CN110715015A - Energy-absorbing type automobile engine suspension - Google Patents
Energy-absorbing type automobile engine suspension Download PDFInfo
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- CN110715015A CN110715015A CN201911057416.6A CN201911057416A CN110715015A CN 110715015 A CN110715015 A CN 110715015A CN 201911057416 A CN201911057416 A CN 201911057416A CN 110715015 A CN110715015 A CN 110715015A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
- F16F13/005—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a wound spring and a damper, e.g. a friction damper
- F16F13/007—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a wound spring and a damper, e.g. a friction damper the damper being a fluid damper
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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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/34—Special valve constructions; Shape or construction of throttling passages
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/53—Means for adjusting damping characteristics by varying fluid viscosity, e.g. electromagnetically
- F16F9/535—Magnetorheological [MR] fluid dampers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2230/00—Purpose; Design features
- F16F2230/0052—Physically guiding or influencing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2230/00—Purpose; Design features
- F16F2230/10—Enclosure elements, e.g. for protection
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- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Electromagnetism (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Vibration Prevention Devices (AREA)
Abstract
The invention discloses an energy-absorbing automobile engine suspension, wherein one end of the energy-absorbing automobile engine suspension is fixedly connected with an engine vibration damping block on an automobile chassis through a mounting buckle, and the other end of the energy-absorbing automobile engine suspension is fixedly connected with an automobile engine through a mounting buckle. The invention comprises a mounting buckle, a shell, a spiral steel wire rope shock absorber, a hydraulic damper and a magneto-rheological damper. The magneto-rheological damper also comprises a piston, a high-permeability magnet, an excitation coil, an annular magnet, a magnetic resistance ring and the like; the hydraulic damper comprises a hydraulic cylinder, an oil storage cylinder, a damping control valve and the like; the spiral steel wire rope shock absorber comprises a limiting plate, a spiral steel wire rope, a guide rod and the like. Compared with the traditional hydraulic mount, the invention also has the advantage of the active mount, and can change the self damping and the rigidity according to the vibration change of the engine so as to meet the requirements of vibration reduction and noise reduction on the broadband of the automobile under multiple working conditions.
Description
Technical Field
The invention relates to an automobile engine suspension assembly, which is used for preventing vibration of an automobile engine from being transmitted to a frame and belongs to the field of automobiles.
Background
With the development of economy, the continuous improvement of road traffic environment and the increasingly prominent energy and pollution problems, the design of automobiles is developed towards the direction of large torque and light weight, which deteriorates the vibration characteristics of the automobiles to a great extent and seriously affects the riding comfort of the automobiles. A large number of researches and experiments show that the vibration of an automobile engine is one of important factors influencing the driving smoothness and the operating stability of the automobile and the fatigue life of automobile parts. The excessive vibration accelerates the fatigue failure of the machine parts and reduces the service life of the engine. Engine vibration can cause fatigue and discomfort to the occupants, affect the accuracy and indication of the instrumentation, and sometimes cause structural and instrumentation damage. Severe vibration also affects the driving speed of the automobile and generates environmental noise pollution. The method for reducing the vibration transmitted to the frame generally adopts rubber suspension and hydraulic suspension, but because the vibration frequency range which can be responded by the rubber suspension and the hydraulic suspension is relatively narrow and the energy storage effect is poor, the requirements of vibration and noise reduction on a wide frequency band under multiple working conditions of an automobile cannot be met, in addition, the engine is large in size, the integrity between the suspensions of all supporting points is not strong, and the vibration reduction effect is finally influenced.
Therefore, in order to effectively isolate the transmission of engine vibration to the vehicle body, reduce the vibration level of the vehicle body, and reduce the influence of engine vibration on the vehicle body, it is necessary to design an engine mount having a good vibration damping effect. A good suspension can not only reduce the vibration condition of the vibration isolation finished machine, but also reduce the transmission rate of the vibration, and generally requires the suspension to have frequency-variable and amplitude-variable characteristics. Reducing the transmission of engine vibration energy is of great significance to improving the durability and riding comfort of the automobile.
Disclosure of Invention
1. The problem to be solved.
The invention aims to provide an energy-absorbing engine suspension with better vibration isolation effect, so as to solve the problem that the existing suspension cannot meet the requirements of vibration attenuation and noise reduction on a wide frequency band under multiple working conditions of an automobile; the defects that the existing suspension vibration reduction effect is poor, the natural vibration frequency is high, and the operation is unstable and unreliable are overcome; and simultaneously, the defect that the integrity between the suspensions of all supporting points of the engine is not strong is overcome.
According to the problems in the prior art, the spiral steel wire rope shock absorber, the hydraulic damper and the magneto-rheological damper are skillfully connected in parallel through the hydraulic mechanism to form an active suspension system, so that the automobile engine suspension can meet the requirements of vibration and noise reduction on a wide frequency band of an automobile under multiple working conditions, the integrity among suspensions of supporting points can be greatly improved, the riding comfort of the automobile is greatly improved, and the service life of the automobile is greatly prolonged.
2. The technical scheme is as follows.
In order to solve the above problems, the present invention adopts the following technical solutions.
The energy-absorbing engine suspension comprises an installation buckle, a shell, a spiral steel wire rope shock absorber, a hydraulic damper, a magnetorheological damper and the like.
Preferably, the shell comprises an upper shell and a lower shell which are installed in a non-contact mode, and the engine suspension is guaranteed not to interfere in the process of moving up and down.
Preferably, the spiral steel wire rope shock absorber comprises a first limiting plate, a second limiting plate, an annular ventilating duct, a spiral steel wire rope, a first guide rod and a second guide rod, wherein circular small holes are respectively formed in the positions, just opposite to the circle center, of the first limiting plate and the second limiting plate, a cylindrical limiting cylinder is further arranged on the first limiting plate and the second limiting plate respectively, and the spiral steel wire rope is sleeved outside the cylindrical limiting cylinder.
Preferably, one end of the first guide rod is provided with a threaded hole, and the other end of the first guide rod is provided with an external thread; and two ends of the second guide rod are respectively provided with an external thread. One end of the first guide rod, which is provided with a threaded hole, is connected with one end of the second guide rod, which is provided with an external thread, through threads, and the other end of the first guide rod, which is provided with the external thread, is connected with the first piston. The other end of the guide rod II, which is provided with the external thread, is connected with the piston II.
Preferably, the first guide rod and the second guide rod respectively pass through circular small holes in the first limiting plate and the second limiting plate, and the second guide rod is sealed at the circular small holes through the rubber sealing rings; and the first guide rod is not in contact with the first limiting plate at the round small hole and is provided with an annular ventilating pipeline, so that the lower cylinder chamber of the hydraulic cylinder is communicated with the atmosphere.
Preferably, the spiral wire rope is a spring made of an aluminum alloy material.
Preferably, the hydraulic damper comprises an oil storage cylinder, a hydraulic cylinder and a damping control valve, wherein the oil storage cylinder is connected with the lower edge of the hydraulic cylinder through pressing and installed on the first limiting plate, and the cylinder cover is provided with two damping control valves installed in opposite directions. Because the damping control valve is a special one-way valve, when hydraulic oil flows through the damping control valve, the hydraulic damper generates damping. The hydraulic oil in the hydraulic cylinder can enter the oil storage cylinder through the damping control valve, and the hydraulic oil in the oil storage cylinder can also enter the hydraulic cylinder through the damping control valve. In addition, a first piston is arranged in the hydraulic cylinder.
Preferably, a piston ring arranged on the first piston is in close contact with the inner wall of the hydraulic cylinder, so that sealing is guaranteed.
Preferably, the damping control valve is a special one-way valve, the valve port is narrow, and when hydraulic oil flows through the damping control valve, the hydraulic damper generates damping.
Preferably, the cylinder body and the cylinder cover are both made of No. 45 steel, and the surfaces of the cylinder body and the cylinder cover are processed by flanges.
Preferably, the hydraulic cylinder and the reservoir cylinder body are filled with hydraulic oil of the L-HFC type.
Preferably, the piston is made of 40Cr, the HRC 28-35 is hardened and tempered, and the HRC 40-45 is high-frequency hardened on the upper surface and the lower surface.
Preferably, the magnetorheological damper comprises a cylinder body, the cylinder body is divided into an inner layer, a middle layer and an outer layer, the inner layer cylinder body and the outer layer are fixed on the second limiting plate through the upper edge of the cylinder body, and the middle layer cylinder body is clamped between the inner layer cylinder body and the outer layer cylinder body.
Preferably, the inner, middle and outer three layers of the cylinder are respectively made of a magnetic resistance material, a high-permeability magnet and a magnetic resistance material.
Preferably, the base is provided with a round magnet, and a second piston is further arranged in the cylinder.
Preferably, the second piston is made of a high-permeability magnet, and is divided into an upper part and a lower part which are respectively marked as the first high-permeability magnet and the second high-permeability magnet. The first high magnetizer and the first high magnetizer are in a dumbbell-shaped structure, and a first magnetic resistance ring is arranged at the upper end of the first high magnetizer; an excitation coil is arranged between the first high magnetizer and the second high magnetizer; the lower end of the second high-permeability magnet is sequentially provided with a second magnetic resistance ring, an annular magnet and a nut downwards, and the second magnetic resistance ring and the annular magnet are fixed on the second piston through the bolt connection of the nut and the top end of the second piston.
Preferably, 2 mm gaps are reserved between the second piston, the excitation coil, the annular magnet and the second magnet-resisting ring and the hydraulic cylinder.
Preferably, a rubber sealing ring is arranged at a round small hole on the second limiting plate of the second guide rod of the magnetorheological damper to ensure sealing.
Preferably, the controllable magnetic field generated by the excitation coil in the magnetorheological damper forms a closed magnetic field between the first high magnetizer, the second high magnetizer and the middle layer cylinder.
Preferably, the field coil is powered by an automotive power supply, and the current variation in the field coil is controlled by a dedicated magnetorheological damper controller.
Preferably, the direction of the controllable magnetic field is perpendicular to the flow direction of the magnetorheological fluid.
Preferably, the hydraulic cylinder is filled with MRF-140CG type magnetorheological fluid, the consistency of the magnetorheological fluid changes along with the change of the magnetic field intensity, the larger the consistency, the larger the damping force generated by flowing through a gap of 2 mm, in other words, the fluidity of the magnetorheological fluid changes along with the change of the magnetic field intensity.
Preferably, the magnetorheological damper controls the change of the magnetic field by changing the current of the exciting coil, so that the flowing property of the magnetorheological fluid is changed, and the damping force of the magnetorheological damper is changed.
Preferably, the annular magnet is opposite to the circular magnet of the base in the same level, so that the piston II cannot impact the base to damage the suspension in the downward movement process.
3. The working principle is as follows.
Since the speed of the automobile is changed during the movement, the movement of the crank-slider mechanism in the engine is not linear, the generated vibration is not constant, and the frequency and amplitude of the vibration transmitted to the suspension are not constant.
And because the ideal automobile engine suspension needs to have large rigidity and large damping when vibrating at low frequency and large amplitude, and has low rigidity and small damping when vibrating at high frequency and small amplitude. Vibrations at low frequencies, which are usually large in amplitude, require a large stiffness to control the amount of displacement and a large damping to dissipate the vibration energy. And in high frequency, the vibration isolation device usually has small amplitude, but the vibration isolation device has high frequency, needs lower rigidity to have better vibration isolation effect, and simultaneously needs small damping to avoid high-frequency dynamic hardening.
The energy-absorbing type engine suspension is characterized in that a spiral steel wire rope shock absorber, a hydraulic damper and a magnetorheological damper are connected in parallel skillfully through a hydraulic mechanism to form an active suspension system. Specifically, the spiral steel wire rope shock absorber has the working performance of high frequency, low rigidity and small damping, and when the vibration amplitude of the engine is low, the transmission rate of the vibration force can be reduced by using the vibration attenuation characteristics of low rigidity and small damping of the spring steel wire rope, so that low-frequency vibration is isolated; the hydraulic damper has the working performance of larger damping and dynamic stiffness, and the amplitude and frequency range of effective vibration reduction are wider, so when the vibration amplitude is in a medium level, the vibration amplitude can be quickly attenuated by utilizing the characteristics of larger damping and variable stiffness, and the vibration of an engine is reduced; however, when the amplitude of the vibration generated by the engine is increased to a certain extent, the spiral steel wire rope and the hydraulic damper cannot effectively control the high-amplitude low-frequency vibration, and the magnetorheological damper is required to absorb the vibration. Because the magnetorheological damper has the characteristic of variable damping, the amplitude of vibration is increased, and the damping of the magnetorheological damper is increased, so that when the amplitude is large, the amplitude can be quickly attenuated by utilizing the characteristic of large damping, and the low-frequency vibration of the engine is weakened.
The spiral steel wire rope vibration absorber has the working performance of high-frequency low rigidity and small damping, and when the vibration amplitude of an engine is low, the vibration reduction characteristics of the low rigidity and the small damping of the spring steel wire rope can be utilized to isolate low-frequency vibration.
The magnetorheological damper utilizes a magnetic field generated by the excitation coil to form a closed loop between the first high-magnetizer, the second high-magnetizer and the middle-layer cylinder, when the piston II reciprocates up and down in the cylinder due to vibration, the piston can also extrude magnetorheological fluid to flow up and down through a gap channel between the piston and the cylinder wall, and a magnetic induction line of the generated magnetic field is vertical to the flowing speed direction of the magnetorheological fluid. When the magnetorheological fluid is extruded and is required to pass through the 2 mm gap, the magnetorheological fluid passes through a magnetic field generated by the magnet exciting coil, and the magnetorheological damper can control the change of the magnetic field intensity by changing the current of the magnet exciting coil, so that the flowing property of the magnetorheological fluid is changed, and the damping force of the magnetorheological damper is changed. When the magnetic field is enhanced, the viscosity of the magnetorheological fluid is increased, the fluidity is weakened, and the damping force generated by the gap of 2 mm is increased. The damping force generated by the magneto-rheological damper can counteract the vibration force of high-amplitude vibration, so that the energy of the vibration is absorbed, and the low-frequency vibration is weakened.
When a piston in the hydraulic damper moves upwards, the piston presses hydraulic oil in the hydraulic cylinder into the oil storage cylinder through the damping control valve for a while, the damping control valve is a one-way valve, the valve port is narrow, the hydraulic oil can be blocked when passing through the valve port, so that damping force is generated, the generated damping force can offset vibration force, and the energy of vibration is absorbed. When a piston in the hydraulic damper moves downwards, the upper cylinder chamber of the hydraulic cylinder is vacuumized, so that pressure difference is formed between the hydraulic cylinder and the oil storage cylinder, namely the pressure in the oil storage cylinder is greater than the pressure in the hydraulic cylinder, hydraulic oil in the oil storage cylinder is pressed into the hydraulic cylinder through the damping control valve due to the existence of the pressure difference, and similarly, damping is generated to absorb energy of vibration, so that broadband vibration of intermediate frequency is isolated.
In addition, in the damping process of the energy-absorbing automobile engine suspension system, one or two suspensions do not act, and four suspensions work in a coordinated mode. Therefore, even when the vibration of the engine is stable and unchanged, the suspension working conditions of each supporting point are different, and each suspension in the suspension system must have the capability of quickly attenuating the vibration to solve the defect that the integrity of each suspension is not strong. The rigidity, the damping and the rigidity and other parameters of the hydraulic damper and the magnetorheological damper, as well as the spiral steel wire rope and the like determined by the invention can enable the hydraulic damper, the magnetorheological damper and the spiral steel wire rope to work according to the vibration reduction rule, so that the vibration reduction effect of the active suspension is achieved, and each supporting point can quickly attenuate vibration, thereby not only greatly improving the vibration reduction effect of the automobile engine suspension, but also enhancing the integrity among the supporting point suspensions, and further greatly improving the riding comfort of an automobile.
4. Has the beneficial effects.
Compared with the prior art, the method has the following innovation.
(1) Compared with the traditional rubber suspension and spring suspension, the energy-absorbing automobile engine suspension has aging resistance, high temperature resistance, corrosion resistance and the like; compared with the traditional hydraulic damper, the energy-absorbing automobile engine suspension has the characteristics that the rigidity and the damping of the energy-absorbing automobile engine suspension are increased by utilizing the hydraulic damping, and the damping and the rigidity of the energy-absorbing automobile engine suspension can be increased or reduced according to different impacts, so that the energy-absorbing automobile engine suspension has the characteristic of active suspension, and can effectively cope with complex engine vibration.
(2) Improve traditional hydraulic damper, be about to install two damping control valve opposite direction on a jar lid, such installation not only can make the damping of production more direct more rapidly, can reduce occupation space moreover, also conveniently tear open and trade. Specifically, when a piston in the hydraulic damper moves upwards, the piston presses hydraulic oil in a hydraulic cylinder into an oil storage cylinder through a damping control valve for a while, the damping control valve is a one-way valve, a valve port of the damping control valve is narrow, the hydraulic oil is blocked when passing through the valve port, so that a damping force is generated, and the generated damping force offsets vibration force, so that the energy of vibration is absorbed. When a piston in the hydraulic damper moves downwards, the hydraulic cylinder is vacuumized, so that pressure difference is formed between the hydraulic cylinder and the oil storage cylinder, namely the pressure in the oil storage cylinder is greater than the pressure in the hydraulic cylinder, hydraulic oil in the oil storage cylinder is pressed into the hydraulic cylinder through the damping control valve due to the existence of the pressure difference, and similarly, damping is generated to absorb energy of vibration, so that broadband vibration with intermediate frequency is attenuated.
(3) The magnetorheological damper can enable the energy-absorbing engine mount to effectively attenuate violent vibration with high amplitude, and the damping of the magnetorheological damper is variable. The magnetorheological damper controls the change of the magnetic field by changing the current of the exciting coil, so that the flowing performance of the magnetorheological fluid is changed, and the damping force of the magnetorheological damper is changed. Specifically, when the magnetic field is increased, the viscosity of the magnetorheological fluid is increased, the fluidity is weakened, and the damping force generated by the gap of 2 mm is increased. The damping force generated by the magneto-rheological damper can counteract the vibration force of high-amplitude vibration, so that the energy of low-frequency vibration is absorbed, and the low-frequency vibration is weakened.
(4) The energy-absorbing engine suspension adopts a hydraulic mechanism structure to connect the spiral steel wire rope shock absorber, the hydraulic damper and the magneto-rheological damper in parallel to form an active suspension, and has the advantages of ingenious and compact structure and small volume.
(5) The energy-absorbing engine mount fully and reasonably associates the vibration attenuation characteristics of low rigidity and small damping of the spiral steel wire rope vibration absorber, the vibration attenuation characteristics of large damping and variable rigidity of the hydraulic damper and the vibration attenuation characteristics of variable damping of the magnetorheological damper, associates the advantages and the characteristics of the three with the complex and changeable vibration of the engine, and fully exerts the three working characteristics, so that the energy-absorbing engine mount has all the characteristics of an ideal automobile engine mount.
(6) The magnitude of the exciting force applied to the suspension at the four supporting points of the engine is different, so that the suspension at each supporting point can be in a tensile state or a compression state. The suspension skillfully connects the spiral steel wire rope shock absorber, the hydraulic damper and the magneto-rheological damper in parallel through a hydraulic mechanism to form an active suspension system, and in the active suspension system, the suspension at each supporting point can quickly and effectively reduce vibration, so that the vibration reduction effect of the automobile engine suspension is greatly improved, and the integrity among the suspensions at the supporting points is enhanced.
(7) The annular magnet is opposite to the circular magnet of the base at the same level, and the homopolar mutual repulsion of the magnets ensures that the piston cannot impact the base to damage the suspension in the downward movement process, and the repulsion force generated simultaneously also plays a certain vibration reduction effect.
Drawings
FIG. 1 is a schematic view illustrating an installation of an energy-absorbing automotive engine mount according to the present invention.
FIG. 2 is a schematic diagram of an internal structure of an energy-absorbing automotive engine mount according to the present invention.
FIG. 3 is a schematic structural diagram of a hydraulic damper in an energy-absorbing automobile engine mount according to the present invention.
FIG. 4 is a schematic structural diagram of a spiral steel wire rope shock absorber in an energy-absorbing automobile engine suspension according to the invention.
FIG. 5 is a schematic structural diagram of a magnetorheological damper in an energy-absorbing automobile engine mount according to the invention.
FIG. 6 is a working schematic diagram of a magnetorheological damper in an energy-absorbing automobile engine mount according to the invention.
Detailed Description
The present invention will be described in detail with reference to the following embodiments and the accompanying drawings.
The energy-absorbing engine suspension comprises an engine vibration reduction block 1, one end of the engine vibration reduction block is fixedly connected to an automobile chassis through a mounting buckle 2, the other end of the engine vibration reduction block is fixedly connected to an automobile engine through a mounting buckle 12, the suspension comprises the mounting buckle 2, the mounting buckle 12, a shell 3, a spiral steel wire rope vibration absorber 4, a hydraulic damper 5, a magneto-rheological damper 6 and the like, the shell 3 comprises an upper shell and a lower shell, and the shell is installed in a non-contact mode, so that the engine suspension is guaranteed not to generate interference in the vertical movement process.
The spiral steel wire rope shock absorber 4 comprises a first limiting plate 7, a second limiting plate 8, an annular ventilating duct 9, a spiral steel wire rope 17, a first guide rod 10 and a second guide rod 11. The positions of the first limiting plate 7 and the second limiting plate 8, which are opposite to the circle center, are respectively provided with a small circular hole, the first limiting plate 7 and the second limiting plate 8 are respectively provided with a cylindrical limiting cylinder 13 and a cylindrical limiting cylinder 14, and the spiral steel wire rope 17 is sleeved outside the cylindrical limiting cylinder 13 and the cylindrical limiting cylinder 14. Threaded holes are formed in one ends of the first guide rods 10, external threads are formed in the other ends of the first guide rods 10, the external threads are formed in the two ends of the second guide rods 11, one ends of the first guide rods 10, provided with the threaded holes, and one ends of the second guide rods 11, provided with the external threads are connected together through threads, one ends of the first guide rods 10, provided with the external threads are connected with the first piston 15, and the other ends of the second guide rods 11, provided with the external threads, are connected with the second piston 16. The first guide rod 10 and the second guide rod 11 respectively pass through the round small holes in the first limiting plate 7 and the second limiting plate 8, and rubber sealing rings are arranged at the round small holes of the second guide rod 11 to ensure sealing; and the first guide rod 10 is not in contact with the first limiting plate 7 at the round small hole and is provided with an annular ventilating pipeline 9, so that the lower cylinder chamber of the hydraulic cylinder is communicated with the atmosphere.
The hydraulic damper 5 comprises an oil storage cylinder 18, a hydraulic cylinder 19 and a damping control valve 20 and 21, the lower edges of the oil storage cylinder 18 and the hydraulic cylinder 19 are fixed on the first limiting plate 7, and the cylinder cover is provided with the damping control valve 20 and the damping control valve 21. Since the damping control valve 21 is a special check valve, the hydraulic damper 5 generates damping when hydraulic oil flows through the damping control valve 21. The hydraulic oil in the hydraulic cylinder 19 can enter the oil storage cylinder 18 through a damping control valve 20, and the hydraulic oil in the oil storage cylinder 18 can also enter the hydraulic cylinder 19 through a damping control valve 21. The hydraulic cylinders and the cylinder bodies of the oil storage cylinder are filled with L-HFC type hydraulic oil. In addition, the piston ring arranged on the first piston 15 is in sealing contact with the inner wall of the hydraulic cylinder 19, so that sealing is guaranteed.
The magneto-rheological damper 6 comprises a cylinder body, wherein the cylinder body is divided into an inner layer, a middle layer and an outer layer, the inner layer cylinder body 23 and the outer layer 24 are fixed on a second limiting plate 8 through the upper edge of the cylinder body, and the middle layer cylinder body 22 is clamped between the inner layer cylinder body 23 and the outer layer cylinder body 24. The inner, middle and outer three layers of the cylinder body are respectively made of a magnetic resistance material, a high magnetizer and a magnetic resistance material, the base is provided with a round magnet 25, the cylinder is also internally provided with a piston II 16, the piston II 16 is made of a high magnetizer and is divided into an upper part and a lower part which are respectively marked as a first high magnetizer 26 and a second high magnetizer 27. The first high magnetizer 26 and the second high magnetizer 27 form a dumbbell-shaped structure, and the upper end of the first high magnetizer 26 is provided with a first magnetic resistance ring 28; an excitation coil 30 is arranged between the first high-permeability magnet 26 and the second high-permeability magnet 27; the lower end of the second high-permeability magnet 27 is further provided with a second magnetic resistance ring 29, a ring-shaped magnet 31 and a nut 32 in sequence, and the second magnetic resistance ring 29 and the ring-shaped magnet 31 are fixed on the second piston 16 through the bolt connection of the nut 32 and the top end of the second piston 16. And 2 mm gaps are reserved between the second piston 16, the excitation coil 30, the annular magnet 31 and the second magnetic resistance ring 29 and the inner wall of the hydraulic cylinder 23, and in addition, the hydraulic cylinder is filled with magnetorheological fluid 33.
A controllable magnetic field formed by the magnet exciting coil 30 in the magnetorheological damper forms a closed loop among the first high magnetizer 26, the second high magnetizer 27 and the middle layer cylinder 22, and the direction of a closed magnetic induction line is vertical to the flowing direction of the magnetorheological fluid. The base 31 is provided with a circular magnet 25, and the ring magnet 31 is arranged in the same stage as the circular magnet 25 of the base 34.
When the automobile is in an idling working condition, the engine generates high-amplitude low-frequency vibration, the spiral steel wire rope and the hydraulic damper cannot effectively control the high-amplitude low-frequency vibration, and the magnetorheological damper is required to be used for absorbing the vibration. Because the magneto-rheological damper has the characteristic of variable damping, the amplitude of vibration is increased, and the damping of the magneto-rheological damper is also increased, so that when the amplitude of vibration is large, the amplitude can be quickly attenuated by utilizing the characteristic of large damping, the low-frequency vibration is weakened, and the vibration absorption effect of the suspension is jointly exerted by matching the spiral steel wire rope and the hydraulic damper.
When the automobile is in a high-speed running working condition, the engine generates low-amplitude high-frequency vibration, and the transmission rate of the vibration force can be reduced by utilizing the vibration reduction characteristics of low rigidity and small damping of the spring steel wire rope, so that the vibration isolation effect is achieved.
When the vibration amplitude of the automobile engine is at the middle level, the vibration amplitude can be quickly attenuated by utilizing the characteristics of larger damping and variable rigidity of the hydraulic damper, and the vibration of the engine can be absorbed.
When the automobile runs on a bumpy road surface, the vibration of the automobile body caused by the impact of the ground on wheels can be transmitted to the engine, at the moment, the high-amplitude low-frequency vibration generated by the automobile body cannot be effectively controlled by the spiral steel wire rope and the hydraulic damper, and at the moment, the vibration needs to be absorbed by the magnetorheological damper. Because the magneto-rheological damper has the characteristic of variable damping, the amplitude of vibration is increased, and the damping of the magneto-rheological damper is also increased, so that when the amplitude of vibration is large, the amplitude can be quickly attenuated by utilizing the characteristic of large damping, the low-frequency vibration is weakened, and the vibration absorption effect of the suspension is jointly exerted by matching the spiral steel wire rope and the hydraulic damper.
When the automobile accelerates or decelerates or turns, the sizes of exciting forces borne by suspensions at four supporting points of the engine are different, no matter the suspensions at the supporting points are stretched or compressed, the suspended hydraulic damper, the magnetorheological damper and the spiral steel wire rope damper can be coordinated with each other, and the suspensions at each supporting point can quickly and effectively reduce vibration, so that the vibration reduction effect of the automobile engine suspension is greatly improved, and the integrity among the suspensions at the supporting points can be enhanced.
Claims (9)
1. An energy-absorbing engine suspension is characterized in that one end of the energy-absorbing engine suspension is fixedly connected to an engine vibration reduction block on an automobile chassis through a mounting buckle, the other end of the energy-absorbing engine suspension is fixedly connected to an automobile engine through a mounting buckle, and the suspension comprises a mounting buckle, a shell, a spiral steel wire rope vibration absorber, a hydraulic damper and a magneto-rheological damper.
2. The energy-absorbing engine mount as claimed in claim 1, wherein the energy-absorbing engine mount is an active mount formed by skillfully connecting a spiral steel wire rope shock absorber, a hydraulic damper and a magnetorheological damper in parallel through a hydraulic mechanism; the vibration reduction and noise reduction device has the function of meeting the requirements of vibration reduction and noise reduction on a wide frequency band under multiple working conditions of an automobile.
3. The energy-absorbing engine mount according to claim 1, wherein the spiral wire rope shock absorber comprises a first limit plate, a second limit plate, an annular ventilating duct, a spiral wire rope, a cylindrical limit cylinder, a first guide rod and a second guide rod; its function is to isolate the high frequency vibrations of the engine.
4. The energy absorbing engine mount of claim 1 wherein the hydraulic damper comprises a first piston, a first reservoir, a hydraulic cylinder, a first damping control valve, and a second damping control valve; its function is to isolate and attenuate broadband vibrations of the engine at intermediate frequencies.
5. An energy absorbing engine mount according to claim 1 wherein said magnetorheological damper comprises piston two, a high flux conductor, a reluctance ring, an excitation coil and a nut; its function is to attenuate low frequency vibrations of the engine.
6. An energy absorbing engine mount according to claim 1 wherein said outer shell comprises upper and lower two-part shells, and wherein the upper and lower two-part shells are mounted in non-contact; the function of the suspension device is to ensure that the engine suspension does not generate interference in the up-and-down movement process.
7. The energy-absorbing engine mount according to claim 3, wherein the first limit plate and the second limit plate are respectively provided with a cylindrical limit cylinder, and the spiral steel wire rope is sleeved outside the cylindrical limit cylinders and used for limiting the radial degree of freedom of the spiral steel wire rope; circular small holes are respectively formed in the positions, opposite to the circle center, of the first limiting plate and the second limiting plate, and the first guide rod and the second guide rod respectively pass through the two circular small holes and are used for limiting the radial freedom degree of the first guide rod and the second guide rod; at the round small hole on the second limiting plate, a rubber sealing ring is arranged on the second guide rod and used for ensuring sealing; and the first guide rod is not in contact with the first limiting plate and is provided with an annular ventilating pipeline for ensuring that the lower cylinder chamber of the hydraulic cylinder is communicated with the atmosphere.
8. The energy-absorbing engine mount according to claim 4, wherein the lower edges of the oil reservoir and the hydraulic cylinder are fixed on the first limiting plate, and a pair of damping control valves with opposite installation directions are arranged on a cylinder cover; the hydraulic oil cylinder has the function that hydraulic oil in the hydraulic cylinder can enter the oil storage cylinder through the first damping control valve, and hydraulic oil in the oil storage cylinder can also enter the hydraulic cylinder through the second damping control valve.
9. An energy-absorbing engine mount according to claim 5 wherein the controllable magnetic field created by the field coil forms a closed loop between the first high-permeability magnet, the second high-permeability magnet and the middle cylinder, and the closed magnetic induction line direction is perpendicular to the flow direction of the magnetorheological fluid; the effect of the magnetic induction cutting device is to enable the magnetic rheological fluid to cut the magnetic induction wire.
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| CN201911057416.6A CN110715015A (en) | 2019-11-01 | 2019-11-01 | Energy-absorbing type automobile engine suspension |
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| CN201911057416.6A CN110715015A (en) | 2019-11-01 | 2019-11-01 | Energy-absorbing type automobile engine suspension |
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| CN110715015A true CN110715015A (en) | 2020-01-21 |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114295383A (en) * | 2021-12-30 | 2022-04-08 | 潍柴动力股份有限公司 | Engine test bed suspension, regulation control system thereof and rigidity regulation method |
| AU2021430345B2 (en) * | 2021-02-23 | 2023-06-01 | Shandong University Of Science And Technology | Composite impact resistance apparatus and applications thereof |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2816484Y (en) * | 2005-08-18 | 2006-09-13 | 哈尔滨工程大学 | Impaction-resisting shock-absorption device based on magnetic current variation technology |
| CN105240444A (en) * | 2015-11-05 | 2016-01-13 | 重庆材料研究院有限公司 | Magneto-rheological shock absorber based on parallel structure |
| CN105422707A (en) * | 2015-12-28 | 2016-03-23 | 大连理工大学 | Electromagnetic vibration damper |
| CN105546023A (en) * | 2016-02-25 | 2016-05-04 | 西安电子科技大学 | Novel combined shock absorber based on magnetorheological damper |
| CN105889404A (en) * | 2016-06-03 | 2016-08-24 | 安徽工程大学 | Dismountable energy-absorbing bumper damper |
| CN107869543A (en) * | 2017-09-28 | 2018-04-03 | 中国船舶重工集团公司第七0九研究所 | Isolation mounting based on magnetic flow liquid |
-
2019
- 2019-11-01 CN CN201911057416.6A patent/CN110715015A/en active Pending
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2816484Y (en) * | 2005-08-18 | 2006-09-13 | 哈尔滨工程大学 | Impaction-resisting shock-absorption device based on magnetic current variation technology |
| CN105240444A (en) * | 2015-11-05 | 2016-01-13 | 重庆材料研究院有限公司 | Magneto-rheological shock absorber based on parallel structure |
| CN105422707A (en) * | 2015-12-28 | 2016-03-23 | 大连理工大学 | Electromagnetic vibration damper |
| CN105546023A (en) * | 2016-02-25 | 2016-05-04 | 西安电子科技大学 | Novel combined shock absorber based on magnetorheological damper |
| CN105889404A (en) * | 2016-06-03 | 2016-08-24 | 安徽工程大学 | Dismountable energy-absorbing bumper damper |
| CN107869543A (en) * | 2017-09-28 | 2018-04-03 | 中国船舶重工集团公司第七0九研究所 | Isolation mounting based on magnetic flow liquid |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| AU2021430345B2 (en) * | 2021-02-23 | 2023-06-01 | Shandong University Of Science And Technology | Composite impact resistance apparatus and applications thereof |
| CN114295383A (en) * | 2021-12-30 | 2022-04-08 | 潍柴动力股份有限公司 | Engine test bed suspension, regulation control system thereof and rigidity regulation method |
| CN114295383B (en) * | 2021-12-30 | 2023-08-18 | 潍柴动力股份有限公司 | Engine test bed suspension, adjusting control system thereof and rigidity adjusting method |
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