WO2020024653A1 - 一种支撑减振装置以及采用该支撑减振装置的车辆 - Google Patents

一种支撑减振装置以及采用该支撑减振装置的车辆 Download PDF

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Publication number
WO2020024653A1
WO2020024653A1 PCT/CN2019/086920 CN2019086920W WO2020024653A1 WO 2020024653 A1 WO2020024653 A1 WO 2020024653A1 CN 2019086920 W CN2019086920 W CN 2019086920W WO 2020024653 A1 WO2020024653 A1 WO 2020024653A1
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WO
WIPO (PCT)
Prior art keywords
valve
force
support
damping device
vibration damping
Prior art date
Application number
PCT/CN2019/086920
Other languages
English (en)
French (fr)
Inventor
陈刚
Original Assignee
陈刚
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Priority claimed from CN201810850830.1A external-priority patent/CN108662069B/zh
Priority claimed from CN201821209280.7U external-priority patent/CN208793507U/zh
Application filed by 陈刚 filed Critical 陈刚
Priority to JP2021504517A priority Critical patent/JP2021532317A/ja
Priority to DE112019003811.7T priority patent/DE112019003811T5/de
Priority to KR1020217003444A priority patent/KR20210027462A/ko
Publication of WO2020024653A1 publication Critical patent/WO2020024653A1/zh
Priority to US17/139,074 priority patent/US20210123496A1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/50—Special means providing automatic damping adjustment, i.e. self-adjustment of damping by particular sliding movements of a valve element, other than flexions or displacement of valve discs; Special means providing self-adjustment of spring characteristics
    • F16F9/512—Means responsive to load action, i.e. static load on the damper or dynamic fluid pressure changes in the damper, e.g. due to changes in velocity
    • 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
    • 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
    • B60G17/018—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 use of a specific signal treatment or control method
    • 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
    • B60G17/019—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 type of sensor or the arrangement thereof
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
    • B60G17/02—Spring characteristics, e.g. mechanical springs and mechanical adjusting means
    • B60G17/04—Spring characteristics, e.g. mechanical springs and mechanical adjusting means fluid spring characteristics
    • B60G17/056—Regulating distributors or valves for hydropneumatic systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
    • F16F13/005—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a wound spring and a damper, e.g. a friction damper
    • F16F13/007—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a wound spring and a damper, e.g. a friction damper the damper being a fluid damper
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/06—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using both gas and liquid
    • F16F9/061—Mono-tubular units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/34—Special valve constructions; Shape or construction of throttling passages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/53—Means for adjusting damping characteristics by varying fluid viscosity, e.g. electromagnetically

Definitions

  • the invention relates to the support and damping of objects that need to be prevented or damped, and is particularly suitable for vehicle suspension and damping.
  • shock absorbers In order to make the vehicle run smoothly under different road conditions, the suspension and vibration reduction methods of the vehicle are very important.
  • the commonly used shock absorbers are divided into passive, semi-active (adjustable) and active shock absorbers.
  • Passive shock absorber The suspension and vibration damping methods commonly used in combination with springs and shock absorbers are passive vibration dampers. Once the shock absorber is designed and installed, the damping value is determined and cannot be adjusted as the load changes. The use process Can not better filter out the vibration of the vehicle during driving.
  • Semi-active shock absorbers Semi-active shock absorbers are not commonly used, and damping can be adjusted conditionally, but due to the relatively high cost and difficult maintenance, the vibration filtering effect of the vehicle during driving is also quite limited.
  • Active shock absorbers have fewer applications. With the aid of computer-aided measurement and control technology, the effect is relatively good, but the cost is very high, the reliability is insufficient, the maintenance is difficult, and the technology is difficult.
  • the current method is similar to the vehicle vibration reduction method. It belongs to passive vibration reduction, and cannot actively adjust the vibration damping according to the force of the object.
  • the shock absorber can automatically adjust the damping of the shock absorber according to the force of the support spring and the shock absorber on the supported object during the vibration process, and reduce the external force applied to the spring and the shock absorber during the vehicle's travel.
  • the effect of the supporting force of the support thereby reducing or eliminating vibration.
  • the vibration and bumps of the vehicle during driving caused by the uneven road surface are reduced.
  • the control component compares the support force value with the set force value or the gravity of the support supported by the vibration damping device.
  • the electronic control and other methods control the damping of the shock absorber, thereby adjusting the supporting force value of the supporting damping device, so that the supporting force value of the supporting damping device is equal to or close to the set force value or the gravity of the object supported by the damping device.
  • a support and vibration damping device includes: a support spring, a hydraulic cylinder, a valve assembly, a force measuring element, and a control component.
  • the characteristic is that the force measuring element measures the value of the support force of the support and vibration damping device on the supported object, and The support force value is compared with the set force value or the gravity of the support supported by the vibration damping device, and the damping of the valve assembly is controlled by the control component according to the comparison result, thereby adjusting the support force value of the vibration damping device to make the vibration damping of the support
  • the supporting force value of the device is equal to or close to the set force value, or equal to or close to the gravity of the object supported by the vibration damping device.
  • Support vibration damping device refers to a device with a supporting effect and a damping effect.
  • pillar-type shock absorbers with supporting springs and shock absorbers such as air spring and shock absorber combinations using air suspension systems; such as spring and shock absorber combinations where load-bearing springs and shock absorbers are separately arranged; and
  • the support vibration reduction system composed of the energy storage device (19), the hydraulic valve (the pressure reducing valve (21), the relief valve (23)) and the single-acting hydraulic cylinder (20) belongs to the support vibration reduction device.
  • Support spring refers to elastic parts with energy storage functions, such as coil springs, disc springs, compressed gas accumulators, air springs, etc.
  • the supporting spring is the main part of the supporting damping device.
  • the compressed gas accumulator plays a supporting role in cooperation with the hydraulic cylinder in the support damping device of this article.
  • Hydraulic cylinder includes single-acting hydraulic cylinder, double-acting hydraulic cylinder, shock absorber, etc.
  • the shock absorber belongs to a special hydraulic cylinder with integrated valve assembly.
  • Shock absorbers include commonly used single-cylinder shock absorbers, double-cylinder shock absorbers, and magnetorheological shock absorbers.
  • the role of the single-acting hydraulic cylinder and the double-acting hydraulic cylinder in supporting the vibration damping device is to transmit the energy of the energy storage device through the liquid flow, and play a supporting role together with the energy storage device.
  • the single-cylinder damper and double-cylinder vibration damper play a major role in supporting the vibration damping device to generate hydraulic damping to reduce vibration.
  • Valve component refers to the component that has a damping effect on the flow or air flow, a shut-off effect or a control of the direction of the flow, including a throttle valve, a check valve, a pressure reducing valve, an overflow valve, a magnetorheological damper, and an electrorheological Dampers, solenoid valves, shock absorber bottom valves, valves on shock absorber pistons, etc.
  • Magneto-rheological dampers, electro-rheological dampers and solenoid valves are collectively referred to as electronically controlled valves in this article; the electronically controlled valves in subsequent cases refer to one of magneto-rheological dampers, electro-rheological dampers and solenoid valves.
  • the main role of the valve assembly in supporting the vibration damping device is to damp the liquid flow or control the direction of the liquid flow.
  • the hydraulic medium should be the corresponding magneto-rheological fluid or electro-rheological fluid.
  • Force measuring element refers to components that can be used to measure or set pressure or force values, such as compression gas springs, coil springs, coil springs, load cells and related circuit components, pressure sensors and related circuit components.
  • Springs used to set or adjust pressure are also load cells, such as pressure regulating springs for pressure reducing valves and relief valves.
  • Control component refers to the intermediate acting component that can directly or indirectly adjust the damping of the valve component through mechanical linkage, electronic control linkage or hydraulic control linkage with the force measuring element.
  • the control component may be a mechanical component or an electronic circuit device.
  • the control component when controlling an electrorheological damper or a magnetorheological damper and a solenoid valve, the control component is an electronic circuit device.
  • the control link (1) in Figures 1, 3, and 5 is also a control component. Its role is to directly apply the measured value to the spool valve, which drives the spool valve to move up and down to increase or decrease the valve port. This control valve assembly is damped.
  • the pressure reducing valve and relief valve in the case of this article belong to the combination of valve assembly, load cell and control assembly.
  • the pressure reducing valve and the relief valve have the functions of a valve assembly, a load cell, and a control assembly.
  • the pressure reducing valve in this article compares the set pressure of the pressure regulating spring with the hydraulic pressure in the hydraulic cylinder, and controls the damping force of the pressure reducing valve according to the comparison result, so as to control the pressure of the liquid flow entering the hydraulic cylinder, thereby controlling the hydraulic pressure.
  • the supporting force of the cylinder is not limited to control the pressure of the liquid flow entering the hydraulic cylinder.
  • the relief valve is to compare the set pressure of the pressure regulating spring with the hydraulic pressure of the hydraulic cylinder, and adjust the damping of the fluid flow by the relief valve according to the comparison result, so as to control the pressure of the fluid flowing out of the hydraulic cylinder, thereby controlling The supporting force of the hydraulic cylinder.
  • the damping value of the pressure reducing valve is controlled by the outlet pressure of the pressure reducing valve, and the damping value of the relief valve is controlled by the inlet pressure of the relief valve. That is, the role of the pressure regulating spring of the pressure reducing valve and the relief valve is to indirectly measure the supporting force of the vibration damping device by measuring the pressure in the hydraulic cylinder.
  • the force of the pressure regulating spring of the pressure reducing valve and the relief valve directly acts on the valve core and interacts with the inlet and outlet pressure of the hydraulic cylinder to adjust the damping value of the valve.
  • the pressure reducing valve and the relief valve are classified as a hydraulic control type, that is, the magnitude of the hydraulic pressure in the hydraulic cylinder controls the damping value of the pressure reducing valve and the relief valve.
  • the pressure reducing valve, relief valve, and check valve in this article are not limited to the conventional pressure reducing valve, relief valve, and check valve. Any component or component that has the same function as the pressure reducing valve, relief valve, and check valve The combination is considered equivalent to the pressure reducing valve, relief valve and check valve in this article.
  • the force-measuring spring (2) measures the supporting force of the supporting vibration damping device, and adjusts the damping of the valve assembly during the compression process through the control link (1) according to the measured force value.
  • the liquid in the liquid storage chamber (18) flows through the check valve (6) on the bottom valve (10) to the compression chamber (9) and the stretching chamber (5).
  • the support and vibration damping device includes: a single-acting hydraulic cylinder (20), a support spring mainly composed of an energy storage device (19), a pressure reducing valve (21), and a single
  • the valve assembly, force measuring element and control assembly composed of a directional valve (6) are characterized in that the energy storage (19) is connected to a single-acting hydraulic cylinder through a pressure reducing valve and a check valve connected in parallel with the pressure reducing valve; When the working hydraulic cylinder (20) is compressed back, the liquid flows through the check valve (6) and flows into the energy storage (19).
  • the pressure of the liquid flow entering the single-acting hydraulic cylinder is compared with the set pressure of the pressure reducing valve, so as to adjust the damping value of the pressure reducing valve, so that the hydraulic pressure flowing from the accumulator into the single-acting hydraulic cylinder
  • the force is not greater than the set force value, thereby limiting the increase in the supporting force of the single-acting hydraulic cylinder.
  • the support and vibration damping device includes: a single-acting hydraulic cylinder (20), a support spring mainly composed of an accumulator (19), a relief valve (23), and a single
  • the valve assembly and force measurement and control assembly formed by the check valve (6) are characterized in that the energy storage device (19) is connected to the single-acting hydraulic cylinder through a relief valve and a check valve connected in parallel with the relief valve;
  • the hydraulic cylinder (20) is stretched, the liquid in the accumulator (19) flows through the one-way valve (6) to the single-acting hydraulic cylinder (20);
  • the single-acting hydraulic cylinder (20) is compressed, the liquid of the single-acting hydraulic cylinder flows out
  • the flow pressure is compared with the set pressure of the relief valve to adjust the damping value of the relief valve.
  • the relief valve (23) makes the hydraulic pressure flowing out of the single-acting hydraulic cylinder not less than the set force value, thereby preventing single-acting The supporting force of the hydraulic cylinder is reduced.
  • the support and vibration damping device described in Scheme 1 includes: a load cell mainly composed of a load cell, a control component mainly composed of a controller (24), The valve assembly composed of the electronic control valve (30) on the piston or (and) the bottom valve (30); etc .; It is characterized in that at least one of the piston (7) and the bottom valve (10) is equipped with Electric control valve (30); when a one-way valve is provided on the fluid flow path of the shock absorber, at least one load cell should be installed to measure the total force supporting the vibration damping device; when the fluid flow path of the shock absorber is not provided For check valves, at least two load cells should be installed in order to measure the total force of the supporting vibration damping device and calculate whether the force state of the shock absorber is tensile or pressure; the control component will support the vibration damping device measured by the load cell The value of the supporting force is compared with the set force value or the gravity of the object supported by the vibration damping device, and the electronically controlled valve (30) is
  • the control method of the electronically controlled damping support vibration damping device is:
  • the supporting force supporting the vibration damping device is greater than the gravity or set force value (target force value) of the object supported by the shock absorber and the supporting spring: if the force received by the shock absorber is a tensile force, increase the stretch of the shock absorber Damping (increasing the damping of electronically controlled stretch valves);
  • the force applied to the shock absorber is a tensile force, reduce the tensile damping of the shock absorber (reducing the damping of the electronically controlled stretch valve);
  • shock absorber If the shock absorber is under pressure, increase the compression damping of the shock absorber (increasing the damping of the electronically controlled compression valve).
  • Stretch valve of shock absorber refers to the valve through which fluid flows out of the piston rod cavity (stretch cavity) of the hydraulic cylinder when the shock absorber is stretched.
  • Compression valve of shock absorber refers to the valve through which fluid flows out of the hydraulic cylinder or out of the compression chamber when the shock absorber is compressed.
  • the support and vibration damping device described in scheme 7 includes: a load cell (25) for measuring the support force value of the support spring (4) and a load cell for measuring the tension or pressure value of the hydraulic cylinder (17) (26) and controller (24), etc .; characterized by calculating the combined force of the support spring and the hydraulic cylinder (17) on the current supporting vibration damping device based on the measured value of the load cell, and determining the impact of the hydraulic cylinder (17)
  • the controller controls the damping of the electric control valve according to the combined force of the supporting vibration damping device and the force state of the hydraulic cylinder; the damping control method is as follows:
  • the support and vibration damping device (Figure 11) according to Option 7 includes:
  • Valve assembly mainly composed of electric control valve (30) and check valve (6) on piston (7)
  • control assembly mainly composed of controller (24) and force measurement mainly composed of load cell (25) Components, etc., which are characterized in that: the check valve (6) on the piston (7) is connected in parallel with the electric control valve (30), and the load cell (25) measures the support spring on the vibration damping device and the hydraulic cylinder (17) The total force, the control component compares the support force value of the support vibration damping device measured by the load cell (25) with the set force value or the gravity of the object supported by the vibration damping device, and controls the electric control valve ( 30) Damping; damping control methods are as follows:
  • a vehicle such as a single-wheel, two-wheel, three-wheel or multi-wheel vehicle, characterized in that one of the support-vibration damping devices described in the above-mentioned items 1-10 is adopted.
  • the support type vibration damping device Compared with the existing adaptive vibration damping technology, the support type vibration damping device has a better adaptive vibration damping function, and its damping value will be automatically adjusted according to the undulation of the road surface, the vibration damping effect is better, the structure is more simple, and the controllable Processes and methods are also simpler and less costly.
  • Figure 1 Schematic of a spring-supported tensile damping controlled support vibration damping device
  • FIG. 1 Enlarged view of the valve assembly in the schematic of Figure 1.
  • FIG. 7 Schematic diagram of a liquid-air-supported tensile damping controlled support-vibration device
  • Fig. 8 Schematic diagram of liquid-air-supported compression damping controlled support vibration damping device
  • Preferred solution 1 Schematic diagram of the spring-supported tensile or (and) compression damping controlled support and vibration damping device shown in FIG. 1, FIG. 2, FIG. 3, FIG. 4, FIG. 5, and FIG.
  • the supporting vibration damping device is mainly composed of a force measuring spring (2), a supporting spring (4), a hydraulic cylinder (vibration absorber) (17), a control valve (a foot valve (10) on the shock absorber or a piston (7) Slide valve (8)) and control link (1).
  • the bottom valve (10) or the piston (7) is provided with a slide valve (8) that is linked with the control link (1).
  • the bottom valve (10) or the piston (7) is also provided with a check valve (6).
  • Support vibration damping device shown in Figures 1 and 2 When the support vibration damping device is compressed by force, the liquid flow can pass from the check valve (6) on the piston (7) through the path (14) and path (15) and The check valve on the foot valve flows.
  • the support damping device changes from compression to extension, the support force changes from large to small, and the force measuring spring (2) changes from short to long, driving the control link (1) and the slide valve (8) on the control link (1).
  • the extension valve port (the valve port through which the fluid flow path (16) flows is the extension valve port) is The closed position gradually opens until the valve is fully open, and the valve damping changes from large to small.
  • the support and vibration damping device shown in Figures 3 and 4 When the support and vibration damping device is extended, the liquid flow path can pass from the check valve (6) and the piston (7) on the bottom valve through the path (13) and path (16). ) On the valve.
  • the support damping device When the support damping device is compressed by force, the support force changes from small to large, and the force measuring spring (2) changes from long to short, driving the control link (1) and the slide valve (8) on the control link (1) from below Move upward, when the support force is greater than the gravity value or set force value of the support to support the vibration damping device, the valve port gradually opens from the closed position until the valve is fully open, and the valve damping changes from large to small.
  • the valve port of the stretch valve (the valve port through which the path (16) flows Is the extension valve valve port) from the closed position to full open, the extension valve damping changes from large to small; when the support vibration damping device is compressed, the supporting force changes from small to large, and the force measuring spring (2) changes from long to short, driving control
  • the sliding valve (8) on the connecting rod (1) and the control connecting rod (1) moves from top to bottom.
  • the valve port flowing through path (14) is the compression valve port.
  • the damping of the compression valve changes from large to small; when the supporting vibration damping device is stretched, the liquid flows through the path 13 through the check valve ( 6) Flow into the compression chamber (9); when the support vibration damping device is compressed, the liquid flows through the path 15 through the check valve (6) and into the stretching chamber (5).
  • the liquid flow during the extension and compression of the support vibration damping device enters and exits the reservoir (22) through the in-out liquid flow path (32).
  • the control link (1) in Figures 1, 3, and 5 can be adjusted up and down, and the position of the slide valve (8) can be adjusted by adjusting the position of the control link (1) to adjust the support when the valve port is opened and when the valve is closed.
  • the critical force value of the vibration damping device can be adjusted up and down, and the position of the slide valve (8) to adjust the support when the valve port is opened and when the valve is closed.
  • the supporting vibration damping device is mainly composed of an energy storage (19), a single-acting hydraulic cylinder (20), a hydraulic valve (a pressure reducing valve (21), a relief valve (23), a check valve (6)), etc.
  • the pressure regulating springs of the pressure valve (21) and the relief valve (23) set the pressure of the liquid flow entering or leaving the single-acting hydraulic cylinder (20), and The set pressure is compared to indirectly measure the supporting force of the single-acting hydraulic cylinder (20), and the damping values of the valve ports of the pressure reducing valve (21) and the relief valve (23) are adjusted according to the comparison result, thereby adjusting the inlet or The pressure of the liquid flow out of the single-acting hydraulic cylinder (20).
  • the supporting vibration damping device shown in FIG. 8 When the single-acting hydraulic cylinder (20) is stretched, the fluid in the energy storage (19) flows through the check valve (6) to the single-acting hydraulic cylinder (20), and the single-acting hydraulic cylinder (20) 20) During compression, the relief valve (23) makes the pressure of the liquid flow flowing out of the hydraulic cylinder not less than the set force value, thereby preventing the supporting force of the hydraulic cylinder from decreasing.
  • the supporting vibration damping device includes: a force measuring element, a supporting spring (4), a hydraulic cylinder (vibration absorber) (17), an electronically controlled valve (that is, a damper bottom valve (10) or a valve (7) on a piston (7) 30)) and controller (24), etc.
  • the load cell is composed of load cell and related circuit elements
  • the controller (24) is composed of electronic circuit elements
  • the role of the controller (24) is to calculate the measurement of the load cell Value and control the damping value of the electronically controlled valve (30) (electrically controlled valve refers to solenoid valve, magnetorheological damper, electrorheological damper, etc.).
  • At least one of the bottom valve (10) or the piston (7) is provided with an electronically controlled valve (30).
  • at least one of the bottom valve (10) or the piston (7) is provided with an electric control valve (30) and a check valve (6).
  • a load cell (25) measures the support force of the support spring (4)
  • a load cell (26) measures the pulling force or pressure of the hydraulic cylinder (vibration absorber) (17).
  • a load cell (25) measures the total support force of the support spring (4) and a hydraulic cylinder (vibration absorber) (17), and a load cell (26) measures the hydraulic cylinder (vibration reduction (17) pull or pressure.
  • the support vibration damping device shown in Figure 11 The load cell (25) measures the total support force of the support spring (4) and the hydraulic cylinder (vibration absorber) (17), the piston (7) or (and) the bottom valve (10) ) Is equipped with a check valve (6) in addition to an electric control valve (30).
  • the control signal output by the controller is only suitable for controlling the piston (7) equipped with an electric control valve (30) or the bottom valve (10) equipped with an electric control valve (30).
  • the change of the damping resistance of the piston (7) of the valve (30) or the bottom valve (10) without using the electronically controlled valve (30) is not controlled by the controller (24).
  • the piston (7) without the electric control valve (30) or the foot valve (10) without the electric control valve (30) works in the same way as the piston or foot valve of a traditional shock absorber.
  • At least one of the piston (7) and the bottom valve (10) in the schematic diagrams of FIG. 9, FIG. 10, and FIG. 11 is equipped with an electric control valve (30), or both can be equipped with an electric control valve (30), but not two Both must be fitted with an electronically controlled valve (30).
  • the controller (24) calculates the resultant force according to the values measured by the load cell (25) and the load cell (26). When the resultant force is greater than the set force value and the hydraulic cylinder ( When the force value of the shock absorber) (17) is the pulling force, the control signal output by the controller (24) increases the damping of the electric control valve (30) on the piston (7) (applicable when the electric control valve (30) is installed on the piston ) To reduce the damping of the electric control valve (30) on the foot valve (10) (applicable when the electric control valve (30) is installed on the foot valve); when the combined force is greater than the set force value and the hydraulic cylinder (vibration absorber) ( 17) When the force value is pressure, the control signal output by the controller reduces the damping of the electric control valve (30) on the piston (7) (applicable when the electric control valve (30) is installed on the piston) and the foot valve (10) The electric control valve (30) on the upper part is damped (applic
  • the control signal output by the controller (24) reduces the damping of the electric control valve (30) on the piston (7)
  • the electric control valve (30) on the bottom valve (10) is damped; when the combined force is less than the set force value and the force value of the hydraulic cylinder (shock absorber) (17) is pressure, the control output of the controller (24)
  • the signal reduces the damping of the electric control valve (30) on the piston (7) (applicable when the electric control valve (30) is installed on the piston), and the damping of the electric control valve (30) on the bottom valve (10) is increased (foot valve (Applicable when an electric control valve (30) is installed on it).
  • the support and vibration damping device shown in Figure 11 The sensor measures the total support force of the support spring (4) and the hydraulic cylinder (vibration absorber) (17).
  • the electric control valve (30) is also equipped with a check valve (20).
  • the controller (24) When the resultant force is greater than the set force value, the controller (24) outputs a control signal to increase the damping of the electric control valve (30) on the piston (7) (applicable when the electric control valve (30) is installed on the bottom valve), reducing the bottom Damping of the electric control valve (30) on the valve (10) (applicable when the electric control valve (30) is installed on the bottom valve).
  • the controller (24) When the total force is less than the set force value, the controller (24) outputs a control signal to reduce the damping of the electric control valve (30) on the piston (7) (applicable when the electric control valve (30) is installed on the piston), and increase the bottom valve Damping of the electric control valve (30) on (10) (applicable when the electric control valve (30) is installed on the bottom valve (10)).

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Abstract

一种支撑减振装置，包括：支撑弹簧（4）、液压缸（17）、阀组件、测力元件、控制组件；测力元件测量支撑减振装置对所支撑物的支撑力值，并将支撑力值与设定力值或支撑减振装置所支撑物的重力进行比较，并根据比较结果由控制组件通过机械、液压或电控等方式控制减振器的阻尼，从而调节支撑减振装置的支撑力值，使支撑减振装置的支撑力值等于或接近于设定力值或支撑减振装置所支撑物的重力。一种具有上述支撑减振装置的车辆。

Description

一种支撑减振装置以及采用该支撑减振装置的车辆 技术领域
本发明涉及到需要防振或减振的物体的支撑和减振，特别适用于车辆悬挂和减振。
 背景技术
为了使车辆在不同路面条件下平稳行驶，车辆的悬挂和减振方法则显得相当重要，常用的减振器分为被动式、半主动式(可调式)和主动式减振器。
被动式减振器：常用的弹簧与减振器配合构成的悬挂和减振方法属于被动式减振，其减振器一旦设计安装完后，阻尼值就已确定，不能随负载变化而调节，使用过程中不能够更好的过滤掉车辆行驶过程中的振动。
半主动式减振器：半主动式减振器应用不太普遍，阻尼可以有条件调节，但由于成本相对较高，且维护较为困难，而且对车辆行驶过程中的振动过滤效果也相当有限。
主动式减振器：主动式减振器则应用更少，借助计算机辅助测控技术，效果相对较好，但成本非常高，可靠性不足，维护困难，技术难度大。
需要防振或减振的物体，目前采用的方法也是同车辆减振方法类似，属于被动式减振，不能够主动地根据物体受力情况调节减振阻尼。
 技术问题
使减振器能根据支撑弹簧和减振器对所支撑物体振动过程中的受力情况，自动地调节减振器的阻尼，减小车辆行进过程中外部施加的力对弹簧和减振器所支撑物的支撑力的影响，从而减小或消除振动。特别是车辆在高低不平时的路面行驶时，减小由于路面不平造成的行驶过程中车辆的振动和颠簸。
 技术解决方案
用测力元件测量支撑减振装置对所支撑物的支撑力值，控制组件将支撑力值与设定力值或支撑减振装置所支撑物的重力进行比较，根据比较结果通过机械、液压或电控等方式控制减振器的阻尼，从而调节支撑减振装置的支撑力值，使支撑减振装置的支撑力值等于或接近于设定力值或支撑减振装置所支撑物的重力。
方案1.  一种支撑减振装置包括：支撑弹簧、液压缸、阀组件、测力元件、控制组件；其特征是：测力元件测量支撑减振装置对所支撑物的支撑力值，并将支撑力值与设定的力值或支撑减振装置所支撑物的重力进行比较，并根据比较结果由控制组件控制阀组件的阻尼，从而调节支撑减振装置的支撑力值，使支撑减振装置的支撑力值等于或接近于设定力值，或者等于或接近于支撑减振装置所支撑物的重力。
支撑减振装置：指具有支撑作用和减振作用的装置。如带支撑弹簧和减振器的支柱式减振器；如采用空气悬挂系统的空气弹簧和减振器组合；如承重弹簧和减振器分开布置的弹簧和减振器组合；以及本文中的储能器(19)、液压阀(减压阀(21)、溢流阀(23))和单作用液压缸(20)构成的支撑减振系统都是属于支撑减振装置。
支撑弹簧：指具有储能作用的弹性部件，如螺旋弹簧、碟簧、压缩气储能器、空气弹簧等。支撑弹簧是支撑减振装置中起支撑作用的主要部件。压缩气储能器在本文的支撑减振装置中与液压缸配合起支撑作用。
液压缸和减振器：液压缸包括单作用液压缸，双作用液压缸，减振器等。减振器属于一种集成有阀组件的特殊的液压缸。减振器包括常用的单筒式减振器、双筒式减振器、磁流变减振器等。单作用液压缸和双作用液压缸在支撑减振装置中的作用是通过液流传递储能器的能量，与储能器一起起支撑作用。单筒式减振器和双筒式减振器在支撑减振装置中主要作用是产生液压阻尼减缓振动。
阀组件：指对液流或气流有阻尼作用，关断作用或控制液流方向作用的部件，包括节流阀、单向阀、减压阀、溢流阀、磁流变阻尼器、电流变阻尼器、电磁阀、减振器底阀以及减振器活塞上的阀、等。 磁流变阻尼器、电流变阻尼器和电磁阀在本文中统称为电控阀；后续案例中的电控阀指磁流变阻尼器、电流变阻尼器和电磁阀中的一种。阀组件在支撑减振装置中主要作用是对液流产生阻尼或控制液流方向。
当使用磁流变阻尼器或电流变阻尼器的支撑式减振装置时，液压介质应为对应的磁流变液或电流变液。
 测力元件：指用可用于测量或设定压力或力值的零部件，如压缩气弹簧、螺旋弹簧、碟簧、测力传感器及其相关电路组件、压力传感器及相关电路组件等。用于设定或调节压力的弹簧也属于测力元件，如减压阀、溢流阀的调压弹簧等。
控制组件：指与测力元件通过机械联动、电控联动或液控联动的可以直接或间接调节阀组件阻尼的中间作用部件。控制组件可以是机械部件，也可以是电子电路器件，例如控制电流变阻尼器或磁流变阻尼器以及电磁阀时则控制组件为电子电路器件。图1、图3和图5中的控制连杆(1)也为控制组件，它的作用是将测量值直接作用于滑阀,带动滑阀上下移动，使阀口增大或减小，以此控制阀组件的阻尼。
本文案例中的减压阀和溢流阀是属于阀组件、测力元件和控制组件的组合。减压阀和溢流阀同时具有阀组件、测力元件和控制组件的功能。本文中减压阀是将调压弹簧的设定压力与液压缸内的液压力进行比较，并根据比较结果控制减压阀的阻尼力，从而控制进入液压缸的液流压力，以此控制液压缸的支撑力。本文中溢流阀是将调压弹簧的设定压力与液压缸的液压力进行比较，并根据比较结果调节溢流阀对液流的阻尼，从而控制流出液压缸的液流压力，以此控制液压缸的支撑力的。减压阀的阻尼值受减压阀的出口压力控制，溢流阀的阻尼值受溢流阀的进口压力控制。即减压阀、溢流阀的调压弹簧的作用是通过测量液压缸内的压力间接测量支撑减振装置的支撑力。减压阀和溢流阀的调压弹簧的力直接作用于阀芯上与液压缸的进出口压力相互作用，调节其阀的阻尼值。减压阀和溢流阀归于液控调节类，即液压缸内的液压力的大小值控制减压阀和溢流阀的阻尼值大小。
本文中减压阀、溢流阀和单向阀不限于常规减压阀、溢流阀和单向阀形式，凡是具有与减压阀、溢流阀和单向阀具有相同功能的组件或组件组合均视为与本文中的减压阀、溢流阀和单向阀等效。
方案2.  (图1，图2)如方案1所述的支撑减振装置其特征是：控制组件主要由控制连杆(1)构成， 减振器活塞(7)上集成有包括单向阀(6)和滑阀(8)在内的阀组件，滑阀(8)连接在控制连杆(1)上，测力元件主要由测力弹簧(2)构成；测力元件测量支撑减振装置的支撑力，并依据测量值通过控制连杆(1)调节滑阀(8)的位置，以此调节拉伸过程中阀组件的阻尼。压缩时，压缩腔(9)内的液流经活塞(7)上的单向阀(6)流向拉伸腔(5)。
方案3.   (图3，图4)如方案1所述的支撑减振装置其特征是：控制组件主要由控制连杆(1)构成，减振器底阀(10)上集成有包括单向阀(6)和滑阀(8)在内的阀组件，滑阀(8)连接在控制连杆(1)上；
测力弹簧(2)测量支撑减振装置的支撑力，并依据测量力值通过控制连杆(1)调节压缩过程中的阀组件的阻尼。拉伸时，储液腔(18)内的液流经底阀(10)上的单向阀(6)流向压缩腔(9)和拉伸腔(5)。
方案4.   (图5，图6)如方案1所述的支撑减振装置其特征是：控制组件主要由控制连杆(1)构成，减振器活塞(7)上集成有包括与拉伸腔(5)相通的单向阀(6)、与压缩腔(9)相通的单向阀(6)以及主要由滑阀(8)构成的与压缩腔相通的压缩阀和与拉伸腔相通的拉伸阀，滑阀(8)连接在控制连杆(1)上，活塞内腔(31)与储液器(22)连通，活塞内腔通过单向阀(6)与拉伸腔(5)和压缩腔(9)相通；减振器压缩或伸张时，测力弹簧(2)测量支撑减振装置的支撑力值并且依据测量力值通过控制连杆(1)调节拉伸阀和压缩阀的阻尼。减振器拉伸腔(5)或压缩腔(9)容积增加时液流通过单向阀(6)补液。
方案5.   (图7)如方案1所述的支撑减振装置包括：单作用液压缸(20)、主要由储能器(19)构成的支撑弹簧、主要由减压阀(21)和单向阀(6)构成的阀组件和测力元件以及控制组件等；其特征是：储能器(19)通过减压阀和与减压阀并联的单向阀与单作用液压缸相连；单作用液压缸(20)受压缩回时，液流经单向阀(6)流入储能器(19)。单作用液压缸伸张时，进入单作用液压缸的液流压力与减压阀的设定压力进行比较，以此调节减压阀的阻尼值，使从储能器内流入单作用液压缸的液压力不大于设定力值，从而限制单作用液压缸的支撑力增加。
方案6.  (图8)如方案1所述的支撑减振装置包括：单作用液压缸(20)、主要由储能器(19)构成的支撑弹簧、主要由溢流阀(23)和单向阀(6)构成的阀组件和测力及控制组件等；其特征是：储能器(19)通过溢流阀和与溢流阀并联的单向阀与单作用液压缸相连；单作用液压缸(20)伸张时，储能器(19)内液流经单向阀(6)流向单作用液压缸(20)；单作用液压缸(20)压缩时，流出单作用液压缸的液流压力与溢流阀的设定压力进行比较，以此调节溢流阀的阻尼值，溢流阀(23)使从单作用液压缸流出的液压力不小于设定力值，从而防止单作用液压缸的支撑力减小。
方案7.   (图9，图10，图11)如方案1所述的支撑减振装置包括：主要由测力传感器构成的测力元件、主要由控制器(24)构成的控制组件、主要由活塞上的电控阀(30)或(和)底阀上的电控阀(30)构成的阀组件、等；其特征是：活塞(7)和底阀(10)上至少有一个装有电控阀(30)；当减振器液流路径上设有单向阀时，则至少应装一只测力传感器测量支撑减振装置的合力；当减振器液流路径上未设有单向阀时，至少应装两只测力传感器，以便测量支撑减振装置的合力并计算减振器的受力状态是拉力还是压力；控制组件将测力传感器所测得的支撑减振装置的支撑力值与设定力值或支撑减振装置所支撑物的重力进行比较，并根据比较结果以及减振器的受力状态控制电控阀(30)阻尼。
 电控阻尼式支撑减振装置的控制方法是：
1．当支撑减振装置的支撑力大于减振器和支撑弹簧所支撑物的重力或设定力值(目标力值)时：如果减振器受到的力为拉力，则增加减振器的拉伸阻尼(增加电控拉伸阀的阻尼)；
      如果减振器受力为压力，则减小减振器的压缩阻尼(减少电控压缩阀的阻尼)。
2．当支撑弹簧支撑力小于减振器和支撑弹簧所支撑物的重力或设定力值(目标力值)时：
    如果减振器受到的力为拉力，则减小减振器的拉伸阻尼(减小电控拉伸阀的阻尼)；
    如果减振器受力为压力，则增加减振器的压缩阻尼(增加电控压缩阀的阻尼。)。
3．当支撑弹簧支撑力接近或等于减振器和支撑弹簧所支撑物的重力或设定力值(目标力值)时，维持减振器当前阻尼值。
 减振器的拉伸阀：指减振器拉伸时，液流流出液压缸的活塞杆腔(拉伸腔)所经过的阀。减振器的压缩阀：指减振器压缩时，液流流出液压缸或流出压缩腔所经过的阀。
方案8.      (图9)如方案7所述的支撑减振装置包括：测量支撑弹簧(4)支撑力值的测力传感器(25)和测量液压缸(17)拉力或压力值的测力传感器(26)以及控制器(24)等；其特征是：通过测力传感器的测量值计算当前支撑减振装置上的支撑弹簧和液压缸(17)的合力，并判定液压缸(17)的受力状态，控制器根据支撑减振装置的合力以及液压缸的受力状态控制电控阀的阻尼；阻尼控制方法如下：
1．当支撑减振装置支撑力值大于设定力值或大于支撑减振装置所支撑物的重力且液压缸(17)上的力为压力时，减小活塞和底阀上的电控阀(30)的阻尼值；
2．当支撑力值大于设定力值或大于支撑减振装置所支撑物的重力且液压缸(17)上的力为拉力时，增大活塞上电控阀(30)的阻尼值，减小底阀上电控阀(30)的阻尼值；
3．当支撑减振装置的支撑力值小于设定力或小于支撑减振装置所支撑物的重力且液压缸(17)上的力为压力时，增大液压缸底阀(10)上的电控阀(30)的阻尼值，减小活塞上电控阀(30)的阻尼值；
4．当支撑减振装置的支撑力值小于设定力或小于支撑减振装置所支撑物的重力且液压缸(17)上的力为拉力时，减小活塞(7)上的电控阀(30)和底阀(10)上的电控阀(30)的阻尼值。
方案9.  如方案7所述的支撑减振装置(图11)包括：
主要由活塞(7)上的电控阀(30)和单向阀(6)构成的阀组件，主要由控制器(24)构成的控制组件和主要由测力传感器(25)构成的测力元件等；其特征是： 活塞(7)上的单向阀(6)与电控阀(30)并联，测力传感器(25)测量支撑减振装置上的支撑弹簧和液压缸(17)的合力，控制组件将测力传感器(25)所测得的支撑减振装置的支撑力值与设定力值或支撑减振装置所支撑物的重力进行比较，并根据比较结果控制电控阀(30)阻尼；阻尼控制方法如下：
  当支撑减振装置的支撑力值小于设定力或小于支撑减振装置所支撑物的重力时，减小活塞上的电控阀(30)阻尼值；
  当支撑减振装置的支撑力值大于设定力或大于支撑减振装置所支撑物的重力时，增大活塞上的电控阀(30)阻尼值。
液压缸(17)压缩时，液压介质通过活塞(7)上单向阀(6)流入拉伸腔，液压缸(17)拉伸时，液压介质通过活塞(7)上的电控阀(30)流出拉伸腔。
方案10.  如方案2、3、4所述的支撑减振装置，其特征是控制组件即控制连杆(1)上下位置可调，即滑阀的初始位置可以通过调节控制连杆(1)上下调节，通过调节控制连杆(1)的位置可以改变支撑减振装置的阀组件在不同负载下的阻尼值以及阀组件开启或关闭时的临界值，以适应不同负载状态。
方案11. 一种车辆，如单轮，两轮，三轮或多轮车辆，其特征是采用了前述方案1~10所述的支撑减振装置中的其中一种支撑减振装置。
 有益效果
  相比现有的自适应减振技术，该支撑式减振装置具有更好的自适应减振功能，其阻尼值会根据路面起伏状况自动调节，减振效果更好， 结构更加简洁，控制的过程和方法也比较简单，成本更低。
 附图说明
图1. 弹簧支撑式拉伸阻尼受控式支撑减振装置示意图
图2. 图1的示意图中的阀组件部分放大图
图3. 弹簧支撑式压缩阻尼受控式支撑减振装置示意图
图4. 图3的示意图中的阀组件部分放大图
图5. 弹簧支撑式拉伸和压缩阻尼双受控式支撑减振装置示意图
图6. 图5的示意图中的阀组件部分放大图
图7. 液气支撑式拉伸阻尼受控式支撑减振装置示意图
图8. 液气支撑式压缩阻尼受控式支撑减振装置示意图
图9. 电控阻尼式支撑减振装置示意图1
图10. 电控阻尼式支撑减振装置示意图2
图11. 电控阻尼式支撑减振装置示意图3
图示编号名称:
 1-控制连杆                  2-测力弹簧             3-活塞杆     
4-支撑弹簧                  5-拉伸腔                6-单向阀        
7-活塞                        8-滑阀                   9-压缩腔      
10-底阀                      11-隔离活塞            12-储气室
13-拉伸时底阀上的液流路径                   14-压缩时底阀上的液流路径
15-压缩时活塞上的液流路径                     16-拉伸时活塞上的液流路径   
17-液压缸                   18-储液腔               19-储能器(压缩气弹簧)
20-单作用液压缸          21-减压阀               22-储液器             
23-溢流阀                   24-控制器               25-测力传感器 (测压力)  
26-测力传感器(测拉力和压力 )            27-信号或控制导线    
 30-电控阀            
31-活塞内腔      32-进出液液流路径
 本发明的实施方式
优选方案1：如图1、图2、图3、图4、图5、 图6所示的弹簧支撑式拉伸或(和)压缩阻尼受控式支撑减振装置示意图
该支撑减振装置主要由测力弹簧(2)，支撑弹簧(4)，液压缸(减振器)(17)，控制阀(减振器上的底阀(10)或活塞(7)上的滑阀(8))以及控制连杆(1)等构成。底阀(10)或活塞(7)上有与控制连杆(1)联动的滑阀(8)，底阀(10)或活塞(7)上还设有单向阀(6)，当测力弹簧(2)所测力值变化时，控制连杆(1)会带动滑阀(8)上下移动，使滑阀(8)与活塞(7)或底阀(10)的阀口开度增大或减小从而改变阻尼。
工作原理：
 图1、图2 所示的支撑减振装置：当支撑减振装置受力压缩时，液流可通过路径(14)和路径(15)从活塞(7)上的单向阀(6)和底阀上的单向阀流动。当支撑减振装置由压缩转为伸张时支撑力由大变小，测力弹簧(2)由短变长，带动控制连杆(1)和控制连杆(1)上的滑阀(8)由下往上移，当支撑力小于支撑减振装置所支撑物的重力值或设定力值时，伸张阀口(液流路径(16)流经的阀口为伸张阀阀口)则由关闭位逐渐打开直到阀全开，阀阻尼由大变小。
图3、图4所示的支撑减振装置： 当支撑减振装置伸张时，液流路径可通过路径(13)和路径(16)从底阀上的单向阀(6)和活塞(7)上的阀流动。当支撑减振装置受力压缩时支撑力由小变大，测力弹簧(2)由长变短， 带动控制连杆(1)和控制连杆(1)上的滑阀(8)由下往上移，当支撑力大于支撑减振装置所支撑物的重力值或设定力值时，阀口则由关闭位逐渐打开直到阀全开，阀阻尼由大变小。
图5、图6所示的支撑减振装置： 当支撑减振装置伸张时支撑力由大变小，测力弹簧(2)由短变长，带动控制连杆(1)和控制连杆(1)上的滑阀(8)由下往上移，当支撑力小于支撑减振装置所支撑物的重力值或设定力值时，伸张阀阀口(路径(16)流经的阀口为伸张阀阀口)则由关闭位打开直到全开，伸张阀阻尼由大变小；当支撑减振装置压缩时支撑力由小变大，测力弹簧(2)由长变短，带动控制连杆(1)和控制连杆(1)上的滑阀(8)由上往下移，当支撑力大于支撑减振装置所支撑物的重力值或设定力值时，压缩阀阀口(路径(14)流经的阀口为压缩阀阀口)则由关闭位打开直到全开，压缩阀阻尼由大变小； 支撑减振装置伸张时，液流经路径13通过单向阀(6)流入压缩腔(9)；支撑减振装置压缩时，液流经路径15通过单向阀(6)流入拉伸腔(5)。支撑减振装置伸张和压缩时的液流通过进出液液流路径(32)进入和流出储液器(22)。
图1、图3、图5的控制连杆(1)可上下调节，通过调节控制连杆(1)的位置可调节滑阀(8)的位置，从而调节阀口开启时和关阀时支撑减振装置的临界力值。
优选方案2：
   如图7、图8所示的液压支撑式拉伸或压缩阻尼受控式支撑减振装置示意图：
   该支撑减振装置主要由储能器(19)，单作用液压缸(20)，液压阀(减压阀(21)、溢流阀(23)、单向阀(6))等构成，减压阀(21)和溢流阀(23)的调压弹簧设定进入或流出单作用液压缸(20)的液流压力，并将进入或流出单作用液压缸(20)的液流压力与设定压力进行比较，以此间接测量单作用液压缸(20)的支撑力大小，并根据比较结果调节减压阀(21)和溢流阀(23)阀口的阻尼值，从而调节进入或流出单作用液压缸(20)的液流压力。
工作原理：
    图7所示的支撑减振装置：单作用液压缸(20)受压缩回时，液流经单向阀(6)流入储能器(19)。液压缸伸张时，减压阀(21)使从储能器内流入液压缸的液压力不大于设定力值，从而限制液压缸的支撑力增加。
图8所示的支撑减振装置：单作用液压缸(20)伸张时，储能器(19)内液流经单向阀(6)流向单作用液压缸(20)，单作用液压缸(20)压缩时，溢流阀(23)使从液压缸流出的液流压力不小于设定力值，从而防止液压缸的支撑力减小。
优选方案3：
    如图9、图10、图11所示的电控阻尼式支撑减振装置示意图：
   该支撑减振装置包括：测力元件，支撑弹簧(4)，液压缸(减振器)(17)，电控阀(即减振器底阀(10)或活塞(7)上的阀(30))以及控制器(24)等构成，测力元件由称重传感器及相关电路元件构成，控制器(24)由电子电路元件构成，控制器(24)的作用是计算测力元件的测量值并控制电控阀(30)的阻尼值(电控阀指电磁阀、磁流变阻尼器、电流变阻尼器等)。图9、图10所示的拉伸或(和)压缩阻尼受控式支撑减振装置其中底阀(10)或活塞(7)上至少有一个设有电控阀(30)，图11所示的拉伸或(和)压缩阻尼受控式支撑减振装置其中底阀(10)或活塞(7)上至少有一个设有电控阀(30)和单向阀(6)。
工作原理：
  图9所示的支撑减振装置：测力传感器(25)测量支撑弹簧(4)的支撑力，测力传感器(26)测量液压缸(减振器)(17)的拉力或压力。
   图10所示的支撑减振装置：测力传感器(25)测量支撑弹簧(4)和液压缸(减振器)(17)的总支撑力，测力传感器(26)测量液压缸(减振器)(17)的拉力或压力。
 图11所示的支撑减振装置：  测力传感器(25)测量支撑弹簧(4)和液压缸(减振器)(17)的总支撑力，活塞(7)或(和)底阀(10)上除了装有电控阀(30)还装有单向阀(6)。
后续工作状态说明中，控制器输出的控制信号仅适用于控制装有电控阀(30)的活塞(7)或装有电控阀(30)的底阀(10)，对于未采用电控阀(30)的活塞(7)或未采用电控阀(30)的底阀(10)，其阻尼阻值变化不受控制器(24)控制。  未采用电控阀(30)的活塞(7)或未采用电控阀(30)的底阀(10)，其工作方式与传统减振器的活塞或底阀的工作方式一样。图9，图10，图11示意图中的活塞(7)和底阀(10)至少有一个装有电控阀(30)，也可以两个都装电控阀(30)，但不是两个都必需装电控阀(30)。
图9，图10所示的支撑减振装置：控制器(24)根据测力传感器(25)和测力传感器(26)测得的值计算合力，当合力大于设定力值且液压缸(减振器)(17)的力值为拉力时，控制器(24)输出的控制信号增加活塞(7)上的电控阀(30) 的阻尼(活塞上装有电控阀(30)时适用)，减小底阀(10)上的电控阀(30)的阻尼(底阀上装有电控阀(30)时适用)；当合力大于设定力值且液压缸(减振器)(17)的力值为压力时，控制器输出的控制信号减小活塞(7)上的电控阀(30)的阻尼(活塞上装有电控阀(30)时适用)和底阀(10)的上的电控阀(30)阻尼(底阀上装有电控阀(30)时适用)。
当合力小于设定力值且液压缸(减振器)(17)的力值为拉力时，控制器(24)输出的控制信号减小活塞(7)上的电控阀(30)的阻尼和底阀(10)的上的电控阀 (30)阻尼；当合力小于设定力值且液压缸(减振器)(17)的力值为压力时，控制器(24)输出的控制信号减小活塞(7)的上的电控阀(30)阻尼(活塞上装有电控阀时(30)适用)，增加底阀(10)的上的电控阀(30)阻尼(底阀上装有电控阀(30)时适用)。
图11所示的支撑减振装置：传感器测量支撑弹簧(4)和液压缸(减振器)(17)的总支撑力，活塞(7)或(和)底阀(10)上除了装有电控阀(30)还装有单向阀(20)。
当合力大于设定力值时，控制器(24)输出控制信号增加活塞(7)上的电控阀(30)的阻尼(底阀上装有电控阀(30)时适用)，减小底阀(10)上的电控阀(30)的阻尼(底阀上装有电控阀(30)时适用)。
当合力小于设定力值时，控制器(24)输出控制信号减小活塞(7)上的电控阀(30)的阻尼(活塞上装有电控阀(30)时适用)，增加底阀(10)上的电控阀(30)的阻尼(底阀(10)上装有电控阀(30)时适用)。
液压缸(17)拉伸且底阀上装有电控阀(30)和单向阀(6)时，液流流经底阀(10)上的单向阀(6)，不受底阀(10)上的电控阀(30)影响。
液压缸(17)压缩且活塞(7)上装有电控阀(30)和单向阀(6)时，液流流经活塞(7)上的单向阀(6)，不受活塞(7)上的电控阀(30)影响。
本文中所选的优选方案仅列举了其中的一部分，凡是采用测量力值直接或间接地通过机械、电控或液控调节和控制阻尼力的减振或采用测量力值直接或间接地通过机械、电控或液控调节和控制物体的支撑力值以减小振动的方法，都是本文中所采用的技术方案的显而易见的方案之列，都应归于本专利技术范围内。

Claims (10)

  1. 一种支撑减振装置包括：
    支撑弹簧、液压缸、阀组件、测力元件、控制组件；
    其特征是：用测力元件测量支撑减振装置对所支撑物的支撑力值，控制组件将支撑力值与设定力值或支撑减振装置所支撑物的重力进行比较，并根据比较结果通过机械、液压或电控等方式控制阀组件的阻尼。
  2. 如权利要求1所述的支撑减振装置其特征是：
    控制组件主要由控制连杆(1)构成，减振器活塞上集成有包括单向阀(6)和滑阀(8)在内的阀组件，滑阀(8)连接在控制连杆(1)上，测力元件主要由测力弹簧(2)构成；
    测力元件测量支撑减振装置的支撑力，并依据测量值通过控制连杆(1)调节滑阀(8)的位置，以此调节阀组件的阻尼。
  3.  如权利要求1所述的支撑减振装置其特征是：
    控制组件主要由控制连杆(1)构成，减振器底阀上集成有包括单向阀(6)和滑阀(8)在内的阀组件，滑阀(8)连接在控制连杆(1)上；
    测力元件测量支撑减振装置的支撑力，并依据测量力值通过控制连杆(1)调节阀组件的阻尼。
  4. 如权利要求1所述的支撑减振装置其特征是：
    控制组件主要由控制连杆(1)构成，减振器活塞上集成有包括与拉伸腔(5)相通的单向阀(6)、与压缩腔(9)相通的单向阀(6)以及主要由滑阀(8)构成的与压缩腔相通的压缩阀和与拉伸腔相通的拉伸阀，滑阀(8)连接在控制连杆(1)上，活塞内腔(31)与储液器(22)连通，活塞内腔通过单向阀(6)与拉伸腔(5)和压缩腔(9)相通；
    减振器压缩或伸张时，测力弹簧(2)测量支撑减振装置的支撑力并且依据测量力值通过控制连杆(1)调节拉伸阀和压缩阀的阻尼。
  5.  如权利要求1所述的支撑减振装置包括：
    单作用液压缸(20)、主要由储能器(19)构成的支撑弹簧、主要由减压阀(21)和单向阀(6)构成的阀组件和测力元件以及控制组件；
    其特征是：储能器(19)通过减压阀和与减压阀并联的单向阀与单作用液压缸相连；单作用液压缸伸张时，进入单作用液压缸的液流压力与减压阀的设定压力进行比较，以此调节减压阀的阻尼值；单作用液压缸(20)受压缩回时，液流经单向阀(6)流入储能器(19)。
  6. 如权利要求1所述的支撑减振装置包括：
    单作用液压缸(20)、主要由储能器(19)构成的支撑弹簧、主要由溢流阀(23)和单向阀(6)构成的阀组件和测力及控制组件；
    其特征是：储能器(19)通过溢流阀和与溢流阀并联的单向阀与单作用液压缸相连；单作用液压缸(20)压缩时，流出单作用液压缸的液流压力与溢流阀的设定压力进行比较，以此调节溢流阀的阻尼值；单作用液压缸(20)伸张时，储能器(19)内液流经单向阀(6)流向单作用液压缸(20)。
  7. 如权利要求1所述的支撑减振装置包括：
    主要由测力传感器构成的测力元件、主要由控制器(24)构成的控制组件、主要由电控阀(30)构成的阀组件；
    其特征是：活塞和底阀上至少有一个装有电控阀(30)，
    当减振器液流路径上设有单向阀时，则至少应装一只测力传感器测量支撑减振装置的合力；
    当减振器液流路径上未设单向阀时，至少应装两只测力传感器，以便测量支撑减振装置的合力并计算减振器的受力状态是拉力还是压力；
    控制组件将测力传感器所测得的支撑减振装置的支撑力值与设定力值或支撑减振装置所支撑物的重力进行比较，并根据比较结果以及减振器的受力状态控制电控阀(30)阻尼。
  8. 如权利要求7所述的支撑减振装置包括：
    测量支撑弹簧支撑力值的测力传感器和测量液压缸拉压力值的测力传感器以及控制器(24)；
    其特征是：通过测力传感器的测量值计算当前支撑减振装置上的支撑弹簧和液压缸的合力，并判定液压缸的受力状态，控制器根据支撑减振装置的合力以及液压缸的受力状态控制电控阀的阻尼。
  9. 如权利要求7所述的支撑减振装置包括：主要由活塞上的电控阀(30)和单向阀(6)构成的阀组件，主要由控制器(24)构成的控制组件和主要由测力传感器构成的测力元件；
    其特征是：活塞上的单向阀(6)与电控阀(30)并联，测力传感器测量支撑减振装置上的支撑弹簧和液压缸的合力，控制组件将测力传感器所测得的支撑减振装置的支撑力值与设定力值或支撑减振装置所支撑物的重力进行比较，并根据比较结果控制电控阀(30)的阻尼。
  10. 一种车辆，其特征是采用了如权利要求1~9所述的支撑减振装置中的其中一种支撑减振装置。
PCT/CN2019/086920 2018-07-29 2019-05-14 一种支撑减振装置以及采用该支撑减振装置的车辆 WO2020024653A1 (zh)

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112923002A (zh) * 2021-02-23 2021-06-08 山东科技大学 一种复合式抗冲击装置及其应用
CN113752926A (zh) * 2021-09-08 2021-12-07 东风柳州汽车有限公司 一种阻尼可调的缓震汽车座椅
CN115320304A (zh) * 2022-08-11 2022-11-11 辽宁工程技术大学 一种混合式多点位汽车减震悬挂装置

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20210293299A1 (en) * 2018-08-01 2021-09-23 Gang Chen Liquid gas supporting shock absorber and vehicle using same
CN115899151B (zh) * 2022-12-05 2024-08-13 山东科技大学 一种锤式破碎机用抗冲击式双向缓冲装置

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1830098A1 (en) * 2006-03-02 2007-09-05 Koganei Corporation Shock Absorber
CN106090111A (zh) * 2016-06-21 2016-11-09 江苏大学 一种带高度调节系统的可变阻尼汽车液压减振器
CN205780534U (zh) * 2016-07-20 2016-12-07 洛阳理工学院 一种具有可变阻尼减震器的汽车减震装置
CN106246792A (zh) * 2016-09-28 2016-12-21 山东文捷智能动力有限公司 可自动调节的车辆用减震装置及减震方法
CN206816742U (zh) * 2017-06-01 2017-12-29 上海众力减振技术有限公司 通过压力传感器监测路况的汽车减震系统
CN108662069A (zh) * 2018-07-29 2018-10-16 陈刚 一种支撑减振装置
CN208793507U (zh) * 2018-07-29 2019-04-26 陈刚 一种支撑减振装置以及采用该支撑减振装置的车辆

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH03203U (zh) * 1989-05-25 1991-01-07
JPH04314610A (ja) * 1991-01-16 1992-11-05 Atsugi Unisia Corp 減衰力制御装置
JPH0740729A (ja) * 1993-07-29 1995-02-10 Daihatsu Motor Co Ltd 車両用懸架力制御装置
DE4414022C2 (de) * 1994-04-22 1996-02-29 Daimler Benz Ag Aktives Federungssystem
JP3052785B2 (ja) * 1995-05-16 2000-06-19 三菱自動車工業株式会社 サスペンション装置
US9884533B2 (en) * 2013-02-28 2018-02-06 Tenneco Automotive Operating Company Inc. Autonomous control damper
DE102018128595A1 (de) * 2018-11-14 2020-05-14 Ovalo Gmbh Vorrichtung zum Verbinden eines Federbeines mit einer Karosserie
WO2020199754A1 (zh) * 2019-03-29 2020-10-08 陈刚 一种电控液气支撑减振器

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1830098A1 (en) * 2006-03-02 2007-09-05 Koganei Corporation Shock Absorber
CN106090111A (zh) * 2016-06-21 2016-11-09 江苏大学 一种带高度调节系统的可变阻尼汽车液压减振器
CN205780534U (zh) * 2016-07-20 2016-12-07 洛阳理工学院 一种具有可变阻尼减震器的汽车减震装置
CN106246792A (zh) * 2016-09-28 2016-12-21 山东文捷智能动力有限公司 可自动调节的车辆用减震装置及减震方法
CN206816742U (zh) * 2017-06-01 2017-12-29 上海众力减振技术有限公司 通过压力传感器监测路况的汽车减震系统
CN108662069A (zh) * 2018-07-29 2018-10-16 陈刚 一种支撑减振装置
CN208793507U (zh) * 2018-07-29 2019-04-26 陈刚 一种支撑减振装置以及采用该支撑减振装置的车辆

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112923002A (zh) * 2021-02-23 2021-06-08 山东科技大学 一种复合式抗冲击装置及其应用
CN113752926A (zh) * 2021-09-08 2021-12-07 东风柳州汽车有限公司 一种阻尼可调的缓震汽车座椅
CN113752926B (zh) * 2021-09-08 2022-09-13 东风柳州汽车有限公司 一种阻尼可调的缓震汽车座椅
CN115320304A (zh) * 2022-08-11 2022-11-11 辽宁工程技术大学 一种混合式多点位汽车减震悬挂装置
CN115320304B (zh) * 2022-08-11 2024-05-24 辽宁工程技术大学 一种混合式多点位汽车减震悬挂装置

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