CN214215473U - Auxiliary supporting device for gearbox and vehicle - Google Patents

Abstract

The utility model relates to a gearbox auxiliary stay device and vehicle, gearbox auxiliary stay device wherein is provided with the vibration isolation unit including the crossbeam that is used for installing the installation unit on the frame and is used for supporting the gearbox between installation unit and the crossbeam, the vibration isolation unit include along X direction extend be used for with crossbeam fixed connection's outer lane skeleton and be used for with frame fixed connection's inner circle skeleton, it has the rubber main spring to fill between outer lane skeleton and the inner circle skeleton. Through above-mentioned technical scheme, can reduce the load that exerts on the gearbox can, avoid the damage of gearbox housing.

Description

Auxiliary supporting device for gearbox and vehicle

Technical Field

The utility model relates to a vehicle technical field specifically relates to a gearbox auxiliary stay device and vehicle.

Background

The integration of a powertrain including an engine and a transmission in a vehicle is a complex problem, and requires that the powertrain not only perform all functions but also have good NVH performance after installation. The power assembly suspension is used as a key component for power assembly installation integration, and mainly plays roles of supporting, limiting and vibration isolating, wherein an auxiliary supporting point positioned above the tail end of the gearbox is called as an E point, the E point auxiliary support is used for ensuring that the E point does not bear any load under a static load working condition, and the E point auxiliary support plays a role of supporting the gearbox only when the gearbox meets a high-g load working condition. In the related art, the design defects of the auxiliary supporting structure for the point E are more, for example: the problems of shell cracking of the gearbox, fatigue cracking of a vulcanized rubber elastomer layer, poor assembly manufacturability, poor universality and the like are easily caused.

SUMMERY OF THE UTILITY MODEL

A first object of the present disclosure is to provide a transmission auxiliary supporting device to partially solve the above-mentioned problems in the related art.

In order to achieve the above object, the present disclosure provides a transmission auxiliary supporting device, including a mounting unit for mounting on a frame and a crossbeam for supporting a transmission, the mounting unit and a vibration isolation unit are provided between the crossbeams, the vibration isolation unit includes an outer ring framework extending along an X direction and used for being fixedly connected with the crossbeam and an inner ring framework fixedly connected with the frame, and a rubber main spring is filled between the outer ring framework and the inner ring framework.

Optionally, the rubber main spring is provided with a plurality of through holes penetrating through the rubber main spring along the X direction, and the through holes are configured to enable the rubber material of the rubber main spring to have different distribution amounts in the Z direction and the Y direction respectively.

Optionally, the through holes include two dumbbell-shaped first through holes symmetrically arranged about a Z-direction center line, and an upper half portion and a lower half portion of each first through hole are respectively symmetric about a Y-direction center line.

Optionally, the through holes include two V-shaped second through holes symmetrically disposed about a Z-direction center line and two V-shaped third through holes symmetrically disposed about a Y-direction center line, wherein an upper half and a lower half of the second through holes are respectively symmetrical about the Y-direction center line, and a left half and a right half of the third through holes are respectively symmetrical about the Z-direction center line.

Optionally, a limiting structure is formed radially outwards on the peripheral edge of the through hole, the limiting structure comprises a first limiting part and a second limiting part, when acting force is applied to the first limiting part and the second limiting part, the rubber materials on two sides of the through hole are abutted, and the first limiting part is closer to the center of the rubber main spring than the second limiting part.

Optionally, the length of the rubber main spring in the X direction is adapted to the axial length of the outer ring framework or the inner ring framework.

Optionally, the mounting unit includes two side plates disposed in parallel at two ends of the vibration isolation unit and used for being fixedly connected with the inner ring framework, and a distance between the two side plates is configured to allow the outer ring framework to move in the X direction relative to the inner ring framework.

Optionally, the cross beam is adjustably mounted on the mounting unit in at least two of the X, Y and Z directions.

Optionally, the auxiliary gearbox support device further comprises at least one adjusting pad arranged between the mounting unit and the frame and used for compensating the Y-direction gap.

A second object of the present disclosure is to provide a vehicle, including a powertrain having a transmission case, and a transmission case auxiliary supporting device for auxiliary supporting the transmission case, wherein the transmission case auxiliary supporting device is the transmission case auxiliary supporting device described above.

Through the technical scheme, the vibration isolation unit comprising the rubber main spring is arranged between the mounting unit and the cross beam, so that the displacement and the load of the power assembly are buffered by utilizing the elasticity and the damping of the rubber material. During the displacement of the power assembly caused by traveling, the rubber main spring can provide enough compression, so that lower rigidity is shown, the load applied to the gearbox can be reduced, and the damage to the gearbox shell is avoided.

Additional features and advantages of the disclosure will be set forth in the detailed description which follows.

Drawings

The accompanying drawings, which are included to provide a further understanding of the disclosure and are incorporated in and constitute a part of this specification, illustrate embodiments of the disclosure and together with the description serve to explain the disclosure without limiting the disclosure. In the drawings:

FIG. 1 is a schematic illustration of a transmission accessory support provided by the present disclosure;

FIG. 2 is a schematic view of another transmission auxiliary support arrangement provided by the present disclosure;

FIG. 3 is a schematic view of a damping unit in the transmission accessory of FIG. 1;

FIG. 4 is a schematic view of the rubber main spring and inner and outer frame portions of the vibration isolation unit of FIG. 3;

FIG. 5 is a schematic view of a portion of the outer sleeve of the vibration isolation unit of FIG. 3;

FIG. 6 is a top view of the vibration isolation unit of FIG. 4;

FIG. 7 is a schematic view of a cross member of the auxiliary support device of the transmission of FIG. 1;

FIG. 8 is a schematic view of a carrier in the auxiliary support of the transmission of FIG. 1;

FIG. 9 is a schematic view of a damping unit in the transmission accessory of FIG. 2;

FIG. 10 is a schematic view of a cross member of the auxiliary support device of the transmission of FIG. 2;

FIG. 11 is a schematic view of a carrier in the auxiliary support of the transmission of FIG. 2;

FIG. 12 is a schematic view of a connecting bracket of the auxiliary support device of the transmission of FIG. 2;

FIG. 13 is a distribution diagram of powertrain suspension points.

Description of the reference numerals

1-mounting unit, 11-first bracket, 111-first side plate, 1111-first elongated hole, 12-second bracket, 121-second mounting platform, 1211-fifth elongated hole, 13-connecting bracket, 131-second side plate, 1311-fourth elongated hole, 132-first mounting platform, 1321-third elongated hole;

2-beam, 21-second elongated hole, 22-second outer sleeve;

3-vibration isolation unit, 31-rubber main spring, 311-first through hole, 312-limit structure, 3121-first limit part, 3122-second limit part, 313-second through hole, 314-third through hole, 32-outer ring framework, 33-inner ring framework, 34-first outer sleeve, 35-support table, 36-projection welding bolt;

4-vehicle frame.

Detailed Description

The following detailed description of specific embodiments of the present disclosure is provided in connection with the accompanying drawings. It should be understood that the detailed description and specific examples, while indicating the present disclosure, are given by way of illustration and explanation only, not limitation.

In the present disclosure, unless otherwise specified, use of directional terms such as "upper, lower, left, and right" generally means that they are defined with reference to the drawing plane directions of the corresponding drawings. "inner and outer" refer to the inner and outer of the respective component profiles. The terms "first," "second," and the like are used herein to distinguish one element from another, and are not intended to be sequential or important. In addition, when the following description refers to the accompanying drawings, like numbers in different drawings represent the same or similar elements, unless otherwise indicated.

The power assembly (engine + gearbox) of a vehicle, especially a heavy truck, is bulky, and usually adopts an arrangement form of 4 suspended cushion assemblies and an auxiliary support of the gearbox. As shown in fig. 13, the front two suspension cushions mounted at the front end of the engine cylinder body in a left-right symmetrical arrangement are called "points a", the middle two suspension cushions mounted at the flywheel housing in a symmetrical arrangement are called "points B", and the auxiliary support mounted at the upper end of the tail of the transmission is called "point E", wherein the point E is an auxiliary support and is only used for bearing high g load encountered by the transmission, and the maximum load of the power assembly cannot exceed 30%.

The practical situation is that the problem of the fault of the gearbox shell connected with the auxiliary support at the point E frequently occurs, the fault form is mainly represented by the steel sleeve falling off, the bolt hole is cracked while the steel sleeve falling off, and the shell around the bolt hole is cracked. The gearbox shell needs to be replaced after cracking, and the cost is high.

The damage of the gearbox shell is only a phenomenon shown, and the fundamental reason of the damage cannot be found only by researching the damaged parts. A large number of simulations and whole vehicle tests find that the unreasonable rigidity distribution of the points A, B and E is a main cause of the shell cracking of the gearbox. In the prior art, the vertical rigidity of the point E is 950N/mm and is slightly higher than that of the point A and the point B, and if a power assembly jumps vertically or laterally, the load borne by the point E is inevitably higher than that of the point A and the point B under the condition of the same displacement, so that the gearbox shell is subjected to stress exceeding the yield strength of materials, and the gearbox shell is easy to crack.

Based on the above findings, in order to avoid the gearbox housing from cracking, the rigidity of the auxiliary support at the point E needs to be reduced, as shown in fig. 1 to 12, the present disclosure provides an auxiliary support device for a gearbox, where the auxiliary support device for a gearbox includes an installation unit 1 for installing on a frame 4 and a beam 2 for supporting a gearbox, a vibration isolation unit 3 is provided between the installation unit 1 and the beam 2, the vibration isolation unit 3 includes an inner ring frame 33 and an outer ring frame 32, the outer ring frame 32 is sleeved on the periphery of the inner ring frame 33, a rubber main spring 31 is filled between the outer ring frame 32 and the inner ring frame 33, and the rubber main spring is joined with the inner ring frame 33 and the outer ring frame 32 by a vulcanization process.

Compared with the case that the engine suspension in a passenger vehicle needs to bear the gravity under the static load, in a heavy truck, the gravity of the power assembly is borne by the point A and the point B under the static load, and the point E is not stressed under the static load, so that the outer ring framework 32 and the inner ring framework 33 can be coaxially arranged.

For convenience of description, X, Y and the Z direction are first defined herein. As shown in fig. 1 and 2, the vertical direction, i.e., the height direction of the vehicle, is the Z direction, the lateral direction, i.e., the extending direction of the cross member 2, is the Y direction, and the longitudinal direction, i.e., the direction orthogonal to the Y direction, is the X direction. In the embodiment shown in fig. 1 and 2, the outer ring bobbin 32 and the inner ring bobbin 33 extend in the X direction. It should be understood that extension of rubber main spring 31 in the X direction or extension in the Y direction due to the difference in the extension direction of the inner and outer race skeletons is equivalent as a result of the force, and is expressed as compression in the Z direction and shear in the X and Y directions.

The power assembly is fixedly mounted on the cross beam 2, when the power assembly moves downwards, the outer ring framework 32 moves downwards along with the power assembly, and the inner ring framework 33 is fixed on the mounting unit 1 so as to keep still. Since the rubber main spring 31 can provide a large compression amount, the outer ring frame 32 has a large enough movement space to buffer displacement and cannot collide with the inner ring frame 33. In the selection of the material of the main rubber spring 31, a rubber material with a lower shore hardness can be selected, so that the main rubber spring 31 can provide a sufficiently large compression amount, and can better realize lower rigidity due to a softer mass. Under the action of force, the rubber body of the rubber main spring 31 above the inner ring framework 33 is compressed, the rubber body below the inner ring framework is stretched, and the upper part and the lower part jointly buffer the load impact on the gearbox shell, so that the gearbox shell is protected more effectively. When the power assembly moves upwards, the action principle is the same, and the detailed description is omitted.

The gearbox housing can be protected more effectively by reasonably optimizing the rigidity of the vibration isolation unit 3 in different directions. As an embodiment capable of implementing the vibration isolation unit 3 in the Z direction and the Y direction, specifically, enabling the rubber main spring 31 in the vibration isolation unit 3 to have different rigidity, a plurality of through holes penetrating the rubber main spring 31 in the X direction may be provided on the rubber main spring 31, and the through holes are configured to enable the rubber material of the rubber main spring 31 to have different distribution amounts in the Z direction and the Y direction, respectively. In other words, the rubber main spring 31 is artificially divided into two different filling portions in the Z direction and the Y direction by using the through hole as a "partition". The amount of distribution here refers to how much rubber material is filled per unit space when the hardness of the rubber material of the rubber main spring 31 is selected. Generally, the more gum material filled in a unit space, the greater the stiffness. By reasonably arranging the distribution amount of the rubber material in the Z direction and the Y direction, the rubber main spring 31 can obtain different rigidities in the Z direction and the Y direction, and based on the rigidities, an optimal parameter range is adjusted.

According to an embodiment of the present disclosure, as illustrated in fig. 4, the through-holes include two dumbbell-shaped first through-holes 311 symmetrically disposed about a Z-direction center line, and upper and lower halves of the first through-holes 311 are respectively symmetrical about a Y-direction center line. The angle α and the main spring width d1 are adjusted so that the rubber material of the rubber main spring 31 has different distribution amounts in the Z direction and the Y direction, respectively. Specifically, under the condition that the main spring width d1 is not changed, the smaller the angle α is, the lower the rigidity in the Z direction is; the smaller the main spring width d1, the lower the Z-stiffness, with the angle α unchanged. The free combination of the glue hardness, the angle α and the main spring width d1 allows a greater adjustment range.

The upper maximum limit of the stiffness of the vibration insulating unit 3 is also related to the stiffness of the glue. The hardness of the rubber compound is the characteristic of the rubber compound, and is determined by the formula of the rubber, for example, in two rubber test pieces with equal length, width and height, when the only difference is the hardness of the rubber compound, the higher the hardness is, the greater the resistance of the rubber compound to deformation is, and the greater the rigidity is finally embodied.

The parameters of the first embodiment are shown in the following table:

the rubber main spring 31 is subjected to shearing action when the locomotion assembly moves along the Y direction and the X direction, and the locomotion assembly has lower rigidity than the Z direction when moving along the Y direction and the X direction by utilizing the inherent characteristic that the rubber main spring 31 shows rigidity far lower than rigidity when being compressed when being sheared.

According to another embodiment of the present disclosure, as illustrated in fig. 9, the through holes include two V-shaped second through holes 313 symmetrically disposed about a Z-direction center line and two V-shaped third through holes 314 symmetrically disposed about a Y-direction center line, wherein upper and lower halves of the second through holes 313 are respectively symmetrical about the Y-direction center line, and left and right halves of the third through holes 314 are respectively symmetrical about the Z-direction center line. The angle β, the angle γ, and the main spring width d2 are adjusted so that the rubber material of the rubber main spring 31 has different distribution amounts in the Z direction and the Y direction, respectively.

Specifically, in the case where the main spring width d1 is constant, the different rigidities of the point E in the Y direction and the Z direction are determined by the opening degrees of the angle β and the angle γ: when the angle beta is equal to the angle gamma, the Z direction and the Y direction have equal sizing material distribution quantity, the compression component and the shearing component in the two directions are equal, and therefore the rigidity in the two directions is also equal; when the angle beta is larger than the angle gamma, the glue distribution amount in the Y direction is less than that in the Z direction, the shearing component in the Y direction is more than that of the compression component, and the rigidity in the Z direction is larger than that in the Y direction according to the inherent characteristics of the rubber material; when the angle beta is smaller than the angle gamma, the glue distribution amount in the Y direction is more than that in the Z direction, the compression component in the Y direction is more than the shearing component, and the rigidity in the Z direction is smaller than that in the Y direction. The expected rigidity performance of the point E structure can be obtained by reasonably designing several parameters of the rubber hardness, the angle beta, the angle gamma, the main spring width d2 and the main spring length.

The second embodiment has the following parameters:

hardness of sizing material

Angle

1

Angle 2

Width of main spring

Length of main spring

Design parameters

46

110°

70°

30mm

70mm

The stiffness of the vibration isolation unit 3 in different directions obtained by the above parameters is shown in the following table:

Direction	Kx	Ky	Kz
				rigidity	200	150	350

The main spring length in the above table refers to the length of the rubber main spring 31 in the X direction, and the length determines the stiffness of the rubber main spring 31 in the X direction. As shown in fig. 6, the length of the rubber main spring 31 in the X direction is adapted to the axial length h1 of the outer ring bobbin 32 or the axial length h2 of the inner ring bobbin 33. For example, the length of the rubber main spring 31 may be equal to the axial length h1 of the outer-ring bobbin 32, that is, the rubber main spring 31 does not leak out of the outer-ring bobbin 32. The longer the length of the rubber main spring 31 in the X direction, the greater the rigidity in the X direction.

When the rubber main spring 31 is joined to the inner and outer race frames by a vulcanization process, a vulcanized layer is generally formed at the joint. When the gearbox jumps vertically or laterally, the tensile load of the gearbox is transmitted to the rubber main spring 31, so that the jumping quantity of the gearbox cannot be effectively inhibited under the condition that the rubber main spring 31 has no limiting structure, and the vulcanized layer at the joint of the rubber main spring 31 and the inner and outer ring frameworks is easy to generate fatigue cracking due to long-term overlarge tensile quantity. According to an embodiment of the present disclosure, referring to fig. 4 and 9 together, the peripheral edge of the through hole is formed with a stopper structure 312 radially outward, the stopper structure 312 includes a first stopper portion 3121 and a second stopper portion 3122 which make the rubber material on both sides of the through hole abut when acted upon by a force, wherein the first stopper portion 3121 is closer to the center of the rubber main spring 31 than the second stopper portion 3122.

In the embodiment shown in fig. 4, when the power train moves downward, the rubber body of the rubber main spring 31 above the inner ring frame 33 is compressed, the rubber body below is stretched, and when the compressed rubber main spring 31 is compressed 2/3, the rubber main spring cannot be further compressed, so that the vulcanized layer can be effectively protected from being easily cracked in the Z direction. When the power assembly moves in the Y direction, the power assembly drives the outer ring frame 32 to move together, and along with the movement of the outer ring frame 32, the first limiting portion 3121 is closer to the center of the rubber main spring 31, or in other words, the first limiting portion 3121 is closer to the inner ring frame 33 in the Y direction than the second limiting portion 3122, and the first limiting portion 3121 first abuts against the inner ring frame 33, so that the load in the Y direction is buffered more gently. The outer ring frame 32 continues to move until the second limit portion 3122 abuts against the inner ring frame 33. If the power assembly moves further until the main rubber spring 31 is compressed to 2/3 of the power assembly, the rigidity of the power assembly in the Y direction is increased in a nonlinear and sharp mode, the main rubber spring 31 cannot be compressed continuously, the power assembly cannot move further, and therefore the vulcanized layer can be effectively protected from being cracked easily in the Y direction. In the embodiment shown in fig. 4, a limiting structure 312 for two-stage buffering is arranged in the Y direction. In the embodiment shown in fig. 9, two-stage buffering can be realized by providing the limiting structures 312 in both the Z direction and the Y direction. The specific force analysis in the buffering process is the same as that in the embodiment of fig. 4, and is not described here again.

It has been mentioned above that the rigidity in the X direction can be adjusted by appropriately configuring the length of the rubber main spring 31 in the X direction. In order to avoid the situation that the vulcanized layer is cracked due to the excessive deformation in the X direction, in the present disclosure, the mounting unit 1 may include two side plates disposed in parallel at both ends of the vibration isolating unit 3, the side plate being the first side plate 111 formed on the first bracket 11 in the embodiment shown in fig. 1, and the side plate being the second side plate 131 formed on the connecting bracket 13 in the embodiment shown in fig. 2. The detailed structure of the mounting unit 1 and the connection form between the mounting unit 1 and the vibration isolation unit 3 will be described in detail later, and will not be described in detail here. The inner ring frame 33 of the vibration isolation unit 3 is fixedly installed between the two side plates. The inner ring frame 33 is internally formed with bolt holes, and the inner ring frame 33 is fixed to the side plates by mounting bolts passing through the side plates and the bolt holes in order in the X direction. A installation direction for installing the bolt on frame 4 with inner circle skeleton 33 is X to, and both sides all have sufficient installation space around, no matter use electric tool or pneumatic tool all need not to use flexible switching device at the in-process of screwing up the bolt, fully guarantee to screw up the moment of torsion, each side only need screw up a bolt moreover can, obviously improve production efficiency.

The distance between the two side plates is configured to allow the outer ring bobbin 32 to move in the X direction relative to the inner ring bobbin 33. Because the inner ring framework 33 is fixed, the outer ring framework 32 is fixedly connected with the power assembly and can move along the X direction along with the power assembly, and the rubber main spring 31 can generate shearing action and deform in the process that the outer ring framework 32 moves along the X direction. In order to avoid the cracking of the vulcanized layer caused by the excessive deformation of the rubber main spring 31, the distance between the two side plates should be set to ensure that the outer ring framework 32 has a certain amount of movement and the vulcanized layer does not crack, for example, the distance between the two side plates can be set to make the maximum movement distance of the outer ring framework 32 be 10 mm.

In the process of installing the power assembly suspension, the cushions at the points a and B are usually installed first, and then the auxiliary support at the point E is installed, so that the problem of assembly tolerance may exist when the auxiliary support at the point E is installed, and the assembly manufacturability is poor. The present application thus designs the cross beam 2 to be adjustably mounted on the mounting unit 1 in at least two of the X, Y and Z directions. Thus, even if there is a tolerance at the time of mounting the E-point auxiliary support, the tolerance can be eliminated by adjusting the positions of the cross member 2 in the X direction, the Y direction, and the Z direction.

In the embodiment shown in fig. 1, referring to fig. 3 to 8 together, the mounting unit 1 may include a first bracket 11, the first bracket 11 having a first side plate 111 arranged in parallel, the first side plate 111 being provided with a first elongated hole 1111 extending in the Z direction, the vibration isolating unit 3 being adjustably mounted on the first side plate 111 in the Z direction through the first elongated hole 1111. Specifically, the vibration isolation unit 3 may further include a first outer sleeve 34 that is sleeved outside the outer ring frame 32 in an interference manner, a support table 35 for supporting the cross beam 2 is disposed on the first outer sleeve 34, a projection welding bolt 36 is disposed on the support table 35, and a second elongated hole 21 that extends in the X direction and is used for the projection welding bolt 36 to pass through is disposed on the cross beam 2. This embodiment enables adjustment of the cross beam 2 in the Z-direction and the X-direction.

In another embodiment shown in fig. 2, with reference to fig. 9 to 12, the mounting unit 1 may further include a second bracket 12 and a connecting bracket 13 connected between the second bracket 12 and the vibration isolation unit 3, and a third elongated hole 1321 extending in the X direction is provided on the first mounting stage 132 of the connecting bracket 13 for connecting with the second bracket 12, so that the connecting bracket 13 is adjustably mounted on the second bracket 12 in the X direction. The connecting bracket 13 has a second side plate 131 arranged in parallel, a fourth elongated hole 1311 extending in the Z direction is provided on the second side plate 131, a second outer sleeve 22 for being fitted over the outer side of the outer ring frame 32 with interference is integrally formed at the end of the cross beam 2, and the vibration isolation unit 3 is adjustably mounted on the second side plate 131 in the Z direction through the fourth elongated hole 1311. The second bracket 12 has a second mounting table 121 for fitting with the first mounting table 132, the second mounting table 121 is disposed obliquely downward and has a fifth elongated hole 1211 extending in an oblique direction, and the adjustment of the cross member 2 in the Y direction is achieved by the cooperation of the fifth elongated hole 1211 and the fourth elongated hole 1311. For example, the second mounting stage 121 may be arranged to be inclined downward by 45 °, and when the gap in the Y direction is large, the connecting bracket 13 is moved along the fifth elongated hole 1211 by 45 ° to fill the allowance. This embodiment enables adjustment of the cross beam 2 in the X, Y and Z directions.

In addition, for different vehicle models or the same vehicle model may also have gearboxes of different models, the position of the auxiliary support at the point E has a large difference, and in order to save development cost, the auxiliary support device of the present disclosure needs to adopt a modular design as much as possible. To this end, the auxiliary support device for a transmission of the present disclosure further includes at least one adjusting pad (not shown in the drawings) for being disposed between the mounting unit 1 and the frame 4, and compensating the gap in the Y direction, i.e., compensating the gap in the Y direction by the thickness of the adjusting pad.

For example, the vehicle model adapted by the invention has three types of vehicle frames, namely 8+7, 8+5 and 8+ 0. The meaning is that "8" on the left side indicates a thickness of 8mm on the outside of the double frame, and "7" on the right side indicates a thickness of 7mm on the side. "8 + 0" means that there is only an outer frame and no inner frame. If the frame is of an 8+7 structure, a base plate is not needed; if the frame is of an 8+5 structure, a base plate with the thickness of 2mm is used; if the frame is 8+0 structure, a shim plate with a thickness of 7mm is used. The shim plate used in this application may be 7mm or 2mm thick.

A second objective of the present disclosure is to provide a vehicle, including a powertrain having a transmission case and a transmission case auxiliary supporting device for auxiliary supporting the transmission case, wherein the transmission case auxiliary supporting device is the transmission case auxiliary supporting device mentioned above, and has all the beneficial effects of the transmission case auxiliary supporting device mentioned above, and the description thereof is omitted here.

The preferred embodiments of the present disclosure are described in detail with reference to the accompanying drawings, however, the present disclosure is not limited to the specific details of the above embodiments, and various simple modifications may be made to the technical solution of the present disclosure within the technical idea of the present disclosure, and these simple modifications all belong to the protection scope of the present disclosure.

It should be noted that the various features described in the above embodiments may be combined in any suitable manner without departing from the scope of the invention. In order to avoid unnecessary repetition, various possible combinations will not be separately described in this disclosure.

In addition, any combination of various embodiments of the present disclosure may be made, and the same should be considered as the disclosure of the present disclosure, as long as it does not depart from the spirit of the present disclosure.

Claims (10)

1. The utility model provides a gearbox auxiliary supporting device, its characterized in that, is including being used for installing installation unit (1) on frame (4) and crossbeam (2) that are used for supporting the gearbox, installation unit (1) with be provided with vibration isolation unit (3) between crossbeam (2), vibration isolation unit (3) including along X direction extend be used for with crossbeam (2) fixed connection's outer lane skeleton (32) and be used for with frame (4) fixed connection's inner circle skeleton (33), outer lane skeleton (32) with it has rubber main spring (31) to fill between inner circle skeleton (33).

2. The auxiliary support device for the gearbox according to claim 1, characterized in that a plurality of through holes penetrating through the main rubber spring (31) along the X direction are arranged on the main rubber spring (31), and the through holes are configured to enable the rubber material of the main rubber spring (31) to have different distribution amounts in the Z direction and the Y direction respectively.

3. The gearbox auxiliary support device according to claim 2, characterized in that the through hole comprises two dumbbell-shaped first through holes (311) symmetrically arranged about a Z-direction center line, and an upper half portion and a lower half portion of each first through hole (311) are respectively symmetrical about a Y-direction center line.

4. The auxiliary gearbox support device according to claim 2, wherein the through holes comprise two V-shaped second through holes (313) symmetrically arranged about a Z-direction central line and two V-shaped third through holes (314) symmetrically arranged about a Y-direction central line, wherein the upper half part and the lower half part of each second through hole (313) are respectively symmetrical about the Y-direction central line, and the left half part and the right half part of each third through hole (314) are respectively symmetrical about the Z-direction central line.

5. The auxiliary support device for the gearbox is characterized in that a limiting structure (312) is formed radially outwards on the peripheral edge of the through hole, the limiting structure (312) comprises a first limiting portion (3121) and a second limiting portion (3122) which enable rubber materials on two sides of the through hole to abut when acting force is applied, and the first limiting portion (3121) is closer to the center of the main rubber spring (31) than the second limiting portion (3122).

6. Auxiliary support device for a gearbox according to claim 1, characterised in that the length of said main rubber spring (31) in the X direction is adapted to the axial length of said outer (32) or inner (33) ring armature.

7. The auxiliary support device for the gearbox according to claim 6, characterized in that the mounting unit (1) comprises two side plates arranged in parallel at both ends of the vibration isolation unit (3) for fixed connection with the inner ring framework (33), and the distance between the two side plates is configured to allow the outer ring framework (32) to move in the X direction relative to the inner ring framework (33).

8. Gearbox auxiliary support arrangement according to claim 1, characterized in that the cross beam (2) is adjustably mounted on the mounting unit (1) in at least two of the X-, Y-and Z-directions.

9. The gearbox auxiliary support device of claim 1, further comprising at least one adjustment pad disposed between the mounting unit (1) and the frame (4) for compensating for Y-direction play.

10. A vehicle comprising a powertrain having a transmission and a transmission auxiliary support device for auxiliary support of the transmission, the transmission auxiliary support device being as claimed in any one of claims 1 to 9.

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