism 4 is selected based on the positional relationship between the mounting points of the elastic retaining mechanism 4 and the set gap size. The elastic parameters of the elastic retaining mechanism 4 are determined based on the size and elastic force of the elastic retaining mechanism 4. Because the elastic retaining mechanism 4 maintains a gap between the rocker arm body 1 and the brake cam 2 and the valve assembly 3 when the rocker arm body 1 is in a non-braking condition, the rocker arm body 1 does not move under the non-braking condition of the engine, which greatly reduces the frequency of use and reduces the engine power consumption. It also solves the problem in the prior art that due to the relatively large force of this spring and the spring offset arrangement on the brake rocker arm, it is easy to generate side load on the bushing of the brake rocker arm, causing wear and tear, which may affect the normal use of the engine.

[0091] In this example, the rocker shaft support 6 is provided with a rocker shaft mounting hole 61 and a camshaft mounting hole 62, respectively for mounting the rocker shaft 5 and camshaft 9. An exhaust rocker arm 8 is also included, and the valve assembly 3 is provided with a valve yoke 7, the upper end of which is used to abut against the exhaust rocker arm 8.

[0092] In the description of this application, it should be noted that the terms "upper" and "lower" and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on this application. Unless otherwise clearly specified and limited, the terms "installed", "connected", and "connected" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection, or an indirect connection through an intermediate medium, or it can be internal communication between two elements. For those of ordinary skill in the art, the specific meanings of the above terms in this application can be understood according to the specific circumstances.

[0093] It should be noted that, in this application, relational terms such as "first" and "second" are used only to distinguish one entity or operation from another entity or operation, and do not necessarily require or imply any actual relationship or order between these entities or operations. Moreover, the terms "include", "comprise" or any other variants thereof are intended to cover non-exclusive inclusion, so that a process, method, article or device comprising a series of elements includes not only those elements, but also other elements not explicitly listed, or also includes elements inherent to such process, method, article or device. In the absence of further restrictions, an element defined by the sentence "comprising a ..." does not exclude the presence of other identical elements in the process, method, article or device comprising the element.

[0094] The foregoing is merely a list of specific embodiments of the present application, intended to enable those skilled in the art to understand or implement the present application. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the general principles defined herein may be implemented in other embodiments without departing from the spirit or scope of the present application. Therefore, the present application is not limited to the embodiments shown herein, but is intended to conform to the broadest scope consistent with the principles and novel features of the present application.

Claims

1. An engine brake rocker arm, characterized in that: include: A rocker arm body (1) is rotatably arranged on a rocker arm shaft (5), with two ends of the rocker arm body (1) respectively used to abut against a brake cam (2) and a valve assembly (3), and an abutment boss (11) is provided on the rocker arm body (1); an elastic retaining mechanism (4), one end of which is connected to the abutting boss (11), and the other end of which is used to be connected to the rocker arm shaft (5) or the rocker arm shaft support (6), wherein the elastic retaining mechanism (4) is used to maintain a gap between the rocker arm body (1) and the brake cam (2) and the valve assembly (3) when the rocker arm body (1) is in a non-braking condition; The elastic retaining mechanism (4) comprises: A straight section (41) for being fixedly arranged on the rocker arm shaft (5); a semicircular arc segment (42), the end of which is connected to the straight segment (41); the semicircular arc segment (42) is used to be wrapped around the abutment boss (11) so that when the rocker arm body (1) is in a non-braking condition, a gap is maintained between the rocker arm body (1) and the brake cam (2) and the valve assembly (3); The semicircular arc section (42) comprises a connecting section (421) and a wrapping section (422), wherein the connecting section (421) is connected to the straight section (41), and the wrapping section (422) is used to wrap around the abutting boss (11), and the outer side of the wrapping section (422) is aligned with the end of the abutting boss (11), and the width of the connecting section (421) is the same as the width of the straight section (41) and is greater than the width of the wrapping section (422).

2. The engine brake rocker arm according to claim 1, characterized in that: The abutting boss (11) is a stepped platform, and the outer diameter of the small-diameter platform of the abutting boss (11) matches the inner diameter of the semicircular arc segment (42).

3. A design method for an engine brake rocker arm, characterized in that: For designing an engine brake rocker arm as claimed in claim 1 or 2, comprising: Obtaining the elastic force that the elastic retaining mechanism (4) needs to provide in order to maintain a gap between the rocker arm body (1) and the brake cam (2) and the valve assembly (3) when the rocker arm body (1) is in a non-braking condition; The size of the elastic retaining mechanism (4) is selected based on the positional relationship of the mounting points of the elastic retaining mechanism (4) and the set gap size; The elastic parameters of the elastic retaining mechanism (4) are obtained according to the size and elastic force of the elastic retaining mechanism (4).

4. The method for designing an engine brake rocker arm according to claim 3, wherein: After obtaining the elastic parameters of the elastic retaining mechanism (4) based on the size and elastic force of the elastic retaining mechanism (4), the method further includes: Determining whether the structural stiffness of the elastic parameters of the elastic retaining mechanism (4) meets the engine resonance requirement; If not, the size of the selected elastic retaining mechanism (4) is adjusted until the structural stiffness in the elastic parameters of the obtained elastic retaining mechanism (4) meets the engine resonance requirement.

5. The method for designing an engine brake rocker arm according to claim 3, wherein: After obtaining the elastic parameters of the elastic retaining mechanism (4) based on the size and elastic force of the elastic retaining mechanism (4), the method further includes: Determining the relationship between the elastic force and the pushing force of the hydraulic piston (12) in the rocker arm body (1); If the difference between the pushing force of the hydraulic piston (12) and the elastic force is smaller than a set value, the size of the elastic retaining mechanism (4) is adjusted.

6. A vehicle, characterized in that: The invention comprises an engine brake rocker arm as claimed in claim 1 or 2.

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