CN113915271A

CN113915271A - Gearbox auxiliary suspension soft cushion assembly for heavy truck

Info

Publication number: CN113915271A
Application number: CN202111121588.2A
Authority: CN
Inventors: 董加加; 胡少峰; 关大鹏; 魏青松; 刘沭靓
Original assignee: Baic Changzhou Automobile Co ltd
Current assignee: Baic Changzhou Automobile Co ltd; BAIC Changzhou Automotive Co Ltd
Priority date: 2021-09-24
Filing date: 2021-09-24
Publication date: 2022-01-11

Abstract

The invention provides a gearbox auxiliary suspension cushion assembly for a heavy truck, which comprises: elastic bushing, crossbeam structure, circular outer sleeve structure. The elastic bushing structure is adopted, so that the power assembly has enough displacement along the radial direction of the elastic bushing, the rigid framework is not easy to collide, the rigidity of the E point rubber elastic body can be fully reduced, and the shell of the transmission case is protected; the cylindrical elastic bushing structure is adopted, so that the rigidity of the rubber main spring can be effectively reduced, excessive displacement of the outer framework can be restrained in all directions, and the problem of fatigue cracking of a rubber vulcanization structure is solved; enough tolerance capacity can be ensured, and no load effect is ensured under the static load working condition and the constant-speed driving working condition.

Description

Gearbox auxiliary suspension soft cushion assembly for heavy truck

Technical Field

The invention belongs to the technical field of vehicle power assembly suspension, and particularly relates to a gearbox auxiliary suspension cushion assembly for a heavy truck.

Background

The power assembly suspension is used as a key component of power assembly installation integration, plays an important role in the whole vehicle integration, and has the main functions of: firstly, the supporting function: ensuring that the powertrain is installed in a desired location; secondly, limiting action: the displacement of the power assembly is restrained, and the displacement of the power assembly under any working condition is ensured to be within an expected range; thirdly, vibration isolation: the transmission of vibration between the power assembly and the frame is reduced as much as possible; fourthly, noise reduction: reducing the energy transfer due to the rigid connection.

As shown in FIG. 1, the suspension cushion assemblies which are arranged on the cylinder body in a left-right symmetrical manner and are positioned at the bottom of the front end of the engine are called points A, and the suspension cushion assemblies which are arranged on the left side and the right side of the flywheel housing of the engine are called points B. The gearbox is directly arranged on the flywheel shell and is similar to a cantilever beam, so that the weight of the whole gearbox needs to be borne by the flywheel shell, and meanwhile, the gearbox also exerts a bending moment effect on the flywheel shell. Under the working condition of static load or uniform speed running, the point A and the point B are suspended to bear all loads, but if the power assembly has the severe working condition of large acceleration loads such as vertical or lateral, in order to avoid the damage of the flywheel shell by excessive self load and bending moment, an additional auxiliary cushion assembly is required to be assembled at the top of the tail end of the gearbox, and the auxiliary cushion assembly is called as the point E suspension.

The E-point suspension requires in practice that only about less than 30% of the powertrain load must be borne under any operating conditions, otherwise damage to the transmission housing will result. Therefore, the rigidity design of the auxiliary supporting rubber elastic body at the point E must ensure that the auxiliary supporting rubber elastic body only bears the load of a gearbox and can not introduce the load of an engine. Therefore, the E-point auxiliary support is required to have proper vertical rigidity in performance, the rigidity in other directions is as small as possible, and meanwhile, the E-point auxiliary support is required to have enough limiting performance, so that the main rubber spring is ensured not to crack, and the reliability of parts is improved.

The publication CN109606091A provides a powertrain mount that utilizes the elastic and damping properties of rubber vibration damping pads to dampen vibrations from the powertrain and to carry the effects of high G loads experienced by the transmission.

However, the rubber vibration isolation unit has overlarge rigidity, so that the gearbox shell is easy to crack. In the prior art, the vertical rigidity of the point E is 950N/mm, which is slightly higher than the rigidity of the points A and B. If the power assembly vertically or laterally jumps, under the condition of moving the same displacement, the load borne by the point E is slightly higher than the load borne by the points A and B, and even the load borne by the point E is higher than 13000N under certain working conditions in practical tests. Since the E-point of the transmission housing is only used to carry the maximum load of the transmission of no more than 6000N, excessive loads occurring in use necessarily result in cracking of the transmission housing at the E-point.

In addition, in the vibration-damping rubber pad structure in the prior art, the total height of the rubber elastomer is 46mm, the thickness of the steel main spring outer framework is 4mm, and the middle part of the elastomer is designed with a steel threaded sleeve structure with the length of 27mm, so that the real effective rubber thickness is only 15 mm. The lack of effective rubber thickness makes the rubber do not have sufficient amount of movement when subjected to compressive loads, ultimately exhibiting excessive stiffness of the rubber elastomer. It is also not feasible to reduce the hardness of the compound directly on the basis of this structure to achieve lower stiffness, because the compound thickness is too thin, the stiffness change resulting from directly reducing the compound hardness is not very significant, but rather leads to a reduction in the fatigue resistance of the rubber.

In addition, the rubber vibration isolation unit has no limit design, and the outer framework and the vulcanized rubber elastomer layer are easy to generate fatigue cracking. The problem of cracking of a vulcanized layer between a rubber elastomer and a metal outer framework is also shown in the prior art in use, if the gearbox jumps vertically or laterally, the tensile load of the gearbox is transmitted on the rubber elastomer, the rubber vibration isolation unit is not provided with a hard limiting design, so that the jumping quantity of the gearbox cannot be effectively inhibited, and the rubber and the vulcanized layer of the outer framework are subjected to fatigue cracking due to long-term overlarge tensile quantity.

Disclosure of Invention

In order to solve the technical problem, the invention provides a gearbox auxiliary suspension cushion assembly for a heavy truck. The following presents a simplified summary in order to provide a basic understanding of some aspects of the disclosed embodiments. This summary is not an extensive overview and is intended to neither identify key/critical elements nor delineate the scope of such embodiments. Its sole purpose is to present some concepts in a simplified form as a prelude to the more detailed description that is presented later.

The invention adopts the following technical scheme:

in some optional embodiments, there is provided a gearbox auxiliary suspension cushion assembly for a heavy truck, comprising: an elastic bushing; the elastic bushing includes: the rubber spring comprises an inner framework, an outer framework and a rubber main spring, wherein the outer framework is sleeved outside the inner framework, and the rubber main spring is arranged in a buffer space formed between the outer framework and the inner framework.

Furthermore, two Y-direction V-shaped groove holes are formed in two sides of the rubber main spring in the horizontal direction of the inner framework, and two symmetrical Y-direction soft limiting structure blocks are formed between the outer groove walls of the two Y-direction V-shaped groove holes and the outer framework.

Furthermore, two Z-direction V-shaped groove holes are formed in two sides of the rubber main spring in the vertical direction of the inner framework, and two symmetrical Z-direction soft limiting structure blocks are formed between the outer groove walls of the two Z-direction V-shaped groove holes and the outer framework.

Further, the rubber hardness of the rubber main spring is 46; the included angle of the Y-direction V-shaped slotted hole is 110 degrees; the included angle of the Z-direction V-shaped slotted hole is 70 degrees; the width of the rubber main spring is 30 mm; the height of the elastic bushing is 70 mm.

Further, the gearbox auxiliary suspension cushion assembly for heavy truck still includes: the gearbox mounting beam and the first outer sleeves are arranged at two ends of the gearbox mounting beam; the elastic bushing is press-fitted in the first outer sleeve in an interference manner.

Further, the gearbox auxiliary suspension cushion assembly for heavy truck still includes: the first bracket and the connecting bracket; one end of the connecting support is connected with the inner framework of the elastic bushing, and the other end of the connecting support is connected with the first bracket; the first bracket is mounted on the frame.

Further, the connection bracket includes: the lower mounting table and the two side plates are arranged on the lower mounting table in parallel; an X-direction long hole is formed in the lower mounting table, Z-direction long holes are formed in the two side plates, the Z-direction long holes are used for connecting the connecting support with the elastic bushing, and the X-direction long holes are used for connecting the connecting support with the first bracket; the first bracket includes: the bracket comprises a main body and an upper mounting platform arranged on the main body, wherein an included angle between the upper mounting platform and a horizontal plane is 45 degrees, a bracket side long hole is formed in the upper mounting platform, and the bracket side long hole is used for connecting the first bracket and the connecting support.

Further, the gearbox auxiliary suspension cushion assembly for heavy truck still includes: the gearbox connecting beam is arranged on the transmission box, the supporting tables are arranged at the bottoms of the two ends of the gearbox connecting beam, the bottom of each supporting table is provided with a second outer sleeve, and the elastic bushing is arranged in the second outer sleeve in an interference press mode; one end of the second bracket is connected with the inner framework of the elastic bush, and the other end of the second bracket is installed on the frame.

Furthermore, two ends of the gearbox connecting beam are provided with first strip holes, and the first strip holes are used for connecting the support table and the gearbox connecting beam; and a second elongated hole is formed in the second bracket and used for connecting the second bracket with the inner framework of the elastic bushing.

Further, the gearbox auxiliary suspension cushion assembly for heavy truck still includes: an active end support; the driving end support is provided with a round hole, and the elastic bushing is arranged in the round hole in an interference pressing mode.

The invention has the following beneficial effects:

1. the invention adopts the elastic bushing structure, so that the power assembly has enough displacement along the radial direction of the elastic bushing, is not easy to collide with a rigid framework, can fully reduce the rigidity of the E-point rubber elastomer and protect the gearbox shell.

2. In the invention, the cylindrical elastic bushing structure is adopted, so that the rigidity of the rubber main spring can be effectively reduced, the excessive displacement of the outer framework can be restrained in all directions, and the fatigue cracking problem of a rubber vulcanization structure is solved.

3. The invention can ensure enough tolerance capability and ensure that the vehicle is not influenced by load under the static load working condition and the constant-speed driving working condition.

Drawings

FIG. 1 is a schematic view of suspension points of a prior art suspension system for a heavy truck;

FIG. 2 is a schematic view of the construction of the in-line bushing of the present invention;

FIG. 3 is a schematic view of the construction of the X-shaped bushing of the present invention;

FIG. 4 is a schematic view of the connection of the elastomeric bushing, transmission mounting cross member, first outer sleeve, first bracket, and connecting bracket of the present invention;

FIG. 5 is a schematic view of one of the present invention as installed on a vehicle;

FIG. 6 is a schematic view of the connection of the transmission mounting cross member to the first bracket of the present invention;

FIG. 7 is a schematic structural view of a transmission mounting cross member of the present invention;

FIG. 8 is a schematic view of the construction of the first bracket of the present invention;

FIG. 9 is a schematic structural view of the linking bracket of the present invention;

FIG. 10 is a top view of the X-shaped bushing of the present invention;

FIG. 11 is a schematic view of the connection of the elastomeric bushing, the second bracket, the transmission connecting cross member and the support platform of the present invention;

FIG. 12 is a schematic view of a support stage according to the present invention;

FIG. 13 is another schematic view of the present invention as mounted on a vehicle;

FIG. 14 is a schematic view of the connection of the second carrier to the transfer case connection cross member of the present invention;

FIG. 15 is a schematic view of the construction of a second bracket according to the present invention;

FIG. 16 is a schematic structural view of a transfer case attachment cross member of the present invention;

FIG. 17 is a schematic view of the cooperative mounting of the flexible bushing with the active end bracket of the present invention;

FIG. 18 is a schematic structural view of the active end mount of the present invention;

FIG. 19 is a schematic view of the active end bracket of the present invention shown mounted on a vehicle;

fig. 20 is a schematic structural view of the elastic bush having the stopper protrusion according to the present invention.

Detailed Description

The following description and the drawings sufficiently illustrate specific embodiments of the invention to enable those skilled in the art to practice them. Other embodiments may incorporate structural, logical, electrical, process, and other changes. The examples merely typify possible variations. Individual components and functions are optional unless explicitly required, and the sequence of operations may vary. Portions and features of some embodiments may be included in or substituted for those of others.

In some illustrative embodiments, a transmission auxiliary suspension cushion assembly for a heavy truck is provided, comprising: an elastic bushing 1. The elastic bushing 1 includes: inner frame 101, outer skeleton 102 and rubber main spring 103, outer skeleton 102 cover is established in inner frame 101's outside, rubber main spring 103 sets up in the buffer space that forms between outer skeleton 102 and inner frame 101, outer skeleton 102 is connected with the structural component of gearbox side, inner frame 101 is connected with the structural component of frame side, rubber main spring 103 plays the cushioning effect between inner frame 101 and outer skeleton 102, the vibration that can also effectual prevention power assembly transmits the frame.

As shown in fig. 2, two Y-direction V-shaped slot holes 104 are formed in the rubber main spring 103, and the two Y-direction V-shaped slot holes 104 are located on two sides of the inner frame 101 in the horizontal direction and are symmetrically arranged. Two symmetrical Y-direction soft limiting structure blocks 105 are formed between the outer groove wall 1041 of the Y-direction V-shaped groove hole and the outer framework 102, namely, the opened Y-direction V-shaped groove hole 104 isolates a part of the main body of the rubber main spring 103 to form an independent Y-direction soft limiting structure block 105, therefore, the Y-direction soft limiting structure block 105 is a part of the rubber main spring 103, and the structure forms a linear bushing as shown in fig. 2.

As shown in fig. 3, the rubber main spring 103 is further provided with two Z-direction V-shaped slot holes 106, and the two Z-direction V-shaped slot holes 106 are located at two sides of the inner frame 101 in the vertical direction and are symmetrically arranged. Two symmetrical Z-direction soft limiting structure blocks 107 are formed between the outer groove wall 1061 of the Z-direction V-shaped groove hole and the outer framework 102, namely, the formed Z-direction V-shaped groove hole 106 separates out a part of the rubber main spring 103 to form an independent Z-direction soft limiting structure block 107, so that the Z-direction soft limiting structure block 107 is also a part of the rubber main spring 103, and the structure forms an X-shaped bush as shown in FIG. 3.

In conclusion, the elastic bushing 1 of the invention has two types of the linear bushing and the X-shaped bushing, and the invention solves the problem that the existing design of a suspension system is easy to cause the cracking of a gearbox shell through the structural design of the elastic bushing 1 and also solves the problem that a vulcanized layer of a rubber main spring is easy to fatigue crack.

To reduce the load at the mounting point of the gearbox, it is necessary to reduce the vertical stiffness at point E to a target value and to ensure that the stiffness in the other two directions is as low as possible. The elastic bushing 1 of the present invention can achieve a certain required stiffness in the Z direction and can ensure that the stiffness in the X and Y directions is as small as possible. The following description will be made by taking an X-shaped bushing as an example.

The exoskeleton 102 is connected to the transmission 2 via a beam structure, and may be used as an extension of the transmission. When the outer frame 102 moves in the Z direction, the main rubber spring 103 in the upper half is subjected to a combined action of compression and shearing, and the main rubber spring 103 in the lower half is subjected to a tensile action. Therefore, the stiffness in the Z direction is obtained by the superposition of the compression and shearing action of the upper half rubber master spring and the tensile action of the lower half rubber master spring. The Z-direction movement amount of the outer framework 102 is the length of the upper Z-direction soft limit structure block 107 after being compressed and the length of the linear segment, and can be basically approximately regarded as the radius length of the elastic bushing, so that enough deformation amount can be provided to resist the vertical movement of the gearbox.

Wherein, the length of the linear segment refers to the width of a channel at the corner of the V-shaped slot hole.

As shown in fig. 3, since the slot formed in the rubber main spring 103 is V-shaped and has a corner, the Y-direction V-shaped slot 104 and the Z-direction V-shaped slot 106 have an included angle, where the angle a is defined as the included angle of the Y-direction V-shaped slot 104, and the angle b is defined as the included angle of the Z-direction V-shaped slot 106.

Adjusting the angle b and the angle a can achieve a specific stiffness adjustment in the Z and Y directions as desired. When the angle b is decreased, the angle a increases, and at this time, the compression component in the Z direction of the rubber main spring 103 increases, and the shear component in the Y direction increases. By utilizing the characteristic that the rigidity of the rubber under the compression action is about 4 times of the rigidity of the rubber under the shearing action, the proper rigidity in the Z direction and the Y direction can be realized by accurately adjusting the angle a and the angle b, so that the rubber main spring 103 has enough compression amount, rubber materials with lower hardness are selected, the proportion of compression components and shearing components can be adjusted, and the proper rigidity characteristic in the Z direction and the Y direction can be realized.

When the angle a is equal to the angle b, the rubber materials in the Z direction and the Y direction are equal, the compression components and the shearing components in the two directions are equal, and therefore Kz is equal to Ky; when the angle a is larger than the angle b, the amount of the rubber material in the Y direction is less than that in the Z direction, the amount of the shearing component in the Y direction is more than that of the compression component, and Kz is larger than Ky according to the inherent characteristics of the rubber material; when the angle a is smaller than the angle b, the amount of the rubber in the Y direction is more than that in the Z direction, the compression component in the Y direction is excessive for the shearing component, and therefore Kz is less than Ky. Where Kz is the Z-direction stiffness and Ky is the Y-direction stiffness.

The exoskeleton 102 is completely sheared during movement in the X-direction, and the structure determines that the stiffness in the X-direction is very low. As shown in fig. 10, the stiffness in the X direction is determined by the axial height H of the elastic bushing, and the higher the axial height, the more the rubber in the axial direction, the more the rubber involved in the shearing motion, and the larger Kx. The highest upper limit of the stiffness of the elastic bushing is determined by the hardness of the rubber compound and the width of the main rubber spring 103. The hardness of the rubber compound is a characteristic of the rubber compound itself, and is determined by the rubber formula, for example, two rubber material test pieces with the same length, width and height are different from each other in the hardness of the rubber compound, so that the higher the hardness of the rubber compound is, the greater the deformation resistance of the rubber compound is, and the greater the rigidity of the rubber compound is finally embodied. However, the final rigidity of the elastic bushing 1 is also related to the width of the main rubber spring 103, and the larger the width of the main rubber spring 103 is, the more rubber material is used in each direction, the stronger the compression and tension resistance is, and the higher the rigidity is finally embodied.

Therefore, the expected rigidity performance of the E point structure can be obtained by reasonably designing several parameters of the rubber hardness, the angle a, the angle b, the width of the rubber main spring and the height of the elastic bushing.

In the invention, the hardness condition range of the rubber material is 40-60 Shore hardness, the adjustment range of the angle a is 0-180 degrees, the adjustment range of the angle b is 0-180 degrees, the width condition range of the rubber main spring is 10-40 mm, and the adjustment range of the height of the elastic bushing is 50-100 mm. It is a complicated matter to adjust these 5 variable parameters to obtain the expected stiffness performance, usually by first selecting a suitable sizing material empirically, then estimating the reasonable above 5 parameters empirically again, and third performing the simulation calculation of the Abaqus nonlinear finite element software based on the Mooney-Rivlin model.

In the present invention, the elastic bushing parameters used are: the rubber hardness of the rubber main spring 103 is 46; the included angle of the Y-direction V-shaped slot hole 104 is 110 degrees; the included angle of the Z-direction V-shaped groove hole 106 is 70 degrees; the width of the rubber main spring is 30 mm; the height of the elastic bush is 70 mm. In this case, the stiffness Kx in the X direction is 200, Ky is 150, and Kz is 350.

The working principle and the action form of the linear bushing are consistent with those of the X-shaped bushing, and the linear bushing can be regarded as a special form of the X-shaped bushing, namely, if the angle b of the X-shaped bushing is designed to be 0, the linear bushing is changed into the linear bushing. The rubber main spring 103 of the linear bush has only a compression component in the Z direction and only a shear component in the Y direction. If it is desired to minimize the Y-direction stiffness in some applications, a straight bushing configuration may be used.

The problem that the E point is easy to cause the shell of the gearbox to crack is solved through the design, and how to solve the problem of fatigue cracking of the vulcanized layer of the rubber main spring is explained by taking an X-shaped bushing as an example.

On the basis that the structure of the elastic bushing meets the rigidity performance, the invention also provides two limit characteristic designs: a Z-direction soft limit structure block 107 and a Y-direction soft limit structure block 105, which are also part of the rubber main spring. The Z-direction soft limit structure blocks 107 are soft limit features and are respectively arranged in the Z direction in an up-and-down symmetrical mode, and the Y-direction soft limit structure blocks 105 are soft limit features in the Y direction and are symmetrically designed in the Y direction. In operation, exoskeleton 102 may be considered a part of a powertrain, moving with the powertrain, and coupled to a transmission. The inner frame 101 as part of the frame may be considered relatively stationary.

The motion amplitudes of the powertrain are divided into three types: small amplitude motion; large amplitude motion; and (4) extreme movement. The motion when the motion displacement amount of the exoskeleton 102 does not exceed the length of the linear segment is called small-amplitude motion; when the outer framework 102 continues to move, the outer framework is in contact with the Z-direction soft limiting structure block 107 or the Y-direction soft limiting structure block 105, and the movement when half of the radial height of the extrusion limiting feature is called large amplitude movement; the motion after a large amplitude motion is called extreme motion. Fatigue cracking of the E-point rubber main spring occurs under a large-amplitude motion working condition and a limit motion working condition.

The Z-direction soft limiting structure block 107 is introduced in the invention to eliminate the fatigue problem of the elastic bushing under the working condition of large-amplitude motion. Taking the Y-direction movement of the outer frame 102 as an example, the outer frame 102 starts to contact the Y-direction soft limit structure block 105 after the displacement of the outer frame exceeds the length of the linear segment, the contact is the elastic contact between the rubber around the inner frame and the rubber of the Y-direction soft limit structure block 105, and the acting force between the two contacted is increased in a nonlinear way along with the increase of the displacement of the inner frame. By adopting the design, the impact load generated after sudden contact can be effectively eliminated, and the fatigue life of the rubber can be effectively prolonged.

The circular outer sleeve structure in the exoskeleton 102 and beam structures of the present invention can effectively prevent the problem of excessive displacement of itself during extreme movements in all directions. The beam structure refers to a gearbox mounting beam 3, a gearbox connecting beam 10 or a driving end bracket 16 which are mentioned below; the circular outer sleeve structure refers to the first outer sleeve 4, the second outer sleeve 12 or the circular hole 17 mentioned below.

Similarly, for the example of the Y-direction movement of the outer frame 102, if the amplitude of the Y-direction movement of the outer frame 102 exceeds the movement amount defined by the large-amplitude movement condition and then continues to move in the Y-direction, the Y-direction soft limit structure block 105 is further compressed, and when the radial height of the Y-direction soft limit structure block 105 is compressed 2/3, the rubber is compressed to the limit position, and the outer frame 102 itself cannot continue to move. At the moment, the incompressible rigid structures of the inner framework and the outer framework are fully utilized to effectively prevent the excessive movement of the rubber, so that the problem of fatigue cracking of a rubber vulcanization structure caused by excessive movement of the rubber is thoroughly solved.

The working principle of the linear bushing is similar to that of the X-shaped bushing, and therefore, the detailed description is omitted.

The present invention provides a first type of structure, as shown in fig. 4-7, the present invention further comprising: the gearbox is provided with a cross beam 3, a first outer sleeve 4, a first bracket 5, a connecting support 6 and a base plate 8.

The structural composition relation of the E point auxiliary support is as follows: the inner frame 101 is connected with the connecting bracket 6 through bolts, so that the inner frame can be regarded as a part of the frame 7; the outer frame 102 is rigidly connected with the first outer sleeve 4 by interference press-fitting. The transmission mounting cross member 3 can be considered as a part of the powertrain after being mounted on the transmission case 2. The gearbox mounting beam 3 and the elastic bush 1 form an assembly, and the two form an auxiliary suspension cushion assembly of the gearbox, and the structural relationship is shown in figures 4-7.

The two first outer sleeves 4 are symmetrically arranged at two ends of the gearbox mounting beam 3, and the elastic bushing 1 is press-fitted in the first outer sleeve 4 in an interference manner, namely the outer framework 102 is rigidly connected with the first outer sleeve 4 by adopting an interference press-fitting process. One end of the connecting bracket 6 is connected with the inner frame 101 of the elastic bush 1, the other end is connected with the first bracket 5, and the first bracket 5 is installed on the frame 7 through a bolt.

The power assembly is flexibly connected with the frame through the elastic bushing 1, and the rigidity and the damping characteristic of the rubber structure are utilized, so that the vibration of the power assembly can be effectively prevented from being transmitted to the frame. If the vehicle runs under the bad working condition, the power assembly can be protected from being damaged by the buffering action of the elastic bush 1.

The invention also achieves the aim of no stress on static load, and particularly solves the tolerance generated in all directions in the design, manufacture and assembly process by using the first bracket 5 and the connecting bracket 6 together.

As shown in fig. 9, the connecting bracket 6 includes: a lower mounting base 601 and two side plates 602 arranged in parallel on the lower mounting base 601. Two X-direction strip holes 603 are formed in the lower mounting table 601, the two X-direction strip holes 603 are located on two sides of the two side plates 602, and Z-direction strip holes 604 are formed in the two side plates 602.

The shape of the X-direction long hole 603 and the Z-direction long hole 604 is a rounded rectangle, and the distance between two circle centers of the long holes is 7 mm. The X-direction elongated hole 603 is used for connecting the bracket 6 and the first bracket 5, so that the gearbox suspension assembly of the invention has a certain displacement in the X direction, and a certain tolerance in the X direction is allowed. The Z-direction elongated hole 604 is used for connecting the connecting bracket 6 with the elastic bushing 1, that is, the bolt is screwed after penetrating through the Z-direction elongated hole 604 and the bolt hole formed in the inner frame 101, so that the connecting bracket 6 can be fixedly connected with the inner frame 101. Thus, the design of the elongated Z-hole 604 allows the transmission suspension assembly to be displaced in the Z-direction, allowing for some tolerance in the Z-direction.

As shown in fig. 8, the first bracket 5 includes: the main part 501 and the last mount table 502 of setting on main part 501, it is 45 with the horizontal plane contained angle to go up mount table 502, set up bracket side rectangular hole 503 on going up mount table 502, bracket side rectangular hole 503 is used for first bracket 5 to be connected with linking bridge 6, and the bolt passes bracket side rectangular hole 503 and screws up with X to rectangular hole 603 promptly, then can realize linking bridge 6 and the fixed connection of first bracket 5.

The tolerances in the Y direction that occur after assembly of the powertrain are achieved by the Z-slots 604 fitting together. Since the upper mounting table 502 of the first bracket 5 is inclined at an angle of 45 °, if the gap in the Y direction is large, the connecting bracket 6 moves downward along the bracket-side elongated hole 503 at an included angle of 45 °, and the tolerance is filled by using its own wedge structure. Instead, the connecting bracket 6 moves upward along the bracket-side elongated hole 503 at an angle of 45 °. The tolerance in the Y direction is well achieved. The structural design of the connecting bracket 6 and the first carrier 5 therefore plays an important role in achieving various directional tolerances.

The present invention also provides a second type of construction, as shown in fig. 11-16, the present invention further comprising: the second bracket 9, the gearbox connecting beam 10, the support platform 11 and the second outer sleeve 12.

The supporting table 11 is arranged at the bottom of two ends of the gearbox connecting beam 10, the bottom of the supporting table 11 is provided with a second outer sleeve 12, the elastic bushing 1 is arranged in the second outer sleeve 12 in an interference press-fitting mode, one end of the second bracket 9 is connected with the inner framework 101 of the elastic bushing 1, and the other end of the second bracket is installed on the frame 7 through bolts.

As mentioned above, if the stiffness of the main rubber spring of the point E auxiliary support is close to the points a and B, the point E auxiliary support will generate a load close to the points a and B when the power assembly generates the same motion displacement. The housing of the gearbox 2 will be stressed beyond the yield strength of the material and will tend to crack the gearbox housing. In order to effectively reduce the rigidity at the point E, the invention introduces an elastic bushing 1, wherein the elastic bushing 1 mainly comprises an outer framework 102, a rubber main spring 103 and an inner framework 101, and the three parts are combined together through a vulcanization process. The elastic bushing 1 is pressed into the second outer sleeve 12 by interference fit to form the auxiliary suspension cushion assembly of the invention.

The exoskeleton 102, the second outer sleeve 12 and the support base 11 are finally connected with the transmission connecting beam 10 as a part of the power assembly, and move along with the movement of the power assembly. The inner frame 101 is connected to the second bracket 9 as a part of the vehicle frame. The rubber main spring 103 is between the powertrain and the frame, and damps the displacement and load of the powertrain using the elasticity and damping of the rubber material.

The assembly relationship of the invention is shown as follows:

the first step is as follows: the second brackets 9 on the left and right sides are mounted to the frame 7 by bolts and nuts and fastened.

The second step is that: the inner frame of the elastic bush is assembled into the second bracket through a bolt and a nut, and the bolt cannot be fastened at the moment, so that the auxiliary suspension cushion assembly needs to be kept in a movable state.

The third step: the auxiliary suspension cushion assembly at the two sides is rotated to enable the projection welding bolt 13 to be in a vertical state. The gearbox is vertically mounted with the cross beam 10 resting on the support 11.

The fourth step: and fastening a connecting bolt of the gearbox.

The fifth step: and fastening nuts and other all bolts and nuts.

In order to ensure that the auxiliary support at the point E is not loaded when the auxiliary support is assembled under a static load state, the invention designs the following structure: the two ends of the gearbox connecting beam 10 are provided with first strip holes 14, the second bracket 9 is provided with second strip holes 15, the tolerance in the X direction is eliminated,

the first strip hole 14 is used for connecting the support platform 11 with the gearbox connecting beam 10, namely the projection welding bolt 13 penetrates through the first strip hole 14 and then is screwed down, and the support platform 11 and the gearbox connecting beam 10 are fixed into a whole. The second elongated hole 15 is used for connecting the second bracket 9 with the inner frame 101 of the elastic bush 1, that is, the bolt is screwed after passing through the second elongated hole 15 and the bolt hole formed in the inner frame 101, so that the inner frame 101 and the second bracket 9 are fixed into a whole. The second elongated hole 15 and the first elongated hole 14 are rounded rectangles, specifically, the second elongated hole 15 has a diameter of 17mm and a length of 7 mm; the first elongated hole 14 has a diameter of 13 mm and a length of 7 mm.

The present invention also provides a third type of structure, as shown in fig. 17-20, the present invention further comprising: an active end support 16. The driving end bracket 16 is provided with a round hole 17, and the elastic bushing 1 is pressed in the round hole 17 in an interference fit mode.

The elastic bushing 1 is pressed in the round hole 17 in an interference fit mode to form a gearbox auxiliary suspension, and the gearbox auxiliary suspension is installed on a shell of the gearbox 2 through a bolt through hole 18. The third type of construction employs the construction of the first bracket 5 and the connecting bracket 6 as in the first type of construction to secure the inner frame of the elastic bush 1 to the vehicle frame 7. The principle that the auxiliary cushion assembly does not bear load under the working conditions of static load and uniform motion after the third structure type is installed is equal to the first structure type, namely the auxiliary cushion assembly does not bear load under the working conditions of static load and uniform motion through the X-direction long holes 603, the Z-direction long holes 604 and the bracket side long holes 503.

As shown in fig. 20, the rubber main spring 20 of the elastic bushing 1 is further provided with a first soft limiting protrusion 19 and a second soft limiting protrusion 20, and the inner frame 101 is elliptical and used in cooperation with the driving end bracket 16 to further improve the buffering effect.

The elastic bushing 1 is connected to the transmission housing by the active end bracket 16 alone, rather than being connected to the transmission mounting cross member 3 and then mounted to the transmission housing. The independent design and installation of the auxiliary suspension of the gearbox can effectively reduce the weight and the cost, and avoid using overlong installation beams.

The active end bracket 16, which is interference-press-fitted with the elastic bushing 1, is called a transmission auxiliary suspension, which is bilaterally symmetric and is also mounted to the frame 7 through the connecting bracket 6 and the first bracket 5. This design and construction form serves as a continuing improvement of the invention, in which the auxiliary gearbox suspension consists of the active end bracket 16 and the elastic bushing 1 and is mounted on the housing of the gearbox 2 by means of bolts.

Those of skill would further appreciate that the various illustrative logical blocks, modules, circuits, and algorithm steps described in connection with the embodiments disclosed herein may be implemented as electronic hardware, computer software, or combinations of both. To clearly illustrate this interchangeability of hardware and software, various illustrative components, blocks, modules, circuits, and steps have been described above generally in terms of their functionality. Whether such functionality is implemented as hardware or software depends upon the particular application and design constraints imposed on the overall system. Skilled artisans may implement the described functionality in varying ways for each particular application, but such implementation decisions should not be interpreted as causing a departure from the scope of the present disclosure.

Claims

1. The utility model provides a gearbox auxiliary suspension cushion assembly for heavy truck which characterized in that includes: an elastic bushing; the elastic bushing includes: the rubber spring comprises an inner framework, an outer framework and a rubber main spring, wherein the outer framework is sleeved outside the inner framework, and the rubber main spring is arranged in a buffer space formed between the outer framework and the inner framework.

2. The auxiliary suspension cushion assembly for the gearbox of the heavy truck as recited in claim 1, wherein two Y-direction V-shaped slot holes are formed in the rubber main spring on two sides of the inner frame in the horizontal direction, and two symmetrical Y-direction soft limit structure blocks are formed between the outer slot walls of the two Y-direction V-shaped slot holes and the outer frame.

3. The auxiliary suspension cushion assembly for the gearbox of the heavy truck as recited in claim 2, wherein two Z-direction V-shaped slot holes are formed in the rubber main spring on two sides of the inner frame in the vertical direction, and two symmetrical Z-direction soft limit structure blocks are formed between the outer slot walls of the two Z-direction V-shaped slot holes and the outer frame.

4. The heavy truck transmission auxiliary suspension cushion assembly of claim 3, wherein said main rubber spring rubber hardness is 46; the included angle of the Y-direction V-shaped slotted hole is 110 degrees; the included angle of the Z-direction V-shaped slotted hole is 70 degrees; the width of the rubber main spring is 30 mm; the height of the elastic bushing is 70 mm.

5. The heavy truck transmission auxiliary suspension cushion assembly according to any one of claims 1-4, further comprising: the gearbox mounting beam and the first outer sleeves are arranged at two ends of the gearbox mounting beam; the elastic bushing is press-fitted in the first outer sleeve in an interference manner.

6. The gearbox auxiliary suspension cushion assembly for heavy-duty trucks of claim 5, further comprising: the first bracket and the connecting bracket; one end of the connecting support is connected with the inner framework of the elastic bushing, and the other end of the connecting support is connected with the first bracket; the first bracket is mounted on the frame.

7. The heavy truck transmission auxiliary suspension cushion assembly of claim 6, wherein said attachment bracket comprises: the lower mounting table and the two side plates are arranged on the lower mounting table in parallel; an X-direction long hole is formed in the lower mounting table, Z-direction long holes are formed in the two side plates, the Z-direction long holes are used for connecting the connecting support with the elastic bushing, and the X-direction long holes are used for connecting the connecting support with the first bracket; the first bracket includes: the bracket comprises a main body and an upper mounting platform arranged on the main body, wherein an included angle between the upper mounting platform and a horizontal plane is 45 degrees, a bracket side long hole is formed in the upper mounting platform, and the bracket side long hole is used for connecting the first bracket and the connecting support.

8. The heavy truck transmission auxiliary suspension cushion assembly according to any one of claims 1-4, further comprising: the gearbox connecting beam is arranged on the transmission box, the supporting tables are arranged at the bottoms of the two ends of the gearbox connecting beam, the bottom of each supporting table is provided with a second outer sleeve, and the elastic bushing is arranged in the second outer sleeve in an interference press mode; one end of the second bracket is connected with the inner framework of the elastic bush, and the other end of the second bracket is installed on the frame.

9. The auxiliary suspension cushion assembly for the gearbox of the heavy truck as recited in claim 8, wherein a first elongated hole is formed at both ends of the gearbox connecting beam, and the first elongated hole is used for connecting the support platform and the gearbox connecting beam; and a second elongated hole is formed in the second bracket and used for connecting the second bracket with the inner framework of the elastic bushing.

10. The heavy truck transmission auxiliary suspension cushion assembly according to any one of claims 1-4, further comprising: an active end support; the driving end support is provided with a round hole, and the elastic bushing is arranged in the round hole in an interference pressing mode.