CN108237859B - Suspension system and vehicle using same - Google Patents
Suspension system and vehicle using same Download PDFInfo
- Publication number
- CN108237859B CN108237859B CN201611206441.2A CN201611206441A CN108237859B CN 108237859 B CN108237859 B CN 108237859B CN 201611206441 A CN201611206441 A CN 201611206441A CN 108237859 B CN108237859 B CN 108237859B
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- axle
- hinged
- elastic element
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- rod
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- 239000000725 suspension Substances 0.000 title claims abstract description 52
- 230000008859 change Effects 0.000 abstract description 6
- 230000002159 abnormal effect Effects 0.000 abstract description 3
- 238000013016 damping Methods 0.000 description 17
- 239000007789 gas Substances 0.000 description 6
- 230000009467 reduction Effects 0.000 description 5
- 230000005284 excitation Effects 0.000 description 4
- 238000007789 sealing Methods 0.000 description 4
- 230000006835 compression Effects 0.000 description 3
- 238000007906 compression Methods 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 239000003921 oil Substances 0.000 description 3
- 230000008569 process Effects 0.000 description 3
- IJGRMHOSHXDMSA-UHFFFAOYSA-N Atomic nitrogen Chemical compound N#N IJGRMHOSHXDMSA-UHFFFAOYSA-N 0.000 description 2
- 230000009471 action Effects 0.000 description 2
- 230000003111 delayed effect Effects 0.000 description 2
- 229910001873 dinitrogen Inorganic materials 0.000 description 2
- 230000006872 improvement Effects 0.000 description 2
- 230000008439 repair process Effects 0.000 description 2
- 230000001154 acute effect Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000011900 installation process Methods 0.000 description 1
- 230000009191 jumping Effects 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000002035 prolonged effect Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 238000010008 shearing Methods 0.000 description 1
Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G11/00—Resilient suspensions characterised by arrangement, location or kind of springs
- B60G11/14—Resilient suspensions characterised by arrangement, location or kind of springs having helical, spiral or coil springs only
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G13/00—Resilient suspensions characterised by arrangement, location or type of vibration dampers
- B60G13/02—Resilient suspensions characterised by arrangement, location or type of vibration dampers having dampers dissipating energy, e.g. frictionally
- B60G13/06—Resilient suspensions characterised by arrangement, location or type of vibration dampers having dampers dissipating energy, e.g. frictionally of fluid type
- B60G13/08—Resilient suspensions characterised by arrangement, location or type of vibration dampers having dampers dissipating energy, e.g. frictionally of fluid type hydraulic
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G13/00—Resilient suspensions characterised by arrangement, location or type of vibration dampers
- B60G13/02—Resilient suspensions characterised by arrangement, location or type of vibration dampers having dampers dissipating energy, e.g. frictionally
- B60G13/06—Resilient suspensions characterised by arrangement, location or type of vibration dampers having dampers dissipating energy, e.g. frictionally of fluid type
- B60G13/10—Resilient suspensions characterised by arrangement, location or type of vibration dampers having dampers dissipating energy, e.g. frictionally of fluid type pneumatic
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
- B60G17/02—Spring characteristics, e.g. mechanical springs and mechanical adjusting means
- B60G17/027—Mechanical springs regulated by fluid means
- B60G17/0272—Mechanical springs regulated by fluid means the mechanical spring being a coil spring
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
- B60G17/06—Characteristics of dampers, e.g. mechanical dampers
- B60G17/08—Characteristics of fluid dampers
Abstract
The invention relates to a suspension system and a vehicle using the suspension system, wherein the suspension system comprises an axle, and further comprises an elastic element, one end of which is hinged with the other end of the frame and hinged with the axle, and a swinging rod, one end of which is hinged with the axle and the other end of which is hinged with the frame, wherein the elastic element is coaxial or parallel to the hinging axis of the axle and the hinging axis of the swinging rod and the axle and is parallel to the axis of the axle, one end of the swinging rod, which is hinged with the frame, is lower than one end of the swinging rod, which is hinged with the axle, after being hinged with the frame, the swinging rod can swing around one end of the swinging rod, which is hinged with the frame, and forms an included angle a with the horizontal plane, the elastic element can swing around one end of the swinging rod, which is hinged with the frame, and the central axis of the elastic element forms a plane included angle or an abnormal included angle b with the swinging rod, and the plane included angle b is 0-90 degrees. The invention solves the technical problems of poor ride comfort and poor riding comfort caused by the fact that the suspension system in the prior art can not change the rigidity of the axle in time according to road conditions.
Description
Technical Field
The present invention relates to a suspension system and a vehicle using the same.
Background
The elastic damping system is arranged on the vehicle suspension, and under the action of the elastic damping system, the vehicle can quickly attenuate impact and vibration from a road surface, so that the running smoothness of the vehicle and the riding comfort of passengers are improved.
The rigidity of the vehicle suspension influenced by the elastic damping system is required to be adjusted in real time according to different driving road conditions in order to ensure riding comfort and driving smoothness, when the vehicle encounters a pit, the axle of the vehicle moves downwards, the rigidity of the suspension is required to be reduced, when the vehicle encounters a bulge, the axle of the vehicle jumps upwards, and at the moment, the rigidity of the suspension is required to be increased. To achieve this object, for example, chinese patent application publication No. 2012.06.12, CN 102678808a discloses a vibration damping system with combined adjustment of stiffness and damping, which includes an elastic element and a damping element, the damping element is a damper, the elastic element is an air spring, the damper is a magnetorheological damper, the air spring and the damper are arranged in parallel between an upper suspension plate and a lower suspension plate, the lower suspension plate is fixedly connected with an axle when the suspension is mounted on a vehicle, the upper suspension plate is fixed with the underside of the vehicle body to bear the weight of the vehicle body, an upper bracket of the air spring is fixedly connected with the upper suspension plate, a lower bracket of the air spring is connected with the lower suspension plate, the upper bracket of the damper is hinged with the upper suspension plate, and the lower bracket of the damper is hinged with the lower suspension plate. The air spring is respectively connected with an additional air chamber and an air supply system, a positioning control valve is arranged between the air spring and the additional air chamber, a height control valve is arranged between the air spring and the air supply system, the height control valve is controlled by a control rod, one end of the control rod is connected with the height control valve, the other end of the control rod is hinged with a suspension base plate, under different bearing working conditions, the initial working position of the air spring is controlled and adjusted by the height control valve, when the air spring is in a compressed or stretched state, the cover control valve opens an inflation valve or an exhaust valve therein under the action of the control rod, the air supply system inflates or exhausts the air spring, when the air spring returns to the balance position, the valve is closed, and thus the working stroke of the air spring can be ensured to be near the balance position.
The rigidity of the suspension can be changed by the vibration reduction system, but the rigidity of the suspension is controlled by the vibration reduction system through the air supply system for inflating or exhausting the air spring, and the inflation or exhausting is controlled by the valve, so that the inflation or exhausting can be delayed for a certain time, the rigidity of the suspension of the vehicle cannot be changed in time by the vibration reduction system, and the technical problems of poor running smoothness and riding comfort of the vehicle still exist in the running process of the vehicle. Meanwhile, when the vibration reduction system is installed, an air spring is needed to be installed, the air supply system and the additional air chamber are connected to the air spring, the air supply system and the additional air chamber are needed to be installed and fixed, a height control valve is arranged between the air spring and the air supply system, a positioning control valve is arranged between the air spring and the additional air chamber, the height control valve is controlled by a control rod, and the control rod is connected to a suspension, so that if the vibration reduction system is arranged on a vehicle suspension, the installation process is very complex and complicated, the additional structure of the air spring occupies a large space, and the burden is increased for a chassis of the vehicle. In addition, the vibration damping system has more additional structures, so that the structure of the vibration damping system is complex, and the vibration damping system is inconvenient to repair and maintain, thereby possibly increasing the repair and maintenance cost.
Disclosure of Invention
The invention aims to provide a suspension system which is used for solving the technical problems of poor running smoothness and poor riding comfort of a vehicle caused by the fact that the suspension system cannot timely change the rigidity of the suspension according to road conditions in the prior art.
In order to achieve the above purpose, the invention adopts the following technical scheme:
the suspension system comprises an axle, an elastic element, an oscillating rod and a plane, wherein the elastic element extends along the up-down direction, one end of the elastic element is hinged with the frame, the other end of the elastic element is hinged with the axle, the axis of the elastic element extends along the front-back direction, one end of the elastic element is hinged with the axle, the other end of the elastic element is hinged with the frame, the elastic element is coaxial or parallel to the hinge axis of the oscillating rod and the axle, the elastic element is parallel to the axis of the axle, the end of the oscillating rod, which is hinged with the frame, is lower than the end of the oscillating rod, which is hinged with the axle, after the end of the oscillating rod is hinged with the frame, the oscillating rod can oscillate around the end of the oscillating rod, which is hinged with the frame, and the elastic element can oscillate around the end of the elastic element, the central axis of the elastic element and the oscillating rod form a plane angle or an off-plane angle b, and the plane angle b is 0-90 degrees.
The central axis of the elastic element and the swing rod are positioned in the same plane, and one end of the elastic element hinged with the axle and one end of the swing rod hinged with the axle are respectively hinged at the same position of the axle.
The automobile frame is characterized by further comprising a damper, the damper comprises a cylinder body fixedly connected with the automobile frame, a piston is assembled in the cylinder body in an up-down guiding manner, a sealed upper cavity and a sealed lower cavity are formed by the cylinder body and the piston in an enclosing manner, a radially extending deflector rod is connected with the piston, and the deflector rod is fixedly connected with the automobile axle and can move along with the up-down movement of the automobile axle in an up-down guiding manner.
The damper is an air damper or an oil damper.
The elastic element is a coil spring.
The utility model provides a vehicle, includes frame and suspension system, suspension system includes the axle, still includes the central axis along upper and lower direction extension, one end with the frame articulated, the other end with the articulated elastic element of axle and the axis along fore-and-aft direction extension, one end with the articulated pendulum rod of axle articulated, the other end with the articulated pendulum rod of axle, the articulated axis of elastic element with the axle, pendulum rod with the articulated axis of axle coaxial or parallel and all parallel with the axis of axle, the articulated one end of pendulum rod with the frame is less than its one end with the axle articulated after articulated, the pendulum rod can swing and form contained angle a with the horizontal plane around its one end with the frame articulated, the elastic element can swing and its central axis with the pendulum rod forms plane contained angle or out-of-plane contained angle b around its one end with the frame articulated, plane contained angle or out-of-plane contained angle b's size is 0~ 90.
The central axis of the elastic element and the swing rod are positioned in the same plane, and one end of the elastic element hinged with the axle and one end of the swing rod hinged with the axle are respectively hinged at the same position of the axle.
The automobile steering device comprises a vehicle frame, and is characterized by further comprising a damper, wherein the damper comprises a cylinder body fixedly connected with the vehicle frame, a piston is assembled in the cylinder body in an up-down guiding manner, a sealed upper cavity and a sealed lower cavity are formed by the cylinder body and the piston, a radially extending deflector rod is connected with the piston, and the deflector rod is fixedly connected with the vehicle axle and can move along with the up-down movement of the vehicle axle in an up-down guiding manner.
The vehicle according to claim 7, characterized in that: the damper is an air damper or an oil damper.
The elastic element is a coil spring.
The beneficial technical effects of the invention are as follows: the suspension system comprises an elastic element and a swing rod, wherein the axis of an axle extends in the left-right direction, the central axis of the elastic element extends in the up-down direction, and the axis of the swing rod extends in the front-back direction; the two ends of the swing rod are respectively hinged with the vehicle axle and the vehicle frame, one end of the swing rod, which is hinged with the vehicle frame, is a fixed end, one end of the swing rod, which is hinged with the vehicle axle, is a movable end, the fixed end of the swing rod is lower than the movable end of the swing rod, the swing rod forms an included angle a with the horizontal plane, the central axis of the elastic element forms a plane included angle or an abnormal included angle b with the swing rod, the size of the plane included angle or the abnormal included angle b is 0-90 degrees, when the vehicle axle moves up and down, the elastic element and the swing rod can rotate around the respective fixed ends at the same time, the included angle a and the included angle b can be increased or reduced at the same time, and the suspension rigidity of the vehicle is obtained according to the stress analysis of the vehicle axleWhen a and b are increased simultaneously, the rigidity of the suspension is increased, when a and b are reduced simultaneously, the rigidity of the suspension is reduced, the swing rod and the elastic element can rotate along with the up-and-down movement of the axle, when the elastic element and the swing rod rotate, the a and b are changed simultaneously, the rigidity of the suspension is changed, the response is rapid and not delayed, the structure is simple, and when the device is installed, only the two ends of the elastic element and the swing rod are hinged with the axle and the frame respectively, so that the device is convenient to install, and the production efficiency is improved.
As a further improvement of the invention, the swing rod and the elastic element are hinged at the same position of the axle, and the acting force of the swing rod on the axle and the acting force of the elastic element on the swing rod act at the same position of the axle, so that the shearing force applied to the axle is reduced.
As a further improvement of the invention, the piston in the cylinder body of the damper and the cylinder body enclose a sealed upper cavity and a sealed lower cavity, one end of the deflector rod is fixedly connected with the axle, the other end of the deflector rod is connected with the piston, when the axle moves up and down, the deflector rod moves up and down along with the axle so as to push the piston to move up and down, the excitation information of the road surface is transmitted to the damper in real time in a mechanical mode, the recognition of the road surface working condition is realized under the condition without the ECU, and the rigidity and the damping are ensured to be simultaneously regulated to the optimal state along with the excitation of the road surface in real time. According to the invention, the elastic element, the swing rod and the damper jointly act, when the vehicle axle jumps up and down, the elastic element and the swing rod change the rigidity of the suspension, and the damper can attenuate the vibration of the vehicle axle caused by road surface excitation in real time, so that the running smoothness and riding comfort of the vehicle are improved.
Drawings
FIG. 1 is a simplified schematic illustration of embodiment 1 of the vehicle of the present invention;
FIG. 2 is a simplified schematic illustration of a damper in embodiment 1 of the vehicle of the present invention;
FIG. 3 is a force analysis diagram of an axle in embodiment 1 of the vehicle of the present invention;
in the figure: 1. the vehicle comprises a vehicle frame, 2 parts of a spiral spring, 3 parts of a swing rod, 4 parts of an axle, 5 parts of a cylinder body, 6 parts of a deflector rod, 7 parts of a piston, 8 parts of a sealing ring.
Detailed Description
An embodiment 1 of the vehicle of the present invention, as shown in fig. 1 and 2, includes a frame 1 for carrying the weight of the vehicle body and a suspension system mounted on the frame 1. The suspension system comprises an axle 4 with an axis extending in the left-right direction, and further comprises an elastic element, a damper and a swing rod 3, wherein the elastic element is a coil spring 2 connected between the frame 1 and the axle 4, the coil spring 2 is obliquely arranged, the central axis of the coil spring is inclined backwards from top to bottom, the upper end of the coil spring is hinged with the frame 1, the lower end of the coil spring is hinged with the axle 4, and the hinge axis is parallel to the axis of the axle. When the axle 4 moves up and down, the coil spring 2 swings around its upper end, the upper end of the coil spring 2 is called a fixed end, and the lower end of the coil spring 2 is called a movable end.
The front end of the swing rod 3 is hinged with the frame 1, the rear end is hinged with the axle 4, and the hinge axes are parallel to the axle axis. After the swing rod 3 is hinged with the frame and the axle, the front end of the swing rod is lower than the rear end, an included angle a is formed between the swing rod 3 and the horizontal plane, and the included angle a is an acute angle. When the axle 4 jumps upwards relative to the frame, the swing rod 3 swings upwards around the hinge axis at the front end of the swing rod, and the included angle a is increased; when the axle jumps downwards relative to the frame, the swing rod 3 swings downwards around the front end hinging axis of the swing rod, and the included angle a is reduced. The front end of the swing rod can be regarded as a fixed end, and the rear end can be regarded as a movable end.
The central axis of the coil spring 2 and the swing rod 3 are positioned in the same plane, the axle is fixedly provided with a hinged bracket, the coil spring and the swing rod are hinged with the axle through the hinged bracket, the coil spring 2 and the swing rod 3 are guaranteed to be hinged at the same position of the axle, and the hinge axis of the coil spring and the axle and the hinge axis of the swing rod and the axle are coaxial. The central axis of the spiral spring 2 and the swing rod 3 form a plane included angle b, and the size of the plane included angle b is 0-90 degrees. In other embodiments, the central axis of the spiral spring and the axis of the swing rod can be different, the spiral spring is parallel to the hinge axis of the axle and the hinge axis of the swing rod and the axle, the spiral spring is hinged to the swing rod at different positions of the axle, the central axis of the spiral spring and the axis of the swing rod form a different-plane included angle b, and the included angle b is 0-90 degrees.
The damper is an air damper and comprises a cylinder body 5, the cylinder body 5 is connected with the frame 1, a piston 7 is assembled in the cylinder body 5 in an up-down guiding way, the piston 7 comprises an upper piston plate and a lower piston plate, the upper piston plate and the cylinder body 5 enclose a sealed upper cavity, the lower piston plate and the cylinder body 5 enclose a sealed lower cavity, and sealing rings 8 are arranged on the upper piston plate and the lower piston plate, so that the tightness of the damper is ensured; the sealing ring 8 is provided with lubricating oil, so that the resistance of the piston in movement is reduced. The upper piston plate and the lower piston plate are fixedly connected together through a connecting rod, the upper piston plate, the lower piston plate and the cylinder body enclose a hollow cavity, and side openings are arranged on the side walls of the hollow cavity. A deflector rod 6 is fixedly arranged on the axle 4, and the deflector rod 6 penetrates into the hollow cavity from the side opening and is connected with the piston 7 along the radial direction of the piston 7; when the axle moves up and down, the deflector rod moves up and down along with the axle and pushes the piston 7 to move up and down, when the piston 7 moves up, air in the upper cavity is pressurized, air in the lower cavity is pulled, and the upper piston plate and the lower piston plate are respectively subjected to downward acting force; conversely, air in the upper cavity is pulled, air in the lower cavity is pressurized, and the upper piston plate and the lower piston plate are respectively subjected to upward forces. In the process that the deflector rod 6 moves up and down along with the axle 4, in order to avoid that the deflector rod 6 is subjected to tensile force or pressure along the axial direction of the deflector rod, the deflector rod 6 is horizontally guided and penetrated on a connecting rod between the upper piston plate and the lower piston plate, so that the deflector rod 6 is movably connected with the piston 7.
In this embodiment, nitrogen gas is filled in the upper cavity and the lower cavity of the cylinder body 5, the boundary of the sealing ring 8 is provided with a gas measuring device for measuring nitrogen gas flow, the gas measuring device is connected with an alarm, and if gas in the upper cavity and the lower cavity leaks, the gas measuring device can detect the gas and send an alarm signal to a driver through the alarm, so that the driver can timely find out whether the air tightness of the damper is good or not, and the safety of vehicle running is ensured. In this embodiment, the cylinder body 5 is of an integral structure, and in other embodiments, the cylinder body may further include an upper cylinder and a lower cylinder that are separately arranged, an upper piston is arranged in the upper cylinder in a guiding manner, a lower piston is arranged in the lower cylinder in a guiding manner, the upper piston and the lower piston respectively enclose an airtight upper cavity and a lower cavity with the upper cylinder and the lower cylinder, and the upper piston and the lower piston are fixedly connected through a connecting rod.
In normal conditions, the axle 4 of the vehicle is subjected to an upward ground force F N Pulling force F of swing rod 3 obliquely forwards L Spring force F of coil spring 2 obliquely downward S By force analysis, as in FIG. 3, after translation, the spring force F S Tension F L Force F N Can be enclosed into a triangle, wherein, the pulling force F L Force F N The line segment forms an included angle c and the elasticity F S And a pulling force F L The included angle d is formed by the line segments, the included angle between the swinging rod 3 and the horizontal plane is a, the included angle between the swinging rod and the spiral spring is b, and c=90-a and d=b can be obtained. In addition, let: initial length of coil spring 2The degree is L1, the instantaneous length of the coil spring 2 after compression is L0, and the elastic coefficient of the coil spring 2 is k; according toThe force F acting on the axle 4 can be derived N The relation between the compression amount (L1-L0) of the coil spring 2 is as follows:
wherein: the original length of the L1-coil spring 2, the instantaneous length of the L0-coil spring 2 after compression, and the elastic coefficient of the k-coil spring 2;
from this, the suspension stiffness of the vehicle is derived
And damping force F= (P1-P0) S
Wherein: p1 is the sum of the pressures of the upper cavity and the lower cavity of the cylinder body, P0 is the external atmospheric pressure, and S is the area of the piston plate;
the change speed of P1 and P0 depends on the change speed of the volume of the damper, when the axle jumps upwards or downwards rapidly, the change speed of the volume of air in the damper is increased rapidly, the damping force F is increased rapidly, the rapid damping vibration quantity can be realized, and the running stability and riding comfort of the vehicle are ensured.
In the running process of the vehicle, when the vehicle encounters a convex road surface, the axle 4 can jump upwards relative to the vehicle frame 1, the spiral spring 2 can be driven to swing anticlockwise around the fixed end of the axle 4, the swing rod 3 swings upwards around the fixed end of the swing rod, the length of the spiral spring 2 can be shortened while the swing rod 3 swings anticlockwise, the included angle b between the swing rod 3 and the spiral spring 2 is increased, sin (b) is increased, the included angle a between the swing rod 3 and a horizontal line is increased, the cos (a) value is reduced, the suspension stiffness C of the vehicle is increased comprehensively, namely, the suspension stiffness C of the vehicle is also increased continuously along with the continuous increase of the upward jump quantity of the axle, so that the upward jump quantity of the vehicle when the vehicle passes over a threshold can be reduced, and the running smoothness and riding comfort are improved. Meanwhile, as the vehicle axle jumps up, the damping force generated by the damper is rapidly increased along with the increase of the jump speed of the vehicle axle, when the vehicle encounters a large protrusion to generate rapid jump, the damper can generate a huge damping force to rapidly attenuate the vibration of the vehicle, so that the vehicle axle can stably move up, and the running smoothness and riding comfort of the vehicle are improved.
When a vehicle encounters a concave road surface, the axle 4 can jump downwards relative to the vehicle frame 1, the axle 4 can drive the spiral spring 2 to swing clockwise around the fixed end of the spiral spring, the swing rod 3 swings downwards around the fixed end of the spiral spring, and the spiral spring 2 swings clockwise and the length of the spiral spring is prolonged; the included angle b between the central axis of the spiral spring and the swinging rod 3 is reduced, sin (b) is reduced, the included angle a between the swinging rod 3 and the horizontal line is reduced, and the cos (a) value is increased, so that the rigidity C of the vehicle suspension is reduced, and the axle can quickly jump down; along with the increase of the vehicle bridge jumping speed, the damping force generated by the damper is also increased sharply, so that the vehicle bridge is ensured not to vibrate greatly, the vibration condition of the vehicle when passing through the concave pavement is weakened, and the running smoothness and riding comfort of the vehicle are improved. By combining the two conditions, when the vehicle passes through the concave-convex road surface, the rigidity of the suspension can be changed in real time, and the damper can quickly attenuate the vehicle vibration caused by road surface excitation, so that the running smoothness and riding comfort of the vehicle are improved.
In this embodiment, the fixed end of the swing rod is located in front of the movable end, the central axis of the coil spring is gradually inclined backward from top to bottom, the fixed end of the coil spring is located in front of the movable end, in other embodiments, the fixed end of the swing rod may be located behind the movable end, the central axis of the coil spring is gradually inclined forward from top to bottom, and the fixed end of the coil spring is located behind the movable end. In other embodiments, the damper may be omitted. The damper may also be an oil damper or a magnetorheological damper. The coil spring may also be replaced with a gas spring or an air bag. The cylinder body can be fixedly connected with the frame, and two ends of the cylinder body can be respectively hinged with the frame.
Embodiments of the suspension system according to the present invention are described above, and are not described herein in detail for the sake of avoiding repetition.
Claims (8)
1. A suspension system comprising an axle, characterized in that: the device comprises a frame, an elastic element, an oscillating rod, a plane angle or an off-plane angle b, wherein the elastic element is arranged in the way that a central axis extends along the up-down direction, one end of the elastic element is hinged with the frame, the other end of the elastic element is hinged with the axle, one end of the elastic element extends along the front-back direction, one end of the elastic element is hinged with the axle, the other end of the elastic element is used for being hinged with the frame, the elastic element is coaxial or parallel to the hinging axis of the axle and is parallel to the axis of the axle, one end of the oscillating rod, which is used for being hinged with the frame, is lower than one end of the oscillating rod, which is hinged with the axle, after being hinged with the frame, the oscillating rod can oscillate around one end of the oscillating rod, which is hinged with the frame, and forms the angle a plane angle or the off-plane angle b, and the size of the plane angle b is 0-90 degrees;
the automobile frame is characterized by further comprising a damper, the damper comprises a cylinder body which is used for being connected with the automobile frame, a piston is assembled in the cylinder body in an up-down guiding manner, a sealed upper cavity and a sealed lower cavity are formed by the cylinder body and the piston in an enclosing manner, a radially extending deflector rod is connected between the parts of the piston, which enclose the upper cavity and the lower cavity, and the deflector rod is fixedly connected with the automobile axle and can move along with the up-down movement of the automobile axle in an up-down guiding manner.
2. The suspension system of claim 1 wherein: the central axis of the elastic element and the swing rod are positioned in the same plane, and one end of the elastic element hinged with the axle and one end of the swing rod hinged with the axle are respectively hinged at the same position of the axle.
3. The suspension system of claim 1 wherein: the damper is an air damper or an oil damper.
4. A suspension system according to any one of claims 1-3, wherein: the elastic element is a coil spring.
5. A vehicle comprising a frame and a suspension system, the suspension system comprising an axle, characterized in that: the device comprises a frame, a central axis, an elastic element, a swing rod and a central axis, wherein the central axis extends along the up-down direction, one end of the elastic element is hinged with the frame, the other end of the elastic element is hinged with the axle, one end of the elastic element extends along the front-back direction, the other end of the elastic element is hinged with the axle, the other end of the elastic element is hinged with the frame, the elastic element is coaxial or parallel to the hinge axis of the axle and is parallel to the axis of the axle, one end of the swing rod, which is hinged with the frame, is lower than one end of the swing rod, which is hinged with the axle, after being hinged with the frame, the swing rod can swing around one end of the swing rod, which is hinged with the frame, and forms an included angle a with the horizontal plane, namely an included angle b, and the size of the included angle b is 0-90 degrees;
the automobile frame is characterized by further comprising a damper, the damper comprises a cylinder body fixedly connected with the automobile frame, a piston is assembled in the cylinder body in an up-down guiding manner, a sealed upper cavity and a sealed lower cavity are formed by the cylinder body and the piston in a surrounding manner, a radially extending deflector rod is connected between the parts of the piston, which are surrounded by the upper cavity and the lower cavity, and the deflector rod is fixedly connected with the automobile axle and can move along with the up-down movement of the automobile axle in an up-down guiding manner.
6. The vehicle according to claim 5, characterized in that: the central axis of the elastic element and the swing rod are positioned in the same plane, and one end of the elastic element hinged with the axle and one end of the swing rod hinged with the axle are respectively hinged at the same position of the axle.
7. The vehicle according to claim 5, characterized in that: the damper is an air damper or an oil damper.
8. A vehicle according to any one of claims 5-7, characterized in that: the elastic element is a coil spring.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
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| CN109305012A (en) * | 2018-09-21 | 2019-02-05 | 共享智能铸造产业创新中心有限公司 | Heavily loaded automatic navigation vehicle hangs driving wheel |
| CN109733151B (en) * | 2019-03-12 | 2023-11-03 | 浙江盘毂动力科技有限公司 | Vehicle and suspension assembly thereof |
| CN110143107B (en) * | 2019-05-28 | 2021-04-13 | 西南交通大学 | Vehicle hybrid secondary suspension system |
Citations (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH1016525A (en) * | 1996-07-04 | 1998-01-20 | Nissan Motor Co Ltd | Rear suspension for vehicle |
| US6247564B1 (en) * | 1999-12-03 | 2001-06-19 | Hyundai Motor Company | Automotive suspension locking device |
| CN2448599Y (en) * | 2000-07-27 | 2001-09-19 | 王海卫 | Front axle float vibration-damping swing mechanism for tilling-conveying vehicle |
| CN1398229A (en) * | 2000-03-30 | 2003-02-19 | 吉布斯技术有限公司 | Hydraulic suspension strut |
| US6837343B1 (en) * | 1998-12-18 | 2005-01-04 | Richard Bugaj | Shock absorber |
| JP2005178492A (en) * | 2003-12-18 | 2005-07-07 | Nissan Motor Co Ltd | Wheel independent suspension device |
| DE102009016571A1 (en) * | 2009-04-06 | 2010-10-07 | Agco Gmbh | Hydraulic control arrangement |
| CN102889329A (en) * | 2012-07-18 | 2013-01-23 | 宁波南方减震器制造有限公司 | High-pressure absorber with double cylinders provided with floating piston assembly |
| CN203876513U (en) * | 2014-05-14 | 2014-10-15 | 三一汽车制造有限公司 | Hydraulic suspension system and vehicle |
| CN104118290A (en) * | 2013-04-24 | 2014-10-29 | 史占彪 | Spring assembly capable of enabling rigidity of vehicle suspension to be variable |
| CN203945937U (en) * | 2014-05-14 | 2014-11-19 | 三一汽车制造有限公司 | Oil gas suspension hydraulic system and there is the wheeled car of this system |
| CN104527363A (en) * | 2014-11-27 | 2015-04-22 | 郑州宇通客车股份有限公司 | Transverse stabilizing device and vehicle using same |
| CN105179551A (en) * | 2015-09-17 | 2015-12-23 | 十堰民乐液压机械有限公司 | Single-piston-rod double-cylinder-barrel hydro-pneumatic spring cylinder |
| CN206475693U (en) * | 2016-12-23 | 2017-09-08 | 郑州宇通客车股份有限公司 | Suspension system and the vehicle using the suspension system |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| ES2223205B1 (en) * | 2001-09-07 | 2007-01-01 | Creuat S.L. | SUSPENSION SYSTEM FOR A MOTOR VEHICLE AND DEVICES FOR THEIR REALIZATION. |
-
2016
- 2016-12-23 CN CN201611206441.2A patent/CN108237859B/en active Active
Patent Citations (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH1016525A (en) * | 1996-07-04 | 1998-01-20 | Nissan Motor Co Ltd | Rear suspension for vehicle |
| US6837343B1 (en) * | 1998-12-18 | 2005-01-04 | Richard Bugaj | Shock absorber |
| US6247564B1 (en) * | 1999-12-03 | 2001-06-19 | Hyundai Motor Company | Automotive suspension locking device |
| CN1398229A (en) * | 2000-03-30 | 2003-02-19 | 吉布斯技术有限公司 | Hydraulic suspension strut |
| CN2448599Y (en) * | 2000-07-27 | 2001-09-19 | 王海卫 | Front axle float vibration-damping swing mechanism for tilling-conveying vehicle |
| JP2005178492A (en) * | 2003-12-18 | 2005-07-07 | Nissan Motor Co Ltd | Wheel independent suspension device |
| DE102009016571A1 (en) * | 2009-04-06 | 2010-10-07 | Agco Gmbh | Hydraulic control arrangement |
| CN102889329A (en) * | 2012-07-18 | 2013-01-23 | 宁波南方减震器制造有限公司 | High-pressure absorber with double cylinders provided with floating piston assembly |
| CN104118290A (en) * | 2013-04-24 | 2014-10-29 | 史占彪 | Spring assembly capable of enabling rigidity of vehicle suspension to be variable |
| CN203876513U (en) * | 2014-05-14 | 2014-10-15 | 三一汽车制造有限公司 | Hydraulic suspension system and vehicle |
| CN203945937U (en) * | 2014-05-14 | 2014-11-19 | 三一汽车制造有限公司 | Oil gas suspension hydraulic system and there is the wheeled car of this system |
| CN104527363A (en) * | 2014-11-27 | 2015-04-22 | 郑州宇通客车股份有限公司 | Transverse stabilizing device and vehicle using same |
| CN105179551A (en) * | 2015-09-17 | 2015-12-23 | 十堰民乐液压机械有限公司 | Single-piston-rod double-cylinder-barrel hydro-pneumatic spring cylinder |
| CN206475693U (en) * | 2016-12-23 | 2017-09-08 | 郑州宇通客车股份有限公司 | Suspension system and the vehicle using the suspension system |
Non-Patent Citations (2)
| Title |
|---|
| 旁通小孔与环形通道并联型轿车磁流变液减振器;郑帅峰;廖昌荣;孙凌逸;吴笃华;张红辉;董继刚;;振动与冲击(第18期);全文 * |
| 连通式油气悬挂装置的设计及性能分析;王玉安;;机械制造与自动化(第05期);全文 * |
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