KR20120032775A - Roll-rod mount for vehicle - Google Patents

Roll-rod mount for vehicle Download PDF

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Publication number
KR20120032775A
KR20120032775A KR1020100094289A KR20100094289A KR20120032775A KR 20120032775 A KR20120032775 A KR 20120032775A KR 1020100094289 A KR1020100094289 A KR 1020100094289A KR 20100094289 A KR20100094289 A KR 20100094289A KR 20120032775 A KR20120032775 A KR 20120032775A
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KR
South Korea
Prior art keywords
bushing
rod
vehicle
housing
rod mount
Prior art date
Application number
KR1020100094289A
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Korean (ko)
Inventor
황철현
Original Assignee
현대자동차주식회사
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Publication date
Application filed by 현대자동차주식회사 filed Critical 현대자동차주식회사
Priority to KR1020100094289A priority Critical patent/KR20120032775A/en
Publication of KR20120032775A publication Critical patent/KR20120032775A/en

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K5/00—Arrangement or mounting of internal-combustion or jet-propulsion units
    • B60K5/12—Arrangement of engine supports
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
    • B60Y2306/00—Other features of vehicle sub-units
    • B60Y2306/09—Reducing noise

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Arrangement Or Mounting Of Propulsion Units For Vehicles (AREA)

Abstract

According to an aspect of the present invention, there is provided a roll rod mount for a vehicle connecting a power train composed of an engine and a transmission to a vehicle body, the rod comprising: cylindrical bushings having both sides opened at a distance from each other; And bushes coupled to the bushings and having a bolt hole formed at a center thereof, wherein the bushings are formed on one side of the rod and connected to the power train and formed on the other side of the rod. Each of the second bushing housing and the third bushing housing is connected to the vehicle body.
The present invention having the configuration described above is configured to transmit forces of opposite phases by using the concept of Center of Percussion (CP), so that the transmission force of the vehicle is canceled. Insulating more efficiently can reduce the vehicle interior transmission sound.

Description

Roll-rod mount for vehicle

The present invention relates to a vehicle roll rod mount, and more particularly, to a vehicle roll rod mount further comprising an additional bush to improve the behavior control and (vibration) insulation performance of a power train composed of an engine and a transmission (transmission). It is about.

Passenger cars use monocoque bodies that are light in weight and highly productive instead of frame bodies. The monocoque body is a structure in which a separate frame is eliminated, and a power train composed of an engine and a transmission is directly mounted on the body. Accordingly, the monocoque body is a frame function of the body itself, the suspension and the chassis components are mounted, respectively, but the sub-frame in the lower part of the vehicle in order to prevent the vibration of the powertrain is directly transmitted to the body and to distribute the impact in the event of a vehicle crash (subframe) is mounted.

The subframe is mounted under the vehicle body so that steering devices such as suspension struts and knuckles and suspension devices can be connected. Vehicles equipped with subframes are generally supported by mounting members in three places (three point mounts) or four places (four point mounts).

That is, the engine mount and the transmission mount are mounted on both sides of the vehicle body to support the load of the power train, but the roll rod mount is mainly mounted on the subframe so as to share displacement control and vibration damping of the power train.

The structure of the conventional roll rod mount is as shown in Fig. 1A. The roll rod mount may have cylindrical bushings opened at both ends of the rod, and a first bushing and a second bushing may be coupled to the bushing, respectively.

The first bushing and the second bushing are elastic materials, and a bolt hole is formed at a center thereof so that the bolt nut can be fastened. The first bushing is coupled to the bracket of the power train (P / T), and the second bushing is a vehicle body. It is mounted on the frame or subframe constituting the. In general, the second bush is formed to have a larger diameter than the first bush, and as shown in accordance with the layout of the engine room, the second bush may be mounted in a twisted manner so that the first bush and the second bush face different directions.

The vibration transmission structure of the conventional roll rod mount is described by showing a free body diagram as shown in FIG. 1B. If the vibration generated from the power train is called X in (displacement) and the transmission force transmitted to the body through the roll rod mount is F t , it can be calculated by the following equation.

"F t = K 1 (X in -X r ) + Mω 2 X r = K 2 X r " (K 1 : elastic modulus of the first bush, K 2 : elastic modulus of the second bush, X r : Displacement, ω: angular velocity, M: mass of rod)

The development of the equation is as follows. MX r "= F t1 -F t and F t1 = K 1 (X in -X r ). Thus, MX r " = K 1 (X in -X r ) -F t . Assuming that the system is in the harmonic range, substituting X in (t) = X in ? Exp (jωt), X r (t) = X r ? Exp (jωt) in the equation, -Mω 2 X r = K 1 (X in -X r )-F t In addition, since X r = F t / K 2 from the definition of elastic force, eventually multiplying both sides of the equation by K 2 and arranging, F t (K 1 + K 2 -Mω 2 X r ) = K 1 K 2 X in . Therefore, it can be summed up as F t / X in = K 1 K 2 / (K 1 + K 2 -Mω 2 X r ).

On the other hand, since the powertrain is a large weight body, it is insensitive to the elastic change of the bushes and has a rod with a constant amplitude (X in ). In this situation, one of the various methods of evaluating the insulation performance through the whole roll rod mount can be considered the transmission force of constant amplitude excitation. Therefore, the F t / X in value can be an indicator of the insulation performance of the roll rod mount.

In addition, in the high frequency region above the resonant frequency of the roll rod mount, the mass term (Mω 2 Xr) which is proportional to the frequency squared becomes larger than the elastic term (K 1 + K 2 ) of the bush, so the insulation performance is Ft / Xin = K 1 K It can be simplified to 2 / (-Mω 2 Xr), and it can be seen that the high frequency insulation performance deteriorates when K 1 or K 2 is increased to limit the power train behavior in the high torque region.

On the other hand, when a high torque driving reaction generated in the power train during rapid acceleration or sudden stop occurs, the spring characteristics (elastic modulus) of the second bush as shown in Figure 1c to control the rolling direction of the power train This changes sharply. Therefore, the dynamic characteristics of the second bush is also sharply changed, there is a problem that the leading rate of vibration is lowered.

That is, as shown in the above equation, the vibration damping characteristics of the conventional roll rod mount are determined by the mass of the rod and the elastic modulus of the first and second bushes. Therefore, the change of the characteristics of the second bush as described above degrades the vibration insulation performance and leads to deterioration of noise and vibration transmitted to the interior of the vehicle.

Accordingly, the present invention is to provide a roll roll mount for a vehicle having improved behavior of vibration control and vibration control of a power train in a high frequency vibration region even when high torque driving repulsion occurs.

According to an aspect of the present invention, there is provided a roll rod mount for a vehicle connecting a power train composed of an engine and a transmission to a vehicle body, the rods having cylindrical openings having both sides opened at a distance from each other; And bushes coupled to the bushings and having a bolt hole formed at a center thereof, wherein the bushings are formed on one side of the rod and connected to the power train on the other side of the first bushing housing and the rod. And a second bushing housing and a third bushing housing each of which is connected to the vehicle body.

In addition, the first bushing coupled to the first bushing housing may be mounted such that a bolt hole is perpendicular to the second bushing and the third bushing coupled to the second bushing housing and the third bushing housing. The second and third bushes are larger in diameter than the first bushing.

In addition, the first bushing housing is formed at one end of the rod and the third bushing housing is formed at the other end of the rod, the second bushing housing is opened in a position closer to the third bushing housing than the first bushing housing It is formed side by side so that the directions are parallel. The center of percussion is formed between the second bushing housing and the third bushing housing.

The present invention having the configuration described above is configured to transmit forces of opposite phases by using the concept of Center of Percussion (CP), so that the transmission force of the vehicle is canceled. Insulating more efficiently can reduce the vehicle interior transmission sound.

In particular, a larger effect is expected in a diesel vehicle that generates a relatively large torque, and has a greater attenuation effect in the mid- and high-frequency ranges, so that it is possible to more efficiently attenuate high-frequency motor noise of an electric vehicle to be developed later.

In addition, the roll rod mount of the present invention is different from the conventional vertical roll rod mount in terms of layout, it can be selectively applied to the vehicle. That is, the conventional roll rod mount has a high spring characteristic (elasticity) only in the longitudinal direction of the rod, a relatively low spring characteristic in the vertical direction, and the left and right directions, but a certain space must be secured in the longitudinal direction. Since it is mounted in a horizontal shape and can be mounted in a position where a conventional roll rod mount is difficult to mount, it can be selectively mounted in a vehicle not only in a subframe but also in other positions, thereby increasing behavior control and vibration insulation performance.

1A is a side view showing a perspective view of a conventional roll rod mount and a state in which the roll rod mount is mounted between a power train and a vehicle body;
Figure 1b is a free body showing the vibration transmission structure of a conventional roll rod mount,
1C is a graph showing spring characteristics of a second bush of a conventional roll rod mount;
2 is a side view showing a state in which the roll rod mount and the roll rod mount is mounted between the powder train and the vehicle body according to a preferred embodiment of the present invention;
Figure 3 is a free body showing the vibration transmission structure of the roll rod mount of the present invention.

Hereinafter, a vehicle roll rod mount according to a preferred embodiment of the present invention with reference to the drawings in more detail.

Referring to FIG. 2, the vehicle roll rod mount of the present invention includes a rod 10 and bushes 20, 30, and 40 coupled to each other to connect the power train and the vehicle body, and the bushes 20, 30, and 40 are coupled to each other. ), Bushings 11, 12, 13 are formed in the rod.

The bushings 11, 12, and 13 have a cylindrical shape in which both sides thereof are opened, and a bolt hole of the first bushing 20 is parallel to the length direction of the rod 10 at one end of the rod 10. A first bushing housing 11 configured to be mounted and a third bushing housing formed in a direction perpendicular to the first bushing housing 11 at the other end of the rod 10 and on an opposite surface of the first bushing housing 11; 13) and the second bushing housing 12 formed to be parallel to the third bushing housing 13 at a predetermined distance.

Each of the bushings 11, 12, and 13 is coupled to the first bushing 20, the second bushing 30, and the third bushing 40, respectively, and the bushes 20, 30, and 40 are respectively Bolt holes are formed so that bolt nuts can be fastened to brackets formed in the vehicle body and the power train.

Therefore, in the above structure, the bolt holes of the first bushing 20 are disposed at right angles with the bolt holes of the second bushing 30 and the third bushing 40. The first bushing 20 is coupled to the powertrain (P / T) side bracket, and the second bushing 30 and the third bushing 40 are coupled to the vehicle body side bracket.

In addition, the second bushing 30 and the third bushing 40 have a larger diameter than the first bushing 20 so as to increase the insulation performance of the vibration transmitted to the vehicle body side.

Hereinafter, the insulating characteristics of the roll rod mount according to the present invention will be described in more detail with reference to FIG. 3.

Assuming that a conventional roll rod mount the second bush 30, the spring characteristic in order to provide a conventional roll rod mount the same or more power train behavior control (displacement) K 2eq, in Figure 3, the load through the K 1 The force (F t1 ) transmitted to (10) is F t1 -F t2 -F t3 = 0 by the balance of the static force.

At this time, the length, as shown in the figure based on the location of the (when applied an external force to the P 1 point does not move due to the translational motion and the superposition of the rotational motion of the weight center point of the rotation center point) severe (CP) If you set up the equation of motion with L, displacement X, elastic modulus K, and acting force F, F t2 (L 2 + L 3 )-(L 1 + L 2 + L 3 ) F Since t1 = 0, F t2 = F t1 (L 1 + L 2 + L 3 ) / (L 2 + L 3 ), and F t3 = -F t1 L 1 / (L2 + L3). At this time, since the rod is rigid, X 1 = X 2 + (X 2 -X 3 ) L 1 / (L 2 + L 3 ), X 1 = X 2 (L 1 + L 2 + L 3 ) / (L 2 + L 3 )-X 3 L 1 / (L 2 + L 3 ) can be established.

From the definition of spring characteristics (elasticity of the bushes), X 2 = F t2 / K 2 , X 3 = F t3 / K 3, so substituting it in the above equation, X 1 = (F t2 / K 2 ) (L 1 + L 2 + L 3 ) / (L 2 + L 3 )-(F t3 / K 3 ) L 1 / (L 2 + L 3 ). From the above equations, X 1 = (F t1 / K 2 ) (L 1 + L 2 + L 3 ) 2 / (L 2 + L 3 ) 2 + (F t1 / K 3 ) L 2 / (L 2 + L 3 ) 2 and X 1 / F t1 = (1 / K 2 ) (L 1 + L 2 + L 3 ) 2 / (L 2 + L 3 ) 2 + (1 / K 3 ) L 1 2 / (L 2 + L 3 ) 2 is derived.

And, in order to control the same behavior control and rigid body mode as the conventional roll rod mount, K 2eq = F t1 / X 1 , which is substituted into the equation above, K 2eq = F t1 / X 1 = (L 2 + L 3 ) 2 / [(1 / K 2 ) (L 1 + L 2 + L 3 ) 2 + (1 / K 3 ) L 1 2 ] can be derived.

Therefore, in the control of the behavior of the power train, the tuning factor for meeting the requirements required for the design except the elastic modulus of the bushes and the weight of the rod has been conventionally lacked. Various changes can be made to control the spacing, giving designers design flexibility.

In addition, in terms of minimizing the transmission force of the high frequency vibration, it is required to make Ft2 + Ft3 = 0 to cancel the vibration transmission in the high frequency band, i.e., F t2 and F t3 are the same magnitude in opposite directions. It's power. High-frequency band in the hardly affected by the spring property of the bush only can be assumed to be dominated by only the force of inertia of the external excitation force and the load itself, rotating the severe (CP) when external force is applied to load the position P 1 to the rotational axis You exercise. At this time, if the dynamic minute rotation angle 'θ', X 2 = L 2 θ, X 3 = -L 3 θ. And, F t2 = K 2 X 2 , F t3 = K 3 X 3 because, by using the preceding formula to set such that the F t2 + F t3 = 0 for the transfer force minimization of the vehicle body F t2 + F t3 At = 0, the equations K 2 L 2 θ = K 3 L 3 θ and K 2 L 2 = K 3 L 3 are derived.

Therefore, the vibration and noise of the high frequency region can also be more efficiently attenuated by tuning the distance between the second bushing housing 12 and the third bushing housing 13 and the center of gravity forming position.

The roll rod mount for a vehicle of the present invention further includes a third bushing 13 and a third bush 40 to prevent deterioration of vibration insulation performance due to an increase in spring characteristics of a high load region.

In other words, by placing the second bushing 30 and the third bushing 40 at both ends of the rod's severe core, the forces of opposite phases are transmitted to the vehicle body in the high frequency band to offset the vibration transmission force to drive the high frequency during vehicle operation. It is configured to suppress room permeation. In addition, it is possible to further improve design flexibility by providing a tuning factor that can more efficiently provide tuning to the characteristics and design needs of the vehicle.

As described above, the embodiments disclosed in the specification and the drawings are only presented as specific examples to aid the understanding of the present invention, and are not intended to limit the scope of the present invention. It will be apparent to those skilled in the art that other modifications based on the technical idea of the present invention are possible in addition to the embodiments disclosed herein.

10: load
11: First Bush Housing
12: Second Bushing Housing
13: Third Bushing Housing
20: first bush
30: second bush
40: third bush

Claims (4)

In a vehicle roll rod mount that connects a power train composed of an engine and a transmission to a vehicle body,
A rod having cylindrical openings having both sides opened at a distance from each other; And bushes coupled to the bushings and having a bolt hole formed in the center thereof.
The bushing housings may include a first bushing housing formed on one side of the rod and connected to a power train, and a second bushing housing and a third bushing housing formed on the other side of the rod and connected to the vehicle body, respectively. Car roll rod mount.
The method of claim 1, wherein the first bushing coupled to the first bushing housing, the second bushing and the third bushing coupled to the second bushing housing and the third bushing housing are mounted at right angles. Car rolling rod mount.
3. The roll rod mount for a vehicle according to claim 2, wherein the second bushing and the third bushing have a larger diameter than the first bushing.
4. The bushing according to any one of claims 1 to 3, wherein the first bushing housing is formed at one end of the rod and the third bushing housing is formed at the other end of the rod, and between the second bushing housing and the third bushing housing. Roll rod mount for a vehicle, characterized in that the core of the rod is formed.
KR1020100094289A 2010-09-29 2010-09-29 Roll-rod mount for vehicle KR20120032775A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
KR1020100094289A KR20120032775A (en) 2010-09-29 2010-09-29 Roll-rod mount for vehicle

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Application Number Priority Date Filing Date Title
KR1020100094289A KR20120032775A (en) 2010-09-29 2010-09-29 Roll-rod mount for vehicle

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KR20120032775A true KR20120032775A (en) 2012-04-06

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20230126526A (en) 2022-02-23 2023-08-30 현대자동차주식회사 Press-fit type motor mounting double insulated bush structure

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20230126526A (en) 2022-02-23 2023-08-30 현대자동차주식회사 Press-fit type motor mounting double insulated bush structure

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