JP6430798B2 - Vehicle suspension - Google Patents

Description

  The present invention relates to a vehicle suspension provided with a beam that is installed on left and right suspension arms and couples the left and right arms together.

  Conventionally, there is a suspension of the vehicle described in Patent Document 1 below. According to this publication, each suspension extends in the front-rear direction of the vehicle body, and each front end side pivots to the vehicle body by a pivotal support so that each rear end portion supports the wheel and can swing up and down. A pair of left and right suspension arms, and a beam that is installed on the left and right arms and couples the left and right arms together.

  When the vehicle turns, the left and right arms swing around the pivot tool and are displaced relative to each other in the vertical direction by an external force (reaction force) applied to each wheel from the road surface against the weight of the vehicle. . Due to this relative displacement, the beams installed on the left and right arms are elastically torsionally deformed, and a torsional stress is generated in the beams. As a result, this beam is elastically repelled and acts mainly as a stabilizer as well as a torsion bar. As a result, a stable turn is obtained in the vehicle, and the desired maneuverability is ensured in the vehicle. It has become.

JP 2004-34866 A

  By the way, as described above, when the vehicle is turning, the beam is torsionally deformed due to the relative displacement of the left and right arms, and a torsional stress is generated in the beam. The ends of the beam in the longitudinal direction are rigidly connected to the right arm.

  For this reason, in the vicinity of the left and right arms in the beam, the rigidity tends to be excessively reinforced by these arms. Therefore, the torsional deformation of the beam at the time of turning of the vehicle is insufficient, and there is a possibility that the vehicle cannot reliably obtain a stable turn.

  The present invention has been made by paying attention to the above-described circumstances, and an object of the present invention is to provide a stable turning to the vehicle when the vehicle suspension includes a beam for connecting the left and right suspension arms. Is to ensure that it is obtained more reliably.

According to the first aspect of the present invention, each front end portion extends to the vehicle body 2 by the pivotal support 14 so as to extend in the front-rear direction of the vehicle body 2 and each rear end portion thereof supports the wheels 4 and 5 and can swing up and down. In a vehicle suspension comprising a pair of left and right suspension arms 12 and 13 that are pivotally supported and a beam 24 that spans the left and right arms 12 and 13 and connects the left and right arms 12 and 13 together.
The front portions 12a and 13a of the arms 12 and 13 are formed of a flat plate material in which the cross-section of each portion in the longitudinal direction is a rectangle that is long in the vertical direction, and the rear portions 12b and 13b of the arms 12 and 13 are formed. , Each of the longitudinal sections of each part is a rigid material having a hollow closed cross section ,
The front ends of the rear portions 12b and 13b of the left and right arms 12 and 13 are pivotally supported on the vehicle body 2 by the pivotal support 14 , respectively.
The cross section of each part in the longitudinal direction of the beam 24 has a U-shaped open cross-sectional structure in which the inner space opens forward ,
The coupling portion between each end of the longitudinal direction of the front 12a, the beam 24 which definitive to 13a of the respective arms 12 and 13, the front portion 12a of each of the arms 12, 13 in the width direction of the vehicle body 2, 13a each of butt-coupled to each end of the beam 24 and the inner side surface, the front portion 12a of the arms 12, 13 in the coupling portion, to 13a, if the inner space 29 shape of the cross section of each end of the beam 24致The vehicle suspension is characterized in that a notch 30 is formed toward the front .

  In addition, in this section, the reference numerals and drawing numbers appended to the above terms are not intended to limit the technical scope of the present invention to the “Example” section and the contents of the drawings described later.

  The effects of the present invention are as follows.

According to the first aspect of the present invention, a pair of left and right sides each extending in the front-rear direction of the vehicle body, each front end side being pivotally supported by the pivotal support so that each rear end portion can support a wheel and swing up and down. A suspension arm of the vehicle, and a suspension of the vehicle provided with the left and right arms and a beam connecting the left and right arms.
The front portions of the left and right arms are pivotally supported on the vehicle body by the pivot support.

  For this reason, the beam is prevented from being reinforced by the pivotal support, and the rigidity of the beam is prevented from becoming excessive.

  Further, the cross section of each part in the longitudinal direction of the beam has an open cross section structure in which the inner space opens outward.

  For this reason, the torsional rigidity of the beam can be suppressed to a reasonably low level as compared with the case where the beam is made of a long rigid material such as a pipe material.

  Therefore, when the vehicle turns, the beam smoothly twists and deforms with the relative displacement of the left and right arms, and a desired torsional stress is generated in the beam. As a result, stable turning of the vehicle is ensured. Will be obtained.

  Further, a notch that substantially matches the inner space shape in the cross section of the beam is formed in the beam coupling portion of each arm.

  For this reason, the improvement of the rigidity around the joint portion between each arm and the beam is suppressed by the formation of the notch. Therefore, when the vehicle turns, the beam is smoothly twisted and deformed in the entire longitudinal direction without being obstructed by the rigidity around the coupling portion due to the relative displacement of the left and right arms. The desired torsional stress occurs more reliably. As a result, it is possible to prevent stress concentration from occurring around the coupling portion, thereby preventing damage to this portion and further ensuring a stable turn in the vehicle.

It is a top view. It is a rear view. It is a side view. It is a fragmentary perspective view. FIG. 5 is an enlarged cross-sectional view taken along line VV in FIG. 1.

  The vehicle suspension according to the present invention achieves the object of ensuring that a stable turn can be obtained more reliably when the vehicle suspension includes a beam that couples the left and right suspension arms. Therefore, the form for carrying out the present invention is as follows.

  That is, the suspension of the vehicle extends in the front-rear direction of the vehicle body, and a pair of left and right wheels whose front end portions are pivotally supported on the vehicle body by the pivotal support so that their rear end portions can support the wheels and swing up and down. Suspension arms and a beam that is erected on the left and right arms and couples the left and right arms together. The front portions of the left and right arms are pivotally supported on the vehicle body by the pivot support. Each cross section in the longitudinal direction of the beam has an open cross-sectional structure in which the inner space opens outward. A cutout that substantially matches the shape of the inner space in the cross section of the beam is formed at the beam coupling portion of each arm.

  In order to explain the present invention in more detail, an embodiment thereof will be described with reference to the accompanying drawings.

  In the figure, reference numeral 1 in the figure is a vehicle exemplified by an automobile, and an arrow Fr indicates the front in the traveling direction of the vehicle 1. The left and right described below refer to the width direction of the vehicle body 2 of the vehicle 1 toward the front.

  The vehicle 1 includes a vehicle body 2 and a pair of left and right rear wheels 4 and 5 suspended by a rear suspension 3 at a rear portion of the vehicle body 2. The vehicle body 2 is supported on the traveling road surface 6 by the suspension 3, the rear wheels 4 and 5, and a pair of left and right front wheels (not shown). The vehicle body 2, the suspension 3, and the left and right wheels 4 and 5 are symmetric with respect to a vehicle body center line 7 that passes through the center of the vehicle body 2 in the width direction.

  The suspension 3 extends in the front-rear direction of the vehicle body 2, and a pair of left and right suspension arms 12, 13 that support the wheels 4, 5 by the wheel support 11 at the respective rear ends thereof, and the arms 12, 13. A pivot support 14 for pivotally supporting the front end of each arm 12, 13 on the vehicle body 2 so that each rear end of the vehicle can swing up and down together with the wheels 4, 5, and the left and right arms. 12 and 13, the left and right arms 12 and 13 are connected to each other, a cross member 15 formed in an X shape in a plan view of the vehicle body 2 (FIG. 1), the vehicle body 2 and the arms 12 and 13. The shock absorber 16 is provided between the rear end portion and a coil spring and a shock absorber. In this case, a fastening hole 17 for fastening the lower end of the shock absorber 16 is formed at the rear end of each arm 12, 13.

  The front portions 12a and 13a of the arms 12 and 13 are each formed of a metal flat plate material in which the cross section of each portion in the longitudinal direction forms a rectangle that is long in the vertical direction. Further, the front portions 12a and 13a of the arms 12 and 13 extend linearly toward the outer side of the vehicle body 2 toward the rear of the vehicle body 2 in a plan view of the vehicle body 2 (FIG. 1), respectively. Inclined with respect to line 7.

  The rear portions 12b and 13b of the arms 12 and 13 are metal rigid members whose cross sections in the longitudinal direction form a hollow closed cross section. The rear portions 12b and 13b of the arms 12 and 13 are respectively viewed from the rear end portions of the front portions 12a and 13a of the arms 12 and 13 toward the rear of the vehicle body 2 in a plan view of the vehicle body 2 (FIG. 1). The vehicle body 2 is inclined with respect to the vehicle body center line 7 so as to go outward.

  Each pivot support 14 is connected to the front end of each rear portion 12b, 13b of each arm 12, 13 by welding, and has a cylindrical body 19 whose longitudinal axis is oriented vertically, and the axial center of this cylindrical body 19. A pivot shaft 20 positioned above and penetrating through the cylindrical body 19 and supported at both ends by the vehicle body 2, and an annular space between the cylindrical body 19 and the pivot shaft 20 is filled. And a rubber bush 21 having an annular shape which is vulcanized and bonded to 19 and 20 and elastically connects the 19 and 20 to each other. As a result, the front portions of the left and right arms 12 and 13 are pivotally supported on the vehicle body 2 by the pivotal support 14, respectively.

  The cross member 15 extends in the width direction of the vehicle body 2 and is mounted on the front portions 12a and 13a of the left and right arms 12 and 13 so as to connect the front portions 12a and 13a to each other by welding. A rear beam 25 made of a sheet metal that extends in the width direction of the vehicle body 2 and extends over the rear portions 12b and 13b of the left and right arms 12 and 13 to join the rear portions 12b and 13b together by fastening. And a ball joint 26 that pivotally supports the longitudinal central portions of the front and rear beams 24 and 25, respectively.

  The front beam 24 has a dogleg shape that is bent rearward in a plan view of the vehicle body 2 (FIG. 1), and the rear beam 25 is forward in the plan view of the vehicle body 2 (FIG. 1). It is in the shape of a dogleg bent. The bent portions of the front and rear beams 24 and 25 are located at the center portions in the longitudinal direction of the front and rear beams 24 and 25, respectively.

  As described above, the front and rear beams 24 and 25 are bent in the shape of a dogleg in the front-rear direction, and these bent portions are pivotally supported by the ball joint 26. Then, as described above, the cross member 15 has an X shape in the plan view of the vehicle body 2 (FIG. 1), and the ball joint 26 has the X shape due to the arrangement configuration of the members 24, 25, and 26. It constitutes the intersection of shapes.

  Each cross section in the longitudinal direction of the front beam 24 has an open cross-sectional structure in which the inner space 29 opens toward the front outer side. Specifically, each cross section in the longitudinal direction of the front beam 24 has a U shape in which the inner space 29 is open toward the front, and is substantially the same shape and size. Further, the shear center of the front beam 24 is located on the rear side of the front beam 24. The cross-section of each part of the front beam 24 may be an open cross-sectional structure having other shapes such as a U-shape, C-shape, V-shape, L-shape, and the inner space 29 is located above, below, or You may open toward these inclination directions.

  At the joints between the arms 12 and 13 and the longitudinal ends of the front beam 24, the front surfaces of the front portions 12a and 13a of the arms 12 and 13 in the width direction of the vehicle body 2 Each end of the partial beam 24 is butt welded. In this case, the vertical width dimension of the front portions 12a and 13a of the arms 12 and 13 is made sufficiently larger than the vertical thickness dimension of the front beam 24. , 13 to the front portions 12a and 13a, the coupling strength at each end of the front beam 24 is sufficiently secured.

  Further, the front portions 12a and 13a at the joints between the front portions 12a and 13a of the arms 12 and 13 and the end portions of the front beam 24 are crossed by the end portions of the front beam 24. A notch 30 is formed that substantially matches the shape of the inner space 29 on the surface. In this case, the shear center of the front beam 24 is located in the vicinity of the rear of the front beam 24 and the notch 30, and penetrates the front portions 12a and 13a of the arms 12 and 13, respectively. Note that, in the coupling portion, each end portion of the front beam 24 or a longitudinal intermediate portion of each end portion is fitted in each notch 30 of the front portions 12a and 13a of the arms 12 and 13. May be connected by welding, and the connection may be by a fastener.

  Each cross section in the longitudinal direction of the rear beam 25 has an open cross-sectional structure in which the inner space opens outward. The rear beam 25 has left and right rear members 33, 33 constituting the rear side of the ball joint 26 that is an X-shaped intersection of the cross member 15. Each of these rear members 33 includes a strip-shaped long plate material 36 that extends linearly from the side of the ball joint 26 that is the intersecting portion toward the rear portion of each of the arms 12 and 13, and the long plate material 36. Other lengths extending linearly and projecting integrally from one end edge (rear end edge) in the width direction of the long plate 36 to the outer side (upper side) in the thickness direction of the long plate 36 And a scale plate member 37.

  Specifically, the thicknesses of the long plate members 36 and 37 are the same as each other. In each cross section of the rear member 33, the long plate 36 extends substantially horizontally, the other long plate 37 extends in the vertical direction, and the other length is longer than the width of the long plate 36. The width dimension of the scale plate material 37 is increased. As a result, the cross-sections in the longitudinal direction of the rear members 33 of the rear beam 25 are substantially the same shape and size, and the inner space is L-shaped and opens outward in the front upper direction. . Further, the center of shear of each rear member 33 of the rear beam 25 is located on the rear side of these rear members 33. The cross section of each part of the rear beam 25 may be U-shaped, U-shaped, C-shaped, or V-shaped.

  The ball joint 26 includes a main ball 39, a support arm 40 projecting integrally from the ball 39 toward the outer side in the radial direction (forward), and the longitudinal center of the rear beam 25. Is inserted into a socket 43 that is supported by a bracket 41 and includes the ball 39 so as to be rotatable around a center point 42 thereof, and a fitting hole 44 formed in the longitudinal center of the front beam 24. And a bracket 46 that is coupled by welding and that removably fixes the protruding end of the support arm 40 with a fastener 45.

  The bracket 41 is joined to the outer surface of the rear beam 25 by welding W1 and W2. The bracket 41 is made of sheet metal, and extends integrally from the left and right outer edges of the main plate 41a to the main plate 41a facing the other long plate 37 of the rear beam 25 with a slight distance to the front. Left and right side plates 41b and 41b are provided. The lower edge of the main plate 41a is joined to the upper surface of the long plate 36 of the rear beam 25 by welding W1, and the rear edge of each side plate 41b is connected to the front of another long plate 37 of the rear beam 25. Joined by welding W2. Thereby, the bracket 41 is joined to the outer surface of the rear beam 25.

  In the above case, the left and right side plates 41b and 41b of the bracket 41 are spaced apart from each other in the width direction of the vehicle body 2 toward the long plate 36. Thereby, a trapezoidal box-shaped body having a large rigidity in a front view of the vehicle body 2 is formed by the central portion in the longitudinal direction of the rear beam 25 and the bracket 41.

  An insertion hole 48 for inserting and supporting the socket 43 in the main plate 41a of the bracket 41 is formed by burring the main plate 41a. In addition, an insertion hole 49 for inserting the socket 43 when the socket 43 is inserted into the insertion hole 48 is formed in the other long plate member 37 of the rear beam 25.

  In the work of forming the suspension 3 of the vehicle 1, when the cross member 15 is assembled, first, the left and right arms 12 and 13 and the front and rear beams 24 and 25 constituting the cross member 15 are connected. Each is formed, and these 12, 13, 24, and 25 are joined together to form a frame-shaped intermediate product. Next, in this frame-shaped intermediate product, with reference to the left and right fastening holes 17 and 17 formed at the rear end portions of the left and right arms 12 and 13 on the side of each end of the rear beam 25, The bracket 41 is joined to a desired position along the outer surface of the rear beam 25.

  Next, the socket 43 of the ball joint 26 is fitted together with the ball 39 into the fitting hole 48 of the bracket 41 and is supported by the bracket 41. At this time, the support arm 40 of the ball joint 26 is fastened to the front beam 24 by a fastener 45 via another bracket 46. Thereby, the assembly work of the cross member 15 is completed.

  When the vehicle 1 turns, the left and right arms 12 and 13 move around the pivotal support 14 due to an external force (reaction force) applied to the wheels 4 and 5 from the traveling road surface 6 against the weight of the vehicle 1. Oscillates and relatively displaces in the vertical direction (dashed line in FIG. 2). Due to this relative displacement, the front and rear beams 24 and 25 installed on the left and right arms 12 and 13 are relatively rotated around the center point 42 of the ball 39 of the ball joint 26 and elastically respectively. Thus, a desired torsional stress is generated in the front and rear beams 24 and 25 by torsional deformation. As a result, the front and rear beams 24 and 25 are elastically repelled and function mainly as a stabilizer and a torsion bar. As a result, the vehicle 1 can obtain a stable turn and can have a desired maneuverability. Is to be secured.

  In the above case, before turning the vehicle 1, the rear beams 24 and 25 are torsionally deformed by the external force from the wheels 4 and 5 as described above. At this time, the bending moment due to the external force is applied to the ball joint. In order to prevent unnecessary application to 26 and to smoothly achieve the torsional deformation of the front and rear beams 24 and 25, the following configuration is provided.

  That is, the respective shear centers (twist centers) of the left side portion of the front beam 24 and the right side portion of the rear beam 25 are positioned on a common first imaginary straight line 50. Further, the respective shear centers (twist centers) of the right side portion of the front beam 24 and the left side portion of the rear beam 25 are positioned on a second imaginary straight line 51 that is common to each other. The center point 42 of the ball 39 of the ball joint 26 is located as close as possible to the intersection of the first and second virtual straight lines 50 and 51 (corresponding to the torsion center of the front and rear beams 24 and 25). Be made. The first imaginary straight line 50 of the front beam 24 intersects the central portion of the axial center of the pivot shaft 20 of the pivot tool 14 in the longitudinal direction.

  In addition, as described above, the cross member 15 includes the front and rear beams 24 and 25 and the ball joint 26 that pivotally supports the center portions of the respective longitudinal directions of the 24 and 25. In a plan view (FIG. 1), the ball joint 26 has an X shape with the intersection.

  Here, when the vehicle 1 turns, an external force is applied to the arms 12 and 13 from the wheels 4 and 5 supported on the rear ends of the arms 12 and 13 in the width direction of the vehicle body 2. When the external force is given a larger bending moment, the arms 12 and 13 tend to be greatly deformed.

  However, as described above, the front and rear beams 24 and 25 installed on the left and right arms 12 and 13 are formed in an X shape in a plan view of the vehicle body 2 (FIG. 1) via the ball joint 26. The external force is supported in the axial direction by the front and rear beams 24 and 25 through the ball joint 26, that is, the external force is firmly supported by the vehicle body 2 through the front and rear beams 24 and 25. In other words, it is possible to prevent a large bending moment from being applied to the arms 12 and 13. Therefore, when the vehicle 1 turns, the arms 12 and 13 are prevented from being greatly deformed, whereby a stable turn is obtained in the vehicle 1 and desired operability is ensured.

  According to the above configuration, the front portions of the left and right arms 12 and 13 are pivotally supported on the vehicle body 2 by the pivot support 14.

  For this reason, the front beam 24 is prevented from being reinforced by the pivot support 14, and the rigidity of the front beam 24 is prevented from becoming excessive.

  In addition, each cross section in the longitudinal direction of the front beam 24 has an open cross-sectional structure in which the inner space 29 opens outward.

  For this reason, the torsional rigidity of the front beam 24 can be suppressed to a reasonably low level as compared with the case where the front beam 24 is made of a long rigid material such as a pipe material.

  Therefore, when the vehicle 1 turns, the front beam 24 is smoothly torsionally deformed with the relative displacement of the left and right arms 12 and 13, and a desired torsional stress is generated in the front beam 24. As a result, Thus, a stable turn in the vehicle 1 can be obtained more reliably.

  Further, a notch 30 that substantially matches the shape of the inner space 29 in the cross section of the front beam 24 is formed at the joint of the front beam 24 in each of the arms 12 and 13.

  For this reason, improvement in the rigidity around the joint between the arms 12 and 13 and the front beam 24 is suppressed by the formation of the notch 30. Therefore, when the vehicle 1 turns, the front beam 24 is smoothly twisted over the entire length thereof without being obstructed by the rigidity around the coupling portion due to the relative displacement of the left and right arms 12 and 13. As a result of the deformation, the front beam 24 is more reliably subjected to the desired torsional stress. As a result, it is possible to prevent stress concentration from occurring around the coupling portion, thereby preventing damage to this portion and further ensuring a stable turn in the vehicle 1.

  In addition, the joint portions (front portions 12a and 13a) of the front beams 24 in the arms 12 and 13 are flat plate members whose cross sections in the longitudinal direction of the arms 12 and 13 are long in the vertical direction. .

  For this reason, the improvement of the rigidity of the joint portions (front portions 12a, 13a) of the front beams 24 in the arms 12, 13 is suppressed more effectively, particularly in the width direction of the vehicle body 2. Therefore, when the front beam 24 is torsionally deformed with the relative displacement of the left and right arms 12 and 13 when the vehicle 1 is turning, the connecting portions (front portions 12a and 13a) are also elastically elastic in conjunction with this. Due to the deformation, the torsional deformation of the front beam 24 is sufficiently achieved and the desired torsional stress is more reliably generated. As a result, a stable turn in the vehicle 1 can be obtained more reliably.

  The bracket 41 may be joined to the rear beam 25 by a fastener. Further, the attachment of the ball joint 26 to the front and rear beams 24 and 25 may be reversed from the above example. Further, without providing the ball joint 26, the cross member 15 may be constituted by front and rear beams 24, 25, and the intersections of these beams 24, 25 may be rigidly connected to each other.

  Further, the end portions of the front beam 24 to the left and right arms 12 and 13 are coupled to the front portions 12a and 13a of the arms 12 and 13, respectively, in the longitudinal direction of the arms 12 and 13, respectively. A support plate having a shape such as 13a may be provided so as to connect the ends of the front beam 24 to the protruding ends of the support plates and to form the notches 30. Further, the coupling structure between the arms 12 and 13 and the end portions of the front beam 24 may be applied to the coupling portion between the arms 12 and 13 and the end portions of the rear beam 25.

DESCRIPTION OF SYMBOLS 1 Vehicle 2 Car body 3 Suspension 4 Wheel 5 Wheel 6 Running road surface 7 Car body centerline 11 Wheel support body 12 Arm 12a Front part 12b Rear part 13 Arm 13a Front part 13b Rear part 14 Pivoting tool 15 Cross member 16 Shock absorber 17 Fastening hole 19 Tubular body 20 Pivot shaft 21 Rubber bush 24 Front beam 25 Rear beam 26 Ball joint (intersection)
29 inner space 30 notch 33 rear member 36 long plate material 37 long plate material 39 ball 40 support arm 41 bracket 42 center point 43 socket 48 fitting hole 49 insertion hole 50 first virtual straight line 51 second virtual straight line

Claims (1)

A pair of left and right suspension arms, each extending in the longitudinal direction of the vehicle body, each front end side being pivotally supported on the vehicle body by a pivotal support so that each rear end portion can support a wheel and swing up and down. In the suspension of the vehicle provided with a beam that is installed on the right arm and couples the left and right arms,
The front part of each arm is formed of a flat plate whose cross section in the longitudinal direction is a rectangle that is long in the longitudinal direction, and the cross section of each part in the longitudinal direction is closed in the rear part of each arm. A rigid material with a cross-section
The front end of each rear part of the left and right arms is pivotally supported on the vehicle body by the pivotal support,
The cross section of each part in the longitudinal direction of the beam has a U-shaped open cross-sectional structure in which the inner space opens forward ,
The coupling portion between each end of the longitudinal direction of the beam definitive the front portion of each arm, and butt-coupled to each end of the beam to the inner surfaces of the front portion of the respective arm of the vehicle body in the width direction, the front of each arm of the coupling portion, the suspension of the vehicle, characterized in that the formation of the notch toward the case matches the labels forward the inner space shape of the cross section of each end of the beam.

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