CN108488306B - Self-adaptive multi-inertia-channel hydraulic suspension and self-adaptive method thereof - Google Patents
Self-adaptive multi-inertia-channel hydraulic suspension and self-adaptive method thereof Download PDFInfo
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- CN108488306B CN108488306B CN201810263952.0A CN201810263952A CN108488306B CN 108488306 B CN108488306 B CN 108488306B CN 201810263952 A CN201810263952 A CN 201810263952A CN 108488306 B CN108488306 B CN 108488306B
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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
- F16F13/04—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper
- F16F13/06—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper
- F16F13/08—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper
- F16F13/10—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper the wall being at least in part formed by a flexible membrane or the like
- F16F13/105—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper the wall being at least in part formed by a flexible membrane or the like characterised by features of partitions between two working chambers
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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
- F16F13/04—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper
- F16F13/06—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper
- F16F13/08—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper
- F16F13/10—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper the wall being at least in part formed by a flexible membrane or the like
- F16F13/105—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper the wall being at least in part formed by a flexible membrane or the like characterised by features of partitions between two working chambers
- F16F13/107—Passage design between working chambers
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Combined Devices Of Dampers And Springs (AREA)
Abstract
The invention discloses a self-adaptive multi-inertia-channel hydraulic suspension and a self-adaptive method thereof. The vibration isolation mechanism is arranged in the cavity of the hydraulic suspension and comprises a partition plate, a moving frame and a telescopic structure. The cavity is divided into an upper liquid chamber and a lower liquid chamber by the partition plate, at least one first blind hole is formed in one side, facing the upper liquid chamber, of the partition plate, at least one second blind hole corresponding to the first blind hole is formed in one side, facing the lower liquid chamber, of the partition plate, at least one mounting groove communicated with the upper liquid chamber and the lower liquid chamber is further formed in the partition plate, and a flow channel between the first communicated blind hole and the corresponding second blind hole is formed in the partition plate. A decoupling film is fixed in the mounting groove and partitions a way for communicating the upper liquid chamber and the lower liquid chamber through the mounting groove. The hydraulic suspension provided by the invention can adjust the cross-sectional area of the inertia channel by moving the movable frame up and down, so that the purpose of adjusting the output damping force and rigidity is achieved, the hydraulic suspension can meet different requirements under different working conditions, and the vibration isolation effect is improved.
Description
Technical Field
The invention relates to a hydraulic suspension in the technical field of suspension, in particular to a self-adaptive multi-inertia-channel hydraulic suspension and a self-adaptive method thereof.
Background
The hydraulic suspension of the automobile engine is an elastic connection system between an engine power assembly and a frame, and the design superiority and inferiority of the vibration damping performance of the system are directly related to the transmission of the engine vibration to an automobile body. The common rubber suspension developed at first is widely applied due to low price and simple structure. However, the dynamic characteristics of the rubber suspension elements have two disadvantages: firstly, the vibration damping is small, and the requirements on the vibration isolation and vibration damping performance of a vehicle power assembly suspension system in a low frequency domain cannot be met; and secondly, a dynamic hardening phenomenon can occur during high-frequency vibration, so that the dynamic stiffness of the suspension system is obviously increased, and the requirements of the suspension system of the automobile power assembly on vibration isolation and noise reduction performance in a high-frequency domain can not be met.
The existing hydraulic mount has better vibration isolation capability and mainly comprises a simple throttling hole type, an inertia channel-decoupling film type and the like. However, the existing hydraulic mount usually has a good damping effect only in a certain frequency range, and cannot meet the damping requirement in the whole working range of the automobile. The newly proposed semi-active magnetic rheological fluid hydraulic mount and the active control type hydraulic mount have good vibration isolation and damping performance, but most of the semi-active magnetic rheological fluid hydraulic mount and the active control type hydraulic mount have complex structures and high cost and are not widely applied. In addition, structures such as an electromagnetic valve and a motor need to be added to some semi-active control hydraulic suspensions, so that the cost and the implementation difficulty are increased.
For a single inertia channel type hydraulic suspension with a general structure form, the frequency of the peak value of the lag angle is usually in the range of 7-15 Hz. In the design of hydraulic mount, the shape of the rubber main spring and the hardness of the rubber material are usually designed to satisfy its static characteristics, and the adjustment of the peak frequency of the lag angle is usually achieved by changing the size of the inertia channel. For a four cylinder engine, when the engine is idling at 710r/min, the primary frequency of vibration excitation at idle is 23.7 Hz. In order to reduce the vibration of systems such as a steering wheel and a gear lever caused by the excitation of an engine and simultaneously expect that the engine is near the idle speed, a suspension system has low rigidity, and a hydraulic suspension needs to have high lag angle peak frequency (above 20 Hz). Such high peak frequency of lag angle is difficult to achieve by simply adjusting the size of the single inertia track. Therefore, a need exists for a multi-inertia channel hydraulic mount that is simple in construction, low in cost, and automatically adaptable to a variety of environments.
Disclosure of Invention
Aiming at the defects of the prior art, the invention provides a self-adaptive multi-inertia-channel hydraulic suspension and a self-adaptive method thereof.
The invention is realized by adopting the following technical scheme: the utility model provides a many inertia passageway formula hydraulic pressure of self-adaptation formula is suspended, sets up vibration isolation mechanism in its cavity, vibration isolation mechanism includes:
the partition plate divides the cavity into an upper liquid chamber and a lower liquid chamber, one side, facing the upper liquid chamber, of the partition plate is provided with at least one first blind hole, one side, facing the lower liquid chamber, of the partition plate is provided with at least one second blind hole corresponding to the at least one first blind hole, the partition plate is further provided with at least one mounting groove for communicating the upper liquid chamber and the lower liquid chamber, and a flow channel for communicating the first blind hole and the corresponding second blind hole is formed in the partition plate; the mounting groove is positioned in the center of the partition plate, a decoupling film is fixed in the mounting groove, and the decoupling film partitions a way for communicating the mounting groove with the upper liquid chamber and the lower liquid chamber;
the movable frame is arranged in the upper liquid chamber, the movable frame is provided with at least one pipeline corresponding to the at least one first blind hole, one end of the pipeline penetrates through the movable frame to be communicated with the upper liquid chamber, the other end of the pipeline is inserted into the corresponding first blind hole, and the pipeline, the corresponding first blind hole, the corresponding flow channel and the corresponding second blind hole sequentially form a channel communicated with the upper liquid chamber and the lower liquid chamber; the movable frame is provided with at least one through hole for communicating the upper liquid chamber with the mounting groove; the movable frame is of a symmetrical structure, the pressurizing disc is arranged on the movable frame, and the pressurizing disc and the mounting groove are coaxially arranged;
and one end of the telescopic structure is arranged on the partition plate, the other end of the telescopic structure is arranged on the movable frame, and the lifting distance of the movable frame relative to the partition plate is limited through the elasticity of the telescopic structure.
As a further improvement of the above, the flow passage extends in the partition plate to the upper liquid chamber so as to be U-shaped in cross section, and the moving frame is provided with a projection embedded in the flow passage, and the pipe is provided in the projection.
As a further improvement of the scheme, a plurality of parallel partition walls are respectively arranged on the upper side and the lower side of the decoupling film in the mounting groove, and the partition walls are perpendicular to the decoupling film.
As a further improvement of the scheme, chamfers are arranged at openings at two ends of the flow channel.
As a further improvement of the above solution, the telescopic structure comprises a plurality of guide structures and a plurality of springs; each guide structure comprises a rod sleeve and a guide rod movably sleeved with the rod sleeve; the guide rod is arranged on the movable frame, and the rod sleeve is arranged on the partition plate; the two ends of each spring are respectively arranged on the movable frame and the partition plate.
As a further improvement of the scheme, at least one positioning column corresponding to the at least one blind hole II is arranged on one side, facing the partition plate, of the movable frame, and the positioning column is inserted into the corresponding blind hole II.
As a further improvement of the scheme, the flow channels are in a C shape, the number of the flow channels is at least one pair, and each pair of the flow channels surrounds the mounting groove.
As a further improvement of the scheme, the outermost edge of the movable frame is provided with a guard rail which surrounds the area of the partition board in the upper liquid chamber.
The invention also provides a self-adaptive multi-inertia channel type hydraulic suspension self-adaptive method, which comprises the following steps: the pressure increasing disc drives the movable frame to move downwards under the action of hydraulic pressure, the distance of the movable frame relative to the partition plate is automatically changed, the cross section area of a channel is automatically changed, the decoupling film is utilized to vibrate up and down during high-frequency vibration of the hydraulic suspension, the high-frequency dynamic hardening phenomenon of the hydraulic suspension is reduced, and the self-adaption process of the hydraulic suspension is realized.
According to the invention, the cross section area of the inertia channel is adjusted by moving the movable frame up and down, so that the purpose of adjusting the output damping force and rigidity is achieved, the hydraulic mount can meet different requirements under different working conditions, and the vibration isolation effect is improved. The purposes are achieved without needing expensive magnetorheological bodies and coils which are necessary for semi-active control type suspension, and without needing complex control modules and complex calibration processes of active control type hydraulic suspension, so that the cost is saved, the structure is simplified, the manufacturing is convenient, and the energy consumption is reduced. The invention adopts two inertia channels, increases the damping coefficient of liquid, improves the vibration absorption capacity of the hydraulic suspension, and thus increases the vibration absorption effect. Different lag angle peak frequencies are obtained by changing the cross sectional area of the inertia channel, so that the transmission of the vibration of the power assembly can be reduced in a plurality of frequency sections, and the vibration reduction effect is improved.
Drawings
Fig. 1 is a schematic structural diagram of an adaptive multi-inertia-channel hydraulic mount according to embodiment 1 of the present invention;
FIG. 2 is a schematic structural view of the inertial channel of FIG. 1;
FIG. 3 is a schematic structural view of the movable frame of FIG. 1;
FIG. 4 is a schematic representation of the variation in cross-sectional area of the inertial passage of FIG. 1;
FIG. 5 is a graph of the flow damping coefficient of the inertia track of FIG. 1 as a function of cross-sectional area;
FIG. 6 is a graph of the mass inertia coefficient of the inertia track of FIG. 1 as a function of cross-sectional area;
FIG. 7 is a graph showing the dynamic stiffness of the suspension at different cross-sectional areas of the inertia track in embodiment 1 of the present invention;
FIG. 8 is a graph of suspension lag angles for different cross-sectional areas of inertia track in embodiment 1 of the present invention;
FIG. 9 is a schematic structural view of example 2 of the present invention;
FIG. 10 is a schematic structural view of an inertia track according to embodiment 3 of the present invention;
fig. 11 is a schematic structural diagram of a moving rack in embodiment 3 of the present invention.
Description of the symbols:
1 upper cover 16 pipe
2 lower cover 17 blind hole one
3 moving rack 18 blind hole two
4 partition 19 has an opening
5 rubber main spring 20 sealing ring
6 upper bolt 21 through hole
7 reinforcing block 22 decoupling film
8 lower bolt 23 runner
9 vent hole 13a first drive unit
10 leather cup 13b second driving unit
11 liquid feeding chamber 36 mounting groove
12 lower liquid chamber 37 partition wall
13 pressure increasing disk 38 positioning column
14 guide structure 39 rail guard
15 spring
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, the present invention is described in further detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the invention and are not intended to limit the invention.
Example 1
Referring to fig. 1-3, the adaptive multi-inertia-channel hydraulic mount of the present embodiment includes an upper cover assembly, a lower cover assembly, a vibration isolation mechanism, a cup 10 and a seal ring 20.
The upper cover assembly comprises an upper cover 1, a rubber main spring 5, an upper bolt 6 and a reinforcing block 7. Wherein, the top of upper bolt 6 is installed on the engine, and boss 7 is installed in the bottom of upper bolt 6. The rubber main spring 5 is arranged at the bottom of the reinforcing block 7, and the upper cover 1 is arranged at the bottom of the rubber main spring 5. Wherein, the rubber main spring 5, the upper bolt 6 and the reinforcing block 7 can be fixed by adopting a vulcanization process. Through the process, the rubber main spring 5, the upper bolt 6 and the reinforcing block 7 can be more stably installed, so that long-term use of the hydraulic suspension is guaranteed, and safety of the hydraulic suspension is improved.
The lower cover assembly comprises a lower cover 2 and a lower bolt 8. Wherein, the bottom of lower bolt 8 is installed on the frame, and lower cover 2 is installed in the top of lower bolt 8. The lower cover 2 is provided with a vent hole 9 and a cavity formed by the leather cup 10 and the lower cover 2 is communicated with the outside. The vent hole 9 can balance the air pressure between the cavity surrounded by the leather cup 10 and the lower cover assembly and the outside, so that the leather cup 10 can be freely deformed.
The vibration isolation mechanism is arranged in a cavity of the hydraulic suspension and used for isolating the vibration of the engine and the vibration of the frame, and comprises a partition plate 4, a moving frame 3 and a telescopic structure.
The partition 4 divides the hydraulically suspended chamber into an upper liquid chamber 11 and a lower liquid chamber 12. Two first blind holes 17 are formed in one side, facing the upper liquid chamber 11, of the partition plate 4, two second blind holes 18 corresponding to the two first blind holes 17 are formed in one side, facing the lower liquid chamber 12, of the partition plate 4, and an installation groove 36 for communicating the upper liquid chamber 11 with the lower liquid chamber 12 is formed in the partition plate 4. The mounting groove 36 is positioned in the center of the partition plate 4, a decoupling film 22 is fixed in the mounting groove 36, and the decoupling film 22 cuts off the path of the mounting groove 36 communicating the upper liquid chamber 11 and the lower liquid chamber 12. A plurality of partition walls 37 which are parallel to each other are respectively arranged on the upper side and the lower side of the decoupling film 22 in the mounting groove 36, and the partition walls 37 are vertical to the decoupling film 22. And a flow channel 23 communicated between the first blind hole 17 and the corresponding second blind hole 18 is formed in the partition plate 4, the flow channel 23 is C-shaped, and chamfers are arranged at openings at two ends of the flow channel 23 and are beneficial to liquid to enter and exit the flow channel 23. The number of the flow channels 23 is two, the mounting groove 36 is surrounded by the two flow channels 23, namely, each first blind hole 17 is communicated with the corresponding second blind hole 18 through one flow channel 23, the second blind hole 18 is communicated with the first opening 19, and the first opening 19 is communicated with the lower liquid chamber 12.
The movable frame 3 is arranged in the upper liquid chamber and has a symmetrical structure, and two pipelines 16 corresponding to the two first blind holes 17 are arranged on the movable frame. One end of each pipeline 16 penetrates through the moving frame 3 to be communicated with the upper liquid chamber 11, and the other end of each pipeline is inserted into the corresponding first blind hole 17 and seals the first blind hole 17, so that the liquid in the upper liquid chamber 11 can only flow into the first blind hole 17 from one end of each pipeline 16 and then flow out of the first blind hole 17 from the other end. Each pipeline 16, the corresponding first blind hole 17, the corresponding flow channel 23 and the corresponding second blind hole 18 sequentially form a channel for communicating the upper liquid chamber 11 and the lower liquid chamber 12. Two channels, namely two inertia channels, are formed in the embodiment, so that the damping coefficient of liquid is increased, the vibration absorption capacity of the hydraulic suspension is improved, and the vibration absorption effect is improved. The cross-sectional area of the double-inertia channel can be adjusted by the up-and-down sliding of the movable frame 3, so that the purpose of adjusting the output damping force and the rigidity is achieved, the hydraulic suspension can meet different requirements under different working conditions, and the vibration isolation effect is improved.
The movable frame 3 is further provided with a through hole 21 for communicating the upper liquid chamber 11 with the mounting groove 36, and the number of the through holes 21 may be one or more. One side of the movable frame 3 facing the partition plate 4 is provided with two positioning columns 38 corresponding to the two second blind holes 18 respectively, and each positioning column 38 is inserted into the corresponding second blind hole 18. The pressurizing disc 13 is arranged on the movable frame 3, and the pressurizing disc 13 and the mounting groove 36 are coaxially arranged. After adopting this kind of structure of pressure increasing disk 13, because the removal frame 3 is equipped with through-hole 21 and has reduced the effective area that removes frame 3, makes its downforce that receives reduce, pressure increasing disk 13 has increased the downforce on removing frame 3, and this power is the main effort that drives removal frame 3 and move down. Meanwhile, the pressure increasing disc 13 has a turbulent flow effect, and the high-frequency hardening phenomenon of the hydraulic suspension can be reduced. The guard rail 39 is provided at the outermost edge of the moving frame 3, and the guard rail 39 surrounds the area of the partition 4 located in the upper liquid chamber 11, which facilitates more precise up and down movement of the moving frame 3 relative to the partition 4.
The decoupling film 22 is used to decouple the upper liquid chamber 11 and the lower liquid chamber 12. When high-frequency vibration occurs, the displacement of the movable frame 3 is small, the cross-sectional areas of the two inertia channels are large, liquid mainly reaches the decoupling film 22 from the through hole 21 of the movable frame 3, and the decoupling film 22 vibrates up and down in the free stroke of the decoupling film, so that the phenomenon of high-frequency dynamic hardening of the hydraulic suspension is reduced. When low-frequency large vibration occurs, the decoupling film 22 moves to a limit position at the moment, liquid mainly reaches the lower liquid chamber 12 from the inertia channel, the displacement of the moving frame 3 is large, the cross section area of the inertia channel is small at the moment, and large rigidity and damping are suspended in the corresponding frequency range at the moment, so that the vibration is favorably attenuated. Under the idle working condition, the amplitude is small, the displacement of the movable frame 3 is small, the cross-sectional area of the inertia channel is large at the moment, the suspension has small rigidity corresponding to the idle vibration frequency, and the idle vibration is restrained. The hydraulic suspension attenuates the vibration generated by the power assembly in a plurality of frequency range ranges, reduces the vibration transmitted to the vehicle body, reduces the noise in the passenger compartment, and improves the driving and riding comfort of the vehicle.
And a telescopic structure, one end of which is installed on the partition plate 4 and the other end of which is installed on the movable frame 3, and which limits the distance of the movable frame 3 ascending or descending relative to the partition plate 4 by its elasticity. The telescopic structure comprises a plurality of guiding structures 14 and a plurality of springs 15. Each guide structure 14 comprises a rod sleeve and a guide rod movably sleeved with the rod sleeve. The guide rod is arranged on the movable frame 3, and the rod sleeve is arranged on the clapboard 4. Both ends of each spring 15 are respectively installed on the moving frame 3 and the partition plate 4. The guide structure 14 can limit the excessive ascending and descending of the moving frame 3, and the spring 15 can play a role of protection and can balance the gravity of the moving frame 3.
The sealing ring 20 is installed at the joint of the upper cover 1 and the lower cover 2, and is used for sealing the upper liquid chamber 11 and the lower liquid chamber 12, preventing the liquid in the inner cavity from leaking, and improving the safety and the practicability of the hydraulic suspension. In the present embodiment, the liquid injected into the upper liquid chamber 11 and the lower liquid chamber 12 is a glycol liquid, and the hydraulic mount has a vibration isolating function.
In the present embodiment, the flow channel 23 extends in the partition 4 to the upper liquid chamber 11, and thus has a U-shaped cross section, and the moving frame 3 is provided with a projection embedded in the flow channel 23, and the pipe 16 is provided in the projection. The up and down movement of the moving frame 3 and the partition plate 4 changes the sectional area of the inlet of the inertial passage (i.e., the junction of the duct 16 and the flow path 23), thereby changing the sectional area of the outlet, and also changes the sectional area of the flow path 23 by the movement of the protrusion in the flow path 23. Next, the adaptive process and principle of the multi-inertia channel hydraulic mount in this embodiment are analyzed.
Referring to fig. 4, in the present embodiment, the initial cross-sectional areas of the two inertia paths are both S, and the limit position to which the moving frame 3 can move downward is changed by adjusting the limit compression amount of the guide structure 14, so that the minimum cross-sectional areas of the two paths are 50% S. The influence on relevant parameters in four cases of the cross-sectional area S, 75% S, 50% S and 25% S is selected in simulation analysis. As shown in fig. 5 and 6, as the cross-sectional area increases, the flow damping coefficient and the mass inertia coefficient of the inertia track decrease. As shown in fig. 7 and 8, the frequency of occurrence of the dynamic stiffness and hysteresis angle peaks of the hydraulic mount increases as the cross-sectional area of the inertia track increases. The larger the cross-sectional area of the inertia path, the wider the low stiffness region of the hydraulic mount, and the higher the peak value of the lag angle. This is because, when the passage cross-sectional area increases, that is, the passage of the inertial passage increases, the reynolds number increases, the resistance coefficient of the on-way loss decreases, and the on-way loss of the liquid decreases. However, the increase of the cross section area of the channel increases the volume of the liquid in the inertia channel, simultaneously increases the mass of the liquid, increases the resonance frequency of the liquid, causes the increase of inertia loss, and the loss caused by inertia action has larger contribution to suspension damping than the loss along the way, so that the peak value of the lag angle is increased. When the cross section area is 50% S, the dynamic stiffness reaches the maximum value at about 15Hz, the lag angle reaches the maximum value at about 12Hz, and the lag angle is larger in the frequency range of 5-15Hz, so that the damping of the vibration near the rigid body mode of the power assembly suspension system is facilitated. When the cross section area is S, the dynamic stiffness is close to the minimum value at the idle excitation frequency point of about 23.7Hz according to the corresponding dynamic stiffness and lag angle curves, the suspended lag angle is larger near the excitation frequency point, the vibration at idle speed is favorably and rapidly attenuated, and the peak frequency of the lag angle is larger than 20Hz, so that the requirement is met.
According to the law that the dynamic stiffness and the lag angle change along with the cross section area of the inertia channel, under low-frequency vibration, when the automobile power assembly is in an idling working condition, the vibration amplitude is small, the downward moving distance of the moving frame 3 is small, the cross section area of the two inertia channels is close to S, and according to simulation analysis, the dynamic stiffness is close to the minimum value at the idling excitation frequency point of about 23.7Hz, and the suspended lag angle is large near the excitation frequency point, so that the idling vibration of an engine can be effectively inhibited, and the comfort of an automobile is improved. When the automobile is in a starting working condition, a rapid acceleration working condition or an impact working condition such as an uneven road surface, the vibration amplitude is large at the moment, the distance of the downward movement of the moving frame 3 is large, the cross sectional area of the two inertia channels is near 50% S, the suspension has large dynamic rigidity around 15Hz, a large lag angle around 12Hz is provided, vibration can be effectively attenuated, overlarge displacement is inhibited, the engine is prevented from breaking through limitation, and the support is guaranteed to be effective. At low frequency large vibrations, the decoupling membrane 22 moves to its extreme position and liquid reaches the lower liquid chamber 12 mainly from the two inertial channels. Under high-frequency vibration, namely when the automobile power assembly is in a high-speed cruising working condition, the vibration amplitude is smaller at the moment, the distance of downward movement of the movable frame 3 is smaller, the cross sectional areas of the two inertia channels are close to S at the moment, liquid mainly reaches the decoupling film 22 from the through hole 21 on the movable frame 3 at the moment, and the decoupling film 22 vibrates up and down in the free stroke of the decoupling film, so that the hydraulic suspension high-frequency dynamic hardening phenomenon is favorably reduced.
The embodiment also provides an adaptive method of the adaptive multi-inertia-channel hydraulic mount, which comprises the following steps: the pressure increasing plate 13 drives the moving frame 3 to move downwards under the action of hydraulic pressure, the distance between the moving frame 3 and the partition plate 4 is automatically changed, the cross section area of an inertia channel is changed, the decoupling film 22 is utilized to vibrate up and down during high-frequency vibration of the hydraulic suspension, the high-frequency dynamic hardening phenomenon of the hydraulic suspension is reduced, and the self-adaption process of the hydraulic suspension is realized.
Example 2
Referring to fig. 9, the present embodiment is similar to and the only difference from embodiment 1 in that the up-and-down movement of the moving frame 3 in the present embodiment is controlled by the first driving unit 13a and the second driving unit 13b, and the pressurizing plate 13, the guide structure 14 and the spring 15 are eliminated. The first and second driving units 13a and 13b have their lower ends mounted on the partition plate 4 and have their other ends mounted on the side of the moving frame 3 facing the partition plate 4. The first and second driving units 13a and 13b may be driven using a motor or a hydraulic cylinder. The size of the cross-sectional area of the inertia passage, which is achieved by the first driving unit 13a and the second driving unit 13b controlling the movement of the moving frame 3, is the same as that of the embodiment 1 under the idle condition, the starting condition, the rapid acceleration condition or the impact condition of passing through an uneven road surface. Under high-frequency vibration, namely when the automobile power assembly is in a high-speed cruising working condition, the first driving unit 13a and the second driving unit 13b control the movable frame 3 to move downwards to a contact surface with the partition plate 4, namely the cross sectional areas of the two channels are zero at the moment, namely the movable frame is in a closed state, at the moment, liquid can only reach the decoupling film 22 from the through hole 21 on the movable frame 3, and the decoupling film 22 vibrates up and down in the free stroke of the decoupling film, so that the phenomenon of hydraulic suspension high-frequency dynamic hardening is favorably reduced. Although the driving mechanism is added in the embodiment, the energy consumption and the structural complexity are increased, the moving distance of the moving frame 3 can be controlled more accurately, the corresponding cross-sectional area of the inertia channel can be optimized according to various different working conditions, and the driving mechanism is used for controlling accurately.
Example 3
Referring to fig. 10 and 11, in the present embodiment, 3 arc-shaped flow channels 23 corresponding to a central angle of 110 degrees are adopted, and the lengths of the three flow channels are not limited to be the same, and may also be different lengths. The three flow passages 23, the three pipelines 16, the first three blind holes 17 and the second three blind holes 18 correspond to one another to form three inertia passages. The three inertia channels can enable the liquid of the hydraulic device to flow more quickly, the structure is more stable, and meanwhile, the total cross section area of the inertia channels is also increased, so that the damping coefficient of the liquid is further increased, the vibration absorption capacity of the hydraulic suspension is further improved, and the vibration absorption effect is increased.
In conclusion, the cross-sectional area of the inertia channel is adjusted by moving the movable frame 3 up and down, so that the purpose of adjusting the output damping force and the rigidity is achieved, the hydraulic suspension can meet different requirements under different working conditions, and the vibration isolation effect is improved. The purposes are achieved without needing expensive magnetorheological bodies and coils which are necessary for semi-active control type suspension, and without needing complex control modules and complex calibration processes of active control type hydraulic suspension, so that the cost is saved, the structure is simplified, the manufacturing is convenient, and the energy consumption is reduced. The invention adopts a plurality of inertia channels, increases the damping coefficient of liquid, and improves the vibration absorption capacity of the hydraulic suspension, thereby increasing the vibration absorption effect. Different lag angle peak frequencies are obtained by changing the cross sectional area of the inertia channel, so that the transmission of the vibration of the power assembly can be reduced in a plurality of frequency sections, and the vibration reduction effect is improved.
The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the invention, and any modifications, equivalents and improvements made within the spirit and principle of the present invention are intended to be included within the scope of the present invention.
Claims (8)
1. The utility model provides a many inertia passageway formula hydraulic pressure of self-adaptation formula is suspended, sets up vibration isolation mechanism in its cavity, its characterized in that: the vibration isolation mechanism includes:
the partition plate (4) divides the cavity into an upper liquid chamber (11) and a lower liquid chamber (12), at least one first blind hole (17) is formed in one side, facing the upper liquid chamber (11), of the partition plate (4), at least one second blind hole (18) corresponding to the at least one first blind hole (17) is formed in one side, facing the lower liquid chamber (12), the partition plate (4) is further provided with at least one mounting groove (36) communicated with the upper liquid chamber (11) and the lower liquid chamber (12), and a flow channel (23) communicated between the first blind hole (17) and the corresponding second blind hole (18) is formed in the partition plate (4); the mounting groove (36) is positioned in the center of the partition plate (4), a decoupling film (22) is fixed in the mounting groove (36), and the decoupling film (22) cuts off the way of communicating the mounting groove (36) with the upper liquid chamber (11) and the lower liquid chamber (12);
the movable frame (3) is arranged in the upper liquid chamber (11), the movable frame (3) is provided with at least one pipeline (16) corresponding to at least one first blind hole (17), one end of the pipeline (16) penetrates through the movable frame (3) to be communicated with the upper liquid chamber (11), the other end of the pipeline (16) is inserted into the corresponding first blind hole (17), and the pipeline (16), the corresponding first blind hole (17), the corresponding flow channel (23) and the corresponding second blind hole (18) sequentially form a channel for communicating the upper liquid chamber (11) with the lower liquid chamber (12); the movable frame (3) is provided with at least one through hole (21) for communicating the upper liquid chamber (11) with the mounting groove (36); the movable frame (3) is of a symmetrical structure, the pressurizing disc (13) is arranged on the movable frame (3), and the pressurizing disc (13) and the mounting groove (36) are coaxially arranged;
one end of the telescopic structure is arranged on the partition plate (4), the other end of the telescopic structure is arranged on the movable frame (3), and the lifting distance of the movable frame (3) relative to the partition plate (4) is limited through the elasticity of the telescopic structure.
2. The adaptive multi-inertia track hydraulic mount of claim 1, wherein: the flow channel (23) extends in the partition (4) to the upper liquid chamber (11) and is thus U-shaped in cross section, and the moving frame (3) is provided with a projection embedded in the flow channel (23) and in which the duct (16) is arranged.
3. The adaptive multi-inertia track hydraulic mount of claim 1, wherein: a plurality of partition walls (37) which are parallel to each other are respectively arranged on the upper side and the lower side of the decoupling film (22) in the mounting groove (36), and the partition walls (37) are perpendicular to the decoupling film (22).
4. The adaptive multi-inertia track hydraulic mount of claim 1, wherein: chamfers are arranged at openings at two ends of the flow passage (23).
5. The adaptive multi-inertia track hydraulic mount of claim 1, wherein: the telescopic structure comprises a plurality of guide structures (14) and a plurality of springs (15); each guide structure comprises a rod sleeve and a guide rod movably sleeved with the rod sleeve; the guide rod is arranged on the movable frame (3), and the rod sleeve is arranged on the partition plate (4); two ends of each spring (15) are respectively arranged on the movable frame (3) and the partition plate (4).
6. The adaptive multi-inertia track hydraulic mount of claim 1, wherein: one side of the moving frame (3) facing the partition plate (4) is provided with at least one positioning column (38) corresponding to the at least one second blind hole (18), and the positioning column (38) is inserted into the corresponding second blind hole (18).
7. The adaptive multi-inertia track hydraulic mount of claim 1, wherein: the flow channels (23) are C-shaped, the number of the flow channels is at least one pair, and each pair of flow channels (23) surrounds the mounting groove (36).
8. An adaptive method for an adaptive multi-inertia channel hydraulic suspension is characterized by comprising the following steps: the adaptive multi-inertia channel hydraulic suspension is applied to the adaptive multi-inertia channel hydraulic suspension as claimed in any one of claims 1 to 7, and the adaptive method comprises the following steps: increase pressure dish (13) and drive under hydraulic pressure and remove frame (3) downstream, the automatic distance that changes and remove frame (3) relative baffle (4) to the cross-sectional area of automatic change passageway, and utilize decoupling zero membrane (22) to be in vibration from top to bottom during hydraulic suspension high frequency vibration reduces hydraulic suspension high frequency dynamic hardening phenomenon, realizes hydraulic suspension's self-adaptation process.
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| CN201810263952.0A CN108488306B (en) | 2018-03-28 | 2018-03-28 | Self-adaptive multi-inertia-channel hydraulic suspension and self-adaptive method thereof |
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| CN201810263952.0A CN108488306B (en) | 2018-03-28 | 2018-03-28 | Self-adaptive multi-inertia-channel hydraulic suspension and self-adaptive method thereof |
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| CN108488306B true CN108488306B (en) | 2020-04-14 |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN112140866B (en) * | 2019-06-28 | 2023-01-06 | 比亚迪股份有限公司 | Suspension structure, suspension control method, suspension controller and vehicle |
| CN110426343B (en) * | 2019-09-18 | 2021-08-27 | 中国空气动力研究与发展中心低速空气动力研究所 | Material damping coefficient measuring method and device based on vibration table |
| CN110630678B (en) * | 2019-09-23 | 2021-02-09 | 安徽誉林汽车部件有限公司 | Engine hydraulic suspension structure capable of prolonging inertia channel |
| WO2021090886A1 (en) * | 2019-11-07 | 2021-05-14 | 株式会社ブリヂストン | Vibration-damping device |
| CN113464599B (en) * | 2021-07-02 | 2023-10-13 | 安徽誉林汽车部件有限公司 | Runner body structure in hydraulic suspension |
| CN113983114B (en) * | 2021-11-27 | 2023-02-17 | 安徽江淮汽车集团股份有限公司 | Multi-inertia channel type power assembly hydraulic suspension with switchable states |
| CN114312280B (en) * | 2021-12-29 | 2023-06-02 | 江苏徐工工程机械研究院有限公司 | Semi-active suspension with adjustable dynamic stiffness and damping value and control system thereof |
| CN114508560B (en) * | 2022-03-07 | 2023-03-28 | 奇瑞汽车股份有限公司 | Hydraulic suspension structure |
| CN114941684A (en) * | 2022-06-21 | 2022-08-26 | 郑州日产汽车有限公司 | Hydraulic suspension capable of automatically adjusting damping |
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| JPS646543A (en) * | 1987-06-29 | 1989-01-11 | Bridgestone Corp | Vibration isolating device |
| JPH0771515A (en) * | 1993-09-06 | 1995-03-17 | Nippondenso Co Ltd | Electronic control engine mount |
| KR20130020499A (en) * | 2011-08-19 | 2013-02-27 | 현대자동차주식회사 | Hydro mount having multiple fluid path |
| CN102829127B (en) * | 2012-09-20 | 2014-02-12 | 重庆大学 | Magneto-rheological damper of automobile engine suspension system |
| CN203962842U (en) * | 2014-05-27 | 2014-11-26 | 亚新科噪声与振动技术（安徽）有限公司 | A kind of bend flow channel half is hydraulic mount initiatively |
| CN205064690U (en) * | 2015-03-26 | 2016-03-02 | 上海豪骋机电科技有限公司 | Hydraulic pressure suspension of matcing high -speed electric automobile power assembly |
| CN106704470A (en) * | 2017-01-09 | 2017-05-24 | 重庆市锋盈汽车配件有限公司 | Self-adjusting automobile hydraulic mount |
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