CN116039308A - Slow active hydraulic suspension system driven by exhaust gas turbine and control method - Google Patents
Slow active hydraulic suspension system driven by exhaust gas turbine and control method Download PDFInfo
- Publication number
- CN116039308A CN116039308A CN202211491343.3A CN202211491343A CN116039308A CN 116039308 A CN116039308 A CN 116039308A CN 202211491343 A CN202211491343 A CN 202211491343A CN 116039308 A CN116039308 A CN 116039308A
- Authority
- CN
- China
- Prior art keywords
- hydraulic
- hydraulic cylinder
- vehicle
- energy accumulator
- vehicle body
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Images
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G11/00—Resilient suspensions characterised by arrangement, location or kind of springs
- B60G11/26—Resilient suspensions characterised by arrangement, location or kind of springs having fluid springs only, e.g. hydropneumatic springs
- B60G11/27—Resilient suspensions characterised by arrangement, location or kind of springs having fluid springs only, e.g. hydropneumatic springs wherein the fluid is a gas
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G11/00—Resilient suspensions characterised by arrangement, location or kind of springs
- B60G11/26—Resilient suspensions characterised by arrangement, location or kind of springs having fluid springs only, e.g. hydropneumatic springs
- B60G11/30—Resilient suspensions characterised by arrangement, location or kind of springs having fluid springs only, e.g. hydropneumatic springs having pressure fluid accumulator therefor, e.g. accumulator arranged in vehicle frame
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
- B60G17/015—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load the regulating means comprising electric or electronic elements
- B60G17/0152—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load the regulating means comprising electric or electronic elements characterised by the action on a particular type of suspension unit
- B60G17/0155—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load the regulating means comprising electric or electronic elements characterised by the action on a particular type of suspension unit pneumatic unit
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
- B60G17/015—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load the regulating means comprising electric or electronic elements
- B60G17/016—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load the regulating means comprising electric or electronic elements characterised by their responsiveness, when the vehicle is travelling, to specific motion, a specific condition, or driver input
- B60G17/0162—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load the regulating means comprising electric or electronic elements characterised by their responsiveness, when the vehicle is travelling, to specific motion, a specific condition, or driver input mainly during a motion involving steering operation, e.g. cornering, overtaking
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
- B60G17/015—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load the regulating means comprising electric or electronic elements
- B60G17/016—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load the regulating means comprising electric or electronic elements characterised by their responsiveness, when the vehicle is travelling, to specific motion, a specific condition, or driver input
- B60G17/0164—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load the regulating means comprising electric or electronic elements characterised by their responsiveness, when the vehicle is travelling, to specific motion, a specific condition, or driver input mainly during accelerating or braking
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
- B60G17/015—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load the regulating means comprising electric or electronic elements
- B60G17/016—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load the regulating means comprising electric or electronic elements characterised by their responsiveness, when the vehicle is travelling, to specific motion, a specific condition, or driver input
- B60G17/0165—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load the regulating means comprising electric or electronic elements characterised by their responsiveness, when the vehicle is travelling, to specific motion, a specific condition, or driver input to an external condition, e.g. rough road surface, side wind
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N5/00—Exhaust or silencing apparatus combined or associated with devices profiting from exhaust energy
- F01N5/04—Exhaust or silencing apparatus combined or associated with devices profiting from exhaust energy the devices using kinetic energy
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2202/00—Indexing codes relating to the type of spring, damper or actuator
- B60G2202/10—Type of spring
- B60G2202/15—Fluid spring
- B60G2202/152—Pneumatic spring
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2202/00—Indexing codes relating to the type of spring, damper or actuator
- B60G2202/10—Type of spring
- B60G2202/15—Fluid spring
- B60G2202/154—Fluid spring with an accumulator
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2202/00—Indexing codes relating to the type of spring, damper or actuator
- B60G2202/40—Type of actuator
- B60G2202/42—Electric actuator
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2800/00—Indexing codes relating to the type of movement or to the condition of the vehicle and to the end result to be achieved by the control action
- B60G2800/01—Attitude or posture control
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2800/00—Indexing codes relating to the type of movement or to the condition of the vehicle and to the end result to be achieved by the control action
- B60G2800/18—Starting, accelerating
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2800/00—Indexing codes relating to the type of movement or to the condition of the vehicle and to the end result to be achieved by the control action
- B60G2800/22—Braking, stopping
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2800/00—Indexing codes relating to the type of movement or to the condition of the vehicle and to the end result to be achieved by the control action
- B60G2800/24—Steering, cornering
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Abstract
The invention discloses a slow active hydraulic suspension system driven by an exhaust gas turbine and a control method, comprising an air spring, a hydraulic system, an exhaust gas turbine system and an ECU; the air spring is fixed between the vehicle body and the hydraulic cylinder, the exhaust gas turbine system is connected with the hydraulic system, and the ECU is simultaneously in communication control connection with the hydraulic system and the exhaust gas turbine system; the hydraulic system comprises a hydraulic cylinder, a bidirectional adjustable damping valve, an overflow valve, an upper energy accumulator, a lower energy accumulator and a one-way hydraulic pump; the exhaust turbine system comprises a turbine, a friction clutch and an engine exhaust pipe, wherein the turbine is arranged in the engine exhaust pipe, an output shaft of the turbine is connected with a driving part of the friction clutch, a driven part of the friction clutch is connected with an input shaft of a one-way hydraulic pump, and the one-way hydraulic pump is communicated with a two-position four-way reversing valve and forms a loop with the hydraulic system. The invention utilizes the engine exhaust gas to drive the turbine to provide power for the unidirectional hydraulic pump, saves energy, shortens the endurance mileage of the vehicle and reduces the energy of the engine exhaust gas.
Description
Technical Field
The invention belongs to the technical field of suspension of passenger cars. More particularly, the present invention relates to an exhaust turbine driven slow active hydraulic suspension system and control method.
Background
The suspension is a generic term for all force-transmitting connections between the body and the wheels. The vehicle has the function of transmitting vertical counterforce, longitudinal counterforce and lateral counterforce of the road surface acting on the wheels and moment caused by the counterforces to the vehicle body so as to ensure the normal running of the vehicle.
The rigidity and the damping of the traditional hydraulic suspension are determined according to experience or an optimal design method, and in the running process of a vehicle, the rigidity and the damping of the suspension cannot be adjusted, so that the traditional hydraulic suspension can only reach the best performance under specific roads and running speeds and cannot adapt to complex and changeable running conditions.
The rigidity and the damping of the active suspension system can be dynamically and adaptively adjusted according to the change of the running condition of the vehicle, and the suspension system can be actively acted to ensure that the suspension system is always in an optimal damping state, so that the active suspension system greatly improves the riding comfort and the operating stability of the vehicle and is a trend of future suspension technology development.
The active suspension system requires an actuator to actively apply work, so that an additional power source, typically a high-power motor, is required. This not only increases the cost of the active suspension system, but more importantly, the motor consumes a large amount of electrical energy during operation, which is a significant challenge for low carbon and environmental protection and vehicle use costs. Reducing the energy consumption of active suspension systems is one of the prerequisites for the large scale popularity of active suspension systems.
Disclosure of Invention
In order to solve the problems of high energy consumption, high cost and the like of a slow active hydraulic suspension system, the invention provides the slow active hydraulic suspension system driven by the exhaust gas turbine and the control method, and the turbine is driven by the engine exhaust gas to provide power for the unidirectional hydraulic pump, so that not only can energy be saved, the endurance mileage of a vehicle be improved, the carbon emission of the vehicle be reduced, and the pollution of the vehicle to the atmosphere be reduced. But also reduces the kinetic energy of the engine exhaust, which will reduce noise due to engine exhaust emissions, which is beneficial to improving the NVH performance of the vehicle and enhancing the comfort of the vehicle.
The invention aims at being realized by the following technical scheme, and the following technical scheme is combined with the accompanying drawings:
an exhaust turbine driven slow active hydraulic suspension system comprises an air spring 12, a hydraulic system, an exhaust turbine system and an ECU 14; the upper end of the air spring 12 is fixed at the bottom of the vehicle body 13, and the lower end of the air spring 12 is fixed at the upper part of the hydraulic cylinder 11; the exhaust turbine system and the hydraulic system are driven by the friction clutch 4, and the ECU is in communication control connection with the hydraulic system and the exhaust turbine system; the hydraulic system comprises a bidirectional adjustable damping valve 1, an upper energy accumulator 2, a unidirectional hydraulic pump 3, an overflow valve 7, a lower energy accumulator 9 and a hydraulic cylinder 11; the lower end of a hydraulic cylinder 11 is fixed on a wheel 10, a piston rod of the hydraulic cylinder 11 is fixed at the lower end of a vehicle body 13, and the hydraulic cylinder 11 is connected with an air spring 12 in parallel; the bidirectional adjustable damping valve 1 is arranged between the upper cavity of the hydraulic cylinder 11 and the upper energy accumulator 2, the lower cavity of the hydraulic cylinder is communicated with the lower energy accumulator 9, and the upper energy accumulator 2 and the lower energy accumulator 9 are respectively connected with the two-position four-way reversing valve 8; an overflow valve 7 is arranged between the upper energy accumulator 2 and the lower energy accumulator 9; the exhaust gas turbine system comprises a turbine 6, a friction clutch 4 and an engine exhaust pipe 5, wherein the turbine 6 is arranged in the engine exhaust pipe 5, an output shaft of the turbine 6 is connected with a driving part of the friction clutch 4, an input shaft of the one-way hydraulic pump 3 is connected with a driven part of the friction clutch 4, and the one-way hydraulic pump 3 is communicated with a two-position four-way reversing valve 8 and a hydraulic cylinder 11 to form a loop.
Furthermore, the ECU is simultaneously connected with the bidirectional adjustable damping valve 1, the friction clutch 4 and the two-position four-way reversing valve 8 in a communication signal manner to control each working mode of the slow active hydraulic suspension system.
The invention also provides a control method of the slow active hydraulic suspension system driven by the exhaust gas turbine, wherein the slow active hydraulic suspension system comprises the following control modes:
1) A passive suspension mode, in which the opening of a valve core of the bidirectional adjustable damping valve is unchanged, the vehicle buffers road surface unevenness through an air spring, an upper energy accumulator and a lower energy accumulator, and the bidirectional adjustable damping valve damps vibration of a vehicle body caused by the road surface unevenness;
2) A semi-active suspension mode in which damping of the suspension system is adjusted by controlling a spool opening of the bi-directional adjustable damping valve;
3) An active suspension mode, wherein the damping of the suspension is regulated by regulating the opening degree of a valve core of a bidirectional adjustable damping valve, and meanwhile, the suspension system is actively operated by a unidirectional hydraulic pump;
4) And a vehicle body posture adjusting mode, wherein the transient state value and the steady state value of the vehicle body posture change during acceleration, braking and turning of the vehicle are controlled by controlling the bidirectional damping valve and the unidirectional hydraulic pump.
Further, the working principle of the exhaust turbine system is as follows:
the turbine rotates all the time as long as the engine is in a working state, the rotating speed of the input shaft of the one-way hydraulic pump can be controlled by controlling the engagement degree of the friction clutch, and the rotating speed of the input shaft of the one-way hydraulic pump determines the speed of active work of the suspension system.
Further, in the passive suspension mode, the specific working process of the vehicle passing through the deceleration strip is as follows:
when the vehicle encounters a deceleration strip on a flat road, the wheels will move upwards; because the air spring is connected with the hydraulic cylinder in parallel, the deformation of the air spring is equal to the displacement of the piston of the hydraulic cylinder, the piston of the hydraulic cylinder moves downwards along the inner wall of the hydraulic cylinder, the volume of the upper cavity of the hydraulic cylinder is increased, the pressure is reduced, and the volume of the lower cavity of the hydraulic cylinder is decreased, and the pressure is increased; because the pressure of the upper cavity of the hydraulic cylinder is reduced, the pressure of the oil outlet of the upper energy accumulator is reduced, hydraulic oil flows into the upper cavity of the hydraulic cylinder from the upper energy accumulator, the pressure of the upper energy accumulator is reduced, and energy is released; similarly, the pressure of an oil inlet of the lower energy accumulator is increased, hydraulic oil flows into the lower energy accumulator from a lower cavity of the hydraulic cylinder, the pressure of the lower energy accumulator is increased, energy is stored, and in addition, the hydraulic oil generates pressure loss through a bidirectional adjustable damping valve; at the moment, the upper cavity and the lower cavity of the hydraulic cylinder form a pressure difference, the pressure difference acts on the piston of the hydraulic cylinder to enable the vehicle body to generate an upward acting force, and the acting force and the elastic force of the air spring act on the vehicle body together to enable the vehicle body to generate upward acceleration;
the wheels start to descend after reaching the highest point, the piston of the hydraulic cylinder moves upwards along the inner wall of the hydraulic cylinder, the volume of the upper cavity of the hydraulic cylinder is reduced, the pressure intensity is increased, and the volume of the lower cavity of the hydraulic cylinder is increased, and the pressure intensity is reduced; because the pressure of the upper cavity of the hydraulic cylinder is increased, the pressure of the oil outlet of the upper energy accumulator is increased, hydraulic oil flows into the upper energy accumulator from the upper cavity of the hydraulic cylinder, the pressure of the upper energy accumulator is increased, and energy is stored; similarly, the pressure of an oil inlet of the lower energy accumulator is reduced, hydraulic oil flows into a lower cavity of the hydraulic cylinder from the lower energy accumulator, the pressure of the lower energy accumulator is reduced, energy is released, and in addition, the hydraulic oil generates pressure loss through a bidirectional adjustable damping valve; at the moment, the upper cavity and the lower cavity of the hydraulic cylinder form a pressure difference, the pressure difference acts on the piston of the hydraulic cylinder to enable the vehicle body to generate a downward acting force, and the acting force and the elastic force of the air spring act on the vehicle body together to enable the vehicle body to generate downward acceleration;
in the whole process that the wheels pass through the speed reducing belt, hydraulic oil continuously flows through the bidirectional adjustable damping valve, and the vibration of the vehicle body caused by the passing through the speed reducing belt is rapidly attenuated.
Further, the working process of the semi-active suspension mode is as follows:
the vehicle-mounted sensor measures the motion state and road surface information of the vehicle in real time, when the vehicle accelerates, decelerates and turns, the ECU sends out a control instruction for improving the damping of the suspension, and then the damping of the suspension is increased by controlling the bidirectional adjustable damping valve so as to keep the grounding performance of the posture of the vehicle body and the tires; when the vehicle runs at a high speed on a bad road surface, the ECU sends out a control instruction for reducing the damping of the suspension, and then the damping of the suspension is reduced by controlling the bidirectional adjustable damping valve, so that the smoothness of the vehicle is improved.
Further, in the active suspension mode, the working process of the vehicle passing through the deceleration strip is as follows:
the vehicle-mounted sensor measures the motion state of the vehicle in real time, when the sensor detects that the wheels move upwards through the deceleration strip, the ECU sends out a control instruction, then the clutch is controlled to be gradually attached, the clutch drives the one-way hydraulic pump to pump hydraulic oil into the upper cavity of the hydraulic cylinder, the wheels move upwards, and therefore the acceleration of the vehicle body and the dynamic load of the wheels are reduced; when the sensor detects that the wheels move downwards, the ECU sends out a control instruction, then the two-position four-way reversing valve is controlled to reverse, at the moment, the rotation direction of the unidirectional hydraulic pump is unchanged, and after the hydraulic oil passes through the two-position four-way reversing valve, the hydraulic oil is pumped into the lower cavity of the hydraulic cylinder, so that the wheels move downwards, and the acceleration of a vehicle body and the dynamic load of the wheels are reduced. Reducing the acceleration of the vehicle body and the dynamic load of the wheels will greatly improve the smoothness and steering stability of the vehicle.
Further, in the vehicle body posture adjustment mode, the working process of the vehicle passing through the curve is as follows:
when the vehicle passes through a curve, the vehicle body starts to roll under the action of inertia force, at the moment, the acceleration sensor detects a lateral acceleration signal, then the acceleration signal is sent to the ECU, and the ECU sends a control instruction, so that on one hand, the damping of the bidirectional adjustable damping valve is increased, and the transient value of the roll motion of the vehicle body can be reduced; on the other hand, the friction clutch is controlled to start to be engaged, the exhaust turbine drives the hydraulic pump to start acting, the inner side of the automobile body generates a downward acting force, the outer side of the automobile body generates an upward acting force, and therefore the automobile body generates a moment opposite to the inertia force, and the steady-state value of the rolling motion of the automobile body can be reduced. Finally, through the integrated control of the suspension system, the roll angle speed of the vehicle body is reduced, and the roll angle of the vehicle body is reduced, so that the smoothness and the steering stability of the vehicle are improved.
Compared with the prior art, the invention has the following beneficial effects:
the existing slow active suspension system takes a high-power motor as a power source, the high-power motor not only increases the cost of the slow active suspension system, but also consumes a large amount of electric energy during the work of the motor, so that the energy consumption of the suspension is greatly increased, and the use cost of the suspension is increased. The invention utilizes the engine exhaust gas to drive the turbine to provide power for the unidirectional hydraulic pump, so that not only can energy be saved, the endurance mileage of the vehicle can be improved, the carbon emission of the vehicle can be reduced, and the pollution of the vehicle to the atmosphere can be reduced. And the kinetic energy of the exhaust gas is reduced, so that the noise generated by the exhaust gas of the engine can be reduced, the NVH performance of the vehicle can be improved, and the comfort of the vehicle can be improved.
Because the tail gas has the circulation, the arrangement of the suspension is greatly convenient, and the four unidirectional hydraulic pumps can be simultaneously powered by reasonably designing the layout of the engine exhaust pipe.
Drawings
FIG. 1 is a schematic diagram of the architecture of an exhaust turbine driven slow active hydraulic suspension system according to the present invention;
FIG. 2 is a schematic diagram of an exhaust turbine system according to the present invention;
in the figure:
1-a bi-directional adjustable damping valve; 2-upper accumulator; 3-one-way hydraulic pump; a 4-friction clutch; 5-an engine exhaust pipe; 6-a turbine; 7-an overflow valve; 8-two-position four-way reversing valve; 9-a lower accumulator; 10-wheels; 11-a hydraulic cylinder; 12-an air spring; 13-vehicle body; 14-ECU; 15-road surface.
Detailed Description
The technical scheme of the invention is further described below with reference to the accompanying drawings and examples:
example 1
As shown in fig. 1, the slow active hydraulic suspension system driven by the exhaust gas turbine comprises an air spring 12, a hydraulic system, an exhaust gas turbine system and an ECU 14, wherein the upper end of the air spring 12 is connected with a vehicle body, the lower end of the air spring is connected with a hydraulic cylinder 11, the exhaust gas turbine system and the hydraulic system are driven by a friction clutch 4, and the ECU is simultaneously connected with the hydraulic system and the exhaust gas turbine system in a communication way.
The hydraulic system comprises a bidirectional adjustable damping valve 1, an upper energy accumulator 2, a unidirectional hydraulic pump 3, an overflow valve 7, a two-position four-way reversing valve 8, a lower energy accumulator 9 and a hydraulic cylinder 11; the hydraulic cylinder 11 is fixed on the wheel 10, a piston rod of the hydraulic cylinder 11 is fixed on the vehicle body 13, and the hydraulic cylinder 11 is connected with the air spring 12 in parallel; the bidirectional adjustable damping valve 1 is arranged between the upper cavity of the hydraulic cylinder 11 and the upper energy accumulator 2, the lower cavity of the hydraulic cylinder is communicated with the lower energy accumulator 9, and the upper energy accumulator 2 and the lower energy accumulator 9 are respectively connected with the two-position four-way reversing valve 8; an overflow valve is arranged between the upper accumulator 2 and the lower accumulator 9.
As shown in fig. 2, the exhaust gas turbine system comprises a friction clutch 4, an engine exhaust pipe 5 and a turbine 6, wherein the turbine 6 is arranged in the engine exhaust pipe 5, an output shaft of the turbine 6 is connected with a driving part of the friction clutch 4, and an input shaft of the one-way hydraulic pump 3 is connected with a driven part of the friction clutch 4; the unidirectional hydraulic pump 3 is communicated with the two-position four-way reversing valve 8 and the hydraulic cylinder to form a loop.
The ECU is simultaneously connected with the bidirectional adjustable damping valve 1, the friction clutch 4 and the two-position four-way reversing valve 8 in a communication signal manner to control each working mode of the slow active hydraulic suspension system.
Example 2
A method of controlling an exhaust gas turbine driven slow active hydraulic suspension system comprising the following control modes:
(1) Passive suspension mode
The response frequency of the actuator is 0.5 Hz-5 Hz, and when the response frequency is exceeded, the actuator is converted into a passive suspension system, and the working principle is similar to that of the traditional passive suspension system.
Since the road surface is unlikely to be absolutely flat, which will cause an impact to the vehicle body, the suspension system between the wheels and the vehicle body is designed to be elastic, the weight of the vehicle body is borne by the suspension springs and the impact caused to the vehicle body by the road surface is buffered. The elastic system generates vibration after being impacted, which causes uncomfortable feeling or tiredness to the driver and passengers, so the bidirectional adjustable damping valve is used for damping the vibration of the vehicle body, the vibration of the vehicle body is quickly damped, and the riding comfort of the vehicle is improved.
Taking the example that the vehicle passes through the deceleration strip, the specific working process is as follows:
when a vehicle running on a flat road encounters a deceleration strip, the tire has some elasticity but is insufficient to counteract the displacement of the deceleration strip, so that the wheel will move upward. Because the air spring is connected with the hydraulic cylinder in parallel, the deformation of the air spring is equal to the displacement of the piston of the hydraulic cylinder, the piston of the hydraulic cylinder moves downwards along the inner wall of the hydraulic cylinder, the volume of the upper cavity of the hydraulic cylinder is increased, the pressure is reduced, and the volume of the lower cavity of the hydraulic cylinder is decreased, and the pressure is increased. Because the pressure of the upper cavity of the hydraulic cylinder is reduced, the pressure of the oil outlet of the upper energy accumulator is reduced, hydraulic oil flows into the upper cavity of the hydraulic cylinder from the upper energy accumulator, the pressure of the upper energy accumulator is reduced, and energy is released. Similarly, the pressure of an oil inlet of the lower energy accumulator is increased, hydraulic oil flows into the lower energy accumulator from a lower cavity of the hydraulic cylinder, the pressure of the lower energy accumulator is increased, and energy is stored; in addition, hydraulic oil will generate pressure losses through the bi-directional adjustable damping valve. At this time, the upper and lower chambers of the hydraulic cylinder form a pressure difference, and the pressure difference acts on the hydraulic cylinder piston to enable the vehicle body to generate an upward acting force, and the acting force and the elastic force of the air spring act on the vehicle body together to enable the vehicle body to generate upward acceleration, so that the motion of the vehicle body is transmitted to the driver and the passengers through the seat supporting surface, the seat backrest and the foot supporting surface, and the riding comfort of the vehicle is adversely affected.
After the wheels reach the highest point, the wheels start to descend, the piston moves upwards along the inner wall of the hydraulic cylinder, the volume of the upper cavity of the hydraulic cylinder is reduced, the pressure is increased, and the volume of the lower cavity of the hydraulic cylinder is increased, and the pressure is reduced. Because the pressure of the upper cavity of the hydraulic cylinder is increased, the pressure of the oil outlet of the upper energy accumulator is increased, hydraulic oil flows into the upper energy accumulator from the upper cavity of the hydraulic cylinder, and the pressure of the upper energy accumulator is increased to store energy. Similarly, the oil inlet pressure of the lower energy accumulator is reduced, hydraulic oil flows into a lower cavity of the hydraulic cylinder from the lower energy accumulator, the pressure of the lower energy accumulator is reduced, and energy is released; in addition, hydraulic oil will generate pressure losses through the bi-directional adjustable damping valve. The upper and lower chambers of the hydraulic cylinder form a pressure difference, and the pressure difference acts on the hydraulic cylinder piston to enable the vehicle body to generate a downward acting force, wherein the acting force and the elastic force of the air spring act on the vehicle body together, so that the vehicle body generates a downward acceleration, and the motion of the vehicle body is transmitted to a driver and a passenger through the seat supporting surface, the foot supporting surface and the seat backrest, so that the riding comfort of the vehicle is adversely affected.
In the whole process that the wheels pass through the deceleration strip, the vehicle can buffer the vibration of the vehicle body through the air spring, the upper energy accumulator and the lower energy accumulator, so that the acceleration of the vehicle body is reduced. However, the air spring and the accumulator can store energy but cannot attenuate the energy, so that a bidirectional adjustable damping valve is also required to consume the energy generated by the vibration of the vehicle body, so that the vibration of the vehicle body is rapidly attenuated, and the riding comfort of a driver and passengers is improved.
(2) Semi-active suspension mode
The semi-active suspension mode is similar to the working principle of the passive suspension mode, but the passive suspension mode can only achieve the best performance under the conditions of specific roads and vehicle speeds because the opening degree of the bidirectional adjustable damping valve is unchanged, which can adversely affect the smoothness and the steering stability of the vehicle. The bidirectional adjustable damping valve can control the damping of a suspension system by adjusting the opening degree of the valve core, so that the bidirectional adjustable damping valve has the function of a semi-active suspension. The specific implementation process is as follows:
the vehicle-mounted sensor measures the motion state and road surface information of the vehicle in real time, when the vehicle encounters working conditions such as turning, braking, accelerating and the like, the damping of the suspension system is required to be increased so as to keep the grounding property of the posture of the vehicle body and the tires, at the moment, the ECU sends out a control instruction for increasing the damping of the suspension, and then the damping of the suspension system is increased by controlling the bidirectional adjustable damping valve; when the vehicle is traveling at a high speed on a poor road surface, it is necessary to improve the smoothness of the vehicle, that is, to reduce the damping of the suspension system. At this time, the ECU issues a control command to reduce the damping of the suspension, and then reduces the damping of the suspension system by controlling the bi-directional adjustable damping valve. The damping of the suspension system is continuously changed, so that different requirements of different running conditions on the damping of the suspension system are met, and the purpose of improving the smoothness and the steering stability of the vehicle is finally achieved.
(3) Active suspension mode
The invention not only can utilize the bidirectional adjustable damping valve to adjust the damping of the suspension, but also can utilize the unidirectional hydraulic pump to actively apply work to the suspension system, thereby leading the invention to have an active suspension mode. Taking the wheel as an example through a deceleration strip, the specific implementation process is as follows:
the vehicle-mounted sensor measures the motion state of the vehicle in real time, when the sensor detects that the wheels move upwards through the deceleration strip, the ECU sends out a control instruction, then the friction clutch is controlled to be gradually attached, the clutch drives the unidirectional hydraulic pump to pump hydraulic oil into the upper cavity of the hydraulic cylinder, the wheels move upwards, and therefore the acceleration of the vehicle body and the dynamic load of the wheels are reduced; when the sensor detects that the wheels move downwards, the ECU sends out a control instruction, and then the two-position four-way reversing valve is controlled to reverse, at the moment, although the rotation direction of the unidirectional hydraulic pump is unchanged, hydraulic oil is pumped into the lower cavity of the hydraulic cylinder after passing through the two-position four-way reversing valve, so that the wheels move downwards, the acceleration of a vehicle body and the dynamic load of the wheels are reduced, the acceleration of the vehicle body is closely related to the smoothness, the dynamic load of the wheels directly influences the operation stability, and therefore the smoothness and the operation stability of the vehicle can be greatly improved in an active suspension mode.
The rotating speed of the hydraulic pump can be controlled through the engagement degree of the clutch of the controller, so that the acting speed of the active suspension is controlled, and the requirements of different running conditions are met.
(4) Vehicle body posture adjustment mode
The pitch and roll of the vehicle body occur during acceleration, braking and turning, which has a great influence on riding comfort and steering stability, and thus it is desirable to minimize the variation in the posture of the vehicle body during acceleration, braking and turning.
The transient value of the vehicle body posture change during acceleration, braking and turning of the vehicle can be reduced by improving the damping of the suspension, but the steady value of the vehicle body posture change cannot be changed; the steady state value of the posture change of the vehicle body can be changed by controlling the hydraulic cylinder to do work. Therefore, the transient state value and the steady state value of the vehicle body posture change during acceleration, braking and turning of the vehicle can be controlled through the integrated control of the bidirectional adjustable damping valve and the hydraulic cylinder, so that the riding comfort and the steering stability of the vehicle under the working conditions are improved.
Taking a vehicle passing through a curve as an example to illustrate the working process of a vehicle body posture adjustment mode:
when the vehicle passes through a curve, the vehicle body starts to roll under the action of inertia force, at the moment, the acceleration sensor detects a lateral acceleration signal, then the acceleration signal is sent to the ECU, and the ECU sends a control instruction, so that on one hand, the damping of the bidirectional adjustable damping valve is increased, the angular speed of the vehicle roll is reduced, on the other hand, the clutch is controlled to start to be connected, the exhaust turbine drives the hydraulic pump to start acting, the inner side of the vehicle body generates a downward acting force, the outer side of the vehicle body generates an upward acting force, and therefore the vehicle body generates a moment opposite to the inertia force, the inertia force born by the vehicle body is offset, and finally the aim of reducing the roll angle of the vehicle body is achieved. The two-way adjustable damping valve and the one-way hydraulic pump are controlled in a combined mode, so that the roll angle speed and the roll angle of the vehicle body are limited in a certain range, and the riding comfort and the steering stability of the vehicle are greatly improved.
In this example, the turbine works on the principle:
the engine can discharge a large amount of waste gas in the working process, and the waste gas pressure can reach 0.5MPa, so that the waste gas of the engine has huge energy.
The turbine is arranged in the exhaust pipe of the engine, so that the turbine always rotates as long as the engine is in an operating state. A friction clutch is arranged between the turbine and the one-way hydraulic pump, and the rotating speed of the one-way hydraulic pump is controlled by controlling the engagement degree of the friction clutch, so that the speed of active work of the suspension system is controlled.
Claims (8)
1. An exhaust gas turbine driven slow active hydraulic suspension system characterized by comprising an air spring (12), a hydraulic system, an exhaust gas turbine system and an ECU (14); the upper end of the air spring (12) is connected with the vehicle body, and the lower end of the air spring is connected with the hydraulic cylinder (11); the exhaust turbine system and the hydraulic system are driven by a friction clutch (4), and the ECU (14) is in communication control connection with the hydraulic system and the exhaust turbine system at the same time; the hydraulic system comprises a bidirectional adjustable damping valve (1), an upper energy accumulator (2), a one-way hydraulic pump 3, an overflow valve (7), a two-position four-way reversing valve 8, a lower energy accumulator (9) and a hydraulic cylinder (11); the hydraulic cylinder (11) is fixed on the wheel (10), a piston rod of the hydraulic cylinder (11) is fixed on the vehicle body (13), and the hydraulic cylinder (11) is connected with the air spring (12) in parallel; the bidirectional adjustable damping valve (1) is arranged between an upper cavity of the hydraulic cylinder (11) and the upper energy accumulator (2), a lower cavity of the hydraulic cylinder is communicated with the lower energy accumulator (9), and the upper energy accumulator (2) and the lower energy accumulator (9) are respectively connected with the two-position four-way reversing valve (8); an overflow valve is arranged between the upper energy accumulator (2) and the lower energy accumulator (9); the waste gas turbine system comprises a one-way hydraulic pump (3), a turbine (6), a friction clutch (4) and an engine exhaust pipe (5), wherein the turbine (6) is arranged in the engine exhaust pipe (5), an output shaft of the turbine (6) is connected with a driving part of the friction clutch (4), an input shaft of the one-way hydraulic pump (3) is connected with a driven part of the friction clutch (4), and the one-way hydraulic pump (3) is communicated with a two-position four-way reversing valve (8) to form a loop with the hydraulic system.
2. The exhaust turbine driven slow active hydraulic suspension system as claimed in claim 1, wherein the ECU is simultaneously in communication signal connection with a bi-directional adjustable damping valve (1), a friction clutch (4) and a two-position four-way reversing valve (8) for controlling each working mode of the slow active hydraulic suspension system.
3. A method of controlling an exhaust gas turbine driven slow active hydraulic suspension system as claimed in claim 1 wherein said slow active hydraulic suspension system comprises the following control modes:
1) A passive suspension mode, in which the opening degree of a valve core of the bidirectional adjustable damping valve is unchanged, the vehicle buffers the vibration of wheels through an air spring, an upper energy accumulator and a lower energy accumulator, and the bidirectional adjustable damping valve damps the vibration of the vehicle body;
2) A semi-active suspension mode in which damping of the suspension system is controlled by adjusting a spool opening of the bi-directional adjustable damping valve;
3) An active suspension mode, wherein damping of a suspension system is adjusted by adjusting the opening degree of a valve core of a bidirectional adjustable damping valve, and meanwhile, the suspension system is actively acted by a unidirectional hydraulic pump;
4) And a vehicle body posture adjusting mode, wherein the transient state value and the steady state value of the vehicle body posture change during acceleration, braking and turning of the vehicle are controlled by controlling the bidirectional adjustable damping valve and the hydraulic cylinder.
4. A method of controlling an exhaust gas turbine driven slow active hydraulic suspension system according to claim 3 wherein the exhaust gas turbine system operates on the principle of:
the turbine rotates all the time as long as the engine is in a working state, the rotating speed of the input shaft of the one-way hydraulic pump can be controlled by controlling the engagement degree of the clutch, and the rotating speed of the input shaft of the one-way hydraulic pump determines the speed of the suspension system to actively do work.
5. A method of controlling an exhaust gas turbine driven slow active hydraulic suspension system as claimed in claim 3 wherein in said passive suspension mode the vehicle passes through a deceleration strip by:
when a vehicle running on a flat road encounters a deceleration strip, the wheels will move upwards; because the air spring is connected with the hydraulic cylinder in parallel, the deformation of the air spring is equal to the displacement of the piston of the hydraulic cylinder, the piston of the hydraulic cylinder moves downwards along the inner wall of the hydraulic cylinder, the volume of the upper cavity of the hydraulic cylinder is increased, the pressure is reduced, and the volume of the lower cavity of the hydraulic cylinder is decreased, and the pressure is increased; because the pressure of the upper cavity of the hydraulic cylinder is reduced, the pressure of the oil outlet of the upper energy accumulator is reduced, hydraulic oil flows into the upper cavity of the hydraulic cylinder from the upper energy accumulator, the pressure of the upper energy accumulator is reduced, and energy is released; similarly, the pressure of an oil inlet of the lower energy accumulator is increased, hydraulic oil flows into the lower energy accumulator from a lower cavity of the hydraulic cylinder, the pressure of the lower energy accumulator is increased, and energy is stored; in addition, hydraulic oil will produce the pressure loss through the two-way adjustable damping valve; at the moment, the upper cavity and the lower cavity of the hydraulic cylinder form a pressure difference, the pressure difference acts on the piston of the hydraulic cylinder to enable the vehicle body to generate upward acting force, and the acting force and the elastic force of the air spring act on the vehicle body together to enable the vehicle body to generate upward acceleration;
the wheels start to descend after reaching the highest point, the piston moves upwards along the inner wall of the hydraulic cylinder, the volume of the upper cavity of the hydraulic cylinder becomes smaller, the pressure intensity is increased, hydraulic oil flows into the upper accumulator from the upper cavity of the hydraulic cylinder, the pressure intensity of the upper accumulator is increased, and energy is stored; the piston moves upwards along the inner wall of the hydraulic cylinder, the volume of the lower cavity of the hydraulic cylinder is increased, the pressure of the oil inlet of the lower energy accumulator is reduced, hydraulic oil flows into the lower cavity of the hydraulic cylinder from the lower energy accumulator, the pressure of the lower energy accumulator is reduced, and energy is released; in addition, the hydraulic oil passes through the bidirectional adjustable damping valve to generate pressure loss, and at the moment, the upper cavity and the lower cavity of the hydraulic cylinder form pressure difference, the pressure difference acts on the piston of the hydraulic cylinder to generate downward hydraulic pressure on the vehicle body, and the hydraulic pressure and the elastic force of the air spring act on the vehicle body together to generate downward acceleration on the vehicle body;
in the whole process of the wheel passing through the deceleration strip, the air spring, the upper energy accumulator and the lower energy accumulator play a role in buffering uneven pavement; the bidirectional adjustable damping valve plays a role in damping vibration.
6. A method of controlling an exhaust gas turbine driven slow active hydraulic suspension system as claimed in claim 3 wherein said semi-active suspension mode is operated as follows:
the vehicle-mounted sensor measures the motion state and road surface information of the vehicle in real time, and when the vehicle accelerates, decelerates and turns, the ECU sends out a control instruction for improving the damping of the suspension, and then the damping of the suspension is increased by controlling the bidirectional adjustable damping valve; when the vehicle runs at a high speed on a bad road surface, the ECU sends out a control instruction for reducing the damping of the suspension, and then the damping of the suspension is reduced by controlling the bidirectional adjustable damping valve.
7. A method of controlling an exhaust gas turbine driven slow active hydraulic suspension system as claimed in claim 3 wherein in said active suspension mode the vehicle is operated through a deceleration strip by:
the vehicle-mounted sensor measures the motion state of the vehicle in real time, when the sensor detects that the wheels move upwards through the deceleration strip, the ECU sends out a control instruction, then the friction clutch is controlled to be gradually attached, the clutch drives the unidirectional hydraulic pump to pump hydraulic oil into the upper cavity of the hydraulic cylinder, the wheels move upwards, and therefore the acceleration of the vehicle body and the dynamic load of the wheels are reduced; when the sensor detects that the wheels move downwards, the ECU sends out a control instruction, and then the two-position four-way reversing valve is controlled to reverse, at the moment, the rotation direction of the unidirectional hydraulic pump is unchanged, and after the hydraulic oil passes through the two-position four-way reversing valve, the hydraulic oil is pumped into the lower cavity of the hydraulic cylinder, so that the wheels move downwards, and the acceleration of a vehicle body and the dynamic load of the wheels are reduced.
8. A method of controlling an exhaust gas turbine driven slow active hydraulic suspension system as claimed in claim 3 wherein in said body attitude adjustment mode, the vehicle is operated through a curve by:
when the vehicle passes through a curve, the vehicle body starts to roll under the action of inertia force, at the moment, the acceleration sensor detects a lateral acceleration signal, then the acceleration signal is sent to the ECU, and the ECU sends a control instruction, so that on one hand, the damping of the bidirectional adjustable damping valve is increased to reduce the transient value of the roll motion of the vehicle body; on the other hand, the friction clutch is controlled to start to be engaged, the exhaust turbine drives the hydraulic pump to start acting, the inner side of the automobile body generates a downward acting force, the outer side of the automobile body generates an upward acting force, and accordingly the automobile body generates a moment opposite to the inertia force, and the steady-state value of the rolling motion of the automobile body is reduced.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202211491343.3A CN116039308A (en) | 2022-11-25 | 2022-11-25 | Slow active hydraulic suspension system driven by exhaust gas turbine and control method |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202211491343.3A CN116039308A (en) | 2022-11-25 | 2022-11-25 | Slow active hydraulic suspension system driven by exhaust gas turbine and control method |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN116039308A true CN116039308A (en) | 2023-05-02 |
Family
ID=86122581
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202211491343.3A Pending CN116039308A (en) | 2022-11-25 | 2022-11-25 | Slow active hydraulic suspension system driven by exhaust gas turbine and control method |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN116039308A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN116252769A (en) * | 2023-05-09 | 2023-06-13 | 吉林大学 | Electronic hydraulic braking system and vehicle |
-
2022
- 2022-11-25 CN CN202211491343.3A patent/CN116039308A/en active Pending
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN116252769A (en) * | 2023-05-09 | 2023-06-13 | 吉林大学 | Electronic hydraulic braking system and vehicle |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US8489300B2 (en) | Vibration control apparatus for automotive vehicle | |
| JP5830379B2 (en) | Multi-point hydraulic suspension system for land vehicles | |
| CN207523391U (en) | A kind of vehicle and its suspension system | |
| US9120469B2 (en) | Vehicle behavior control apparatus | |
| CN108058562B (en) | Active suspension device and control method thereof | |
| US20060060750A1 (en) | Vehicle suspension system and method for operating | |
| JP2008520490A (en) | Method for controlling and tuning an active chassis system | |
| CN112549893B (en) | Intelligent electronic control suspension vibration damping system of automobile | |
| CN116039308A (en) | Slow active hydraulic suspension system driven by exhaust gas turbine and control method | |
| CN204263873U (en) | A kind of energy pair of transverse arm active suspension | |
| CN203114998U (en) | Damping-adjustable inflatable absorber | |
| CN101301847A (en) | Vehicle combined damping system | |
| CN1128073C (en) | Electrically controlled hydraulic vehicle with individual drive and brake of wheels and recovery of braking energy | |
| CN104709025A (en) | Self-road-adaption hydraulic active suspension system | |
| CN202156256U (en) | Cushioning device for automobile chassis | |
| CN204184152U (en) | A kind of plane scroll spring electromagnetism energy pair of transverse arm active suspension | |
| CN204526714U (en) | A kind of road self-adaptive hydraulic active suspension system | |
| WO2022141264A1 (en) | Integrated suspension and braking system | |
| CN216478644U (en) | Shock absorber valve system with low-speed multistage regulation characteristic | |
| JP2023160544A (en) | Active suspension device for vehicle | |
| CN104553664A (en) | Air spring based active suspension device | |
| CN117885487A (en) | Hydraulic suspension system with mode switching function, switching method and vehicle | |
| CN112172440B (en) | Active control device for resisting front pitching of car during braking | |
| CN216833108U (en) | Motor vehicle and vehicle body attitude adjusting system based on magnetorheological damper and gyroscope | |
| CN116729040A (en) | Energy feedback suspension system of hybrid electric vehicle and working method thereof |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination |